Note: Descriptions are shown in the official language in which they were submitted.
~27~8
1 The movement of the ejection panel occurs on an incremental
2 basis until the pressure of the refuse against the ejection
3 panel decreases to a second particular value lower than the
4 first particular value.
A refuse compacting apparatus having a storage ]~
6 for refuse and a movable panel positioned within the storage
7 body. A support member is provided for the movable panel,
8 which member has a movable end and a fixed end with -the fixed
9 end pivotally connected to the storage body. A link connects
the movable end to the movable panel such that the movement
li of the panel causes pivotal movement of the support member.
12 Means are provided to transmit a force to the movable panel~
13 from a point on the support member which is intermediate the
1~ fixed end and movable end. Thus, as the panel undergoes move-
ment within the storage body, the support member undergoes
16 rotational movement with the intermediate point on the support
17 member moving in an arcuate path in the direction of movement
18 of the movable panel.
19 A refuse compacting apparatus having a container for
storing refuse under pressure and a loading hopper in communica-
21 tion with the storage container. Refuse compacting means are~
22 positioned to sweep through the hopper to compact refuse and
23 to move the refuse fxom the loading hopper into the storage
24 con-tainer. A retainer panel is positioned to move between an
opened and a closed position. With the retainer panel in its
26 closed position, the retainer panel impedes the flow of refuse
27 from the container into the hopper. In its opened position,
28 the retainer panel permits the flow of refuse from the hopper
29 into the storage container. Control means are provided to
move the retainer panel to an opened position, while moving
31 the refuse compac-ting means through the hopper to move refuse
32 into the storage container and to move the retainer panel to
llZ71~8
1 a closed position, while returning the refuse compacting means
2 to a position to begin sweeping through the hopper.
3 A refuse compacting apparatus having a container for
4 storing refuse under pressure, a loading hopper in co~munica-
tion with the storage container and a packing panel mounted
6 to sweep through the hopper to compact refuse therein and to
7 move the refuse from the loading hopper and into the storage
8 contalner. The loading hopper includes a curved inner surface
g and a sill over which refuse is inserted into the hopper. An
edge on the pac]cing panel is positioned adjacent to the curved
11 inner surface as the packing panel sweeps through the loading
12 hopper. Means are provided to maintain a minimum distance
13 between an edge on the packiny panel and the curved inner
1~ surface at a point adjacent to the sill, which distance is
slightly greater than the depth of the human finger. The
16 distance between the edge on the packing panel and the curved
17 inner surface is then increased slightly after the packing
18 panel moves past the sill in sweeping through the hopper.
19 The minimum spacing between the edge of the packing panel
and the inner surface at the sill reduces the level of forces
21~ applied to the sill area during packing of refuse while also
22 protecting the worker's fingers. The increases spacing
23 between the edge on the packing panel and the curved inner
24 surface as the panel sweeps through the loading hopper
provides a gripping force to refuse caught between the
26 edge and the inner surface such that refuse is pulled over
27 the sill and into the hopper as the panel sweeps through
28 the hopper.
29 A refuse compacting apparatus having a panel
positioned for working movement in a first direction, a
31 ///
32 ///
~j
" ~
~ , :
~ D-1101
,_~
l~Z71~B
1 relatively large first hydraulic motor for driving t]le ~ -
2 panel in the first direction, and the panel undergoing
3 return movement in a second direction with a relatively
4 small hydraulic motor driving the panel in the second
direction. Means provide pressurized hydraulic fluid
6 for driving the first and second hydraulic motors with
the first and second hydraulic motors being mechanically
8 interconnected such that movement of the first motor to
9 drive the panel in said first direction causes movement
of the second motor in a direction opposite to its r~ e-
11 ment in driving the panel in said second direction.
12 Similarly, movement of the second motor to drive the panel
13 in said second direction causes movement of the first
14 motor in a direction opposite to its movement to drive
15 the panel insaid first direction. - ~
lG The first motor has a first opening and a
17 second opening and the second motor has a first opening
18 and a second opening. Means are provided to connect the
19 second opening of the first motor with the second open-
ing of the second motorj and means are provided to connect
21 the second opening of the first motor and the second
22 opening of the second motor to sump means. Valve means
23 are positioned between the first and second motors and
24 the means to supply pressurized hydraulic fluid with the
valve means having a first operative position to direct
26 hydraulic fluid to the first opening of the first motor
27 to cause movement of the first motor to drive the panel
28
29
31
32
-4-
D-llOl
- - -
7~
1 in the said first direction. The valve means in its firs-t
2 operative position also transmits hydraulic fluid from the
3 first opening in the second motor to the sump means as the
second motor moves in a direction opposite to its movement
~ to drive the panel in said second direction. Hydraulic
6 fluid flowing from the second opening of the first motor
q may flow into the second opening of the second motor and
8 may also flow into the sump as the first motor moves to
9 drive the panel in said first direction.
The valve means has a second operative position
11 to direct hydraulic fluid to the first opening of the
12 second motor to cause movement of the second motor to drive
13 the panel in said second direction while also causing
14 movement of the first motor in a direction opposite to
its movement in driving the panel in said first direction.
16 The valve means in its second operative position transmits
17 hydraulic fluid from the first opening of the first motor
18 to the sump and means interconnect the first and second
19 openings of the first motor which means are actuated
when the pressure of hydraulic fluid supplied -to the first
21 opening of the second motor reaches a predetermined pres-
22 sure level to permit hydraulic fluid to flow from the
23 first opening of the first motor into the second opening
24 Of the first motor. The second motor, therefore, a~c~ as
an accumulator for hydraulic fluid from the first motor
26 as the first motor is driving the panel in its first
27 direction, and the second motor is moving in a direction
28
29
31
32
--5--
~ D-llOl
, ~
opposite to its movement to drive the panel in said second
2 direction. Also, the first motor acts as its own accumu-
3 lator when the second motor is driving the panel in said
4 second direction and the first motor is moving in a
direction opposite to its movement in driving the panel
6 in its first direction with hydraulic fluid being trans-
mitted from the first opening in the first motor to the
second opening of the first motor.
9 A refuse compaction apparatus having a refuse
container, a loading hopper and a passage from the hopper
into the refuse container. A packing panel is positioned
12 within the loading hopper for rotational movement from a
13 rest position in a working direction in sweeping through the
1~ hopper to compact refuse and to move the refuse through
the passage into the refuse container. Means for driving
16 the panel include a drive shaft rotatabl~ supporting the
17 panel and a drive member connected to the panel with the
18 drive member having a drive surface. A drive lever is
19 connected to the drive member and a flexible drive member
having a drive end and a fixed end has its fixed end
21 connected to the drive lever. A motor is connected to the
22 driving end of the flexible drive member with the flexible
23 drive member being positioned to contact the drive surface
2~ in driving the panel during movement of the panel in a
working direction from its rest position during the initial
26 portion of its movement through the hopper. The flexible
27 drive member then moves out of contact with the drive
28
29
31
32
--6--
O-LiOl
~2~
1 surface to drive the packing panel through the connec-
2 tiOll between the fixed end of the drive membex and the
3 drive lever during the latter portion of the movemen-t
4 of the packing panel in a working direction through the
hopper.
6 A refuse compaction apparatus including a
7 hopper and a panel rotatably positioned for movement
8 through the hopper. The panel has a body with a gcnerally
9 elliptical cross-sectional configuration and a high torque-
transmitting capability. Drive means are conn-cL~
11 only one end of the panel with the drive means imparting
12 a rotational force to the panel at said one end, which
13 force is transmitted throughout the panel by the generally
14 elliptically-shaped body.
A refuse compaction apparatus having a container
16 for storing refuse under pressure and means for pressurizing
17 refuse within the container. The container includes a first
18 rigid frame positioned at one end and a second rigid frame
19 positioned at the other end of the container. A plurality
20 of longitudinal members interconnect the first and second
21 frames and a plurality of flexible metal sheet members~
22 enclose the cnntainer with the sheet members being supported
23 by the first and second frames and by the longitudinal
24 members. The flexible sheet members are bowed outwardly
25 from their points of support, such that the sheet members
26 are placed in tension in resisting pressure within the
27 storage container.
28
29
31
32
--7--
1101.
`~18
1 A refuse compactioll apparatus including a con-
2 tainer for storing refuse under pressure, a tailgate
3 rotatably mounted on the container for movement ~etween
an opened and a closed position. The tailgate in its
opened pOSitiOIl permits refuse to be discharged from the
6 container and the tailgate in its closed position forms
7 a closure with the storage container. In maintaining
the tailgate in its closed position, a latch member is
9 engageahle with a keeper member with means to provide
rotational movement of the latch member into a position
11 to make contact with the keeper member. After rotational
~2 movement of the latch member, means are provided to cause
13 translational movement of the latch member into contact
la with the keeper member to maintain the tailgate in a
closed position.
16 A refuse compaction apparatus including a con-
17 tainer for storing refuse under pressure, a tailgate
18 rotatably mounted on the container for movement between
19 an opened and a closed position with the tailgate in-
cluding a loading hopper to receive refuse and packing
21 means within the hopper to move refuse rom the hopper
~2 into the storage container. Drive means are provided
23 within the hopper to drive the packing means in moving
2a refuse from the loading hopper into the storage container
when the tailgate is in its closed position in abutting
26 relation with the storage body. The tailgate in its
27 opened position is rotated upwardly to expose the
28 storage body for the discharge of refuse.
29 ///
///
31
32
--8--
,.~ '~--1101
-
l~Z7118
~- The drive means within the tailgate is
2 positioned at one side of the tailgate to drive the
3 packing means from said one side with the weight of
said one side of the tailgate being greater than the
~ weight of the other side of the tailgate. An upper
6 beam is provided within the tailgate with the tailgate
q being rotatably connected to the storage container
8 through the upper beam. A stiffener assembly in the
9 upper beam is positioned adjacent to the rotatable
connection of the heavier side of the tailgate to the
11 storage container with the stiffener assembly having a
12 configuration which provides a high resistance to
13 torque. A lifting force applied to the tailgate for
la raising the tailgate to its opened position is, there-
fore, transmitted through the upper beam with the
16 twisting forces applied to the upper beam by the weight
17 of the heavier one side being resisted by the stiffener
18 assembly.
19
* * * * *
21
22
23
24
26
27
28
2~
31
32
_g_
~ - D-]101
i~27118
1 Background of the Invention
3 There is a direct correlation between the
4 affluence and industrialization of a society and the
~ quantity of refuse which is generated by that society.
6 Thus, in the industrialized nations, the quantity of
q refuse which is generated may be many times that
8 generated in a more primitive society.
9 In modern refuse collection apparatus, the
refuse is compacted within a pressurized storage con-
~1 tainer. The storage container may, for example, be
12` mounted on the frame of a truck with the tailgate ro-
13 tatably secured to the rear of the container. Within
14 the tailgate, there is generally a packing mechanism,
with refuse being placed in a loading hopper in the
16 tailgate and the packing mechanism forcing the refuse
~7 under high pressures into the storage container. By
18 forcing the refuse into the storage container under
high pressures, the refuse is compacted so that a rela-
tively large quantity of refuse may be carried within
21 the storage container. This permits the refuse collec-
22 tion apparatus to function for a long period of time
23 before it becomes necessary to empty the storage con-
2~ tainer. The time spent in driving to a landfill or
refuse transfer point to empty the storage container
26 is time lost from the primary function of the apparatus
27 in picking up the refuse at a home or a business and
28
29
31
32
10-
. ~ , , .
D-llOl
1~27118
1 placing the refuse in a compacted form which is convenient
2 for :its disposal. Accordingly, it is essential to the
3 function of a refuse collection apparatus that the
quanti-ty of refuse carried within the refuse container be
maximized.
6 To maximize the quantity of refuse which may be
7 packed under pressure within the refuse storage container,
8 it has previously been necessary to construct the apparatus
9 of heavy structural members to provide great strength.
This has resulted in the refuse compaction apparatus being
11 relatively large and heavy. These requirements have in-
12 creased the costs of refuse compaction apparatus and have
13 made the apparatus a high consumer of energy for operation.
14 Additionally, the weight of previous refuse collection
apparatus may be injurious to street surfaces over which
16 the apparatus is driven.
17 In addition to being relatively heavy and ex-
18 pensive, previous refuse collection apparatus has been
19 relatively complicated. In previous apparatus, it has
generally been necessary to place hydraulic cylinders on
21 either side of the tailgate to drive the packing mechanism
22 in forcing the refuse from the loading hopper into the
23 refuse storage container. The weight and expense of the
2~ hydraulic cylinders have, thus, contributed to the overall
weight and expense of the refuse collection apparatus.
26 Additionally, to control a plurality of hydraulic cylin-
27 ders to insure that the driving forces applied to each
28 ///
29 ///
31
32 -11-
D-llO]
l~Z7il8
1 end of the packing mechanism are synchronized has re-
2 quired the use of complex hydraulic circuitry. This
3 may reduce the reliability of the refuse collection
4 apparatus, since the reliability of a complex mechanism
is generallyinversely proportional to the complexity
6 of the mechanism.
7 In view of the above problems, it would be
8 desirable if a refuse compaction apparatus could be
9 provided which would be lighter than previous apparatus
and which would consume a smaller quantity of energy
11 for operation. Such an apparatus would also be cheaper
12 because of the use of lighter and less expensive struc-
13 tural members used in its construction. These would
14 be considerable advantages in view of the ever-increasing
cost of energy in the form of oil, gasoline and other
16 fossil fuels for operation of industrial equipment.
17 Additionally, by being lighter than previous collection
18 apparatus, such an apparatus would be less injurious to
19 the public streets in its operation.
In addition to providing a refuse compaction
21 apparatus which would be cheaper and lighter, it would be
22 desirable to provide an apparatus which would be simpler
23 in its construction, and, therefore, more reliable and
24 less likely to break down. Desirably, such an apparatus
would provide a mechanical interconnection between the
26 hydraulic motors used to drive the packing mechanism.
27 This would serve to eliminate the previous problems of
29
31
32
-12-
" ~ .
D-llOl
1127118
1 synchronizing the movement of hydraulic cylinders to
2 drive the packing mechanism by means of a complex
3 hydraulic circuit. Also, it would be desirable if such
4 a refuse compaction apparatus could function by driving
~ the packing mechanism from only one end, since this
6 would tend to avoid the many problems which may result
7 from the use of duplicate drive cylinders positioned
8 at either end of the packing mechanism, which cylinders
9 must be synchronized in their movement~s.
In addition, it would be desirable if a re
11 fuse compaction apparatus could be provided in which the
12 refuse could be suhjected to very high pressures before
13 being placed within the refuse storage container. This
1~ would permit the retention of highly compacted refuse
within the storage container at reduced pressures. The
16 storage container could then be made lighter while still
17 performing its function of containing a maximum quantity
18 of refuse to reduce the amount of lost time required to
19 periodically empty the container.
21
22
23
26
27
28
29
31
32
-13-
r)-l~ o
1 Summary of the Invention
3 In providing a solution to the aforementioned
problems, the present invention provides a refuse com-
paction apparatus which is relatively light in weight, is
6 relatively inexpensive, and is also less complex than
q previous refuse compaction apparatus. Accordingly, the
refuse compaction apparatus of the invention is admirably
9 suited for meeting the complex problems posed by the con-
tradictory demands of providing efficient and uniform
11 compaction of refuse at high pressures, while reducing
12 the weight and complexity of the apparatus and the energy
13 required for its operation.
14 One aspect of the invention concerns a refuse
compacting apparatus in which a passage having a narrowed
16 throat is positioned between a container for storing re-
17 fuse under pressure and a loading hopper. Refuse compac-
18 ting means may be positioned to sweep through the hopper
19 to compact refuse and to move the refuse from the loading
hopper into the storage container. As the refuse is moved
21 through the passage by the refuse compacting means, the
22 refuse may be squeezed and subjected to very high localized
23 pressures within the narrowed throat as the refuse passes
2~ through the narrowed throat.
A movable ejection panel may be positioned with-
26 in the storage container, with the panel being movable from
27 a position adjacent the passage when the container is empty
28
29
31
32
-14-
- `1101
1127118
1 to a position displaced from the passage when the con-
2 tainer is full. Means may be provided to control the
3 movement of the ejection panel away from the passage in
response to the pressure of refuse which is exerted
against the panel. Thus, as refuse is moved into the
6 container from the passage, the refuse may he packed
7 àgainst the panel until the pressure of refuse against
8 the ejection panel exceeds a predetermined level with
9 the panel then being moved an incremental distance to
~ a new position to reduce the pressure of refuse against
11 the panel. Additional refuse may then be packed against
12 the ejection panel in its new position until the pressure
13 against the panel exceeds the predetermined level with
14 the panel being again moved an incremental distance to
a new position, etc., such that the alternate packing of
16 refuse and moving of the ejection panel is continued until
17 the storage container is uniformly filled with refuse.
18 The passage leading from the loading hopper
19 into the refuse container may include a surface at the
enlarged opening from the passage into the storage con-
21 tainer which surface imparts movement of the refuse that
22 is directed toward the panel. Additionally, the pressure
23 exerted on the re~use passing through the narrowed throat
2~ within the passage may greatly exceed the pressure which
is exerted by refuse against the ejection panel and the
26 interior of the refuse storage container. Accordingly,
27 the high localized pressures which may be exerted on
28
29
31
32
-15-
11271~8
l refuse as it passes through the narrowed throat wi-thin
2 the passage need not be transmitted to the interior of
3 the storage container.
It is desirable that the pressures of the refuse
directed through the narrowed throat of the passage be
6 regulated. If the pressures exerted on the refuse in the
7 narrowed throat are excessive, the movement of the refuse
8 through the narrowed throat of the passage tends to become
g blocked. On the other hand, if the pressures exerted on -the
refuse in the narrowed throat are not sufficient, a relatively
1l little amount of compaction or fragmentation is produced on
12 the refuse in the narrowed throat. The regulatior of the
13 pressures on the refuse in the narrowed throat is pro~lded
la by controlling the pressure of the refuse in the storage
body. When the pressure of the refuse on the ejection panel
16 in the storage body reaches a first particular value, the
17 ejection panel is moved in a direction to relieve such
18 pressure. Such movement of the ejection panel occurs on
l9 an incremental basis until the pressure of the refuse against
the ejection panel decreases to a second particular value
21 lower than the first particular value.
22 The ability to regulate the pressure of -the refuse
23 in the narrowed throat of the passage by regulating the
24 pressure exerted by the refuse against the ejection panel
can be seen from the following. For example, the pressure
26 f the refuse against the ejection panel corresponds to the
27 pressure of the refuse in the enlarged opening in the passage
28 at a position adjacent to the storage body. Furthermore,
29 ///
~0 ///
31
32
-16-
~1271~8
1 the pressure in the enlarged opening causes a back pressure
2 to be exerted against the refuse in the narrowed throat to
3 control the pressure of the refuse in the narrowed throat.
4 As a result, the pressure of the refuse in the narrowed
5 throat of the passage is directly related to the pressure
6 of the refuse against the ejection panel. In this way, a
7 servo action is obtained for providing an optimal churning,
8 fragmentation and compaction of the refuse as the refuse
g is directed through the narrowed throat.
In moving refuse from the loading hopper through
li the passage into the refuse storage container, a movable
12 retainer panel may be positioned for movement between a ~irst
13 position in which the retainer panel is positioned away from
14 the passage and a second position in which the retainer panel
15 at least partially blocks the passage. When the refuse
16 compacting means is moved away from the passage, the retainer
17 panel may be moved to its second position to impede the move-
18 ment of the refuse from the passage back into the loading
19 hopper. Additionally, as the retainer panel moves from its
20 first position to its second position, the retainer panel may
21 be shaped and positioned to sweep refuse from the refuse
22 compacting means during this movement with the refuse swept
23 from the refuse compacting means being moved into the passage
24 by the retainer panel.
With the retainer panel in its first position which
26 does not impede the movement of refuse from the loading hopper
27 through the passage into the storage container, the retainer
28 panel may include a surface which merges into and forms an
29 extension of the surface of the passage. The configuration
30 of the retainer panel may, thereby, assist the movement of
31 the refuse into the passage from the loading hopper.
32 ///
-16a-
~ D,~101
l~Z'7118
1 In another aspect of the invention, a refuse
2 compacting apparatus may be provided in which a movable
3 panel is positioned within a storage body for refuse. A
support member for the movable panel may have a movable
end and a fixed end with the fixed end pivotally con-
6 nected to the storage body. A link may connect the
q movable end of the support member to the movable panel
8 such that movement of the panel causes pivotal movement
9 of the support member. Means may be provided to transmit
a force to the movable panel from a point on the support
11 member which is positioned intermediate the fixed end and
12 the movable end. As the panel undergoes movement within
13 the support body to cause rotational movement of the
1~ support member, the intermediate point on the support
15 member may then move in an arcuate path in the direction
16 of movement of the panel. The means to transmit a force
~17 from the support member to the movable panel may comprise
18 a hydraulic cylinder having one end connected to the inter-
19 mediate point Oll the support member and the other end con-
~20 nected to the movable panel. The expansion of the hydrau-
21 lic cylinder may, thus, cause movement of the panel away
22 from the fixed end of the support member while contraction
23 of the hydraulic cylinder may cause movement of the panel
24 toward the fixed end of the support member.
The intermediate point on the support member may
26 be positioned out of alignment with the fixed and movable
27 ends of the support member with the fixed and movable ends
28
29
31
32
-17-
1.,1~) 1.
l~Z7~8
1 lying on a straight line and the movable panel being
2 positioned transverse to the straight line. The inter-
3 mediate point on the support member may then be positioned
transversely with respect to the straight line but in a
direction opposite to the position of the panel wi-th
6 respect to the straight line. The support member may
q have a generally triangular configuration with the fixed
8 end and the movable end of the support member lying at
9 two of the apices of a triangle. The intermediate point
on the support member may then lie at the other apex
11 of the triangle. The panel may be positioned transversely
12 to a line through the fixed and movable ends with the
~3 intermediate point being positioned transversely to the
14 line but in a direction opposite to the position of the
panel with respect to the line.
16 The refuse storage body may have an open end and
17 a closed end with the movable panel forming a closure for
18 the open end. The generally triangular support n!~rlher may
19 then be positioned adjacent to the open end with the
intermediate-point apex of the support member extenc~;ng
21 outside of the storage body through said open end. In this
22 manner, the movable panel may be positioned more closely
23 adjacent to the open end with less interference from the
2~ position of the means to transmit force from the support
member to the panel.
26 As a further aspect of the invention, a refuse
27 compacting apparatus may be provided in which a loading
28
29
31
32
-18-
~ D-llOl
1 hopper is in communication wlth a container for storing
2 refuse under pressure. A refuse compacting means may be
3 positioned to sweep through the loading ho~er to co~pact
refuse therein and to move the refuse from the loading
hopper into the storage container. A retainer panel
6 may be positioned to move between an opened and a closed
q position with the retainer panel impeding the flow of
8 refuse from the s-torage container into the hopper with
9 the retainer panel in its closed position and permitting
the flow of refuse from the hopper into the storage con-
11 tainer by the refuse compacting means with the retainer
12 panel in its opened position. Control means may be
13 provided to move the retainer panel to an opened position
1~ while moving the refuse compacting means through the hop-
per to move refuse from the hopper into the storage con-
16 tainer. The control means may also function to move the
17 retainer panel to a closed position while returning the
18 refuse compacting means to a return position to begin
19 sweeping through the loading hopper.
In providing control of the movement of the
21 retainer panel and the refuse compacting means, a source
22 of pressurized hydraulic fluid may be used to drive a
23 first hydraulic ~otor means that is operatively connected
2~ to the retainer panel and a second hydraulic motor means
which is operatively connected to the refuse compacting
26 means. A first valve means may control the flow of hy-
27 draulic fluid to the first motor means in moving the
28
29
31
32
--19--
~- 1 1 0 1
1 retainer panel between an opened and a closed position.
2 A second valve means may control the flow of hydraulic
3 fluid to the second motor means in moving the refuse
compacting means through the loadiny hopper to sweep re-
fuse from the hopper and to then return to a return
6 position to begin sweeping through the hopper. Means may
7 be provided to move the first and second valves in unison
8 to first direct hydraulic fluid to the first motor means
9 before directing hydraulic fluid to the second motor means.
In this manner, the retainer panel may undergo movement
11 before movement of the refuse compacting means.
12 Coupled with the movement of the refuse compac-
ting means and the retainer panel, an e~ection panel may
1~ be positioned within the storage container. Means may be
~5 provided to move the ejection panel in small increments
16 within the storage container in response to the pressure
17 of refuse against the ejection panel. Thus, as refuse
18 is moved into the storage container and packed against the
~19 ~ejection panel, the ejection panel may be incrementally
20 moved to enlarge the available volume for storing refuse
21 within the storage container. A third hydraulic motor
22 means may be connected to the ejection panel and means may
23 be provided to sense the pressure of hydraulic fluid
24 within the second motor means as the refuse compacting
25 means sweeps through the loading hopper. Means may be
26 provided to momentarily dump hydraulic fluid from the third
27 motor means when the sensed pressure within the second
28
29
31
32
-20-
., _.
"~ r.llol
1~2711~
1 motor means exceeds a predetermined pressure level to
2 move the ejection panel a small incremental distance
3 and, thereby, to reduce the pressure of refuse against
the ejection panel.
The first valve means and second valve means
6 may be positioned in a series relation with respect to
q the source of pressurized hydraulic fluid. Further,
8 the first valve means may be positioned between the
9 second valve means and the ~source of pressuriæed hydraulic
10 fluid with the first valve means returning to its neutral -~
11 position after movement of the first and second valve
12 means in unison. The second valve means may then receive
~3 hydraulic fluid from the source of pressurized hydraulic
1 fluid such that movement of the retainer panel may pre-
cede movement of the packing means within the loading
16 hopper.
17 In a further aspect of the invention, there is
18 provided a refuse compacting apparatus for storing refuse
19 under pressure, a loading hopper in communication with
the storage contalner and a packing panel mounted for
21~ movement through the loading hopper to sweep through the
22 hopper in compacting refuse therein and in moving refuse
23 ~rom the loading hopper into the storage container. The
24 loading hopper may include a curved inner surface with a
sill on the loading hopper over which refuse may be in-
26 serted into the hopper. The packing panel may have an
27 edge which is positioned adjacent to the curved surface
28
29
31
32
-21-
D-llOl
, ~_
llZ7118
1 with:in the loading hopper as the packing panel sweeps
2 through the loading hopper. Means may be provided to
3 maintain a minimum distance between the edge on the
4 pack:ing panel and the curved surface on the hopper at
a point which is adjacent to the sill, which minimum
6 distance may be slightly greater than the depth of a
q human finger.
8 Additionally, the means to maintain a minimum
9 dis`tance between the edge of the packing panel and the
inner curved surface of the hopper may increase the
11 minimum distance slightly as the packing panel sweeps
12 past the sill and through the hopper. The minimum
13 spacing between the edge of the packing panel and the
.~ curved inner surface of the loading hopper of the sill
may reduce forces applied to the sill during downward
16 movement of the packing panel while also protecting the
17 worker's fingers. The increased minimum spacing be-
18 tween the edge of the packing panel and the curved inner
19 surface of the hopper as the panel sweeps through the
loading hopper may provide a gripping force on refuse
21 caught between the edge of the packing panel and the
22 curved inner surface of the hopper which force may pull
23 refuse over the sill and into the hopper as the panel
24 sweeps through the hopper.
A further aspect of the invention concerns a
26 refuse compacting apparatus having a panel positioned for
27 working movement in a ~irst direction/ and a relatively
28 ///
29
31
32
-22-
r~-llol
~Z7118
1 large first hydraulic motor for driving the panel in khe
2 first direction. The panel may undergo return movement
3 in a second direction and a relatively small second hy-
4 draulic motor may drive the panel in said second direc-
tion. A source of pressurized hydraulic fluid may drive
6 the first and second hydraulic motors with means mechani-
7 cally interconnecting the first and second motors such
8 that movement of the first motor to drive the panel in
9 said first direction causes movement of the second motor
in a direction opposite to its movement to drive the
11 panel in the second direction. Similarly, movement of
12 the second motor to drive the panel in said second direc-
13 tion may cause movement of the first motor in a direction
1~ opposite to its movement in driving the panel in said
first direction.
16 The first motor may have a first opening and a
17 second opening with the second motor also having a first opening
18 and~a second opening. Means may be provided for connecting
19 the second opening of the first motor with the second
opening of the second motor, sump means to receive hydraulic
21 fluid and means connecting the second opening of the first
22 motor and the second opening of the second motor to the
23 sump means. Valve means may be positioned between the
24 first and second motors and the means to supply pressurized
hydraulic fluid with the valve means having a first opera-
26 tive position to direct pressurized hydraulic fluid to the
27
28
29
31
32
-23-
D - 1 1 0 1
llZ71~8
1 first opening of the first motor to cause movement of the
2 first motor to drive the panel in said first direction.
3 l~ith the valve means in its first operative position, hy-
4 draulic fluid may also be transmitted from the first
opening of the second motor to the sump as the second n~otor
6 is moved in a direction opposite to its movement when
q driving the panel in said second direction. Hydraulic fluid
8 may also flow from the second opening of the first motor
9 into the second opening of the second motor and may also
flow into the sump as the first motor moves to drive the
11 panel in said first direction.
12 The valve means may also have a second operative
13 position to direct hydraulic f]uid to the first opening of
1~ the second motor to cause movement of the second motor to
drive the panel in said second direction and to cause move-
16 ment of the first motor in a direction opposite to its
17 movement when driving the panel in said first direction.
18 The valve means in its second operative position may trans-
19 mit hydraulic fluid from the first opening of the first
motor to the sump. Means may also be provided to inter-
~1 connect the first and second openings of the first motor
22 when the pressure of hydraulic fluid supplied to the first
23 opening of the second motor reaches a predetermined pressure
2~ level to permit hydraulic fluid to flow from the first open-
ing of the first motor into the second opening of the first
26 motor. In this manner, the second motor may act as an
27 accumulator for hydraulic fluid from the first motor when
28
29
31
32
-24-
~. :
,l 0 1
.--
1~27118
1 the first motor is driving the panel in its irst direc-
2 tion and the second motor is moving in a direction oppo-
3 site to its movement when driving the panel in said
4 second direction.
Additionally, the first motor may act as its
6 own accumulator of hydraulic fluid when the second motor
7 is driving the panel in said second direction and the
first motor is moving in a direction opposite to its
9 movement when driving the panel in its first direction.
The first motor, i~ acting as its own accumulator, may
11 discharge hydraulic fluid through the first opening
12 which may be conveyed back into the second opening in
13 the first motor. In the refuse compacting apparatus,
a the first motor may be a relatively large hydraulic cylin-
der having a first piston which separates the first and
16 second openings within the first motor. The second motor
17 may be a relatively small hydraulic cylinder which includes
18 a second piston that separates the first and second open-
19 ings in the second motor.
i ~
A further aspect of the invention concerns a
21 refuse compaction apparatus having a xefuse container, a
22 loading hopper and a passage from the loading hopper into
23 the refuse container. A packing panel may be positioned
2~ within the loading hopper for rotational movement from a
rest position in a working direction in sweeping through
26 the loading hopper to compact refuse therein and to move
27 the refuse through the passage into the refuse container.
28
29
31
32
-25-
-- D-l10]
1~27118
1 Means may be provided for driving the packing panel which
2 include a drive shaft rotatably supporting the packing
panel and a drive member connected to the panel. The
drive member may include a drive surface with a drive
~ lever connected to the drive member.
6 A flexible dri~ve member having a driving end and
q a fixed end may be connected to the drive lever through
8 said fixed end while a motor is connected to the driving
9 end. The flexible drive member may be positioned to con-
tact the drive surface in driving the packing panel during
11 movement of the packing panel in a working direction from
12 its rest position during the initial portion of its move-
13 ment through the hopper. The flexible drive member may
1~ then move out of contact with the drive surface to drive
the packing panel through the connection between the fixed
1~ end of the flexible drive member and the drive lever during
17 the latter portion of the movement of the packing panel in
18 a working direction through said hopper.
19 The drive surface may have a constant radius such
that contact of the flexible drive member with the drive
21 surace drives the packing panel with a force which is
22 applied through a constant moment arm whose distance is
23 determined by the radius. During movement of the packing
24 panel through the loading hopper, the flexible drive mem-
ber may contact the drive surface during rotation of the
26 drive member through an angle of about 158 with the
27 flexible drive member then moving out of contact with the
28 ///
29
31
32
-26-
~ - D-llOl
1~271~8
1 drive surface to drive the panel directly through the
2 drive lever and to apply a progressive force to the
3 panel during rotation of the drive lever through an
4 angle of about 90.
The packing panel may be rotatable in a re-
6 turn direction towards its rest position after swee~ing
q through the hopper in a working direction. A second
8 flexible drive mebmer having a driving end and a fixed
~ end may havc its fixed end connected to the drive sur-
13 face and its driven end connected to a second motor.
11 The second flexible drive member may, thereby, impart
12 rotational movement of the packing panel in moving the
13 panel in a return direction to said rest position. In
1~ driving the packing panel in a working direction and in
a return direction with the flexible drive member and
16 the second flexible drive member, the connection of the
17 fixed end of the flexible drive member to the drive
18 lever and connection of the fixed end of the second
19 flexible drive member to a point on the drive sur-
face with the connections of the fixed ends of the
21 flexible drive member and the second flexible drive
22 member being displaced a sufficient distance relative
23 to the drive surface to concurrently permit unwinding
2~ of the flexible drive member from the drive surface
and winding of the second flexible drive member onto
26 the drive surface as the packing panel is moved in
27 a working direction. Also, the said displacement
2~ may concurrently permit unwinding of the second flex-
29 ible driv~ ~ember from the drive surface and winding
///
31
32
-27-
D-ll 01
llZ71~8
-
1 of the flexible drive member onto the drive surface as
2 the packing panel is moved in a return direction toward
3 its rest position.
A further aspect of the invention concerns a
refuse compaction apparatus which includes a hopper and
6 a panel which is rotatably positioned for movement
q through the hopper. The panel may have a body with a
8 generally elliptical configuration, and a high torque-
9 transmitting capability. Drive means for the panel may
be connected to only one end of the panel such that a
11 rotational force may be applied to the panel at said one
12 end with the rotational force being transmitted through-
13 out the panel by the elliptical body.
14 A further aspect of the invention concerns a
refuse container for storing refuse under pressure, a
16 loading hopper, a passage leading from the loading hopper
17 into the container, and a packing panel rotatably posi-
18 tioned within the hopper to move from a rest position in
19 a working direction to sweep through the hopper to com-
pact refuse within the hopper and to move the refuse from
21 the hopper through the passage and into the container.
22 The packing panel may be movable in a return direction
23 to return the panel to its rest position with motor means
2~ connected to the panel for providing movement thereof.
Control means may be operatively connected to the motor
26 means to provide movement of the panel in a working direc-
27 tion and movement of the panel in a return direction.
28 ///
2g ///
31
32
-28-
,~ D~
1~27~18
1 The control means may have a neutral position
2 in which the motor means is inactivated with the control
3 means being movable to a first position in which the
4 motor means is activated to move the packing panel in a
working direction. The control means may also be movable
6 to a second position in which the motor means is activated
7 to move the packing panel in a return direction. Actuating
8 means may be provided to return the control means from
9 its first position or its second position to its neutral
position with the actuating means being operably connected
11 to the packing panel. The actuating means may have a third
12 position when the panel is in its rest position and a
13 fourth position when the panel has moved completely through
~4 the hopper in a working direction. The panel may occupy
a pinch-point position with respect to the hopper with the
16 panel moved into close proximity with the hopper during
17 movement of the hopper in a working direction.
la The actuating means may have a fifth position
19 when the panel is in its pinch-point position with the con-
trol means having a manually actuable override to disengage
21 the control means and actuating means when the actuating means
22 is in its fifth position. The actuating means may move the con-
23 trol means from its first position to its neutral position to
~4 stop the panel at its pinc~-point position when the actuating
means is in its fifth position and the override is unac-
26 tuated. Additionally, the actuating means may move the
27 control means from its first position to its neutral position
28
29
31
32
-29-
ll.Ol
1127118
1 when the actuating means is in its fourth position and the
2 packing panel has completed its movement in a working
3 direction. Also, the actuating means may move the control
4 means from its second position to its neutral position
when the actuating means is in its third position and the
6 panel has completed its movement in a return direction.
q A further aspect of the invention concerns a
8 refuse compaction apparatus having a container for storing
9 refuse under pressure and means for pressurizing refuse
within the container. A first rigid frame may be posi-
11 tioned at one end of the container with a second rigid
12 frame positioned at the other end of the container. A
13 plurality of longitudinal rigid members may interconnect
14 the first and second frames. A plurality of flexible
metal sheet members may enclose the container with the
16 sheet members being supported by the first and second
; 17 frames and the longitudinal rigid members. The flexible
18 sheet members may each be bowed outwardly at their points
j~ 19~ Of support. In this manner, the sheet members may be
placed in tension in resisting pressures within the
21 Container-
, .
; 22 A further aspect of the invention concerns a
j 23 reuse compaction apparatus which may include a container
'~4 for storing refuse under pressure and a tailgate rotatably
mounted on the container for movement between an opened
;~ 26 and a closed position. With the tailgate in its opened
27 position, refuse may be discharged from -the container
28
29
31
32
-30-
r 1 101
1127118
1 and with the tailgate in i-ts closed position, a closure
2 may be formed between the tailgate and the storage con-
3 tainer. In fixing the position of the tailgate with
respect to the refuse container with the tailgate in
~ its closed position, a latch member may engage a keeper
6 member. Means may be provided to impart rotational
q movement to the latch member to position the latch member
at a location where it may make contact with the keeper
9 member. Additionally, means may be provided to impart
translational movement to the latch member after its
11 rotational movement to move the latch member into contact
12 with the keeper member and to maintain the tailgate in a
13 closed position.
14 A further aspect of the invention concerns a
refuse compaction apparatus including a container for
16 storing refuse under pressure, a tailgate rotatably mounted
17 on the container for movement between an opened and a
18 closed position and the tailgate including a hopper to
19 receive refuse. A packing means may be positioned within
the loading hopper to move the refuse from the hopper into
21 the storage container with the tailgate in its closed ~
22 position. Drive means may be provided to drive the packing
23 means in moving refuse from the hopper into the storage
2~ container. The tailgate in its closed position may be in
abutting relation with the refuse storage container to form
26 a closure therewith and the tailgate in its opened posi-
27 tion may be rotated upwardly to expose the storage container
28 for discharge of refuse therefrom.
29
31
32
-31-
~ 0 1
11~7118
1 The drive means may be positioned on one side
2 of the tailgate to drive the packing means from said one
3 side. The weight of said one side of the tailgate may
then be greater than the weight of the other side of
the tailgate. An upper beam may be provided within the
6 tailgate with the tailgate being rotatably connected to
q the storage container through said upper beam. The upper
8 beam may include a stiffener assembly positioned adjacent
9 to the rotatable connection of the heavier one side of
the tailgate to the storage container. The stiffener
11 assembly may have a configuration which provides a high
12 resistance to torque. Thus, when a lifting force is
13 applied to the tailgate for raising the tailgate to its
1~ opened position, the force may be transmitted through
the upper beam with the twisting forces applied to the
I6 upper beam by the weight of the heavier one side of the
17 tailgate being resisted by the stiffener assembly.
18
19
21
22
23
2g
2~
26
27
28
29
31
32
-32-
-
D-ll01
1~27~18
1 The Drawings
3 To illustrate a preferred embodiment of the
invention, reference is made to the accompanying drawings
in which:
6 Fig. 1 is a side elevational view of a garbage
7 truck utilizing a refuse compacting apparatus of the in~
8 vention;
9 Fig. 2 is a side elevational view of a gar~age
truck illustrating the movement of an ejection panel within
11 the storage container by a conventional hydraulic cylinder
12 that is supported by a pivotal mounting which imparts trans-
13 lational movement to the cylinder that is in the same
14 direction as the movement of the ejection panel;
Fig. 3 is a side sectional view of the tailgate
16 structure positioned at the rear of the storage container
17 as shown in Fig. 1 with a side plate for the tailgate re-
18 moved to illustrate the position of hydraulic cylinders
19 thereln for moving a packing panel through a loading hop-
per;
21 Fig. 4 is an elevation detailed view of a packing
22 panel and a portion of the drive mechanism for the panel,
23 viewed from the rear of the tailgate as illustrated in
2~ Fig. l;
Fig. 5 is an end elevational view, partly in sec-
26 tion, of the packing panel taken along line 5--5 of Fig. 4;
27
28
29
31
32
-33-
101
l~Z7118
1 Fig. 6 is a sectional view taken along line
2 6--6 of Fig. 4;
3 Fig. 7 is a sectional view taken along line
4 7--7 of Fig. 4;
~ Fig. 8 is a sectional view taken along line
6 8--8 of Fig. 4;
7 Fig. 9 is a side elevational view of a re-
8 tainer panel and retainer panel cylinder illustrating
9 the movement of the retainer panel between an opened
and a closed position;
11 Fig. 10 is a side elevational view of the tail-
12 gate and drive mechanism, similar to Fig. 3, with the
~3 packing panel in a rest position and the retainer panel
I4 in a closed position;
Fig. 11 is a side elevational view, similar to
lG Fig. 10, illustrating the movement of the retainer panel
17 in a working direction through the loading hopper;
18 Fig. 12 is a side elevational view, similar to
19 ~Flgs. 10 and 11, illustrating the position of the pack-
ing panel at its pinch-point location after movement of
Zl~ the panel in a working direction until the lower edge of
2Z the packing panel is positioned closely adjacent to a
23 curved inner surface of the loading hopper at a point
24 adjacent to the sill of the loading hopper;
Fig. 13 is a side elevational view, similar to
Z6 Figs. 10-12, illustrating the position of the packing
27 panel after movement of the packing panel in a working
28
29
31
32
34-
,
1) ' 101
1~27118
1 direction through the loading hopper to force refuse
2 through a passage having a narrowed throat and then into
3 the refuse storing container with very high pressures
being exerted on the refuse as it passes through the
throat;
6 Fig. 14 is an elevational view taken along line
q 14--14 of Fig. 1 illustrating the appearance of the tail-
8 gate as viewed from the rear;
9 Fig. 14a is a sectional view taken along line
14a--14a of Fig. 14;
11 Fig. 14b is a detailed sectional view taken along
12 line 14b--14b of Fig. 14;
13 Fig. 14c is a detailed view, partially in section,
14 of the top beam for the tailgate illustrating a stiffening
15 assembly incorporated into the beam for resisting twisting
16 forces imparted to the beam by the weight of the relatively
17 heavy driving mechanism for the packing panel illustrated
1~ at the left in Fig. 14;
19 Fig. 14d is a sectional view taken along line
14d--14d of Fig. 14c to illustrate the structure of the
21 stiffening assembly within the top beam;
22 Fig. 15 is a sectional view taken along line 15--15
23 of Fig. 1 to illustrate the structure of the refuse storage
24 container and the manner in which flexible plates may be
utilized in forming walls of the container with the plates
26 being bowed outwardly to be placed in tension as pressures
27 are applied to the interior of the refuse container;
28
29
31
32
-~5-
~27118
1 Fig. 16 is a view taken along line 16--16 of
2 Fig. 1 to illustrate the inner appearance of the tail-
3 gate;
Fig. 16a is a sectional view taken along line
16a--16a of Fig. 16 to illustrate the configuration of
6 a seal utilized in sealing the tailgate to the refuse
q storage container when the tailgate is lowered to a
8 closed position;
9 Fig. 17 is an elevational view of the refuse
storage container as viewed from inside the storage
11 body;
12 Fig. 17a is a sectional view taken along line
13 17a--17a of Fig. 17;
14 Fig. 18 is a rear view of the refuse storage
15 body, as viewed from the right in Fig. 1, with the tailgate
16 removed for clarity of illustration;
17 Fig. 18a is a sectional view taken along line
18 18a~ a of Fig. 18;
~19 Fig. 19 is a partial elevational view of the tail-
20 gate as viewed fxom the right side in Fig. 14 to illustrate
21 a control mechanism for causing movement of the packing
22 panel, coupled with a stop mechanism connected to the pack~
23 ing panel for returning the control mechanism to a neutral
position;
Fig. l9a is a partial detailed view taken along
26 line l9a--19a of Fig. 19:
27 Fig. 20 is an elevation view taken along line
28 20--20 of Fig. 19;
29 ///
30 ///
31
32
-36-
;`l ~' : '
,101
7~
1 Fig. 21 is an elevational view of control rods
2 positioned within the tailgate whose movement is con-
3 trolled by movement of the control mechanism of Fig. l9;
4 Fig. 21a is a sectional view taken along line
21a--21a of Fig. 21;
6 Fig. 21b is an elevational view, similar to
q Fig. 21a, illustrating the positioning of the control
8 rods after one of the control rods has returned to its
9 neutral position, with the other control rod remaining
in an activated position;
ll Fig. 21c is a partial sectional view taken along
12 line 21c--21c of Fig. 21 illustrating the functioning of
13 a detent mechanism in holding one of the control rods in
14 an activated postiion while the other control rod may be
returned to its neutral postiion;
16 Fig. 22 is a schematic hydraulic circuit diagram
17 illustrating one embodiment of a hydraulic circuit for con-
18 trolling movement of the refuse compaction mechanism;
l9 Fig. 23 is a schematic hydraulic circuit diagram,
similar to Fig. 22, illustrating a second embodiment of a
21 hydraulic circuit for controlling movement of the reuse
22 compaction mechanism, and,
23 Fig. 24 is an elevational view, similar to Fig. 21,
24 illustrating the use of a single control rod for actuating
a portion of the elements in the hydraulic circuit illus-
26 trated in Fig. 23.
27
28
29
31
32
-37-
~ ~1101
` llZ71~8
1 Detailed Description
3 Figure 1 illustrates the invention embodied
4 in a garbage truck 2 having a cab 4 and a frame 6. A
5 storage body 8 for holding refuse under pressure is
6 positioned on the truck frame 6 with a tailgate 10
7 being rotatably supported at the rear of the storage
~ body. The tailgate in its closed position is indicated
9 in solid line drawing as 10 and is illustrated in
10 phantom line drawing in a raised position as 10'. During
11 the packing of storage body 8 with refuse under pressure,
12 the tailgate is maintained in its lowered position 10
13 and is fixedly positioned against the storage body.
14 ~owever, when the storage body 8 is filled with refuse,
15 the tailgate is then raised to its position 10' and
16 refuse within the storage body may be ejected through
17 the exposed opening at the rear of the storage body.
18 An ejection panel 12 may be slidably positioned
19 within the storage body 8 with movement of the ejection
20 panel serving to vary the volume within the storage body
Zl which is available for storing refuse. To fill the
22 storage body 8 with the maximum amount of refuse, it is
23 important that refuse within the storage body be packed
24 at a relatively uniform pressure. To accomplish this
25 result, the ejection panel may be positioned as shown in
26 solid line drawing 12 at a point adjacent the rear of
27 the storage body 8 during the initial stage of packing
28 refuse within the storage body.
29
31
32
-38-
D-llOl
l~Z'71~8
1 ~s refuse is introduced into the s-torage body
2 8 from tailgate 10, the refuse may exert pressure against
3 the ejection panel 12. When the pressure exerted by
4 refuse against ejection panel 12 exceeds a predetermined
pressure level, the ejection panel may then be moved a
6 small incremental distance toward the front of the
7 storage body 8. This reduces the pressure exerted by
8 refuse against the ejection panel 12 and the packing of
9 refuse into the storage body 8 may then continue until
the pressure exerted by refuse against the ejection
11 panel again exceeds the predetermined pressure level
12 with the ejection panel then being again moved a small
13 incremental distance, etc. Progressive filling of the
14 storage body 8 with refuse may then be aacomplished in
a uniform manner with the refuse being packed within
16 the storage body at a relatively uniform pressure.
17 This results in filling the storage body 8 with the
18 maximum amount of refuse which is beneficial in reducing
19 the time which is lost in trips to a landfill or refuse
2~0 transfer center to discharge refuse.
21 When the storage body 8 is full of refuse, th,e
~2 ejection panel may occupy the position shown in phantom
23 line drawing as 12' adjacent to the forward end of the
24 storage body. To move the ejection panel 12 within the
storage body 8, a telescopic cylinder 1~ may be connected
26 to a pivot 16 at the forward end of the storage body with
27 the other end of the cylinder connected to a pivot 18 on
28
29
31
32
-39-
D - l l O I
liZ7118
1 the frame for the ejection panel. With the ejection
2 panel in its forward position 12', the telescopic
3 cylinder 14 may be completely contracted and with the
ejection panel in its rearward position 12', the
cylinder may be completely extended. Slide rails 20
6 may be positioned along either side of the storage body
7 8 with slots in the frame for the ejection panel 12
8 engaging the slide rails. The upright position of the
9 ejection panel 12 within the storage body 8 may, thus, be
maintained during movement of the ejection panel.
11- As indicated, the storage body 8 may include
12 a front frame 22 positioned adjacent to the cab 4 and
13 a rear frame 24 which supports the tailgate 10 and
14 engages the tailgate in its closed position. The con-
struction of the storage body 8, as will be described,
16 is strong and also surprisingly light as compared with
17 prior constructions. Thus, the storage body 8 does
18 not require support at points intermediate its ends.
19 Only the front and rear frames 22 and 24 may be con-
nected to the truck frame 6 in providing a ligh-ter con-
21 struction with savings in the energy required to power
22 the truck 2 and a reduction in the wear and tear on
23 the highways during usage of the truck.
24 A tailgate cylinder 26 may be employed for
raising and lowering of the tailgate 10. The tailgate
26 10 may be connected to the rear frame 24 through pivots
27 28 positioned on either side of the rear frame. The
28
29
31
32
-40-
~~ D '~'
llZ7~8
1 tailgate cylinder 26 may be connected to the rear frame
2 24 through a pivot 30 with the otner end of the tailgate
3 cylinder being connected to the tailgate 10 through a
4 pivot 32. The cylinder is illustrated in solid line
drawing in an extended condition as 26 with the tailgate
6 in its raised position 10'. With the tailgate in its
7 lowered position 10, the tailgate cylinder is shown in
8 phantom line drawing in its contracted condition as 26'.
9 A hopper generally indicated as 34 may be formed in the
lower portion of the tailgate 10 with the hopper including
11 a curved bottom surface 36, a loading opening 38 to re-
12 ceive refuse, and a loading sill 40 beneath the loading
13 opening. A passage shown in phantom line drawing as 42
14 may lead from the hopper 34 into the storage body 8 and
15 a packing panel, generally indicated as 44, may be ~.
16 positioned within the hopper to move refuse from the
17 hopper through the passage into the storage body.
18 The packing panel 44 may include a main panel
19 indicated in phantom line drawing as 46 and a foldable
2.0 panel in phantom line drawing as 48. As will be described,
21 the fo}dable panel 48 may undergo limited rotational
22 movement with respect to the main panel. 46 with the fold-
23 able panel in an extended position adjacent the surface
24 36 as the packing panel 44 sweeps through the hopper 34
in a working direction to move refuse through the passage
26 42 into the storage body 8. However, when the packing
27 panel 44 then moves in a return direction to return to
28
29
31
32
-41-
D-l101
~1271~8
1 its rest position adjacent the rear of the hopper 34,
2 the foldable panel 48 may undergo rotational movement
3 with respect to the main panel 46 to pass over refuse
within the hopper.
In discussing the various positions of the
6 packing panel 44, the packing panel will be referred to
7 in its extended condition when the foldahle panel 48 is
8 extended to a position adjacent the bottom surface 36
9 during movement of the packing panel in a working
direction. The packing panel 44 will be referred to
11 in its collapsed or partially collapsed condition as
12 the packing panel moves in a return direction to its
13 rest position. To provide movèment of the foldable
14 panel 48 with respect to the main panel 46, friction
pads indicated in phantom line drawing as 49 may be
16 provided in either end of the foldable panel. The
17 friction pads 49 may have an outer surface formed of
18 plastic with the friction pads being spring biased in
19 an outward direction into contact with the sidewalls of
the hopper 34. The friction pads 49 may, thus, cause
21 rotational movement of the foldable panel 48 to an
22 extended condition as the panel sweeps through the
23 hopper 34 in a working direction. However, on movement
24 of the packing panel 44 in a return direction to its
rest position, the frictional contact of the friction
26 pads 49 with the sidewalls of the hopper 34 may cause
27 rotational movement of the foldable panel 48 to a
28 ///
29 ///
31
32
-42-
~ D-llOl
1 collapsed or partially collapsed position such that the
2 foldable panel 48 may ride over refuse within the
3 hopper.
4 In providing movement of the packing panel 44
within the hopper 34, a relatively large hydraulic drive
6 cylinder 50 may be used to drive the packing panel in a
7 working direction while a smaller hydraulic return cylinder
8 52 may be used to move the packing panel in a return
9 direction to its rest position. As indicated, the drive
cylinder 50 may transmit rotational movement to the
11 packing panel 44 through a drive plate 53 which is opera-
12 tively connected to the packing panel and functions as
13 a lever in providing a mechanical advantage in transmitting
14 power to the packing panel.
A retainer panel indicated in phantom line
16 drawing as 54 may be rotatably positioned adjacent the
17 entrance into the passage 42 from the hopper 34. During
18 movement of the packing panel 44 in a working direction
19 through the hopper 34, the retainer panel 54 may positioned
2P in its opened position as indicated in Figure 1 to permit
21 movement of refuse from the hopper into the passage. I~ith
22 the retainer panel 54 in its opened position as indicated
23 in Figure 1, the lower surface of the retainer panel, in
24 effect, forms a continuation of the upper surface of the
passage 42. This is advantageous in assisting the move-
26 ment of refuse from the hopper 34 through the passage 42.
27 However, on movement of the packing panel 44 in a return
28
29
31
32
-43-
101
1~27~18
1 direction away from the passage 42, as will be described,
2 the retainer panel may be rotated to its closed position
3 to at least partially block the opening between the
4 passage and the hopper 34. With the retainer panel 54
in its closed position, the flow of refuse from the
6 passage 42 into the hopper 34 is impeded, which improves
7 the overall efficiency of the packing mechanism in
8 moving refuse from the loading hopper into the storage
9 body ~.
l~ith the packing panel 44 in its rest position
11 in a raised location at the rear of the hopper 34, the
12 packing panel may be in its collapsed condition. During
13 movement of the packing panel 34 from its rest position
14 in a working direction, contact of the friction pads 49
against the sidewalls of the hopper 34 cause the foldable
16 panel 48 to undergo rotational movement with respect to
17 the main panel 46. During this movement of the packing
18 panel 44 in a working direction, it is desirable that the
19 foldable panel 48 should not extend out of the hopper 34
through the loading opening 38 since this could present
21 a safety hazard. Guide rails shown in phantom line draw-
22 ing as 56 may be formed on the side walls of the hopper
23 34. ~he guide rails 56 may extend inwardly to engage
2~ the foldable panel 48 and to maintain the foldable panel
within the confines of the hopper as the packing panel 44
26 moves from its rest position to a position adjacent the
27 hopper sill 40.
28 ///
29 ///
31
32
-44-
~ 1, 1 1
112~118
1 As indicated in Figure 1, the telescopic cylin-
2 der 14 may be used in moving the ejection panel 12 within
3 the storage body ~. A telescopic cylinder, such as
4 cylinder 14, is a relatively complex hydraulic device
with internal passages within the cylinder to supply
6 hydraulic fluid to the various cylinder sections which
7 vary in size. Due to the difference in size between the
8 pressure areas within the telescopic cylinder, problems
9 may be encountered in its use. For example, when there
is an increase in the ambient temperature and the tele-
11 scopic cylinder is full of hydraulic fluid, the expansion
~2 of hydraulic fluid at the large area end of the cylinder
13 may produce undesirably high pressur,es at the small area
14 end of the cylinder. If the ratio between the areas at
the large and small ends of the cylinder is, for example,
16 10 to 1, a one hundred pounds per square inch increase
17 due to expan~.ion of fluid at the large end may produce
18 a thousand pounds per square inch increase at the small
19 end. It would, thus, be desirable if some means could
be provided for providing movement to the ejection panel
21 12 without requiring the use of a telescopic cylinder,~
22 such as cylinder 14. However, due to the large distance
23 through which a hydraulic cylinder must move in provid-
24 ing movement to the ejection panel 12, there has pre-
viously been no alternative except to use a telescopic
26 hydraulic cylinder.
27
28
29
31
32
-45-
~ ~ D-llOl
~:127118
1 ~igure 2 illustrates an embodiment of the in-
2 vention in which a means is provided to produce movement
3 of the ejection panel 12 through use of a conventional
4 hyclraulic cylinder. For simplicity in illustration, like
reference numerals have been used in referring to struc-
6 tural elements in Figure 2 which are the same as those
7 described in Figure 1. As indicated, a pivot 58 may be
8 provided at the forward end of the storage body 8, with
9 a preferably triangular support member 60 rotatably
supported by the pivot. A conventional hydraulic cylinder
11 62 may be rotatably secured to a pivot 64 on the support
12 member 60 positioned at a point intermediate its ends.
13 As indicated, with the ejection panel 12 at its forward
14 position within the storage body 8, the generally trian-
gular configuration of support member 60 may be advan-
16 tageous in permitting the hydraulic cylinder 62 to extend
17 in a forward direction beyond the front frame 22. This
18 permits the storage body 8 to be made shorter since there
19 does not need to be additional length provided simply to
accommodate the hydraulic cylinder 62.
21 The ejection panel 12 may include a transverse
22 frame member 66 with a pivot 68 on the frame member rota-
23 tably engaging the rod of the piston 62. A link member
24 72 may rotatably engage a pivot 70 on the support member
60 with the link member also engaging the pivot 68 on
26 transverse frame member 66. The link member 72, thus,
27 fixes the distance between the pivot 70 on support member
28
29
31
32
-46-
~-1101
ilZ7118
1 60 and the pivot 68 on the transverse frame member G6.
2 As will be described, this permits translation of the
3 hydraulic cylinder 62 during its expansion and contrac-
tion which results from rotational movement of the sup-
port member 60 with respect to the pivot 58.
6 On expansion of the hydraulic cylinder from
7 its position indicated as 62 to a new position indica-
8 ted as 62a, the support member 60 undergoes rotational
9 movement to position 60a. This produces movement of
the pivot 64 to a new position 64' such that the
11 hydraulic cylinder in position 62a has undergone trans-
12 lational movement to follow the movement of the ejec-
13 tion panel to its new position 12a.
14 On further expansion of the hydraulic cylin-
der to position 62b, the ejection panel has been moved
16 to position 12b where it is positioned immediately adja-
17 cent to the rear end of the storage body 8. Also, the
18 support member has undergone further rotational movement
19 to position 60b with further movement of the pivot 64
to position 64b. Thus, the translational movement pro-
21 vided to hydraulic cylinder 62 has permitted the use o~
22 the cylinder in providing a movement of the ejection -
23 panel 12 which is much greater than the total expansion
24 of the hydraulic cylinder. A conventional hydraulic
cylinder 62 may, therefore, now function in a manner
26 which is the e~uivalent of the function of a more com-
27 plex and more expensive telescopic hydraulic cylinder.
28
29
31
32
-47-
D - 1 1 0 1
llZ7118
1 During contraction of the hydraulic cylinder 62, the
2 above sequence of movements is reversed, with the
3 cylinder moving from position 62b to position 62a and
4 then to position 62 as the support member moves from
position 60b to position 60a and then to position 60.
6 Figure 3 is a side sectional view through the
7 tailgate 10 to illustrate the mechanism for packing
8 refuse and moving the refuse from the hopper 34 into
9 the storage body 8. The pivot 30 for the tailgate
cylinder 26, as illustrated, may be formed within a
11 mounting ear 71 which is affixed to the rear frame 24.
12 The hopper 34, as viewed from the left in Figure 3, may
13 include a sidewall 73 which may be formed from several
14 plates connected together in any suitable fashion, such
as by welding. The sidewall 73 may be positioned between
16 the packing panel 44 and the drive mechanism for the
17 packing panel itself such that the drive mechanism is
18 shielded from contact with refuse. The drive cylinder
19 50 may be rotatably connected at its upper end to a
pivot 74 that is secured to the tailgate 10. Similarly,
21 the relatively srnall return cylinder 52 may be connected
22 at its upper end to a pivot 76 secured to the tailgate
23 10. The packing panel 44, as illustrated, has completed
24 its movement in a working direction through the hopper
34 to move refuse from the hopper into the passage 42.
26 At this point, the return cylinder 52 is completely
27 extended, as indicated by the position of the piston rod
28
29
31
32
-48-
0 1
1127118
1 78. Piston rod 78 may be connected to a drive chain 80
2 for transmitting movement to the packing panel ~ during
3 its movement in a return direction to its rest position.
4 With the packing panel 44 positioned as illus-
trated, the drive cvlinder 50 is completely contracted
6 as indicated by the retracted position of piston rod 82.
The piston rod 82 may be connected to a drive chain 84
8 whose lower end is secured to a connection 86 on the
9 drive plate 53. As described, the drive cylinder 50 and
the return cylinder 52 may work together in unison because
11 of their connection to the drive mechanism for the packing
12 panel 44. Thus, as the drive cylinder 50 contracts, the
13 return cylinder 52 expands during the movement of the
14 packing panel 44 in a working direction through the hop-
per 34. Similarly, during movement of the packing panel
16 44 in a return direction to its rest position, the return
17 cylinder 52 contracts while the drive cylinder 50 expands.
18 The retainer panel 54 may be rotatably secured
19 to a pivot 88 for movement between its open and closed
positions. The retainer panel 54 is illustrated in its
21 opened position in Figure 3 as the packing panel is moved
22 in a working direction through the hopper 34 to move refuse
23 from the hopper into passage 42 and into the storage
2~ body 8.
Wi-th the tailgate 10 in its lowered position,
2~ the tailgate may be fixed with respect to the storage
27 body 8 by a tailgate latch generally referred to as 90.
28 ///
29 ///
31
32
-49-
01
~127~8
1 The tailgate latch 90 may be rotatably connected to the
2 tailgate 10 through a pivot 92 while a support member 94
3 on the rear frame 24 supports a keeper 96 which is engaged
4 by the tailgate latch 90. The tailgate latch 90 may in-
clude a threaded rod 98 with a correspondingly threaded
6 sleeve 100 being positioned about the rod. A handle 102
7 may be formed at the outer end of the sleeve 100 such
8 that turning of the handle either threads or unthreads
9 the sleeve with respect to the threaded rod 98. An en-
largement 103 on the rod 98 may engage one side of the
11 keeper 96 while the other side of the keeper may be
12 engaged by the inner end of the sleeve 100 with the keeper,
13 thereby, being tightly gripped between the enlargement
14 and the end of the threaded sleeve. The tailgate 10 may
then be securely latched to the storage body 8.
16 Turning to Figure 4, which is a sectional view
17 taken along line 4--4 of Figure 3, the packing panel 44
18 may be rota-tably mounted on a pair of shafts 104 and 106.
19 In driving the packing panel 44, a torque tube 108 may
be secured to the shaft 104 with a drive plate 110 being
21 rigidly secured to the outer end of the torque tube. ~s
22 illustrated, the shaft 104, the torque tube 108, the
23 drive plate 110 and the drive plate 53 move together in
24 unison in imparting rotational movement to the pac]cing
panel 44. Moving inwardly along the shaft 104, a separa-
26 tor plate 112 is joined to the drive plate 53 and a stif-
27 fening plate 114 is joined to the plate 112 and to the
28 ///
29 ///
31
3~
-50-
-~ ~D-llOl
:~lZ7il:8
1 torque tube 103. A stiffening plate 116 may then be
2 joined to the inner end of the torque tube 108, to the
3 shaft 104 and to the main panel 46.
4 At its undriven end, the main panel 46 may be
connected to the shaft 106 by a stiffening plate 118
6 which is joined to the shaft and also to the main panel.
7 A support member 120 may surround the shaft 106 and be
8 connected to the main panel 46 with a stiffening plate
9 122 being joined to the other end of the support member,
to the shaft and also to the main panel. A collar 124
11 may be positioned about the shaft 104 with the collar en-
12 gaging the exterior surface of the drive plate 110 and
13 a collar 126 may be positioned about the shaft 106 with
14 the collar engaging the exterior surface of stiffening
plate 122.
16 To provide a strong and rigid connection between
17 the torque tube 108, the shaft 104 and the main panel 46,
18 a pair of side plates 128 may be secured to the torque
19 tube and also to the main panel. The side plates 128
with the stiffening plates 114 and 116, joined to the
21 end surfaces of the side plates, form a very rigid s-truc-
2?~ ture through which torque is transmitted from the torque
23 tube 108 to the main panel 46.
24 As illustrated, the drive chains 80 and 84 may
each be connected to the drive plates 53 and 110 through
26 which torque is imparted to the torque tube 108 and to
27 the packing panel 44. In connecting the drive chain 80
28
29
31
32
-51-
L 101
llZ~
1 to plates 53 and 110, a pin 130 may be secured to the
2 drive plates through apertures therein with a clevis
3 132 positioned on the pin and having secured thereto
4 the drive chain 80. A spacer element 134 may also be
positioned on the pin 130 to maintain the position of the
6 clevis 132 relative to the pin 130.
7 In securing the drive chain 84 to the drive
8 plates 110 and 53, the pivot 86 may be secured to the
9 drive plates through apertures therein with a mounting
plate 136 secured to pIate 110 to retain the outer end
11 of the pivot relative to the plate 110. A clevis 138
12 may be rotatably positioned on the pivot 86 with the
13 clevis secured to the drive chain 84~ As indicated, the
14 connection between the drive chain 84 and clevis 138 is
positioned a greater distance from the axes of the shafts
104 and 106 than the connection between drive chain 80
17 and the clevis 130. Thus, forces transmitted to packing
18 panel 44 through the drive chain 84 may act through a
19 greater moment arm than the forces transmitted to the
2P packing panel by the drive chain 80. This is advanta-
21 geous in providing a mechanical advantage during movement
22 of the packing panel 44 in a working direction by the
23 drive chain 34.
24 The side wall 73 of the hopper 34, as illus-
trated in Figure 4, may extend into a space between the
26 plates 53 and 114 such that the drive mechanism for the
27 packing panel 44 is isolated from refuse within the
28 ///
29 ///
31
32
-52-
--~-1101
~iZ7i 18
l loading hopper 34. A second sidewall 140 of loading
2 hopper 34 may also be positioned in close proximity to
3 the other end of the packing panel 44. The foldable panel
4 48 may be rotatably mounted with respect to the main panel
5 46 within slots 142 formed in the main panel. Tongue
6 members 144 joined to the foldable panel 48 may be posi-
7 tioned within the slots 142 with the tongue members each
8 being rotatably secured to pins 146 which extend between
9 the sidewalls of the slots to engage apertures formed in
lO the tongue members. Stop members 148 may be secured to
11 the main panel 46 to permit limited rotational movement
12 of the foldable panel 48 with respect to the main panel 46.
13 The rotational movement of panel 48, as discussed
14 previously, may be provided by friction pads 49 positioned
15 at either end of the foldable panel 48 in contact with the
16 sidewa~ls 73 and 140. As the main panel 46 is moved, the
17 frictional engagement of pads 49 with the sidewalls 73 and
18 140 causes rotational movement of the foldable panel 43
l9 with respect to the main panel 46. Additionally, the
2,0 movement of the foldable panel 48 is controlled to some
21 extent by the guide rails 56 which may extend inwardly a
22 short distance from the sidewalls 73 and 140 to engage
23 guide members 150 on the foldable panel 48.
24 Figure 5 is a sectional view taken along line
25 5--5 of Figure 4 which illustrates the position of fold-
26 able panel 48 with respect to main panel 46 and the manner
27 in which rotational movement of the foldable panel is
28 ///
29 ///
31
32
-53-
_, 1101
lB
l limited with respect to the main panel. As indicated,
2- support brackets 147 secured within the foldable panel
3 48 by bolts 149 may rotatably engage the pins 146 mounted
4 to the main panel 46. The support brackets 147 may be
secured to the foldable panel 48 by bolts 149. Stop
6 members 148 secured to the main panel 46 may each pro-
7 vide stop surfaces 152 and 154 which are engagable by
8 a stop member 156 secured to the foldable panel 48 by a
9 support bracket 158. As indicated, contact between the
stop member 156 and stop surfaces 152 and 154 effectively
ll limits the rotational movement of the foldable panel
12 between the limiting positions provided by the stop
13 surfaces.
14 Figure 5 illustrates the foldable panel 48 in
its extended condition after rotation of the foldable
16 panel in a clockwise direction with respect to the pin
17 146 to engage the stop member 156 with the stop surface
18 152. This is the position of the foldable panel 48 when
l9 the packing panel 44 rotates in a counter-clockwise
2P direction from its direction shown in Figure 5 in moving
21 in a working direction through the hopper 34 as shown in
22 Figure 3. During rotational movement of the packing
23 panel 44 in a return direction, i.e., clockwise from its
24 position shown in Figure 5, the foldable panel 48 may
undergo rotational movement in a counter-clockwise direc-
26 tion until the stop member 156 contacts the stop surface
27 154. At this point, the packing panel 44 is in a collapsed
28
29
31
32
-54-
101
~12711S
1 position such that the foldable panel 48 may pass over
2 refuse within the hopper 34 during movement of the
3 packing panel in its return direction.
4 Figure 6 is a sectional view taken along the
line 6--6 of Figure 4 to illustrate the construction of
6 the main panel 46 and that of the stop members 148 which
7 control the degree of rotational movement of the foldable
8 panel 4~. As indicated, the torque tube 108 may be
9 directly connected to the main panel 46 which may be dis-
placed from the axis of the torque tube. Additionally,
11 the side plates 128 may extend from the exterior surface
12 of the torque tube 108 to the exterior surface of the
13 main panel 46 to provide a very strong and rigid connec-
14 tion between the torque tube and main panel. In previous
refuse compaction apparatus, it has been necessary to
16 drive the packing mechanism through hydraulic cylinders
17 positioned at either end of the packing panel. However,
18 in the present apparatus, the main panel 46 may be
19 driven from only one of its ends. This permits a great
reduction in the weight of the drive mechanism and also
21 simplification of the drive mechanism. To achieve these
22 beneficial results, the main panel 46 has a generally
23 elliptical cross-sectional configuration which has great
24 strength in resisting twisting moments and in transmit-
ting torque. The cross-sectional configuration of the
26 main panel 46 together with the strong and rigid connec-
27 tion between the torque tube 108 and the main panel
28
29
31
32
-55-
- -11.01
~271~8
1 permits driving the main panel from only one of its ends
2 with the torque which is imparted to the main panel then
3 being transmitted throughout the main panel.
4 As indicated in Figure 6, an aperture 160 may
be formed in each of the stop members 148 to rotatably
6 support the foldable panel 48 with respect to the main
7 panel 46. Addi-tionally, an aperture 162 may be formed
8 in the stiffening plate 114 to engage the support shaft
9 104 as shown in Figure 4.
Figure 7 is a sectional view taken along the
11 line 7--7 of Figure 4 which illustrates the internal con-
12 struction of the main panel 46 through which the foldable
13 panel 48 is supported. To provide strength within the
14 main panel 46 to support the foldable panel 48, trans-
verse baffle plates 164 may be positioned within the
16 interior of the main panel with the baffle plates being
17 secured to the inner surface of the main panel through
18 any suitable means such as welding. Additionally, the
19 baffle plates 164 may then extend through the exterior
surface of the main panel 46 to be integrally connected
21 to the stop members 148. A channel 166 (shown in phantom
22 line drawing) may then be rigidly secured to the baffle
23 plate and an angle 168 may be connected to the stop mem-
24 ber 148 in providing additional strength for the stop
25 memberS.
26 Figure 8 is a sectional view taken along the
27 line 8--8 of Figure 4 which illustrates the cross-sec-
28
29
31
32
-56-
~ ,- ~01
~Z'71~3
tional configuration of the main panel 46 at its undriven
2 end. In securing the main panel 46 to the shaft 106, an
3 aperture 170 may be formed in the stiffening plate 122
4 to engage the exterior surface of the shaft. During move-
ment of refuse from the loading hopper 34 through the
6 passage 42 into the storage body 8, as discussed in regard
7 to Figures 1 and 3, the movement of the packing panel 44
8 and the retainer panel 54 may be precisely coordinated.
9 Thus, as the packing panel 44 is driven in a working
lO direction through the hopper 34, the retainer panel 54
11 may he positioned in an opened position so that there is
12 unimpeded flow of refuse from the hopper 34 into the pas-
13 sage 42 and then into the storage body 8. However, with
14 movement of the packing panel 44 in a return direction to
15 return the packing panel to its rest position, the retainer
16 panel 54 is moved to a closed position with the retainer
17 panel at least partially blocking the opening between the
18 loading hopper 34 and the passage 42. In its closed po-
19 sition, the retainer panel 54, thus, functions to impede
2P the flow of refuse from the passage 42 into the hopper 34.
21 When the packing panel 44 has completed its
22 movement in a working direction with the retainer panel
23 54 in an opened position (see Figure 3), the retainer
24 panel is positioned closely adjacent to the exterior sur-
25 face of the main panel 46. When the movement of the
26 packing panel 44 is then reversed in moving the packing
27 panel in a return direction, the retainer panel 54 may
28
29
31
32 -57-
D-llOl
llZ7118
1 then be immediately moved to its closed position. During
2 this movement of the retainer panel to a closed position,
3 the retainer panel may move very close to the surface of
4 the main panel to sweep refuse from the main panel which
is forced into the passage 42 by the retainer panel 54.
6 Returning to Figure 8, the main panel 46 may include an
7 inwardly curved surface 172 which is expressly designed
8 to accommodate the movement of the retainer panel 54 rela-
9 tive to the main panel 46 as the retainer panel is moved
from its opened to its closed position. The retainer panel
11 54 may, thus, move along the inwardly curved surface 172
12 in sweeping refuse from the main panel 46 which is, there-
13 by, forced from the main panel 46 into the passage 42.
14 Figure 9 is a detailed view of the retainer
panel, as shown in Figures 1 and 3, with the panel in its
16 opened position indicated in solid line drawing as 54 and
17 the panel in its closed position indicated in phantom
18 line drawing as 54'. With the retainer panel in its opened
19 position 54, the lower panel surface 173, in effect,
forms a continuation of the wall 174 of passage 42. Thus,
21 with the retainer panel in its opened position 54, the
22 configuration of the panel assists in the movement of re-
23 fuse into the passage 42. A cross brace 176 provides
24 strengthening of the wall 174 adjacent to the retainer panel
54 with the retainer panel cylinder 55 having a piston
26 rod 180 which extends through an opening 182 formed in
27 the cross brace. A link 184 is joined at one end to the
2~ ///
29 ///
31
32
-58-
D-llOl
l~Z7118
1 piston rod 180 with the other end being rotatably connected
2 to a pin 186. An eccentric 188 has its upper end rotatably
3 connected to the pin 186 with the eccentric passing through
4 an opening 190 in the cross brace 176 to connect through
S a pin 194 to the pivot 88 for the retainer panel 54. Sup-
6 port members 196 and 198 may be joined to either end of
7 retainer panel 54 to provide additional strengthening
8 thereof.
9 During movement of the retainer panel to its
closed position 54', the cylinder 55 undergoes extension to
11 cause a downward movement of the piston rod 180 and link
12 182 and rotational movement of the eccentric 188. This, in
13 turn, causes rotational movement of the retainer panel to
14 its closed position 54'. During this rotational movement,
the retainer panel may sweep along the inwardly curved
16 surface 172 of the main panel 46 as illustrated in Figure
17 8. To assist in nolding refuse within the passage 42, the
18 retainer panel 54 may include a lip 200. With the retainer
19 panel in its closed position 54', the lip indicated as
200' opposes the movement of refuse along the curved sur-
21 face 173 which is directed inwardly toward the passage 42,
22 to assist in preventing the flow of refuse from the pas-
23 sage back into the loading hopper 34.
24 Figure 10 is the first in a series of figures
which illustrate the movement of the main panel 46 and
26 the foldable panel 48 during their movements withinl the
27 loading hopper 34. As illustrated, the passage 42
28
29
31
32
-59-
'~' ,. ' 1
~Z7118
1 includes an enlarged opening 202 which leads into the
2 storage body 3. The passage 42 also includes a narrowed
3 throat 20~ where the walls of the passage are converged.
4 The narrowed throat 204 serves a very unique and important
function in compacting refuse in a new and improved manner
6 as compared with refuse compacting apparatus of the prior
7 art. In previous refuse compacting apparatus, the refuse
8 was compacted under high pressure by packing panels which
9 squeezed the refuse between the surfaces of the packing
panels and the surface of an ejection panel such as the
11 panel 12 illustrated in Figures 1 and 2. With the ejec-
12 tion panel being mounted within a refuse storage body,
13 such as storage body 8, high compaction pressures were
14 generated by squeezing the refuse between the packing
panels and the ejection panel to create large internal
16 pressures which had to be absorbed by the structure of the
17 refuse storage body. This required that the refuse
18 storage body had to be formed of heavy structural members,
19 which resulted in increased weight of the refuse compac-
tion apparatus. This was, of course, undesirable, since
21 the increased weiyht of the refuse compaction apparatus
2~ increased the energy requirements for movement of the
23 apparatus. Also, the increased weight of the refuse com-
24 paction apparatus caused increased wear and tear to the
road surfaces used by the apparatus and increased the cost
26 of the apparatus.
27 By using a passage 42 in the present apparatus
28 with a narrowed throat 204, extremely high pressures may
29 ///
///
31
32
-60-
",~_, . l,.LQl
l~Z71~8
1 be generated as the refuse passes through the converging
2 surfaces of the passage 42 within the narrowed throat
3 204. These locally high pressures result in squeezing
4 the refuse within the narrowed throat 204 at pressures
which may far exceed the pressures within the refuse
6 storage body 8. For example, in the use of a refuse
7 compaction apparatus of the invention having a narrowed
8 throat 204, the ratio of the pressures exerted on the
9 refuse at the narrowed throat with respect to the pressures
imposed by the refuse against the ejection panel 12 within
11 the storage body 8 (see Figures 1 and 2) may be in the
12 order of 35 to 7. That is to say, when the refuse is
13 subjected to a pressure of 35 psi in passing through
14 the narrowed throat 204, the pressure within the
storage body 8 may only be in the order of 7 psi. This,
16 then, permits constructing the storage body 8 of rela-
17 tively light materials while still uniformly packing the
18 refuse within the storage body at the very h,igh pressures
19 generated within the narrowed throat 204. In this manner,
2,0 the cost of the refuse compaction apparatus may be reduced
21 by the savings in the metal used for construction of the
22 storage body 8 and also the overall weight of the refuse
23 compaction apparauts may be greatly reduced.
24 In its position shown in Figure 10, the packing
25 panel 44 is in its collapsed rest position with the fold-
26 able panel 48 folded with respect to the main panel 46
27 and the packing panel in an elevated location adjacent
28
29
31
32
-61-
~ J--~101
~Z7~8
1 the rear of the hopper 34. Additionally, the retainer
2 pane:L 54 is in its closed position to impede the flow
3 of refuse from the passage 42 into the hopper 34. With
4 the packing panel 44 in its rest position, the drive
cylinder 50 is completely extended and the return cylinder
6 52 is completely contracted. To begin the movement of
7 the packing panel 44 in a working direction from its rest
8 position, control rods indicated in phantom line draw-
9 ing as 206 and 207 may then be moved to initiate the flow
of hydraulic fluid for contraction of the drive cylinder
11 S0, extension of the return cylinder 52 and rotational
~2 movement of the retainer panel 54 from its closed posi-
13 tion to its opened position.
14 Turning to Figure 11, with movement of the con-
trol rods 206 and 207 to initiate movement of the packing
16 panel 44 in a working direction, the first event to take
17 place is the rotational movement of the retainer panel 54
18 from its closed position indicated in Figure 10 to its
19 opened position shown in Figure 11. This provides an
enlarged opening 208 from the hopper 34 into the passage
21 42. Moreover, as illustrated, the lower surface o~ the
22 retainer panel 54 with the retainer panel in its opened
23 position forms an extension of the adjacent surface of
24 the passage 42 to cooperate in promoting the flow of
refuse from the hopper 34 into the passage and in providing
26 high localized pressures within the passage at the narrowed
27 throat 204.
28
29
31
32
-62-
1101
11~7~
l Proceeding to Figure 12, after movement of the
2 retainer panel 54 to its opened position shown in Figure
3 11, the packing panel 44 moves downwardly from its rest
4 position within the hopper 34. During downward movement
of the packing panel 44, the foldable panel 48 undergoes
6 rotational movement with respect to the main panel 46 to
7 move the packing panel from its collapsed condition to
8 its extended condition. As previously described, this
9 takes place because of the frictional engagement of the
friction pads 49 (see Figures 1, 3 and 4) with the side-
ll walls of the hopper 34. During movement of the packing
12 panel from its collapsed to its extended position, the
13 lower edge of the foldable panel 48 is guided through
14 contact with the side rails 56 which may maintain the
foldable panel 48 within the confines of the hopper 34.
16 With the packing panel 44 positioned as shown
17 in Figure 12, the lower edge of the foldable panel 48 is
18 brought into relatively close proximity with the curved
19 bottom 36 at a point adjacent to sill 40, which is termed
the "pinch point" 210. At the pinch point 210, there is
21 a spacing between the lower edge of the foldable panel
22 48 and the inner surface 36 which is sufficiently large
23 to accommodate a worker's fingers. Thus, if the worker
24 were careless and placed his fingers at the pinch point
210 as the packing panel was descending, the spacing at
26 the pinch point would be sufficiently great to prevent
27 the loss of the worker's fingers. Also, as indicated, a
28
29
31
32
-63-
--`~
D-llOl
li~7118
1 considerable distance is provided between the outer end
2 of the sill 40 and the pinch point 210 lgenerally in
3 the order of a foot-and-a-half to two feet) which is a
4 safety feature, since this distance would make it dif-
ficult for the worker to have his fingers at the pinch
6 point.
7 In addition to the safety reasons for main-
8 taining the distance between the panel 4~ and the surface
9 36 at the pinch point 210, the distance at the pinch
lO point reduces the impact forces exerted nn the metal at
11 the sill 40 by the descending force of the packing panel
12 against refuse at the pinch point. In previous refuse
13 compaction apparatus, the packing panel was brought ex-
14 tremely close to the inner surface of the hopper at a
15 point adjacent to the hopper sill. The refuse was then
16 subjected to very high shearing forces exerted thereon by
17 the downward edge of the packing panel. To resist these
18 high shearing forces, it was generally necessary to pro-
19 vide heavy reinforcement within the tailgate structure
20 at the sill at a point approximating the location of the
21 pinch point 210. This had the effect of increasing the
22 overall weight of the refuse compaction apparatus. How-
23 ever, by providing the present distance between the
24 foldable panel 48 and the curved inner surface 36 at the
25 pinch point 210, it is possible to reduce the weight of
26 the structural members in the tailgate 10 in the vicinity
27 of the pinch point 210. This results in making the over-
28 all apparatus lighter and cheaper.
29 ///
30 ///
31
32
-64-
101
llZ7118
1 During downward movement of the packing panel
2 44 from its rest position, shown in Figure 11, to its
: 3 position shown in Figure 12, the drive cylinder 50 may
4 contract, with force being transmitted from the piston
rod 82 to the drive chain 84 and to the drive plate 53
6 and torque tube 108. As illustrated, with this move-
7 ment of the packing panel 44, the drive chain 84 may
8 contact the exterior surface of the torque tube 108.
9 Thus, torque which is transmitted to the packing panel
44 may be supplied through a constant moment arm deter-
11 mined by the radius of the torque tube 108. During
12 this movement of the packing panel 44, the packing panel
13 may be moved relatively rapidly and the force applied
14 to the packing panel by the drive chain 84 may be rela-
tively low. Also, during this movement of the packing
16 panel 44, the panel does not encounter gxeat resistance
17 from refuse within the hopper 34 since the panel is
18 merely moving from its collapsed rest position to a
19 position where the foldable panel 48 is in an extended
condition adjacent to curved inner surface 36 at the
- 21 pinch point 210.
22 During movement of the packing panel 44 from
23 its collapsed rest condition in Figure 11 to its extended
24 condition shown in Figure 12, the return cyli.nder 52 may
undergo expansion with the piston rod 78 being extended
26 and the drive chain 80 being wrapped about the exterior
27 surface of the torque tube 108. As indicated, the posi-
28 ~//
29 ///
31
32
-~ ~D-llOl
llZ7118
1 tioning of the drive chains 80 and 84 with respect to
2 the torque tube 108 permits unwinding of the chain 84
3 from the torque tube while the drive chain ~0 is being
4 wound about the torque tube without interference between
the two drive chains. Further, as illustrated, the
6 movement of the cylinders 50 and 52 may be precisely
7 coordinated due to their mechanical interconnection through
drive chains 80 and 84 with the torque tube 108. In
~ previous refuse compaction apparatus using several cylin-
ders for driving a packing panel, it has been difficult
11 to coordinate the movements of the various cylinders. This
12 has resulted from the fact that the only interconnection
13 between the various cylinders may have been a hydraulic
14 interconnection which, through failure of some element
in the hydràulic system, could permit the various cylinders
16 to get out of balance. This cannot occur in the function-
17 ing of the present apparatus, since the mechanical inter-
18 connec~ion of cylinders 50 and 52 insures that these
19 cylinders must work in unison. Additionally, as will be
described, the cylinders 50 and 52 are hydraulically
21 interconnected. However, the hydraulic interconnection
22 of cylinders 50 and 52 is augmented by their mechanical
23 interconnection which prevents the cylinders from being
24 out of balance in moving the packing panel 44 within the
hopper 34-
26 As discussed, during movement of the packin~
27 panel 44 from its position in Figure 11 to its position
28
29
31
32
-66-
.~n
l~Z7~
1 in Figure 12, the rotational force applied to the pack-
2 ing panel by the drive chain 84 may be applied through
3 a constant moment arm determined by the radius of the
4 torque tube 108. However, on continued rotational
movement of the torque tube 108 and drive plate 53 from
6 their position shown at the right of Figure 12, the
7 connection point 86 moves to a point positioned -to
8 the left of the shaft 104. During this movement, the
9 drive chain 84 is moved out of contact with the exterior
surface of the torque tube 108 and the driving force
11 from the cylinder 50 through drive chain 84 is applied
12 directly to drive plate 53 at the connection point 86.
13 This results in progressively increasing the moment arm
14 through which the drive chain 84 acts in providing torque
for rotational movement of the packing panel 44 with the
16 applied force to the packing panel being progressively
17 increased as the packing panel continues its movement
18 through the hopper 34 in a working direction. During
19 this movement of the packing panel 44, the resistance of
refuse within the hopper is.greatly increased as the
21 refuse is compacted and forced into the passage 42 and
22 through the narrowed throat 204. Accordingly, during
23 this movement of the packing panel 44, it is essential
2~ that a large drivi.ng force be applied to the packing
panel. Also, during this movement of the packing panel
26 94, the rotational speed of movement of the packing
27 panel is progressively decreased as the moment arm
28
29
31
32
-67-
~lln
llZ7118
1 between the drive chain and the axis of rotation of the
2 panel is progressively increased.
3 Figure 13, which is similar to Figures 10
through 12, illustrates the position of the packing panel
44 after completion of its movement in a working direc-
6 tion through hopper 34. During movement of the packing
7 panel 44 from its position in Figure 12 to that shown in
8 Figure 13, the connection point 86 between the drive
9 chain 84 and drive plate 53 is moved further and fur-
ther away from the axis of the shaft 104. This progres-
11 sively increases the torque applied to the packing panel
~2 44 through contraction of the relatively large hydraulic
13 drive cylinder 50. This progressive increase in torque
14 provides a progressively increasing force to refuse
within the loading hopper 34 as the refuse is forced
16 into the passage 42 and through the narrowed throat 204
17 to exert very high localized pressures on the refuse.
18 Also, during this movement of the packing panel 44, the
19 drive chain 80 is wound about the outer surface of
torque tube 108 as the return cylinder 52 continues its
21 expansion-
22 ~s indicated, the inner surface of passage 42
23 includes a curved surface portion 212, whose curvature
24 is directed toward the interior of the storage body 9,
to exert a horizontal flow direction to refuse, indicated
26 as 214, which is directed into the storage body. Thus,
27 after subjecting the refuse to very high localized
28
29
31
32
-68-
~127118
1 pressures within the narrowed throat 204-l the refuse is
2 discharged from passage 42 into storage body 8 with the
3 movement of the refuse directed toward the ejection panel
4 12 as described in Figures 1 and 2. The force exerted on
the ejection panel 12 by refuse in the storage body 8, even
6 though much less than the pressures exerted on refuse at the
7 narrowed throat 204, may be used in providing movement of
8 the ejection panel away from the passage 42 as the storage
9 body 8 becomes progressively filled with refuse. This permits
10 uniform filling of the storage body 8 with refuse which has
li previously been uniformly compacted at relatively high
12 pressures within the narrowed throat 204 with the refuse
13 being stored at the lower pressures determined by the pressure
14 of refuse against the ejection panel 12. The increased moment
15 arm produced by the connection of the drive chain to the
16 connection point 86 on the drive plate 53 is indicated as
17 216 at the right of Figure 13.
18 The various members effectively operate in a servo
19 relationship to provide an optimum compaction of the refuse
in the hopper 34, and particularly in the passage or opening
21 42. This will be seen from the discussion immediately below.
22 As will be appreciated, the main panel 46 and the
23 foldable panel 48 compact the refuse during their movement
24 forwardly from their respective positions shown in Figure 13.
As the refuse becomes compacted, it is directed upwardly and
26 forwardly into the narrowed throat 204 of the passage or
27 opening 42.
28 The distance of movement of the refuse in the
29 narrowed throat 204 is relatively long. Furthermore, the
///
31 ///
32
-69-
l~Z7~18
1 narrowed throat 204 has a progressive constriction with
2 progressive distances along the passage or opening 42.
3 This causes the refuse to become compacted as it is directed
through the passage or opening 42. It also causes the refuse
to become fragmented during the movement of the refuse through
6 the passage, partly because of the venturi effect on the
7 refuse in the passage 42 and partly because of the interaction
~ between the different pieces of refuse with the progressive
9 constriction in the passage.
Since the passage 42 is fairly long, the refuse
11 does not move completely through the passage in a single
12 cycle of movement of the main panel 46 and the foldable panel
13 48. Thus, the refuse introduced into the passage 42 in
14 previous cycles of operation of the panels 46 and 48 is
stuffed further into the passage by refuse introduced into
16 the passage in subsequent cycles of operations of the panels.
17 As the refuse is stuffed deeper into the passage in the sub-
18 sequent cycles, it produces some churning of the refuse
19 introduced into the passage in the previous cycles and also
produces compaction and fragmentation of such refuse as a
21 result of such 9tuffing and churning.
22 As previously described, the pressure against the
23 refuse in the most constricted area of the passage or opening
24 42 is quite large. This pressure is then relieved to a large
extent in the enlarged opening 202 because the enlarged
26 opening 202 flares outwardly with progressive positions
27 toward the storage body 8. Thus, the pressure of the refuse
28 is relatively low as it enters the storage body 8.
29 ///
///
31
32
-69a-
11271~8
1 The servo effect results in part from the control
2 exerted on the positioning of the ejection panel 12 to
3 maintain the pressure of the refuse in the storage body 8
4 against the ejection panel 12 within precisely controlied
limits. Thus, when the pressure of the refuse against the
6 ejection panel 12 exceeds a first particular limit, the
7 ejection panel is moved through an incremental distance in
8 a direction away from the passage 42 to reduce the pressure
9 of the refuse against the ejection panel. This incremental
10 movement continues until the pressure of the refuse against
11 the ejection panel decreases to a second particular value
12 less than the first particular value. As will be described
13 subsequently in detail, the response to pressures of the
14 refuse in the storage body 8 above the first particular value
occurs instantaneously. Furthermore, the incremental move-
16 ment of the ejection panel is provided instantaneously through
17 booster arrangements. In thls way, the ejection panel 12 is
18 moved incrementally through small distances before the move-
19 ments are interrupted by pressures below the second particular
value of the refuse against the ejection panel.
21 A precise control over the pressure of the refuse
22 in the storage body 8 is important in insuring that an optimum
23 action of fragmenting and compacting the refuse occurs in the
24 passage 42. This results from the fact that the pressure of
the refuse in the storage body 8 corresponds to the reduced
26 pressure of the refuse in the enlarged opening 202 of the
27 passage 42.
28 For example, if the pressure of the refuse in the
29 storage body 8 should increase above the first particular
value, the pressure exerted by the refuse in the enlarged
31 opening tends to become excessive. This inhibits the ability
32 ///
-69b-
1~271 ~8
1 of the refuse in the narrowed throat 204 of the passage 42 to
2 become stuffed into the passage by the direction of refuse into
3 the passage in subsequent cycles and to become chrned and
4 compacted as it is stuffed into the passage. In effect, the
5 refuse in the narrowed throat 204 of the passage 42 becomes
6 constipated because of the excessive back pressure exerted
7 against this refuse by the refuse in the enlarged opening 202.
8 Such constipation tends to block further flow of refuse through
9 the passage 42.
Similarly, if the ejection panel 12 becomes moved
11 incrementally when the pressure of the refuse against the
12 ejection panel is below the second particular value, an
13 efficient action of compacting and fragmenting the refuse in
1~ the narrowed throat 2-4 of the passage 42 cannot be obtained.
15 This results from the fact that the refuse in the enlarged
16 opening 202 does not exert a sufficient back pressure against
17 the refuse in the narrowed throat 204 of the passage 42 to
18 cause the refuse in the narrowed throat to become stuffed and
19 accordingly to become fragmented and compacted. In effect,
20 because of the insufficient back pressure of the refuse in the
21 enlarged opening 202, the refuse is moved loosely, or at least
22 too easily, through the passage 42 without being subjected to
23 the forces which normally cause such refuse to be fragmented
2~ and compacted.
Figure 14 is a rear view of the truck with the
26 tailgate 10 in a closed position as indicated by the arrows
Z7 14--14 in Figure 1. The hopper opening is indicated by the
28 distance of the bracket indicated as 218 with a portion of
29 the figure bein~ broken away at the left to illustrate the
support structure 220 for the shaft 104. As indicated, the
31 drive mechanism, including the relatively large drive cylinder
32 50 may be positioned at the left side of tail~ate 10 with the
-69c-
' 101
llZ7118
1 packing panel 44 being driven from only one side to pro-
2 vide a lighter and less complex drive mechanism. By
3 providing the drive mechanism on only one side of the
tailgate 10, there may be a weight imbalance, since ~he
side of the tailgate 10 which houses the drive mechanism
6 may be heavier than the other side. Also, reaction
7 forces which are transmitted from the drive members into
8 the support structure of the tailgate 10 will be greater
9 on the side of the tailgate which supports the drive
mechanism. For these reasons, the construction of the
11 tailgate 10 may be strengthened, as will be indicated,
~2 to absorb the greater weight and the greater reaction
13 forces which may be imposed on the side which houses the
14 drive mechan.ism.
The tailgate 10 may include an upper beam 222,
16 an enlarged side beam 224 and a smaller side beam 226.
17 Turning to Figure 14a, which is a sectional view taken
18 along lines 14a--14a of Figure 14, the movement of the
19 foldable panel 48 is illustrated in various states with-
2P in the hopper 34. In moving from its rest position to
~1 its position at the pinch point 210, the lower end o~ the
22 foldable panel 48 may move along a curved path indica-ted
23 by the arrow ~ with the guide members 150 contacting the
2~ guide rails 56. During this movement, contact of the
friction pads 49 on foldable panel 48 with the sidewalls
26 of the hopper causes rotational movement of the fol~able
27 panel about the pin 146 in the direction indica-ted by the
28 ///
29 ///
31
32
-70-
1101
` 1127118
1 arrow B. In moving in the direction of arrow B, the
2 panel 48, thus, moves from a folded position relative
3 to the main panel 46 to an extended condition relative
4 to the main panel. During the movement of the fold-
able panel 48 in a reverse direction within the hopper
6 34 with the panel undergoing movement in a return di-
7 rection, the frictional contact between friction pads 49
8 and the sidewalls of the hopper 34 produces rotational
9 movement of the panel with respect to pin 146 which is
opposite to that indicated by the arrow B. Thus, during
11 return movement of the foldable panel 48, the panel is
12 moved from its extended condition to its collapsed or
13 folded condition.
14 As described, when the panel 48 is moved down-
wardly to a point adjacent the pinch point 210, there is
16 a distance between the lower edge of the panel 48 and the
17 inner curved surface 36 which may be in the order of
18 1 to 2 inches. This distance provides a margin of safety
19 for the worker who may inadvertently place his fingers
2.0 within the pinch point 210. Also, this distance reduces
21 impact forces which may be transmitted from the panel 48
22 to the structure of the tailgate 10 at the pinch point 210.
23 In its position indicated as 48', the foldable
2~ panel is.positioned adjacent to the pinch point 210 and
this may be the closest point of approach of the panel to
26 the curved inner surface 36 of hopper 34. After passing
27 beyond the pinch point 210, the panel ~8 has a path of
28 ///
29 ///
31
32
-71-
1101
l~Z7~18
1 movement indicated by the line 228. As'illustrated,
2 the line 228 is positioned further away from inner sur-
3 face 36 than the distance between the foldable panel 48
and the curved inner surface at the pinch point 210. This
increased distance, as indicated by the bracket 230, may
6 be in the order of two and a half to four inches, which
7 represents a distinct difference between the present appara-
8 tus as compared with compaction apparatus of the prior
9 art. In previous refuse compaction apparatus, it has been
customary for,the packing panel to pass in very close proxi-
11 mity to the wall of the loading hopper during packing of
12 refuse within the loading hopper. By having the packing
13 panel move in very close proximity to the curved surface
14 of the hopper, as has been done previously, the power re-
quirements for driving the packing panel through the load-
16 ing hopper may be greatly increased. With the panel posi-
17 tioned very close to the wall of the hopper, there is no
18 provision for slippage through which refuse may be permitted
19 to slip by the panel during its movement through the hopper.
However, with the path of movement o panel 48
21 as indicated ~y line 228 in Figure 14a, there is provis~ion
22 for slippage such that refuse may be permitted to remain
23 in the hopper 34 by slipping by the foldable panel 48 as
24 it is moved through the hopper 34. By providing this
degree of slippage, the power requirements for movement
26 of the panel 48 through hopper 34 may be reduced.
27
28
29
31
32
-72-
1 0 1
llZ7118
1 Additionally, the spacing 230 between the path
2 of movement 223 and the curved inner surface 36 provides
3 a further advantage which has been lacking in refuse
4 compaction apparatus of the prior art. For example, in
loading refuse into a hopper, such as hopper 34, the re-
6 fuse may frequently be of a bulky nature such as, for
7 example, a large cardboard box. Due to the size of the
8 object being placed within the hopper, only a small
9 portion of the object may be capable of insertion into
the hopper with the balance of the artic].e extending
11 out of the opening of the hopper and over the sill 40.
~2 In previous refuse compaction apparatus, the downward
13 movement of the packing panel blade into close proximity
14 to the surface of the loading hopper would provide a
shearing force which would sever a large bulky article
16 so that the severed portion would be packed within the
17 hopper as the balance of the bulky article fell to the
18 ground by reason of the weight of the article extending
19 over the loading sill. This would make it necessary to
again lift the article and to feed the remainder of the
21 article sequentially into the hopper as each working
22 movement of the packing panel would, in effect, take another
23 bite out of the article.
24 By providing a distance between the edge of the
packing panel, such as the distance 230 between the fold-
26 able panel 48 and the curved inner surface 36, the panel
27 may not completely shear bulky articles inserted into the
28
29
31
32
-73-
D-llOl
llZ71i8
1 hopper. Thus, the article, if it were a cardboard box,
2 would merely be gripped between the lower edge of the
3 panel 48 and the inner curved surface 36. As the panel
4 48 continues its movement through the hopper 34, the
bulky article may then be dragged into the hopper by the
6 gripping force applied to the article by the movable
7 panel. Following movement of the panel 48 through the
8 hopper, the movement of the panel in its collapsed posi-
9 tion during return movement through the hopper may permit
the panel to pass over the refuse which has been dragged
11 into the hopper. In this manner, instead of the panel
12 48 taking bites out of bulky articles as they are inserted
13 into the hopper 34, the panel may not only pack the bulky
14 article within the hopper in a series of packing motions,
but may also lighten the job of the worker by pulling the
16 bulky article into the hopper with each succeeding move-
17 ment of the foldable panel in a working direction. The
18 movement of the panel 48 through various positions within
19 the hopper 34, as shown in phantom line drawing, is indi-
2.0 cated as 48''.
21 To provide support for the retainer panel cylin-
22 der 55 (see Figure 9) a support plate 232 may be provided
23 on the interior of the tailgate 10 with an aperture 234
24 to pivotally support the retainer panel cylinder. Also,
a pivot support 236 may be provided for rotatably suppor-
26 ting the retainer panel 54 at a point adjacent to passage
27 42. Additionally, a support member 238 may be provided
28
29
31
32
-74-
1~27~18
1 for supporting the shaft 106 (see Figure 4) and a pivot
2 support 240 may be provided for the pivot 74 (see Figure 3)
3 for support of the cylinder 50.
4 As discussed in regard to Figure 1~, the struc-
ture of the tailgate 10 may be designed to compensate for
6 the additional weight and reaction forces which are borne
7 hy the tailgate as a result of housing the drive mechanism
8 for the packing panels at only one slde of the tailgate.
9 Figure 14b is a sectional view taken along the line indi-
cated by the arrows 14b--14b of Figure 14. As indicated,
11 irregularly shaped stiffening plates 242 may be positioned
12 at either side of the side beam 224 to engage the beams
13 244 and 246 which may converge at the pivot support 240.
14 This provides a strong base of support to absorb large
reaction forces which may be transmitted to the pivot
16 support 240 by the relatively la.ge hydraulic drive
17 cylinder 50.
18 Returning to Figure 1~, an enlarged side eleva-
19 tional view of the upper beam 222 is shown in Figure 14c.
As illustrated in Figure 14c, the upper beam 222 may
21 include an outer surface member 248 having a stiffener
22 assembly 250 integrally formed within the upper beam at
23 a position adjacent its left side as indicated by the loca-
24 tion of the arrows 14d--14d in Figure 14. The function
of the stiffener assembly may be to effectively isolate
~- 26 the high forces generated in the lefthand portion of
27 beam 222 such that these forces are not allowed to twist
28 ///
29 ///
31
32
-75-
D-llOl
llZ~7118
1 or bend the upper beam. As indicated, the stiffener
2 assembly 250 may include a transverse stiffener plate
3 252 positioned at one end and a transverse stiffener
4 plate 254 positioned at the other end of the assembly.
Turning to Figure 14d, which is a sectional
6 view taken along the line 14d--14d of Figure 14c, the
7 transverse stiffener plates 252 and 254 may each have
8 an irregular configuration with enlarged ends joined
9 to the outer surface member 248 and to an outer surface
member 256 which is joined to outer surface member 248.
11 Additionally, longitudinal stiffeners 258 and 256, which
12 may each have a curved configuration corresponding to
13 the shape of the plates 252 and 254, may join the stif-
14 fener plates together. The closed configuration of
the stiffener assembly 250 which may be provided by the
16 interconnection of the transverse plates 252 and 254 with
17 the longitudinal stiffener plates 258 and 260 may pro-
18 vide a very stiff and strong structure having a high
19 resistance to twisting and bending. In this manner,
large forces which may be generated in the left portion
21 of the upper beam 222 (see Figure 14) due to mounting
22 of the drive mechanism on the left side of the tailgate
23 10 are successfully resisted by the upper beam 222.
24 Figure 15 is a sectional view through the
storage body 8 taken along line 15--15 of Figure 1. As
26 indicated, the storage body 8 may be supported by upper
27 longitudinal stiffeners 262 and 264 and lower longitudinal
28 ///
29 ///
31
32
-76-
D-llOl
l~Z'7118
1 stiffeners 266 and 26g. The slide rails 20 may be
2 formed integrally with the lower stiffeners 266 and 268
3 to extend inwardly into the storage body 8. As des-
4 cribed previously in regard to Figures 1 and 2, the
ejection panel 12 may slidingly engage the rails 20
6 with the slide rails engaging grooves formed in the
7 lower portion of the frame for the ejection panel.
8 As discussed, the present apparatus may be
9 lighter than previous refuse compaction ap~!~ratus. To
provide a strong and yet light construction for the
11 storage body 8, the sidewalls of the storage body may be
12 formed of flexible metal sheets, indicated as 270, 272,
13 274 and 276. The flexible sheets 270, 272, 274 and 276
14 may be bowed outwardly from their points of connection
to the longitudinal stiffeners 262, 264, 266 and 268
16 This insures that the flexible metal sheets 270, 272,
17 274 and 276 may be placed in tension by pressures
18 generated within the storage body 8. Since the metal
19 sheets may have a high tensile strength as compared to
their strength in compression, this may permit the
21 relatively thin and lightweight sheets 270, 272, 27~
22 and 276 to be used in forming the storage body 8. The
23 storage body 8 may, thus, be made lighter. Also, as
2~ discussed previously, by subjecting the refuse to high
pressures within the narrowed throat 204 of passage 42
26 prior to introduction of the refuse into the storage
27 body 8, the storage body may be designed to function at
28
29
31
32
-77-
~~ D-llOl
llZ7118
1 lower pressures. This also may reduce the need for rela-
2 tively heavy structural members in the construction of
3 the storage body 8.
4 As indicated in Figure 15, a conduit passa~e
278 may be formed on the surface of the upper sheet
6 member 274 and a corresponding conduit passage 280 may
q be formed on the surface of the lower sheet member 276.
8 The conduit passages 278 and 280 may be used for running
9 hydraulic or electrical lines between the front and rear
portions of the storage body 8.
11 Figure 16 is a front view of the tailgate 10 in
12 its lowered position as indicated by line 16--16 of Figure 1.
13 As indicated, seal members 281 and 282 may be positioned
14 on the side beams 224 and 226 for contact with the rear
of the storage body 8 with the tailgate 10 in its lowered
16 position. A transverse brace 283 may provide support for
17 the upper wall of the passage 42 and a lower frame member
18 284 may be positioned between the side beams 224 and 226.
19 A flat surface ~86 may be formed below the
portion of the passage 42 with the flat surface positioned
21 in close proximity to a corresponding flat surface on
22 the storage body 8 with the tailgate in itS lowered posi-
23 tion as illustrated in Figures 1 and 3. A seal 285 may
24 be positioned about a portion of the flat surface 286, which
seal may engage the storage body 8 with the tailgate 10
26 in its lowered position to form a fluid-tight barrier.
27 As refuse is compacted within the loading hopper, fluid
28
2~
31
32
-78-
~ D l.n1
l~Z7~18
1 may be expressed from the refuse with the fluid collec-
2 ting in the region bounded by the seal 285. The seal 285,
3 thus, functions to prevent a leakage of fluid from the
4 joint between the lowered tailgate 10 and the storage
body 8.
6 Figure 16a is a sectional view taken along
7 the line 16a--16a of Figure 16 to illustrate the configura-
~ tion of the seal member 285. As indicated, the seal mem-
9 ber 285 may include a base portion 287 that may be posi-
tioned against the side beams 224 and 226 and the lower
11 frame member 284 with a curved upstanding portion 288
12 positioned at a generally right angle with respect to
13 the base portion 287. The curved upstanding portion 288
14 may include a hollow region 289 that permits deformation
of the curved upstanding portion during usage in forming
16 a liquid-tight barrier between the storage body 8 and
17 the tailgate 10.
18 In supporting the seal 285, a support member 290
19 may extend outwardly in a generally perpendicular direc-
tion with respect to the surface of the side beams 224 and
21 226 and the lower frame member 284 and a support
22 clamp member 291 may extend in an angular relation to the
23 seal to engage the upper surface of base portion 287. For
24 ease in replacement of seal member 285, the support clamp
291 may be somewhat flexible such that the clamp member
26 can be pulled outwardly away from contact with the base
27 member 287. This permits the removal of the seal member
28
29
31
32
-79-
1101
l~Z7118
1 285 with the clamp member 291 being pulled outwardly as
2 a new seal member is inserted. Following this, the clamp
3 member 291 may be released to clamp the replacement seal
4 member 285 firmly in place.
Figure 17 is a front elevational view of the
6 forward support frame 22 as viewed from inside the storage
q body 8. As indicated, the forward frame 22 may include
8 a top frame member 292 having a curved lower surface 294
9 for engagement with the curved sheet member 274 (see
Figure 15). Additionally, side frame members 296 and
11 298 may be joined to the top ~rame member 292 and a
12 cross channel ~00 may interconnect the side frame members.
13 This provides the forward frame 22 with a structure which
14 is both rigid and strong. A pair of generally triangular
shaped plates 302 and 304 may be positioned against the
16 channel 300 and ~enerally triangular shaped support chan- -
17 nels 306 and 308 may be positioned beneath the cross
18 channel 300 to provide a su~port between the
19 structure of the refuse storage body 8 and the truck
frame 6.
21 A plate 310 may extend between the inner ends
22 of the channels 306 and 308 with plates 312 and 314 being
23~ affixed to the inner ends of the channels 306 and 308 and
2~ also with the cross channel 300- Downwardly extending
connecting members 316 and 318 may be affixed respectively
26 to the plates 312 and 314 with the connecting members
27 being joined at their lower ends to the truck frame 6.
28
29
31
32
-80-
D~
11~7118
A hydraulic fluid reservoir 320 may be positioned on the
2 upper surface of the cross channel 300 and a pivot sup-
3 port 322 for the ejection panel 12 (see Figure 1) may
4 be formed between the legs of the cross channel 300
Figure 17a is a side sectional view taken along
6 the lines 17a--17a of Figure 17. As indicated in Figure
7 17a, the connecting members 316 and 318 may each be joined
~3 to the respective plates 312 and 314 with the connecting
9 members extending through openings in the lower surface
of the support channels 306 and 308. Connecting member
11 316, for example, extends through opening 323 in the
12 channel 306 to engage plate 312. Additionally, the
13 connecting members 316 and 318 may each include a
14 plurality of apertures 324 within which bolts may be
placed in securing the connecting members to the vehicle
16 frame 6.
17 Figure 18 is an elevational view of the storage
18 body 8 as seen from the rear of the truck 2 with the tail-
19 gate removed (see Figure 1). As indicated, the rear
2.0 frame 24 of the storage body 8 may include rigid side
21 members 326 and 328 joined at their upper ends by a top
22 member 330. The lower por-tions of side members 326 and
23 328 may be connected by a cross beam 332 with the cross
24 beam being joined to the truck frame 6 through angle
i 25 braces 334 and 336. One leg of each of the angle braces
26 334 and 336 may be positioned in contact with the upper
27 surface of -the longitudinal members of the truck frame 6
28 ///
29
31
32
-81-
~ D-llOl
l~Z71~8
1 with the angle braces being secured to the frame
2 through any convenient means such as connecting bolts
3 or welding. Additionally, the angle braces 334 and 336
4 may include upstanding legs which may bear against the
cross beam 332 and may be secured therto, by example,
6 by welding.
7 A rear plate 338 may be joined to cross beam
8 332 with the rear plate forming a flat downwardly ex-
9 ter.ding surface at the rear of storage body 8 which sur-
face may be positioned in close proximity to the flat
11 surface 286 of tailgate 10 (see Figure 16) when the
12 tailgate is in its lowered position at the rear of the
13 storage body. The upper edge of the rear plate 338 may
14 be curved to correspond with the curvature of the
flexible metal sheet 276 of the storage body 8. Simi-
16 larly, the side members 326 and 328 may be suitably
17 curved to support the flexible metal sheets 270 and 272
18 forming the sides of the storage body 8 while the top
19 member 330 may also be curved to support the flexible
sheet 274.
21 Plate support members 340 and 342 may be
22 joined to the cross beam 332 with the plate support mem-
23 bers extending downwardly from the cross beam to provide
24 support for the downwardly extending rear plate 338.
A cross brace 344 may be joined to the plate support
26 members 340 and 342 with the cross brace being secured
27 to the lower extremity of the flat plate 338. Plate
28
29
31
32
-82-
n o~
l~Z7118
l support members 340 and 342, together with the cross brace
2 344 may, thus, form a rigid frame for support of the
3 downwardly extending rear plate 338 which may bear against
the tailgate lO in its lowered position.
A pivot member 346 may be formed at the upper
6 extremity of side member 328 with the pivot member rotatably
q supporting one side of the tailgate 10 with respect to the
8 storage body 8 (see Figure l). The other side of the
9 tailgate lO may be supported by the pivot 28 which may be
supported by a channel brace 348 connected to the top
ll member 330. As described previously in Figure 14, hydraulic
12 cylinders within the tailqate lO may be mounted at one side
13 thereof such that the packing panel 44 may be driven from only
14 one side, as described in Figures 4 and 5. This positioning
15 of the hydraulic cylinders may produce a weight imbalance
16 within the tailgate 10 such that one side of the tailgate is
17 heavier than the other side. The heavier side of the tail-
18 gate 10, which contains the hydraulic ~cylinders, may be
19 pivotally connected to the pivot 28 with the channel brace
20 348 providing additional strength in rotatably supporting
21 the heavier side of the tailgate. In addition, a support
22 channel 350 may be joined to the top member 330 to further
23 strengthen the top member at the region adjacent to the
24 pivot 28 in rotatably supporting the heavier side of the
tailgate lO.
26
27
28
29
31
32
-83-
1101
~lZ7118
1 As indicated, support beams 352 may be positioned
2 along either side of the storage body 8 at the lower ex-
3 tremities thereof to provide strengthening of the storage
body at these regions. Also, curved plates 354 may be
joined to the support beams 352 with the curved plates
6 being connected to the upper ends of support members 340 and
q 342. The curved configuration of plates 354, as illustrated,
8 may merge smoothly into the curvature of the flexible
9 metal sheet 276. The connection of the plates 354 to the
flexible metal sheet 276 may, therefore, serve to fix the
11 curvature of the metal sheet at its extremities, while also
12 providing strengthening of the lower portions of the
~-3 storage body 8.
14 Figure 18a is an elevational view taken along the
line 18a--18a of Figure 18, which illustrates the configura-
16 tion of side member 328. The pivot 346 formed at the upper
17 extremity of side member 328 may extend rearwardly from the
18 storage body 8 with the pivot 30 for the tailgate lifting
19 cylinder 26 (see Figure 1) likewise extending rearwardly
and being positioned below the pivot 346. The plate sup-
21 port membex 342 may include a rearwardly inclined surface
22 355, Additionally, the other plate support member 340
23 (see Figure 18) may also include an inclined surface simi-
2~ lar to surface 355. The effect of inclined surface 355 is
to reduce the weight of the support member 342 while still
26 providing support for the rear plate 338.
27
28
29
31
3~
-8~-
J" `.01
~2~ii8
1 Figure 19 is a fragmentary side elevational
2 view taken from the right side of the tailgate 10 shown
3 in Figure 14 to illustrate the operation of the control
mechanism. A control member 356 which may be grasped
by the operator may include an outer tube 358 which is
6 secured to a plate 360. The plate 360 may be connected
7 to a rotatable rod 362 through a pin 364. With the con-
8 trol member 256 positioned as shown in Figure 19, the
9 control member is in its neutral position and there is
no movement of the packing panel 44. With the packing
11 panel 44 in its rest position as shown in Figure 10, move-
12 ment of the control member 356 in the direction of the
13 arrow B initiates the movement of the packing panel in a
14 working direction and movement of the retainer panel 54
from a closed to an opened position. Conversely, with the
16 packing panel 44 and retainer panel 54 positioned as
17 shown in Figure 13, movement of the control member 356
18 in the direction of the arrow C initiates movement of
19 the retainer panel 54 from an opened to a closed posi-
tion and movement of the packing panel 44 in a return
21 direction from its position in Figure 13 to that in
22 Figure 10.
23 A rod 366 may be positioned within the tube 358
24 with the rod extending through an aperture in the closed
bottom 370 oE the tube. A spring 372 may be positioned
26 about the rod 366 at its lower end with one end of the
27 spring engaging the bottom 370 and the other end of the
28
29
31
32
-85-
r)-llOl
i8
1 spring engaging A spring stop 374 positioned about the
2 rod. A handle 376 may be positioned about the outer
3 tube 358 at its lower end with the handle including a
4 cross member 378 which engages the lower end of the rod
366. With the rod 366 connected to a connector 380, as
6 will be described, the connector 380 may, in turn, be
7 joined to a rod 382, then to a connector 384 and to a
8 rod 386. The rod 386 may be positioned adjacent to a
9 tailgate sidewall 387 and extend through a transverse
wall 388 extending from the tailgate sidewall and through
1 a passage 390. The passage 390 may extend into a housing
12 392 with a ta~ 393 being formed at the lower end of the
13 rod 386.
14 A rotatable stop mechanism generally indicated
as 394 may be rotatably positioned within the housing 392
16 with the rotational position of the stop mechanism being
17 coordinated with the rotational movement of the pac~ing
18 panel 44 as illustrated in Figures 10-13.
19 The stop mechanism 394 may include a first plate
396 in abutting relation to a second plate 398. To adjust
21 the angular relationship between the first plate 396 and
22 second plate 398, slots 400 may be formed in the second
; 23 plate with bolts 402 extending through the slots and
~- 24 threadably engaging apertures in the first plate. Thus,
when the bolts 402 are tightened, the rotational position
26 of the second plate 398 may be fixed with respect to the
27 rotational position of the first plate 396. A bolt 404
28 ///
29 ///
31
32
-86-
-- llOl
llZ71~8
1 may extend through both the first plate 396 and second plate
2 398 to engage the shaft 106 which supports the undri~en
3 end of the packing panel 44 (see Figure 4).
4 On movement of the control member 356 in the
direction of the arrow B, the shaft 106 rotates in the
6 direction of the arrow denoted D as the packing panel 44
moves in a working direction through the hopper 34 as
8 illustrated in Figures 10-13. However, on movement of the
9 control member 356 in the direction of the arrow C, the
shaft 106 rotates in the direction of the arrow E as the
11 packing panel 44 moves in a return direction to its rest
~2 position shown in Figure 10.
13 On rotation of the shaft 106 in the direction
14 of arrow D, with the control member 356 moved in the
direction of arrow B, a stop member 406 may be rotated
16 into engagement with the tab 393. The stop member 406
17 may include a stop surface 408 which engages the tab 393
18 to exert a force through the connecting members 386, 384,
19 382 and 380 that may exert a rotational force on plate
360 to return the control member 356 to its neutral
21 position. I~hen the stop surface 408 encounters tab 393,
22 the packing panel 44 may be generally positioned adjacent
23 to the pinch point 210 as illustrated in Figure 12. Thus,
2~ through contact of the stop surface 408 with tab 393, the
packing panel 44 may not proceed beyond this point in a
26 working direction unless some action is taken by the opera-
27 tor to move the tab 393 so that the tab does not contact
~8 ///
29
31
32
-87-
'-~ ~ 01
7118
1 the stop surface 408. This may provide an additional
2 factor of safety by insuring that the operator consciously
3 move the tab 393 out of contact with the stop surface
4 408 to have a continuation of the movement of the pack-
lng panel 44 through the hopper 34.
6 To move the tab 393 out of contact with the
7 stop surface 408, the operator may pull downwardly on the
8 handle 376 which may cause movement of the rod 366 in a
9 downward dlrection relative to the tube 358 against the
force of the biasing spring 372. This, in turn, may pro-
11 vide a rotational movement of the rod 382, as will be
12 described, in the direction of the arrow F to rotate the
13 tab 393 out of contact with the stop surface 408. As
1~ the operator pushes the control member 356 in the direction
of arrow B to initiate movement of the packing panel 44
16 in a working direction, the operator may then keep his
17 hand on the handle 376 until the packing panel approaches
18 the pinch point 210 as shown in Figure 12. At this point,
19 the operator may then pull downwardly upon the handle 376
such that the packing panel 44 moves past the pinch point
21 210 in a continuous mo~ement in a working direction thr~ough
22 the hopper 34.
23 During movement of the packing panel 44 in a re-
24 turn direction from its position shown in Figure 13, it is
desirable that the movement of the packing panel not be
26 stopped when the packing panel reaches the general location
27 of the pinch point 210. Thus, a slide surface 410 may be
28
31
32
-88-
~7118
1 formed on the stop member 406 with the slide surface
2 being shaped and positioned to slide over the tab 393
3 during movement of the packing panel in a return direc-
4 tion and to not interrupt the movement of the packing
panel at the pinch point 210.
6 With the packing panel 44 moving in a working
7 direction and the shaft 106 rotating in the direction
8 of the arrow D, when the stop 406 has rotated beyond
9 the tab 393 as described, the rotation of the shaft
may continue until stop member 412 on the first plate
11 396 encounters the tab 393. At this point, the plate
12 360 and control member 356 may be rotated in a direction
13 counter to that shown by arrow B to return the plate
14 and control member to the neutral position indicated in
Figure 19. At this point, the movement of the packing
16 panel 44 may cease. With the packing panel 44 occupying
17 the position shown in Figure 13, the member 356 and
1~ plate 360 may then be moved in the direction indicated
19 by arrow C. This may cause rotation of the shaft 106 in
the direction indicated by arrow E in which the slide
21 surface 410 of stop member 406 rides over the tab 393~ Ro-
22 tational movement of the shaft 106 may, thus, continue in the
23 direc-tion of the arrow E until a stop member 414 on first
2a plate 396 contacts the tab member 393. At this point, the
plate 360 and the control member 356 may be rotated in a di-
26 rection counter to that indicated by the arrow C to return
27 the plate and operating member to their neutral positions
28 shown in Figure 19. At this point, the movement of the pack-
29 ing panel 44 may cease and the packing panel may be posi-
tioned at its rest position shown in Figure 10.
31 ///
3Z ///
-89-
r ~ .
~;Z71~8
1 As described, the angular position of the second
2 plate 398 with respect to first plate 396 may be varied
3 by loosening bolts 402 and 404, rotating the second plate
4 with respect to the first plate, and re-tightening the
bolts. The position of the stop member 406 may, thus, be
6 varied with respect to the positions of the stop members
7 412 and 414. This, in turn, may vary the point at which
8 the stop surface 408 encounters the tab 393 such that the
9 packing panel 44 may be stopped at the pinch point 210 as
shown in Figure 12 or at a point in advance of the plnch
11 point, as desired.
12 Figure l9a is a detailed view taken along the
13 line l9a--19a of Figure 19 to illustrate the construction
14 of the stop member 406 and its function of sliding over
the tab 393, during rotational movement of the stop member
16 in the direction of the arrow E. As indicated, the stop
17 member 406 may include a transverse portion 416 from which
18 may depend the stop surface 408. The slide surface 410,
19 which lies behind the stop surface 408 in Figure l9a may
be inclined upwardly from the stop surface toward a sur-
21 face 409 whose length is less than that of surface 408
22 as indicated by the brackets identifying the surfaces
23 and their length. In usage, the tab 393 does not con-
24 tact the surface 409 due to its decreased length as
the stop member 406 moves in the direction of the
26 arrow E. Rather, the tab 393 then encounters the
27 inclined slide surface 410 with the surface 410 then
28 riding over the tab 393 due to the resiliency of the
29 transverse portion 416. However, when the stop member
///
31 ///
32
-90-
~lZ~il8 D-llOl
1 406 encounters the tab 393 during movement of the packin~
2 panel 44 in a working direction with rotation of the
~ shaft 106 in the direction of the arrow D, the longer stop
4 surface 408 may directly contact the tab 393. As des-
cribed, this may move the control member 356 to its neu-
6 tral position unless the operator has rotated the tab 393
7 out of contact with the stop member 406 by pulling down-
8 wardly on handle 376.
9 Figure 20 is a view taken along the line 20--20
of Figure 19 which further illustrates the functioning of
11 the control mechanism. As indicated, the rod 382 may
12 connect at i.ts upper end through a universal joint 418 to
13 the plate 360. Additionally, the rod 382 may be fixedly
14 connected to an L-shaped bracket 420 which may, in turn,
be connected through a universal joint 422 to the rod 366.
16 Thus, when the rod 366 is pulled downwardly by handle 376,
lq as discussed in regard to Figure 19, the downward movement
18 of the rod 366 may have no effect upon the position of the
19 tube 358 which is fixedly connected to plate 360. The
20 downward movement of the rod 366 does, however, exert a
21 downward force upon the L-shaped bracket 420 whose posi-
~2 tion is angled outwardly away from the plane of the paper
23 as it is shown in Figure 20. The downward force exerted
24 upon L-shaped bracket 420, thus, may exert a turning moment
25 on the rod 382 which may rotate the rod in the direction
26 indicated by arrow F to move the tab 393 out of engagement
27 with the stop member 406. Due to the presence of the
28
29
31
32
--91--
D- l l O l
~127118
1 universal joints 418 and 422, the rotational movement
2 ov the L-shaped bracket 420 and the rod 382 does not
3 disturb the position of the plate 360 and tube 358.
4 Thus, the control handle 356 remains in its position even
though the rod 382 is rotated. The universal joint 418,
6 while permitting rotational movement of the rod 380 with
7 respect to plate 360 does not, however, permit transla-
8 tional movement of the rod 382 with respect to the plate
9 360. Thus, when the tab 393 is engaged by any of the
stops 412, 414, 416 to produce translational movement of
11 the rod 382, this translational movement causes movement
~2 of the plate 360 and tube 358 as described previously.
13 As indicated, in the lower portion of Figure 20,
14 a support bearing 424 may be provided for the shaft 106
with the first and second plates 396 and 398 being secured
16 to the shaft at a mounting location which is positioned
17 outboard from the support bearing. Further, a closure
18 plate 426 may be positioned over the housing 392 with the
19 closure plate being secured to the housing in any conven-
tional manner, such as the use of bolts 428.
21 Figure 21 is a detailed view illustrating the
22 movement of control rods 206 and 207 in transmitting
23 movement from the rotatable rod 362 shown in Figure 19 to
24 valves for controlling the hydraulic mechanism. As indi-
cated, the rotatable rod 362 may extend from the right
26 rear side of the tailgate 10 where the control mechanism
27 may be located to the left rear side of the tailgate where
2~ the drive mechanism may be located (see Figure 14).
29
31
32
-92-
O 1
l~Z71~8
1 At the terminus of the rotatable rod 362 at the
2 left rear side of the tailgate 10, the rod may be supported
3 by a bearing plate 430 secured to a support plate 432. A
4 partial closure 434 may extend about the rotatable rod 362
as it crosses the back of the tailgate 10 to protect the
6 rod. An eccentric 436 may be secured to the rotatable
7 rod 362 at a position which is inboard from the bearing
8 plate 430. The control rods 206 and 207 may be connected
9 to a pin 442 joined to the eccentric 436 such that rota-
tional movement of the rod 362 in the direction indicated
11 by arrow G may cause simultaneous movement of the control
12 rods in the direction indicated by arrow H. The control
13 rod 207 may be connected to a valve actuation member 444
14 while the control rod 206 is connected to a valve actuation
member 446. As will be described, a detent mechanism 448
16 may be positioned adjacent to the valve actuation member
17 446 to hold the valve actuation member in a desired posi-
18 tion after movement of the rod 206.
19 Figure 21a is a sectional view taken along the
2.0 lines 21a--21a of Figure 21 to demonstrate the manner in
21 which the rods 206 and 207 may be connected to the eccen-
22 tric 436. The rod 206 may include a slot 450 formed at
23 its outer end with the rod 207 including a slot 452 formed
2~ at its outer end. With rotation of the rod 362 in the
direction of arrow G as shown in Figure 21, the pin 442
26 may move to the right hand ends of the two slots 450 and
27 452. This contact may, then, move both the rods 206 and
28 207 in the direction of arrow H as shown in Figure 20.
29 ///
31
32
-93-
D-llOl
Z7118
1 As will be described, rod 207 may be used to
2 actuate the movement of the retainer panel 54 from a
3 closed to an opened position (see Figures 10 and 11) or to
4 actuate movement of the retainer panel from its opened
to its closed position. As described previously with
6 regard to Figures 10-13, movement of the retainer panel
7 54 may precede the movement of the packing panel 44. For
8 example, the retainer panel 54 may move from a closed to
9 an opened position before movement of the packing panel
44 in a working direction through the hopper 34 (see
11 Figures 10 and 11~. Similarly, the movement of the re-
12 tainer panel 5a from an opened to a closed position may
13 precede the movement of the packing panel 44 from its
14 position shown in Figure 13 in a return direction to its
rest position shown in Figure 10. To provide this result,
16 a spring centered valve may be used for providing move-
17 ment of the retainer panel 54 which valve may be actuated
18 by movement of the rod 207. The spring centered valve
19 may be biased to a neutral position in which no hydraulic
fluid flows to the retainer panel cylinder 55 (see Figure 9).
21 On movement of the pin 442 to the right from its position
22 shown in Figure 21a, the rod 207 may be held in position
23 by the operator with control member 356 held in the direc-
24 tion of arrow B until the retainer panel 54 (see Figures
2~ 10-13) has completed its movement from a closed to an
26 opened position. At this point, the operator may then re-
27 turn the control member 356 to its neutral position shown
28 ///
2g /// ...
31
32
-94-
D- 1 1 0 1
`" 1~27118
1 in Figure 19 which may cause the pin 442 to occupy the
2 position shown in Figure 21b.
3 The spring centered valve may then automatically
return the rod 207 to its centered position shown in
Figure 21b. Elowever, the rod 206 may remain held in the
6 direction of the arrow H shown in Figure 21 by the detent
7 mechanism 448. The rod 206 rnay, thus, occupy the posi-
8 tion shown in Figure 21b with the pin 442 positioned
9 closely adjacent to the left end of the slot 450. With
reference to Figure 19, the rod 206 may continue to
11 occupy the position as shown in Figure 21b until the tab
~2 393 is contacted by the stop member 406 or 412 to move
13 the pin 442 slightly to the left from its position shown
14 in Figure 21b and into contact with the left end of slot
450. At this point, the rod 206 may become disengaged
16 from the detent mechanism 448 with a biasing spring of
17 the valve returning the rod 206 to its neutral position.
18 At this point, both the rods 206 and 207 may occupy the
19 positions shown in Figure 21a in which the pin 442 is
centered within slots 450 and 452.
21 Again, referring to Figure 19, when the con-
22 trol member 356 is moved in the direction of arrow C,
23 the rod 362 shown in Figure 21 may be rotated in a
24 direction opposite to that indicated by arrow G. This
may cause the pin 442 to move to the left from its
26 position shown in Figure 21a into contact with the left
27 ends of the slots 450 and 452. As a result, the rods
28 ///
29 ///
31
32
-95-
---' `1101
l~Z71~8
1 206 and 207 may then be moved in a direction opposite
2 to that indicated by arrow H in Figure 21. The con-
3 trol member 356 shown in Figure 19 may then be held ln
4 the direction of arrow C until the retainer panel 54
has completed its movement from an opened to a closed
6 position (see Figure 1) with the control member then being
7 returned to its neutral position and with the rod 207 re-
8 turning to its neutral position to occupy the position
9 shown in Figure 21b. However, the rod 206 may remain in a
~ held position opposite to that indicated by the arrow H in
11 Figure 21 under the influence of the detent mechanism 448
12 with the right end of the slot 450 as shown in Figure 21b
13 being positioned closely adjacent to the pin 442. The rod
14 206 may remain held in this position by the detent mechanism
448 until the tab 393 (see Figure 19) is contacted by the
16 stop member 414 as the shaft 106 rotates in the direction
17 Of the arrow E. At this point, the pin 442 (see Figure
18 21b) may be moved slightly to the right into contact
19 with the right end of slot 450. This may disengage the
detent mechanism 448 from the rod 206 such that the rod
21 returns to its neutral position with rods 206 and 207
22 and pin 442 occupying the position shown in Figure 21a.
23 Figure 21c is a detailed side elevation view,
24 partly in section, taken along line 21c--21c as shown
in Figure 21 to indicate the ~unctioning o~ the detent
26 mechanism 448 in holding the rod 206. As indicated, the
27 detent mechanism 448 may include a base member 454 with
28
29
31
32
-96-
1101
~Z7118
1 a rotatable arm 456 mounted thereon through a pivot 458
2 and an arm support member 460 that supports the pivot
3 for engagement with the rotatable arm. The arm 456 may
4 be biased in any convenient manner, such as by a spring,
for rotation in a clockwise direction from its position
6 shown in Figure 21c with a roller 462 at the outer end
7 of the arm being forced into contact with the rod 206.
8 Notches 464 may be formed in the rod 206 with the posi-
9 tion of the notches corresponding to the position of the
rod when it is moved in the direction of the arrow H
11 shown in Figure 21 to actuate the packing panel 44 in a
~2 working direction (see Figures 10-13), or when the rod
13 206 is moved in a direction opposite that of arrow H to
14 actuate movement of the packing panel in a return
direction.
16 As indicated, when the roller 462 engages one
17 of the notches 464, the upward force of the roller against
18 the notch may hold the rod 206 in a given position. A
19 valve 466, which may be actuated by movement of the rod
206, may be a spring-centered valve. Thus, when either
21 the right or left end of the slot 450 in rod 206 is con-
22 tacted by the pin 442 (see Figure 21b) the rod may under-
23 go sufficient movement to disengage the roller 462 from
24 one of the notches 464. At this point, the spring-cen-
tering action of valve 466 may return the rod 206 to its
26 neutral position as indicated in Figure 21a with the
27 valve 466 then being in a neutral position such that the
28 movement of the packing panel 44 ceases (see Figures 10-13).
29 ///
///
31
32
-97-
llZ71~8
l Figure 22 is a schematic representation of a
2 hydraulic circuit which may be used in actuating the
3 present apparatus. As indicated, hydraulic fluid from
4 the reservoir 348 may be transported through a supply
line 468 and a valve 470 to a pump 472. From the pump
6 472 the hydraulic fluid may be supplied under pressure
7 through a line 474 which is joined to a branch line 476.
8 Branch line 476 leads to a pilot-operated relief valve 478
9 that may be conveniently set at a pressure such as 2950 psi
psi. When the pressure in the line 474 and the branch
ll line 476 reaches the predetermined pressure, the pressure
l2 transmitted through a pressure line 479 may cause the
13 valve 478 to open to permit fluid to pass through the
14 valve to a return line 511 leading to the reservoir 348.
In permitting fluid to pass through the valve 478 at a
16 predetermined pressure of about 2950 psi, the
17 relief valve 478 acts as a safety valve for the entire
18 hydraulic system to insure that pressures within the
l9 system do not exceed the predetermined pressure level.
The line 474, after passing the branch line
21 476, leads to a branch line 480 and to a spring-centered
22 valve 482. With the spring-centered valve 482 in its
23 neutral position as shown in Figure 22, hydraulic fluid
24 in line 474 may flow through the valve. The valve 482
may include a control handle 484 through which the
26 valve may be moved to a raised or a lowered position from
27 its neutral position shown in Figure 22. On movement
28 ///
29 ///
31
3~
-98-
~ D-1101
27~8
1 of the handle 484 to move the valve upwardly ~rom its
2 posit:ion shown in Figure 22, hydraulic fluid from line
3 474 may flow through a check valve 486 and through the
valve 482 to a line 488. The line 488 may lead to a
branch line 490 which leads to a pilot-operated relief
6 valve 492. The relief valve 492 may be set to open
7 at a predetermined pressure of about 3100 psi which
8 may be transmitted through a pressure line 493 to open
9 the relief valve such that hydraulic fluid from line
490 may flow to return line 511 and to the reservoir
11 348. The relief valve 492 which may be set at a pressure
12 less than the opening pressure for relief valve 478
13 may, thus, function to permit the release of hydraulic
14 fluid from line 490 when the telescopic ejection cylinder
14 encounters an undesirable pressure buildup during,
16 for example, movement of the ejection panel 12 from the
17 front to the rear of the storage body 8 during the
18 ejection of refuse from the storage body (see Figure 1).
19 The line 488, after passing the branch line
490, may lead to two lines 494 and 496. Line 494 may
21 lead to a solenoid valve 495 which, when actuated, as will
22 be described, will permit hydraulic fluid -to flow to a
23 return line 497 and to the reservoir 348. The line 496
24 may lead to the large end of the telescopic hydraulic
cylinder 14 which may have, for example, a pressure area
26 in the order c ten times the pressure area at the small
27 end of the telescopic cylinder. A line 498 may lead from
28
29
31
~2
_99_
~ D-1101
l~Z7~18
1 the small end of the telscopic cylinder 14 to a line
2 512 directed to the valve 482. With valve 4a2 in its
3 raised position, hydraulic fluid may, thus, flow
4 through the valve to lines 488 and 496 to expand the
telescopic cylinder 14 while fluid from the small end
6 of the telescopic cylinder may flow through lines 498
7 and 512 through the valve to a line 514 to return line
8 511 and to the sump 348. A strainer 515 may be posi-
9 tioned between the return line 511 and the reservoir .
0 348 to remove particles from the hydraulic fluid to
11 prevent clogging of the valves in the hydraulic system
~2 by the particles.
13 When the handle 484 is actuated to move the
14 valve 482 in a downward direction from that shown in
Figure 22, pressurized hydraulic fluid may flow through
16 the check valve 486 and the valve 482 into the lines 512
7 and 498. This may introduce pressurized hydraulic fluid
18 into the small end of the telescopic cylinder 14 with
~19 fluid from the large end of the cylinder being returned
through lines 496 and 498 to the valve 482. The returned
21 fluid rom the large end of telescopic cylinder 14 may
22 then be conveyed through through the valve 482 to line
23 514 to the return line 511 and the sump 348. As this
24 occurs, the telescopic cylinder may undergo contraction
to move the ejection panel. 12 from the rear to the front
2~ of the storage body 8 (see Figure 1).
27
28
29
31
32
--1 00--
-~ "~-1101
~lZ7118
1 When valve 482 is in its neutral position as
2 shown in Figure 22 with the telescopic cylinder 14 being
3 filled with hydraulic fluid, a problem may arise if there
4 is, for example, an increase in the ambient temperature.
Due to the substantial difference between the pressure
6 area at the large end of the telescopic cylinder 14 as
7 compared with the pressure area at the small end of the
8 cylinder, a pressure increase at the large end due to
9 thermal expansion of fluid at the large end may produce
0 a tenfold pressure increase at the small end of the tele-
11 scopic cylinder. To protect against undesirable pressure
12 buildup at the small end of telescopic cylinder 14, the
13 line 498 from the small end of the cylinder may lead to a
14 branch line 500 leading to two lines 502 and 504. A
check valve 506 may be positioned in line 502 to prevent
16 the flow of hydraulic fluid from line 502 to a line 510 and
17 to the return line 511.
18 However, line 504 may lead to a pilot-operated
19 relief valve 508 which may be set to open at a pressure
of about 3100 psi. When the pressure in line 504
~1 reaches this pressure level, pressure ~ay be transmitted
22 to the valve 508 through a pressure line 509 to open the
23 relief valve such that fluid may flow to line 510 to the
24 return line 511 and to the reservoir 348.
After passing the valve 482, the line 474 may
26 lead to a spring-centered valve 516 which may be used to
27 actuate the tailgate lifting cylinder 26. With valve 516
28 ///
29 ///
31
32
-101-
- 1)-11()1
~2~71~8
1 in its neutral position as shown in Figure 22, hydraulic
2 fluid may flow directly through the valve. A handle 518
3 connected to the valve 516 may be used in moving the
4 valve to a raised or a lowered positlon from that shown
in Figure 22. When valve 516 is moved to a lowered
6 position, hydraulic fluid may flow from line 480 through
7 a check valve 520 and through the valve 516 to a line 522.
8 The line 522 may lead to a hydraulic choke 524 with
9 hydraulic fluid expanding the cylinder 26 during movement
of the tailgate 10 to its raised potiion shown in
11 Figure 1. When the cylinder 26 is expanded to a desired
12 extent, the valve 516 may be moved to its neutral posi-
13 tion shown in Figure 22 to isolate the cylinder 26 and
14 to insure that the cylinder remains in its expanded con-
dition.
16 When it is then desired to lower the tailgate 10
17 (see Figure 1), the valve 516 may be moved to its raised
18 position from that shown in Figure 22. At this point,
19 the weight of the tailgate structure 10 may be exerted
against the fluid within the cylinder 26 through a piston
21 rod 525. The weight of the tailgate 10 may, thus, force
22 a piston 527 downwardly within the cy].inder 26 with ~luid
23 flowing from the cylinder through choke 524, line 522 and
24 the valve 516. After flowing through valve 516, the fluid
may be conveyed through a line 526 to the return line 511
26 and to the sump 348. The choke 524 may function to re-
27 duce the flow rate of hydraulic fluid through line 522
28
29
31
32
-102-
.
D_ 1101
:1127118
1 to a relatively low flow rate. This may insure that the
2 tailgate descends slowly in moving from its raised posi-
3 tion 10' to its lowered position 10 as shown in Figure 1.
4 After passing beyond the valve 516, the line 474
may reach two branch lines 528 and 530. The branch line
6 530 may lead to a pilot-operated relief valve 532 having
7 a pressure line 533 connected to the line 474. When the
8 pressure within line 474 reaches a predetermined value of
9 about 3100 psi, the pressure transmitted through line
533 may open the valve 532 to permit pressurized fluid
11 to flow through the valve to a return line 546 which
12 leads to line 511 and to the reservoir 348. The relief
13 valve 532 may, thus, control the pressure of hydraulic
14 fluid which is fed to the cylinder 55 for actuation of
the retainer panel 54 and which is fed to the cylinders
16 52 and 50 for actuation of the packing panel 44 as il-
17 lustrated in Figures 10-13.
18 As described in Figures 21, 21a, 21b and 21c,
19 the control rods 206 and 207 may be moved together in
unison. With the rods 206 and 207 moved together in
21 unison in the direction of arrow H as shown in Figure 21,
22 a spring-centered valve 538 may be moved upwardly from
23 its neutral position as shown in Figure 22 and the spring-
24 centered valve 466 may also be moved upwardly. Hydraulic
fluid may then flow from the line 474 through a line 528
26 to a line 534 and through a check valve 536. After
27 flowing through check valve 536, pressurized hydraulic
28
29
31
32
-103-
~ D-llOl
~ l~Z7118
1 fluid may then flow through the valve 538 and through a
2 line 540 to the cylinder 55. This may cause the cylinder
3 55 to contract with fluid from the head end of the
cylinder flowing through a line 542, through valve 538
and through a line 544 to the return line 546.
6 Since the volume of the hudraulic cylinder 55
7 may be relatively small, the contraction of the cylinder
8 may be relatively rapid to provide rapid movement of
9 the retainer panel 54 from its closed position shown in
Figure 10 to its opened positioIl shown in Figure 11. At
11 this point, the control handle 356, after first being
12 moved in the direction of arrow B, may be moved in a
13 direction opposite that of arrow B to its neutral posi-
14 tion as shown in Figure 19. This may permit the spring-
centered valve 538 to return to its neutral position to
16 cause the rod 207 to return to its neutral position shown
17 in Figure 21b with the pin 442 centered within the slot
18 452 in rod 207. The rod 206 may, however, remain in the
19 direction of arrow H through the action of the detent
mechanism 448 as described in Figures 21b and 21c. With
2~ the valve 538 returned to its neutral position, and the
22 valve 466 in its raised position from that shown in
23 Figure 22, hydraulic fluid may flow from line 474 through
2~ the valve 538 and to a branch line 545, through a check
valve 548 and the valve 466 and to a line 550. Line 550
26 may lead to a line 552 to the rod end of the relatively
2~ large drive cylinder 50 which may be used in moving the
28 ///
29 ///
~1
32
-104-
r~ 0 1
~.Z`~1~8
1 packing panel 44 in a working direction, as described in
2 Figures 10-13.
3 On the introductlon of pressurized hydraulic
4 fluid into cylinder 50 through line 552, a piston 554
may be moved upwardly from its position shown in Figure
6 22 to contract the cylinder in moving the packing panel
7 44 in a working direction as described in Figures 10-13.
8 As described in regard to Figure 3, the relatively large
9 hydraulic drive cylinder 50 may be mechanically coupled
with the relatively small hydraulic return cylinder 52.
~1 Thus, as the piston 554 of cylinder 50 is moved moved
12 upwardly to contract the cylinder 50, a piston 555 of
13 return cylinder 52 may be moved downwardly to expand the
14 return cylinder. On downward movement of piston 555,
hydraulic fluid within the rod end of cylinder 52 may be
16 exhausted through a line 574 and through the valve 466
17 to a line 557 to line 546 and to line 511 and reservoir
18 348.
19 As hydraulic fluid is fed to the rod end of the
drive cylinder 50, through line 552, a pilot-operated
j 21 check valve 562 may prevent the flow of hydraulic fluid
22 from the line 550 past the check valve. A line 560 con-
23 nected to the head end of the drive cylinder 50 may lead
24 to the head end of the return cylinder 52. Thus, as the
piston 554 is moved upwardly with the piston 555 moving
26 downwardly, hydraulic fluid which is exhausted from the
27 head end of drive cylinder 50 may pass through the line
28 ///
29 ///
31
32
~105-
- D-llOl
~1271~8
1 560 into the head end of the return cylinder 52. In
2 this manner, the return cylinder 52 may act as an accumu-
3 lator of the hydraulic fluid which is discharged from
the head end of cylinder 50. Additionally, a line 561
may interconnect line 560 with the return line 511 to
6 the reservoir 348. Hydraulic fluid which is discharged
7 from the head end of the cylinder 50 may, thus, also
8 flow from line 560 into line 561 and to the return line
9 511. However, to encourage flow of hydraulic fluid be-
tween the cylinders 50 and 52, the line 560 may be re-
11 latively large to offer less resistance to flow than the
12 line 561.
13 As the piston 554 is moved upwardly within drive
14 cylinder 50, a pressure port 559 in the wall of the
cylinder 50 may be uncovered to receive pressure from
16 fluid on the underside of piston 554. The port 559 may,
17 for example, be uncovered when the packinq panel 44 moves
18 beyond the pinch point 210 during its movement in a work-
19 ing direction as illustrated in Figures 12 and 13. As the
2.0 packing panel 44 passes beyond the pinch point 210, greater
21 resistance may be encountered by the panel from refuse
22 within the hopper 34 which may result in higher pressures
23 at the rod end of the drive cylinder S0. As also dis-
24 cussed in regard to Figures 10-13, during movement of the
packing panel 44 in a working direction through the hop-
26 per 34, refuse within the hopper is subjected to high
27 pressures as the refuse passes through the narrowed throat
28 ///
29 ///
31
32
-106-
,, ___._._ _ .. , . . _ .. -- .. , . .. . .. .,_
D-llOl
~127~18
1 204 in passage 42 leading to the storage body 8. Thus,
.,
2 the pressure of refuse within the storage body 8 which
3 is exerted against the ejection panel 12 may be of a
4 relatively low magnitude even though high pressures are
experienced by the refuse within the narrowed throat
6 204 and high pressure hydraulic fluid is supplied through
7 line 552 to the rod end of the cylinder 50.
8 Since the pressure of refuse within the storage
- ~ 9 body 8 exerted against the ejection panel 12 may be re-
latively low, in comparison to previous refuse compacting
11 apparatus, the pressure which is experienced at the large
~2 end of the telescopic cylinder 14 by refuse bearing
13 against the ejection panel may also be relatively low. If
14 the means for dumping hy.draulic fluid from the large end
of the cylinder 14 were a purely hydraulic mechanism, the
16 speed of actuation of the mechanism might not be suffi-
17 ciently rapid. To provide a more rapid and more controlled
18 dumping of hydraulic fluid from the large end of the tele-
19 scopic cylinder 14 when the ejection panel 12 moves in
small incremental steps from its rearward position 12 to
21 its forward position 12' (see Figure 1), an electr.ical
22 system may be used to control the dumping of hydraulic
23 fluid from the telescopic cylinder 14. The pressure port
24 559 in the drive cylinder 50, as described, may lead to
a pressure sensing line 556 to a pressure actuated switch
.. 26 558. The switch 558 is opened in its position shown in
27 Figure 22. However, when the pressure at the rod end of
28
29
31
32
-107-
.. . _ . .........
- l:lZ'~118 llol
1 drive cylinder 50 reaches a predetermined level, such as
2 240() psi, a switch member 563 may be moved downwardly
3 by the pressure in line 556 into contact with a pole 565 to
4 complete a circuit between an electrical power source 566 and
the solenoid valve 495 through wires 568, 570 and 572.
6 With the switch 558 closed, the solenoid valve
q 495 may, therefore, be actuated to quickly dump fluid from
8 the large end of telescopic cylinder 14 through line 494 -
9 to line 497 and to the reservoir 348. This permits move-
ment of the ejection panel through a small incremental
11 distance as described in regard to Figure 1 to reduce the
12 pressure of refuse against the packing panel 44 and, in
13 turn, to reduce the hydraulic pressures at the rod end of
14 the drive cylinder 50. When the pressure of hydraulic
fluid at the rod end of the cylinder 50 then drops to a
16 predetermined level such as 2150 psi, the switch 558
17 may return to an opened position as shown in Figure 22
18 to return the solenoid valve 495 to its closed position.
19 The packing of refuse may then continue until the pres-
sure at the rod end of the cylinder 50 again reaches the
21 predetermined leveI required to close switch 558 and the
22 whole operation may be completed a~ain, etc., to move
23 the ejection panel 12 in small incremental steps from
24 its rearward position 12 to its forward position 12'
(see Figure 1) as the storage body 8 is progressively
26 filled with refuse.
27 ///
28 ///
29
31
32
-108-
D-llOl
`71J.8
1 When the packing panel 44 has completed its
2 movement in a working direction as shown in Figure 13,
3 the rod 206 may then be returned to a neutral position
4 by contact of the pin 442 with the end of the slot 450
in the rod 206 as described in regard to Figures 21, 21a,
6 21b and 21c. This may, then, overcome the detent
7 mechanism 448 such that the spring-centered valve 466 may
8 be returned to its neutral position shown in Figure 22.
9 With the packing panel positioned as shown in
Figure 13, the rods 206 and 207 may then be moved down-
11 wardly from their positions shown in Figure 22 to actuate
~2 movement of the panel 44 in a return direction to its
13 rest position shown in Figure 10. The simultaneous move-
14 ment of the rods 206 and 207 may move the valves 538 and
466 to.their lowered positions from that shown in Figure
16 22 with hydraulic fluid passing from line 534 through
17 check valve 536 and valve 538 into line 542 to the head
18 end of the retainer panel cylinder 55. This may cause
19 the retainer panel cylinder 55 to expand with hydraulic
fluid exhausted from the rod end of the retainer panel
21 cylinder passing through line 540, valve 538 and into
22 line 544 to the reservoir 348. With the volume of the
23 retainer cylinder 55 ~eing relatively small, the expan-
24 sion of the retainer cylinder to return the retainer
panel 54 to its closed position shown in Figure 10 may
26 occur relatively quickly.
27
28
29
31
32
- 1 0 9 -
... . . , ,., ..... =~, ~ ,~
~ D-llOl
7il8
1 The control member 356 (see Figure 19) may
2 then be returned to its neutral position by moving
3 the control member in a direction opposite to that in-
4 dicated by arrow C. This may permit the spring-centered
valve 538 and the control rod 207 to return to their
6 neutral positions as deseribed in Figures 21, 21a, 21b
q and 21c with the rod 206 being retained in a direction op-
8 posite that of arrow H through the detent mechanism 448.
9 Hydraulic fluid may then pass through valve 538 in its neu-
tral position to ~ine 545, through check valve 548, and
11 valve 466 into line 574 to the rod end of the relatively
12 small return cylinder 52. As described previously,
13 cylinders 52 and 50 may be mechanically interconnected.
14 Thus, as cylinder 52 is contracted, the relatively large
drive cylinder 50 may be expanded. Hydraulic fluid
16 which is exhausted from the rod end of the cylinder 50
lq during its expansion may be conducted through lines 552
18 and 550 to valve 466 and into line 557 to the reservoir
19 34~. However, due to the relatively large volume of
hydraulic fluid whieh may be contained at the rod end of
21 eylinder 50, the resistance to fluid flow eneountered by
22 the fluid within lines 552, 550, ete., may oppose the
23 expansion of hydraulie eylinder 50. This may inerease
24 the resistanee to eontraetion of the return eylinder 52
which may inerease the pressure of hydraulie fluid fed
26 to the rod end of the return eylinder through line 574.
27 ///
28
29
31
32
--110-
1~27118 ~ ol
1 A pilot line 564 leading from line 574 to the
2 pilot-operated check valve 562 may transmit pressure to
3 the check valve which may be set to open at a relatively
4 low pressure of about 500 psi. On opening of the
check valve 562, fluid which is exhausted from the rod
6 end of cylinder 50 may then flow from line 552 through
7 the check valve 562 into the line 560 for return to the
8 head end of cylinder 50. In this manner, the relatively
9 large drive cylinder 50 may act as its own accumulator
during expansion of the cylinder. Hydraulic fluid which
11 is exhausted from the head end of the return cylinder
12 52 during its contraction may also flow through the line
13 560 into the head end of the drive cylinder 50 with the
14 drive cylinder, therefore, also acting as an accumulator
for the return cylinder 52. Additionally, hydraulic
16 fluid may flow through line 561 into the return line 511
17 to the reservoir 348. However, as stated, the size af
18 line 560 may be larger than that of line 561 to encourage
19 the flow of hydraulic fluid between the cylinders 52 and
50 thxough the line 560.
21 Figure 23 illustrates an alternative hydraulic
22 circuit which may be used in controlling the present
23 apparatus. While the hydraulic circuit of Figure 23 is
24 similar to that of Figure 22, it also differs in a number
of important respects. As indicated, a reservoir 576 may
26 supply hydraulic fluid through a supply line 578 to a
27 valve 580 and then to a pump 582. Leading from the pump
28 ///
29 ///
31
~2
J-l lol
llZ~118
1 582 is a line 584 which is joined to an auY.iliary line
2 586, may be used for operating conventional auxiliary
3 equipment. The supply line 584 may then lead to a
4 branch line 588 joined to a pressure-operated pilot
valve 590. The valve 590 may be set to open at a given
6 pressure level such as 2950 psi and a pressure
7 line 591 may be used to transmit pressure from the line
8 588 to open the valve when the predetermined pressure
9 level is reached. Valve 590 may, thereby, function as
a safety valve for the entire hydraulic system with the
11 pressure for opening the valve being the maximum system
12 pressure.
13 After passing branch line 588, the line 584 may
~4 then lead to a spring-centered valve 592 which may be
operated by movement of a handle 594. With the valve
16 592 in its neutral position, as shown in Figure 23,
17 hydraulic fluid may flow through the valve. However,
18 when valve 592 is moved to a raised position from that
19 shown in Figure 22, pressurized fluid may then flow
through a line 596, a check valve 598, and then through
21 valve 592 into a line 600. The line 600 may lead to
22 a branch line 602 which is directed to a solenoid valve
23 606 and also to a line 604 which is directed to the large
2~ area end of the telescopic hydraulic cylinder 14 as shown
in Figure 1. With pressurized hydraulic fluid being fed
26 through line 604 to the large area end of telescopic
27 cylinder 14 the telescopic cylinder may be expanded to
28
29
31
32
-112-
D- 1 1 0 1
~lZ~i~
1 provide movement of the ejection panel l2. Hydraulic
2 fluid which may be exhausted from the small area end of
3 the telescopic cylinder 14 may flow through a line 608
4 to a line 618 and through the valve 592 to a return
line 620. The line 620 may lead to a return line 622
6 which may, in turn, lead to a line 616 through a check
~ valve 617 and strainer 619 and into the reservoir 576.
8 When the valve 592 is moved to its lowered
9 position from that shown in Figure 23, hydraulic fluid
may flow from line 596 through check valve 598 and
11 valve 592 into lines 618 and 608 to the small area end
12 of telescopic cylinder 14. This may produce contrac-
13 tion of the telescopic cylinder 14 with hydraulic fluid
14 being exhausted from the large area end of the telescopic
cylinder through lines 604 and 600, valve 592 and into
16 line 620 to return line 622.
17 When valve 592 is in its neutral position
18 shown in Figure 23, the telescopic cylinder 14 is iso-
19 lated from line 584 and pressure buildup may occur at
the small area end of the telescopic cylinder because
21 Of an increase in the ambient temperature. If a pres-
22 sure buildup occurs in the large area end of the cylinder
23 14, this may, for example, cause a tenfold pressure
2~ buildup in the small area end of the cylinder because of
the area ratio between the pressure area at the large area
26 end and the pressure area at the small area end. To
27 relieve such a pressure buildup, a branch line 610 from
- 29
31
32
-113-
D-llOl
1 line 608 may lead to the pilot-operated valve 612 with a
2 pressure transmitting line 613 from line 610 to the valve
3 to control its operation. The valve 612 may be set, for
4 example, to open at a pressure of about 3100 psi to
permit the exhaust of hydraulic fluid from line 610
6 through the valve and into a line 614 which leads to
7 return line 616.
8 . After passing beyond valve 592 in its neutral
9 position, the supply line 584 may lead to a spring-cen-
tered valve 624 which is shown in its neutral position
11 in Figure 23. The valve 624 may include an operating -
12 handle 626 which may be actuated to move the valve to
13 its lowered position from that shown. With the valve
14 624 in its lowered position, pressurized hydraulic fluid
may then pass from line 584 to line 628, through a check
16 valve 630, and valve 624 and into a line 632. The line
17 632 may lead through a pressure choke 634 to the hydrau-
18 lic cylinder 26 which may be used for lifting of the
19 tailgate 10 as illustrated in Figure 1.
2,0 As hydraulic fluid is fed through line 632 to
21 the head end of the cylinder 26, the cylinder may be
22 expanded to raise the tailgate to its position 10' shown
23 in Figure 1. The valve 624 may then be returned to its
24 neutral position to isolate the cylinder 26 and insure
that the tailgate remains in its raised position 10'.
26 When it is desired to lower the tailgate to its position
27 10 shown in Figure 1, the valve 624 may then be moved
28
29
31
32
-114-
D-ll 01
~Z7~B
1 to its raised position from that shown in Figure 23 with
2 hydraulic fluid passing from the cylinder 26 through the
3 choke 634, the line 632 and valve 624 and into a return
4 line 636. As described in regard to Figure 22, the
weight of the tailgate 10 (Figure 1) may be used to advan-
6 tage in contracting the hydraulic cylinder 26 during
7 lowering of the tailgate. Since the weight of the tail-
8 gate 10 may be borne by the cylinder 26, the weight of the
9 tailgate may force fluid from the head end of the cylinder
when the valve 624 is in its raised condition. However, be-
11 cause of the presence of the hydraulic choke 634, fluid flow
~2 through the line 632 may be maintained at a relatively slow
13 rate to insure that the tailgate is not lowered too rapidly.
14 Proceeding beyond valve 624 in its neutral
position, the supply line 584 may lead to a branch line
16 638 to a pilot-operated valve 640 controlled through a
17 pressure line 641. The pilot-operated valve 640 may be
18 set to open at a pressure of about 3100 psi to permit
19 exhaust of hydraulic fluid through the valve to a line
20~ 642 leading to return line 616 to the reservoir 576.
21 'rhe pilot-operated valve 640 may, thus, be set to deter-
22 mine the maximum pressure of hydraulic fluid which is
23 supplied to the retainer panel cylinder 55, the return
2~ cylinder S2 and the drive cylinder 50 during movement
of the packing panel 44 as illustrated in Figures 10-13.
26 The supply line 584 may then lead to a spring-
27 centered detent valve 648 which may control the flow of
28
29
31
32
-115-
` ~ ~ D- )1
1 hydraulic fluid to cylinders 55, 52 and 50. In this re-
2 spect, valve 648 may perform the functions of both the
3 valves 538 and 466, as discussed in Figure 22. The use
4 of a single spring-centered detent valve 648 in the
circuit of Figure 23, thus, represents an improvement
6 over the hydraulic circuit of Figure 22. With valve 648
7 in its neutral position shown in Figure 23, hydraulic
8 fluid may flow through the valve from line 584 to line
9 616. However, when valve 648 is moved to its raised
position from that shown, hydraulic fluid may flow from
11 line 584 through a line 644 and a check valve 646. Valve
12 648 may be moved to its raised position by an operating
13 rod 650 with the rod being held in a raised position by
14 a detent mechanism 651 which is-similar in its operation
to the detent mechanism 448 described in Figures 21 and
16 21c and Figure 22. That is to say, notches may be formed
17 in operating rod 650 which may be engaged by a roller
18 positioned on a spring biased arm to maintain the opera-
19 ting rod in a desired position with the valve 648 in a
raised or a lowered position as compared with its neutral
21 position shown in Figure 22.
22 With valve 648 in its raised position from that
23 shown in Figure 23, pressurized hydraulic fluid passing
24 through check valve 646 may pass through valve 648 into
a line 652. A branch line 654 leading from line 652 may
26 lead to the rod end of the retainer panel cylinder 55.
27 Thus, flow of hydraulic fluid throu~h line 654 may cause
29
31
32
-116-
.. ~ - .
0 1
7~
1 the c.ylinder 55 to contract to move the retainer panel 54
2 from a closed to an opened position as illustrated in
3 Figures 10 and 11. As this is occurring, hydraulic fluid
4 may be exhausted from the head end of cylinder 55 to a
line 696 which leads to a line 686, through the valve
6 648 and to a line 687. Line 687 is joined to return
7 line 642 which conveys the hydraulic fluid to line 616
8 and to reservoir 576. Since the hydraulic cylinder 55
9 may be relatively small in comparison with the relatively
large drive cylinder 50, the contraction of cylinder 55
11 may occur prior to contraction of the drive cylinder.
12 Pressurized hydraulic fluid flowing through
13 line 652 with valve 648 .in its raised position may flow
14 into a line 656, through a check valve 658 and into a
line 660 leading to the rod end of drive cylinder 50.
16 This may cause the cylinder 50 to contract in moving
17 the packing panel 44 in a working direction as described
18 in Figures 10-13. When the packing panel 44 reaches the
19 approximate position shown in Figure 12, a piston 662
within cylinder 50 may uncover a port 663 leading to a
21 pressure line 674 to a p~essure-actuated switch 676. The
22 switch is in its open position as shown in Figure 23.
23 However, when the pressure at the rod end of cylinder 50
24 reaches a predetermined level such as 2400 psi, a
switch member 677 may be rotated downwardly into contact
26 with a pole 679 to close the switch 676 with the switch re-
27 maining closed until the pressure at the rod end falls to
28 a pressure level such as 2150 psi. The switch 676
29 may be connected through an electrical power source 678
///
31 ///
32
-117-
'- 1lO1
~Z7118
1 with the solenoid valve 606 through wires 680, 682 and
2 684. The functioning of the switch 676 in conjunction
3 with the solenoid 606 is the same as described for
4 switch 558 in conjunction with solenoid 495 in regard
to Figure 22. That is, closing of the switch 676 may
6 close the solenoid valve 606 to provide rapid dumping
7 of hydraulic fluid from the large area end of rapid
8 telescopic cylinder 14 in response to pressures at the
9 rod end of drive cylinder 50. This rapid dumping of
hydraulic fluid permits controlled incremental movement
11 of the ejection panel from its rearward position 12 to
12 its forward position 12' as indicated in Figure 1 during
13 filling of the storage body 8 with refuse.
14 As described, the relatively large drive cylinder
50 may be mechanically interconnected with the relatively
16 small return cylinder 52. As the drive cylinder 50 under-
17 goes contraction, the return cylinder 52 may, thus, under-
18 go expansion with hydraulic fluid from the rod end of
19 return cylinder 52 being exhausted through a line 694, a
2.0 check valve 688 and into the line 686. The fluid flow
21 from line 686 may pass through the valve 648 in its raised
22 position and through the line 687 to return lines 642 and
23 616 leading to the reservoir 576. A line 664 from line
24 660 to a pilot-operated check valve 666 may remain closed
as pressurized hydraulic fluid is fed through line 660 to
26 to the rod end of cylinder 5~. A line 672 may interconnect
: 27 the head ends of the cylinders 50 and 52 such that fluid
28 ///
29 ///
31
32
~ D-ll.01
~Z~i~
1 discharged from the head end of the contracting drive
2 cylinder 50 may flow through line 672 to the expanding
3 head end of the return cylinder 52. In this manner, the
cylinder 52 may act as an accumulator for exhausted oil
from the head end of cylinder 50 during its contraction.
6 Additionally, a line 658 may lead from the head
7 end of the cylinder 52 to a line 670 which may be joined
8 to return line 616. Hydraulic fluid may, then, also flow
9 through lines 668 and 670 to the reservoir 576. However,
to encourage flow between the cylinders 50 and 52 rather
11 than to the reservoir 576, the line 672 may be relatively
12 large as compared with the size of line 670~ After con-
13 traction of the drive cylinder 50 is completed, the
14 packing panel 44 may occupy a position as shown in Figure
13. At this point, as will be described, the operating
16 rod 650 may be moved to disengage the rod from the detent
17 mechanism 651 with the valve 648 being to its neutral
18 position.
19 '.~o c-ause movement of the packing panel 44
in a return direction from its position shown in Figure
21 13 to its rest position æhown in Figure 10, the rod 6S0
22 may be moved downwardly to move the valve 648 to a lowered
23 position from that shown in Figure 23. Hydraulic fluid
24 may then pass from line 644, through check valve 646 and
valve 648 and into line 686. Line 686 may lead to a
26 branch line 696 through which hydraulic fluid may be
27
28
29
31
32
-119-
~27~8 D-llOl
1 conveyed to the head end of the retainer panel cylinder
2 55. This may cause expansion of the retainer panel
3 cylinder 55 with hydraulic fluid being exhausted from the
~L rod end of the cylinder through a line 654 leading to
line 652 and through the valve 648 to line 687. Line
6 687 may convey the exhausted fluid through lines 642 and
q 616 for return to the reservoir 576. As discussed, since
8 the volume of the retainer panel cylinder 55 may be re-
9 latively small, its movement may take place relatively
rapidly such that the retainer panel 54 will complete
11 its movement from an opened to a closed position (see
12 Figures 13 and 10) prior to the movement of the packing
13 panel 44 in a return direction.
14 Pressurized hydraulic fluid flowing through
line 686 may also flow to the pilot-operated check valve
16 688 which may be connected through a pressure-sensing
17 line 690 to line 686. When the pressure in line 686
18 reaches a predetermined level, such as 1500 psi,
19 pressure transmitted through line 690 may then open the
valve 688. Fluid passing through the line 690 for opera-
21 tion of the valve 688 may then be exhaused through a
22 pressure, bleeding line 692 to the return line 616. The
23 function of the pilot-operated check valve 688 may,
24 thus, promote the movement of retainer panel cylinder
55 prior to movement of the return cylinder 52.
,26 With the pilot-operated check valve 688 moved
27 to its closed position, fluid may flow from line 686
28 ///
31
32
-120-
D-' 11
1 through the valve 688 and into line 694. Line 694 may
2 convey the pressurized hydraulic fluid to the rod end of
3 return cylinder 52 to, thereby, contract the return
cylinder. As the return cylinder 52 contracts, the drive
cylinder 50 may expand due to the mechanical connection
6 between the cylinders as discussed previously. On expan-
q sion of the drive cylinder 50, there may be a pressure
8 buildup at the rod end of the drive cylinder since the
9 ourflow of oil from the rod end is blocked by the check
valves 658 and 666. However, the chec~ valve 666 may be
11 set to open at a pressure of about 250 psi in
12 the line 694 which may be conveyed to the valve through
13 a pressure sensing line 698. ~hus, the check valve 666
14 may be opened quickly to permit the flow of hydraulic
fluid from the rod end of the cylinder 50 through line
16 664 and.check valve 666 into line 668 to the head end of
17 the cylinder 50. Cylinder 50 may, thus, act as its own
18 hydraulic accumulator during its expansion, with hydraulic
19 fluid being circulated from the rod end to the head end
Z of the cylinder. Also, hydraulic fluid discharged from
21 the rod end of drive cylinder 50 may flow through line
22 670 to return line 616 and the reservoir 576. However,
23 to encourage flow of hydraulic fluid from the rod end to
2~ the head end of cylinder 50 during its expansion, the
lines 664 and 668 may be relatively large as compared
26 with line 670. Thus, there may be less resistance to
27 flow of fluid from the rod end into the head end of
28 ///
29 ///
31
32
-121-
0 1
1 cylinder 50 as compared with resistance to flow through
2 line 670 to the reservoir 576.
3 As the drive cylinder 50 is expanding, the re-
4 turn cylinder 52 may be contracting due to the mechanical
interconnection between the cylinders. During contraction
8 of the return cylinder 52, fluid may be exhausted from the
7 head end of the return cylinder through line 672 and into
8 the head end of the drive cylinder 50. Thus, the drive
9 cylinder 50 may also act as an accumulator for hydraulic
fluid discharged from the return cylinder 52 during its
11 contraction. When the return cylinder 52 has completed
12 its contraction in moving the packing panel 44 to its rest
13 position, as shown in Figure 10, the operating rod 650 may
14 be moved to disengage the detent mechanism 651 from the
rod and to return the valve 648 to its neutral position
16 shown in Figure 22.
17 Figure 24 is a detailed view similar to
18 Figure 21, which illustrates the manner in which the rod
1~ 650 may be actuated in controlling the movement of the
valve 648 as described in Figure 23. In view of the simi-
21 larity between Figures 24 and 21, like reference numerals
22 have been used in Figure 24 for ease of description. As
23 previously described, movement of the control member 356 in
24 the direction of arrow B (Figure 19) causes rotational
movement of the rod 362 in the direction of the arrow G
26 (Figure 21). This, in turn, causes translational movement
27
28
29
31
32
-122-
1)-1101
li.~,271`~d
1 of the rod 650 in the direction of the arrow H (Figure 24)
2 to move the valve 648 to a raised position as compared with
3 its neutral position shown in Figure 23. In its raised
4 position, the valve 648 functions to provide contraction
of the drive cylinder 50 and movement of the packing panel
6 44 in a working direction through the hopper 34 as described
7 in Figures 10-13.
8 ~fter movement of the control member 356 in the
~ direction of the arrow B, the member may remain in this
position with the rod 650 moved in the direction of the
11 arrow H. The member 356 is not returned to its neutral
12 position as in the apparatus of Figures 21, 21a, 21b, 21c
13 and 22 where two rods 206 and 207 may be actuated by move-
14 ment of the member 356. With the member 356 positioned in
the direction of the arrow B to cause movement of the rod
16 650 in the direction of the arrow H, the member may remain
17 in this position until returned to its neutral position
18 through contact of the tab 393 with stop members 406 or
19 412 as described in Figure 19. As described in Figure 19,
to avoid contact of the tab 393 with stop member 406, the
21 handle member 376 may be pulled downwardly to cause rotation
22 of the rod 382 in the direction of the arrow F.
23 When the member 356 is returned to its neutral
24 position by stop member 412 after movement of the packing
panel 44 in a working direction through the hopper 34 (see
26 Figures 10-13), the rod 650 shown in Figure 24 may be
27 moved in a direction opposite to that of the arrow H and
28
29
31
32
-123-
1 and the rod 362 may be rotated in a direction opposite
2 to that indicated by arrow G to return the rod 650
3 to its neutral position as illustrated. As the rod
4 650 is moved in a direction opposite to arrow H, the
detent mechanism 651 may become disengaged from the
6 rod 650.
7 With reference to Figure 19, when the control
8 member 356 is moved in the direction of the arrow C, this
9 may cause rotation of the rod 362 from its neutral posi-
tion in Figure 24 in a direction opposite to that indicated
11 by arrow G to provide movement of the rod 650 from its
12 neutral position in a direction opposite to that of
13 arrow H. This may move the valve 648 to its lowered posi-
14 tion from its neutral position shown in Figure 23. The
valve 648 may then remain in its lowered position until
16 the stop member 414 contacts the tab 393 to return the con-
17 trol member 356 to its neutral position (Figure 19). As
18 the control member 356 is returned to its neutral position,
19 the rod 650 may also be returned to its neutral position
as shown In Figure 24.
21 In the foregoing description, the movement of
22 structural elements, such as valves, etc., has been des-
23 cribed by referring to the valves as being in a raised po-
24 sition or a lowered position with respect to a neutral posi-
tion. This terminology has been used in regard to Figures 22
26 and 23. It should be understood that the terms "raised"
27 and "lowered" do not imply that ~he valves are positioned
28
29
31
32
-124-
-~ `1)-1101
7~8
1 in a particular manner or that the valves are raised or
2 lowered in the sense of being moved to a higher or
3 lower elevation. The terms "raised" and "lowered" are,
4 therefore, used merely in a relative sense with respect
to the way in which the valves are illustrated in the
6 figures of the drawings. The valves may, however, be
7 mounted any desired manner such that movement of the
8 valves need not have any necessary relation to their
9 being raised or lowered.
Similarly, in the drawings, lettered arrows
11 have been used to illustrate movement of various struc-
12 tural elements. It should be understood that the move-
13 ments illustrated by these arrows are intended merely
14 to demonstrate relative movement of the structural ele-
ments. However, depending upon the physical placement
16 Of the structural elements, the movement of the elements
17 in a particular directio~ may vary depending upon the
18 placement of the structural elements with respect to
19 the overall structure of the apparatus.
In Fiyures 22 and 23, reference has been made to
21 the telescopic cylinder 14 as illustrated in Figure 1 for
22 providing movement of the ejection panel 12. The telescopic
23 cylinder 14 may, however, be replaced with the conventional
24 cylinder 62 mounted on the support member 60 as shown in
Figure 2. With this substitution, the pilot-operated valve
26 508 (Figure 22) and pilot-operated valve 612 (Figure 23)
27 may be eliminated since use of the conventional cylinder 62
28 may avoid the problem of pressure buildup that can occur in
29 the telescopic cylinder 14 with changes in thè ambient
temperature.
31
3~ ///
-125-
