Note: Descriptions are shown in the official language in which they were submitted.
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x'2184109
VERTICAL STORAGE CONVEYOR WITH IMPROVED
LOAD SUPPORT AND DRIVE SYSTEM
This application is a continuation-in-part appli-
cation of an U.S. application serial number 08/201,540,
filed February 25, 1994, which is a continuation-in-part of
the U.S. application serial number 07/004,081 filed January
13, 1993 by the same inventor.
FIELD OF THE INVENTION
The present invention relates in general to a
vertical conveyor, and in particular relates to a new and
improved load support and drive system for a conveyed pan
in a vertical storage conveyor.
BACKGROUND OF THE INVENTION
The present invention is an improvement to a
vertical storage conveyor type apparatus used for parking
or storing automobiles and the like. Prior art examples
include United States patent nos.: 3,424,321; 3,547,281;
and 3,656,608.
The vertical conveyors have two independent,
vertical frames, as well as beams and struts connecting the
frames, and an independent conveyor assembly connected to
each frame. Each vertical conveyor has an endless
compression chain formed of a plurality of rigid, compres-
sion links pivotally connected together with joint pins to
form an endless vertical chain. Rollers or wheels are
mounted at each end of the joint pin and are constrained to
move only within a vertical guide channel.
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A plurality of pickup members are journalled in a
spaced apart generally upright, but slightly pivotal
relationship, and attached to a pickup drive chain. The
compression members engage a compression link joint pin of the
pickup chain when the chain is rotated by the motor.
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The pickup members are guided by a stationary cam surface
and engage the pins to lift the compression links. In the
prior art patents, the bottom sprocket was the drive
sprocket with the load carried by the upper sprocket -
g creating slack in the non-driven side of the pickup chain.
In some of the prior art designs, such as
manufactured by some Japanese companies, a motor for
driving the conveyors is located near the top of the
device. It has been found that the motor is better placed
in the lower vertical half of the device.
Additionally, some prior art designs did not
allow smooth movement of moving parts. For example, in
one design the attachment and support for the top transfer
guide to the top of the fixed tower structure included
vertical captive slides with Hellville washers providing a
friction force to counteract the vertical weight of the
top transfer guide. This arrangement did not allow
sufficient adjustment or smoothness of movement. It would
be desirable to dampen the motion of the guide.
In some prior art designs, the bottom transfer
guide was supported by tie rods to control the lateral
movement. A spring support offset the vertical weight of
the transfer guide. As the pans rotated through the
bottom transfer guide, there was vertical movement of the
guide. Without any means for damping, a vibration and
jerking motion occurred. It would therefore be desirable
to dampen the motion of the guide.
Also, when the tower was stopped, a service
brake prevented rotation of the compression chains. A
Positive locking means is therefore desirable to prevent '
movement of the compression chain while people are
ingressing and egressing the bottom area of the tower.
In the copending parent application, the frame
has a vertically extending first frame section and a
vertically extending second frame section spaced apart
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from the first frame section. Each load support has a
first and second end and is capable of holding a load to
be conveyed in a loop. Each load support is movably
mounted at the first and second ends to the first and
second frame sections. As one support is conveyed
upwardly, another support is conveyed downwardly so that
the supports pass one another at a predetermined, spaced
apart horizontal distance which defines a support spacing.
A first conveyor is mounted to the first frame
section for conveying a first end of the supports. A
second conveyor is mounted to the second frame section for
conveying a second end of the supports. A mounting member
extends in the support spacing, and includes a motor
mounted thereto. The motor drives the first and second
conveyors. The motor includes a first drive shaft which
connects the motor to the first conveyor and a second
drive shaft Which connects the motor to the second
conveyor.
In accordance with the invention disclosed in
the copending, parent application, first and second frame
sections are supportingly connected to each other with a
plurality of connecting members rigidly attached at
respective ends thereof to first and second frame
sections. One of the connecting members extends between
first and second frame sections in the support spacing.
The mounting member is mounted to one connecting member
between first and second frame sections. The motor
mounting member is suspended from one connecting member
substantially centrally between the frame sections.
Although the motor mounting point between the
frame sections and to the frame sections is advantageous,
it is also desirable to further improve the drive
transmission, pickups and associated equipment. For
example, it is desirable to reduce the tendency for the
Pickup chain to stretch and have slack during a quick
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reversal in rotation such as occurs in prior art towers
where the lower sprocket was driven. When the pickup
chain was reversed, the claim tightens quickly, creating
great forces. It would also be desirable to ensure that
the pickup arms are oriented so that each arm engage
respective shafts of the compression chain in a more exact
manner. Additionally, it would be desirable if each
pickup arm could be disassembled from the unit without
disturbing the orientation of the pickup and compression
chains .
The copending '540 parent application is
directed to a vertical conveyor such as used for storing
automobiles having two independent, vertical frames
supportingly connected to each other. The frames and
respective independent conveyor assemblies are connected
to each other. Load supports have first and second ends
supported by a compression chain, a part of the
independent conveyor assembly, and are conveyed in an
endless vertical loop. The compression chains are mounted
to the first and second frame sections for conveying first
and second ends of each support. The first and second
conveying mechanisms also each include a pickup drive
chain assembly having pick-up arms which engage the
compression chain. The pick-up arms are also pivotally
mounted off center on the pick-up drive chain to aid in
the engagement of the pick-up arms with the compression
chain.
In the copending parent application, an upper
drive sprocket is disclosed for the pick-up drive chain
wherein a substantial amount of the load exerted by the
load supports against the pick-up drive chain is imparted
against the upper drive sprocket. Another sprocket is
aligned below the drive sprocket and has a smaller
diameter so that slack produced in the pick-up drive chain
is minimized such as occurs during reversing motion of the
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conveyor.
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Other prior art vertical conveyors used for
storing automobiles and the like typically have different
motors and drive mechanisms for moving the load supports
in a loop configuration so_that as one load support is
raised, another load support is lowered. Balancing is
extremely important, and it is necessary that load
supports which are typically supported at their ends be
raised at either end simultaneously and be supported so
that the entire apparatus will not topple and remain
stable as the load supports are moved.
The present invention is directed to a novel
configuration of the compression chain which supports the
load supports and the drive mechanism for the pick-up
drive chain assemblies which engage the compression chain
through pick-up arms to provide added balance, stability
and force for raising the load supports.
SUN~ARY OF TSE INVENTION
The present invention is advantageous because
the chain slack produced in prior art conveyors is now
minimized so that any reversing action of the conveyor
will not produce large stresses on the pickup chain.
Additionally, the construction of the pickup using the two
piece general construction allows ready disassembly of the
Pickup arms from the pickup chain without disturbing the
pickup chain and the compression chain. Other advantages
will be apparent from the summary and detailed description
which follows.
In accordance with the present invention, the
vertical conveyor has a frame with a first vertical frame
section and a second vertical frame section spaced apart
from, but supportingly connected to each other. A
plurality of load supports each have first and second ends
that are capable of holding a load to be conveyed around
an endless loop. Each support is movably mounted at its
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first and second ends to first and second frame sections.
As one support is conveyed upwardly, another support is
conveyed downwardly so that the supports pass one another
at a predetermined, spaced apart horizontal distance which
defines a support spacing.
First and second conveying means mounted to the
first and second frame sections for conveying a first and
second end of each support. The first and second
conveying means each comprises a drive chain assembly and
means interconnecting the drive chain assembly with each
of the supports. A motor simultaneously drives the first
and second drive chain assemblies.
In one aspect of the invention, the first and
second drive chain assemblies each comprises a pickup
drive chain which drives a compression chain supporting
the load supports, and an upper drive sprocket of the
pickup drive chain driven by a motor wherein a substantial
amount of the load exerted by the supports against the
pickup drive chain is imparted against the upper drive
sprocket. An idler sprocket is aligned below the drive
sprocket and has a smaller diameter than the drive
sprocket. Thus, the slack produced in the pickup drive
chain is minimized such as occurs during reversing motion
of the conveyor.
In one aspect of the invention, a plurality of
pickup arms are pivotally connected to the pickup drive
chain such that the pickup arms engage and drive the
compression chain so as to move the load supports. The
pickups are pivotally mounted offset on the pickup chain
to aid in engagement of the pickups with the compression
chain. The compression chain includes an endless roller
chain comprised of interconnecting, elongate compression
links and transverse axles mounted at each end of the
compression links such that the pickup arms engage the
axles for pushing the compression links upward. The
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offset mounting of the pickups enables receiving notches
on the pickups to engage the axles as the chain moves in
its lower portion of the loop.
In one aspect of the invention, the load
supports include load support mounting arms, which are
pivotally mounted to the compression links. A mounting
member extends in the support spacing. The motor is
mounted to the mounting member. A connecting member
supportingly connects the first and second frame sections.
The motor mounting member is suspended from the connecting
member substantially centrally between the frame members.
In still another aspect of the invention, the
pickup chain comprises two spaced roller chains. Each
through-pin connects the roller chains. The pickups are
Pivotally connected to the roller chain between the
pickups. The pickup chain also includes a link, and a
link pin interconnecting the link. The through-pins are
offset from the link pins. The pickups comprise an upper
head portion and a smaller lower bifurcated tail portion.
The upper head portion includes opposing receiving notches
for engaging the through-pins of the compression chain.
In one aspect of the invention, as a pan
traverses through the top transfer guide, the guide moves
upward and then returns to its original height. In
addition, as the compression chain links shorten over the
life of the conveyor, the reference starting point for the
top transfer guide moves slightly downward.
As the pan traverses through the bottom transfer
guide, a vibration develops due to a lack of dampening of
the guide motion which moves downward from a reference
point and returns. The present invention provides for a
vertical floating motion with a dampening effect.
In still another aspect of the invention, a
positive locking device prevents movement of the
compression chain while the rotational movement of the pan
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is at rest. The locking device is capable of transferring
any load imbalance to the frame structure.
In accordance with the present invention, a
vertical conveyor has a frame with a first vertical frame
section and a second vertical frame section spaced apart
from, but supportingly connected thereto. A looped
compression chain is mounted respectively to each of the
first and second frame sections. A plurality of load
supports have first and second ends, with each load
suPPort being capable of holding a load to be conveyed
around in a looped path. A support mechanism
interconnects the compression chain and respective first
and second ends of the load supports so that the
compression chains support the load supports such that as
one support is conveyed upwardly, another load support is
conveyed downwardly. The load supports pass through a
predetermined, spaced apart, horizontal distance, which
defines a support spacing.
First and second pick-up drive chain assemblies
are mounted respectively to each of the first and second
frame sections. A plurality of pick-up arms are pivotally
connected to each pick-up drive chain assembly, and the
pick-up arms engage and drive the compression chain.
A motor is mounted within the spacing defined by
the load supports. A first drive shaft connects the motor
to the first pick-up drive chain assembly and a second
drive shaft connects the motor to the second pick-up drive
chain assembly. The drive shafts simultaneously drive the
first and second drive chain assemblies so that the pick-
uP arms engage and drive the compression chain and move
the load supports.
In one aspect of the present invention, the
pick-ups are pivotally mounted offset on the pick-up drive
chain assembly to aid in engagement of the pick-ups with
the compression chain. Each pick-up drive chain assembly
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comprises two spaced roller chains and a through-pin
interconnecting the roller chains. The pick-up arms are
pivotally connected to each through-pin. The pick-up
drive chain assembly includes a link and a link-pin
interconnecting the links. The through-pins are offset
from the link-pins. The pick-up arms comprises an upper
head portion and a smaller, lower bifurcated tail portion.
The compression chain includes axles, and the upper head
portion includes two receiving notches for receiving axles
Positioned on the compression chain.
The mounting member mounts the motor
substantially centrally between the frame sections. The
motor is an electrical motor having first and second motor
shaft ends, located at respective sides of the motor, and
respectively connected to the first and second drive
shafts. The motor is mounted at a vertical height less
than one half the vertical height of the vertical frame
sections.
In another aspect of the present invention, each
compression chain also includes an endless roller chain
comprising interconnecting, elongate compression links and
transverse axles mounted at each end of the compression
links. Each load support also includes load support
mounting arms at first and second ends of the load
suPPorts. The mounting arms are pivotally connected to
the compression links so that the load supports are
supported by the compression chain. Pick-up arms are
pivotally connected to each pick-up drive chain assembly,
such that the pick-up arms engage the axles while pushing
the compression links upward.
BRIEF DESCRIPTION OF THE DRAWINGS
The foregoing advantages of the present
invention will be appreciated more fully from the
following description, with reference to the accompanying
drawings, in which:
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Fig. 1 is an front end elevation view of a
vertical conveyor according to one embodiment of the
present invention.
Fig. 2 is a side elevation view of the vertical
conveyor shown in Fig. 1.
Fig. 3 is an enlarged, front elevational view of
the major weldment of the frame and depicting the pickup
drive chain mechanism for the vertical conveyor.
Fig. 4 is an enlarged front elevational view
similar to Fig. 3, showing features of the endless pickup
chain drive and of the secondary compression chain lock.
Fig. 4a is an enlarged, front elevation view of
the front upper guide plate subassembly.
Fig. 5 is an enlarged side elevation view
looking in the direction of arrow 4 of Fig. 4.
Fig. 6 is an enlarged front elevation view of
the drive gear sprocket.
Fig. 7 is a cross-sectional view taken along
line 7-7 of Fig. 6;
Fig. 8 is an enlarged engineering scale front
elevation view of the idler sprocket.
Fig. 9 is a cross-sectional view taken along
line 9-9 of Fig. 8.
Fig. 10 is an enlarged front elevation view of
one of the pickup arm assemblies which engages with and
conveys a compression link in the secondary chain.
Fig. 11 is a sectional view taken along line 11-
11 of Fig. 10.
Fig. 12 is a front elevation view of the double-
stranded conveyor chain in the pickup drive chain.
Fig. 12a is a sectional view of the pickup chain
taken along line 12a-12a of Fig. 12.
Fig. 13 is an enlarged side elevation view of
the bottom pickup guide assembly.
Fig. 14 is an enlarged plan view taken along
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line 14-14 of Fig. 1 depicting the mounting and
' stabilizing structures of one end of a conveyed pan.
Fig. 15 is a sectional view of the upper column
section taken along line 15-15 of Fig. 1.
Fig. 16 is a sectional view of the lower column
section taken along line 16-16 of Fig. 1.
Fig. 17 is an enlarged, front elevation view of
the top stabilizing transfer guide assembly.
Fig. 18 is a top plan view of the conveyor shown
in Fig. 1.
Fig. 19 is a partial rear elevation view taken
along line 19-19 of Fig. 18 and showing the guide channel
cross-over.
Fig. 20 is an enlarged, front elevation view of
the bottom stabilizing transfer guide assembly.
Fig. 21 is a side elevation of the bottom
stabilizing transfer guide assembly shown in Fig. 20.
Fig. 22 is a top plan engineering scale view of
the bottom stabilizing transfer guide assembly depicted in
Fig. 20.
Fig. 23 is an enlarged, top plan view of the
tower locking assembly.
Fig. 24 is an enlarged, front elevation of the
circled portion of Fig. 17 to delineate the shock
mechanism.
Fig. 25 is an enlarged section view of the
sliding guide for the top transfer guide shown in Fig. 24.
Fig. 25a is an enlarged section view of Fig. 25a
delineating the friction mechanism components of the top
transfer guide.
Figure 26 is a front and elevational view of a
' vertical conveyor according to one embodiment of the
present invention.
Figure 27 is'~a side elevation view of the
vertical conveyor show in Figure 26.
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Figure 28 is an enlarged, front elevational view
of the major weldment of the frame and depicting the
pickup drive chain mechanism for the vertical conveyor.
Figure 29 is an enlarged front elevational view
similar to figure 28, showing features of the endless
pickup chain drive and of the secondary compression chain
lock.
Figure 30 is an enlarged, front elevation view
of the front upper guide plate subassembly.
Figure 31 is an enlarged side elevation view
looking in the direction of arrow 31 of Figure 29.
Figure 32 is an enlarged from elevation view of
the drive gear sprocket.
Figure 33 is a cross-sectional view taken along
line 33-33 of Figure 32.
Figure 34 is an enlarged engineering scale front
elevation view of the idler sprocket.
Figure 35 is a cross-sectional view taken along
line 35-35 of Figure 34.
Figure 36 is an enlarged front elevation view of
one of the pickup arm assemblies which engages with and
conveys a compression link in the secondary chain.
Figure 37 is a sectional view taken along line
37-37 of Figure 36.
Figure 38 is a front elevation view of the
double-stranded conveyor chain in the pickup drive chain.
Figure 39 is a sectional view of the pickup
chain taken along line 39-39 of Figure 38.
Figure 40 is an enlarged side elevation view of
the bottom pickup guide assembly.
Figure 41 is an enlarged plan view depicting the
mounting and stabilizing structures of one end of a
conveyed pan.
Figure 42 is a sectional view of the upper
column section.
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Figure 43 is a sectional view of the lower
' column section taken along line 43-43 of Figure 1.
Figure 44 is an enlarged, front elevation view
of the top stabilizing transfer guide assembly.
Figure 45 is a top plan view of the conveyor
shown in Figure 1.
Figure 46 is a partial rear elevation view taken
along line 46-46 of Figure 45 and showing the guide
channel cross-over.
Figure 47 is an enlarged, front elevation view
of the bottom stabilizing transfer guide assembly.
Figure 48 is a side elevation of the bottom
stabilizing transfer guide assembly shown in Figure 47.
Figure 49 is a top plan engineering scale view
of the bottom stabilizing transfer guide assembly depicted
in Figure 47.
Figure 50 is an enlarged, top plan view of the
tower locking assembly.
Figure 51 is an enlarged, front elevation of a
Portion of Figure 44 to delineate the shock mechanism.
Figure 52 is an enlarged section view of the
sliding guide for the top transfer guide shown in Figure
51.
Figure 53 is an enlarged section view of Figure
52 delineating the friction mechanism components of the
top transfer guide.
Figure 54 is a top plan view of the mounting and
stabilizing structures which support a conveyed pan.
Figure 55 is a schematic, elevational view
showing the compression chain supporting the load support.
Figure 56 is a front elevational view depicting
the pick-up drive chain assembly and pick-up arms engaging
the compression chain.
Figure 57 is an enlarged view showing the load
support mounting mechanism engaged with the compression
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chain.
Figure 58 is an elevation view of the motor and
drive shafts of the present invention.
Figures 59 and 60 depict the inner link assembly
of the compression chain, with Figure 59 being a plan view
and Figure 60 being an elevation view.
Figures 61 and 62 depict the outer link assembly
of the compression chain, with Figure 61 being a plan view
and Figure 62 being an elevation view.
DETAINED DESCRIPTION OF T8E PREFERRED EMBODIb~NT
Referring now to Figs. 1 and 2, a vertical
conveyor 10 according to a presently preferred embodiment
is depicted. The conveyor 10 has a skeletal frame 12. A
compression chain vertical conveyor system 14 (Fig. 2)
includes a left subsystem 14a and a substantially
identical right subsystem 14b. A plurality of platform
cells or pans 16 are hung from the conveyor system 14 and
are rotated in either direction in an endless racetrack
(looped) path.
The illustrated conveyor 10 has fourteen pans
16. Each pan 16 is designed to carry a static load of up
to 5,000 pounds, and thus can carry a full size
manufactured automobile. In this illustrated embodiment,
the conveyor 10 has an overall height of about 52 feet, an
overall width of about 20 feet, and an overall length of
about 25 feet. The conveyor 10 can be designed to have
more than thirty pans 16 and have a height of about 103
feet. The zoning laws in a particular location where the
conveyor is installed will sometimes dictate height
requirements.
Frame 12 (Figs. 1 and 2),, is a fixed support
structure and is substantially transversely symmetrical
about a central plane 18 as depicted in Fig. 2 and is
substantially longitudinally symmetrical about a central
Plane 20. A top guide strut brace 52 is at the top. As
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shown in Figs. 2 and 18, the frame 12 includes a front
' vertical frame section 22 (shown in side elevation in Fig.
1) and a substantially identical rear vertical frame
section 24 mounted on a rectangular base section 26.
The base section 26 has two transverse headers:
1) a front transverse header 28 and 2) a rear transverse
header 30 connected at substantially similar top cornices
32 to two longitudinal side headers (not shown). The
front, rear and side headers define an annular rectangle.
The base section 26 also includes four legs (three shown)
located at and connected to each cornice 32.
As shown in Fig. 2, the front header 28 has a
rotated °G" shaped cross-section and rests above the
automobile entrance. The "G° shaped cross-section forms a
stronger, lighter and more economically manufactured
member which can be easily installed and removed. In
addition, other conveyor equipment can be mounted inside
the G-shaped header frame including operating equipment
for a gate (not shown) used to block the entrance to the
conveyor 10.
As shown in Fig. 2, a plurality of internal
braces on each side of the vertical conveyor 10 connect
the frame sections 22 and 24 together and provide
structural rigidity, equalizing the loading between the
frame sections. The internal bracing includes horizontal
struts 34, 54, 56, 58 (Fig. 2), each of which is rigidly
mounted at respective ends to frame sections 22 and 24.
Lateral stability is provided by diagonal bracing 60, 62
and 64. The bracing for the top transfer guide 102 Figs.
1~ 17, and 18 is shown in section 50 and includes a top
guide strut brace 52, two top guide spacing struts 51 and
' 57, and four top guide braces 53, 55, 59 and 61 bolted
together to form an °X~~ configuration.
As shown in Fig. 1, the frame section 22 has
substantially the form of an A-frame. The frame section
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22 has a base formed by header 28 and legs 38 and 40, and
has an upper section formed by diagonal columns 66 and 68.
The diagonal columns 66 and 68 are bolted at their lower
ends to respective cornices 32 of the A-frame base, and
g are bolted at their upper ends to each other and to a
transverse midpoint of f rout column 70.
A substantially similar rear column 70' (Fig. 2)
is provided for the frame section 24. The column 70
includes a lower section 72 and an upper section 74 that
are spliced together with bolts at a vertical mid-portion
joint 76 (described below). The height of the mid-portion
joint 76 above the foundation 11 depends upon the total
number of conveyor pans and the overall height of conveyor
10. The lower column section 72 includes a solid one-
Piece weldment.
The columns 70 and 70' form a fixed tower
structure and provide a conveyor housing and track for a
secondary conveyor assembly that includes a rolling
compression chain 78 (Fig. 14).
For the purposes of the description of the
present invention, the detailed construction of
compression chain 78 and of columns 70 and 70' is not
described in detail. Details of such construction can be
obtained by referring to the aforementioned U.S. patent
3656608 to Lichti. Each column 70 and 70' serves as part
of a main frame extending upwardly from the front header
28 (or the rear header for rear frame section 24) through
a joint adjacent the top of conveyor 10 where it supports
the upper end of endless conveyor compression chain 78
located at the point where chain 78 crosses over from one
side to the other.
Each platform pan 16 has a slightly, upwardly
curved, rectangularly configured bottom plate 80. The
bottom plate 80 is supported at each corner by a vertical
Pan hanger or post 83. Those posts 83 are located on the
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same side of the bottom plate 80 and connected at the tops
thereof to a horizontal, V-shaped top pan header 84 (Fig.
14). A horizontal, tubular top strut 85 connects the
apices of each header 84 and, with two braces 86, are
welded thereto.
Referring to Figure 14, each platform pan 16 is
mounted and stabilized during its travel around conveyor
through a mounting assembly 87. A stub shaft 88
connects the mounting assembly 87 to the pan 16. The stub
10 shaft 88 extends outwardly from the other side of the apex
of each header 84 and is welded thereto. A bearing
housing 89 is mounted on the stub shaft 83. The apex of a
~~v~~ shaped link hanger 90 is pivotally mounted to the
bearing housing 89. The link hanger 90 has two coplanar
ass (arrn 92 shown in Fig. 14) , which are pivotally
mounted at their respective free ends to a compression
link of the endless compression chain 78. Thus, a pan 16
is cantilever mounted at each end to the corresponding
conveyor subsystem 14a or 14b by a link hanger 90.
As shown in Figs. 1 and 14, the apex of a V-
shaped stabilizer 96 is also mounted to the stub shaft 88.
The stabilizer 96 pivotally mounts guide shoes 98. The
stabilizer 98 stabilizes the pan 16 as it is conveyed
around the top and bottom of the conveyor 10. Mounted to
the top and bottom of front and rear conveyor housings 70
and 72 are a top guide 102 and a bottom guide 104 which
contain crossing channels 100 and 102 (see also Fig. 19).
Guide shoes 98 of each pan 16 are received in the channels
100 and 101 as a pan 16 is conveyed.
In general, the vertical conveyor 10 includes a
motor means 120, a pickup drive chain assembly 122 rotated
by the motor, and a compression drive chain assembly 124,
driven by the pickup drive chain assembly 122. The
compression chain assembly 124 includes a compression
chain 78 that carries pans 16.
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In the present invention, the motor means
includes a motor 130 which is a double ended, reversible,
three phase 460 AC volt input, 500 volt DC output,
regenerative electric motor. The motor is connected to
the primary drive chain assembly 122 of each frame section
22 and 24 through drive subassemblies 146 and 148 (Fig.
2). Each drive subassembly 146 and 148 comprises a
commercially available universal joint 150 which connects
a drive shaft 152 to motor 130. A second, distal
universal joint 154 is connected to the distal end of the
drive shaft 152. Connected to the other end of the distal
universal joint, through a keyed fitting (not shown) is a
conventional, hydraulically actuated electrically operated
friction brake 156, which is connected and mounted to a
speed reduction gearing 158 with a splice fitting (not
shown). The housing containing the reduction gearing 158
is mounted at the other end to the corresponding vertical
frame section 22 or 24. The reduction gearing 158 is
operatively connected to and drives the pickup drive chain
assembly 122.
Referring now to Figs. 1 through 5, each pickup
drive chain assembly 122 is mounted on a solid, one piece
weldment 160 which includes a lower frame section 72 of
the frame portion 22. More particularly, the pickup drive
chain assembly 122 is mounted inside an interior cavity
162 of the weldment 160.
The pickup drive chain assembly 122 (Figs. 3 and
12) includes an upper toothed drive sprocket subassembly
166 (Fig. 7), a lower toothed idler sprocket subassembly
168 (Fig. 9), a dual drive chain subassembly 170 (Fig.
12A) and five pickups 172 (Fig. 10) attached to the drive
chain subassembly 170 with a through-pin 194 (Fig. 12a)
and rotated in a racetrack path. In the illustrated
embodiment, there are only five pickups 172. For
explanation and clarity, one of the pickups 172 is shown
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in phantom (Fig. 3) in an advanced position at the top of
drive chain subassembly 170. In Figure 4 the bottom-most
pickup 172 has been omitted.
An upper toothed drive sprocket subassembly 166
is an integral, one-piece, molded element (Figs. 6 and 7)
and includes an outside drive sprocket 176, a
substantially similar inside drive sprocket 178, and an
interconnecting, hollow tube 179. A solid shaft 180 (Fig.
5) is keyed to and mounted inside the tube 179 and
terminates on its inner end in a splice (not shown), which
in turn is mounted to and driven by reduction gearing 158.
The outer end of the shaft 180 is mounted in a bearing 183
(Fig. 5), which in turn is rigidly mounted to the weldment
160. Each drive sprocket 176 and 178 has a mean diameter
of about 23 inches, a total of 18 standard teeth 181, and
two sets of two reduced diameter teeth 181' located 180
degrees apart. The teeth 181' terminate inside the mean
diameter circle 177. The radial size of the teeth is
smaller so as to provide clearance for the diameter of the
through-pin 194.
The lower toothed idler sprocket subassembly 168
is shown in Figs. 4, 5, 8, 9, and 13 and includes an
outside idler sprocket 184, a substantially similar inside
idler sprocket (not shown), and coaxial, spaced apart
shaft 188 for respectively mounting inside and outside
idler sprockets. The 186 spacing between the adjacent
ends of shafts 188 is selected so that pickups 172 can
pass therebetween. Idler sprocket 184 has a diameter of
about 12 1/4 inches and a total of nine teeth 185 and two
teeth 185'. The teeth 185' terminate inside the mean
diameter circle 187 and the pitch between them is deeper
so as to provide clearance for the larger diameter of the
through-pin 194.
The pickup drive chain subassembly 122 (Figs. 12
and 12a) is comprised of a first roller chain 190 and a
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second roller chain 192 each with five interconnected,
matched strands. The center lines of the roller chains
190 and 192 are spaced apart about 8 1/2 inches and the
two chains are interconnected with five through-pins 194.
Each of the five strands of each chain 190 and 192 is
about 34 1/4 inches long and terminates in a master link
195 which connects to the adjacent strand and which mounts
through-pin 194. In this particular embodiment, each
chain 190 and 192 has an average tensile strength of
150,000 pounds per strand. The center axis line of the
through-pins 194 is offset from a center line drawn from
chain link-pins 197 (Fig. 12).
As shown in Figs. 3, 4, 11 12 and 12a a pickup
172 is pivotally mounted at the bottom section thereof on
each heat-treated through-pin 194.
The pickups 172 of the present invention have a
split body. Each pickup 172 includes an upper head
portion 196 and a smaller, lower bifurcated tail portion
198 that is mounted to upper head portion with bolts and
nuts (not shown). In a preferred embodiment, pickup 172
is almost 26 inches long and a little over 14 inches wide
at the top and tapers down to 7 inches wide at the bottom
of head portion 196 with a 10 inch radius curare. Each
pickup 172 is journalled onto the through-pin 194 and is
held centered thereon with snap rings 199 on either side.
A notch 200 (Fig. 10) on each side of the centerline of
pickup 172 in the upper head portion 196 engages with and
picks up a connecting pin assembly, shown at 210 (Fig 3),
in compression chain 78 (Fig. 14).
The mating ends of the head portion 196 and tail
portion are provided with mating half-circular cutouts.
The cutout in the head portion 196 has a nominal radius of
1.5 inches so it can receive a semi-circular bearing
insert 201 having integral end flanges. The cutout in the
tail portion 198 has a nominal radius of 1.25 inches,
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which matches with the inner surface of insert 201. A
sleeve 202 has a thickened central portion with a central
circular slot therein for engaging the head portion. The
sleeve 202 has a reduced shoulder to support ball bearings
203 at each end. Each ball bearing supports 203 a metal
wheel 204, which has been heat treated to a surface
hardness of Rc 44/47. The wheels 203 have an outer
diameter of 4.625 inches in a preferred embodiment and
engage and ride on a bottom guard 205 (see Fig. 4), which
helps orient the pickup 172.
Located near the top of head portion 196 (Fig.
10) is a hole having a radius of 1 3/4 inches for mounting
a upper shaft 206. Mounted onto each end of shaft 206
(Fig. 11) are ball bearings 207 which in turn mount a top,
inner flanged wheel 208, which has an base outer diameter
of 4.5 inches and a flange outer diameter of 5.25 inches
in a preferred embodiment. Wheel 208 engages and is
guided by a plurality of track guides 209 (Fig. 4) and 352
(Fig. 4). Mounted between upper wheel 208 and lower wheel
204 on either side of pickup 172 is a somewhat triangular
safety lug 211 (Fig. 10) which restricts the back fall of
the pickup traversing the top guide 350 (Fig. 4).
As shown in Figs. 3 and 14, the compression
chain 78 includes a plurality of outer compression links
212 and a plurality of inner compression links 214, which
are similar to and fit inside outer compression links 212.
The inner and outer compression links are pivotally
interconnected by connecting pin assemblies 210. Also
. mounted to the inner link 214 are two angled connecting
lugs 228, only one of which is depicted in Fig. 14, for
connecting link hanger arms 91 and 92 of the pan 16.
As shown in Fig. 3, the bearing roller 238 is
engaged in one of the notches 200 of the pickups 172 as
the engaging pickup 172 lifts or pushes it and the
associated compression link upwards. Thus the weight of
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0
the whole load on the side of the upwardly rotated
conveyor 10 is realized through bearing roller 238.
The guide and channel subassemblies for the
compression chain assembly 124 (Fig. 2) are integral
components with the other elements of the conveyor 10.
For the upper frame section 74 (Figs. 1 and 15), the
outwardmost components have spaced apart left hand guide
rails 252 and right hand guide rails 254 (Fig. 15). The
guide rails 252 include an inner guide channel 256 and an
outer guide channel 258 spaced apart to the plate 260.
The guide rails 254 are formed of an inner guide channel
262 and an outer channel 264 spaced apart to a plate 266.
Each guide channel also serves as a vertical structural
component and has a bevelled U-shaped channel that is
welded to the upper frame section 74. The compression
chain rollers 242 (Fig..l4) have a similar size, shape and
bevel to the slope of the guide channels. The upper and
lower ends of channels 252 and 254 are flared inwardly to
permit the compression links 214 to "bend over" the top of
frame sections 74 (Fig. 1) and 74a (Fig. 2).
The guide and channel subassemblies for the
lower tower section are parts of the weldment 160 (shown
in Figs. 3, 4, 5 and 16). As shown in Fig. 16, the
weldment 160 is formed of a welded metal sheet base plate
270 having side plates 272 and 274 welded to each end to
form a somewhat rectangular box. In the middle section of
side plates 272 and 274 are slots 276 and 278 to
accommodate pickups 172 entering the channel area and
engaging connecting pin 210 of compression chain 78. The
weldment, 160, as shown in Fig. 16, also contains suitable
mounting plates, such as mounting plate 280, for mounting
the pickup dive chain assembly 122.
Directly welded to side plate 272 is a guide
rail 282. A guide rail 284 is welded to side plate 274.
The guide rail 282 has an inner guide channel 286 (Fig.
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16) and an outer guide channel 288 spaced apart and
connected to side plate 274 by welding. Similarly, the
guide rail 284 has an inner guide channel 290 and an outer
channel 290 mounted spaced apart and connected to side'
plate 274 by welding. Each guide channel 286, 288, 290
and 292 also serves as vertical structural component and
is a bevelled U-shaped channel that is connected to
weldment 160. Also, each U-shaped channel has the same
size and shape as channels 256, 258, 262 and 264.
The weldment 160 (Figs. 3, 4 and 5) has three
pickup guides - the bottom guide 205, side guide 209, and
a top guide 302. The bottom guide 205 is also shown in
Fig. 13 and has a mounting plate 304 rigidly attached at
the bottom to a square mounting tube 306. Two
substantially identical spaced guides 308 and 309 (not
shown) are rigidly mounted at their respective bottoms to
the mounting tube 306. Each guide 308 and 309 is
comprised of a U-shaped guide plate 310 (Fig. 4) with
removably mounted tip portions 312 bolted thereto and
suPPorting side gusset plates 314. A flat polyurethane
guide bar 316 is mounted perpendicularly along the inner
edge of guide plate 310 (Fig. 4). The pivot pin 320 also
catches the tail portion of the pickup 172 as the pickup
172 is rotated in either direction to it. This holds the
bottom of the pickup 172 stationary, and permits the top
portion, connected to chains 190 and 192, to be rotated
with respect to the bottom in the proper direction.
The side guides 209 have an outer guide plate
326 which extends out of the paper (Fig. 3) and an inner
guide plate 328 which is bolted to the primary drive
mounting plate 272 and 274 (Fig. 16).
The top guide 302 (Fig. 3) has a front upper
guide plate 340 rigidly mounted on the weldment 160 and a
lower guide plate 342 spaced below the upper guide plate
340. A similarly shaped rear upper guide (not shown) is
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spaced 2~ inches behind the front guide. Together the
front and rear guides form a captive path 352 for the
upper wheel 208 of a pickup 196 to traverse the top of the
drive. A plurality of U-shaped jointing plates 344 are
g perpendicular to the plates 340 and 342 and welded at its
respective feet to plates 340 and 342. As seen in Fig.
4a, the upper guide plate 340 has a lower concave
curvilinear surface 346 with a circular upper mid-portion
cutout 348 which is symmetrical about the centerline. The
curvilinear surface 346 has a preferred lower circular
segment with a 4.75 inch radius and an upper circular
segment with a 39.75 inch radius. The cutout 348 has a
2.25 inch radius. The bottom length of upper guide plate
is 27.5 inches. The lower guide plate 346 has a pentagon
shape with an upper convex curvilinear surface 350 that is
symmetrical about the centerline. Each half of surface
350 has a circular segment to produce a guide path 352
(Fig. 4) .
As upper wheel 208 of pickup 172 enters either
end of guide path 352, it will cause pickup 172 to rotate
slightly in the direction of motion. When pickup upper
wheel 288 enters cutout 348, the top of pickup 172 is
prevented from rotating and the pickup tail will then
rotate in the direction through the center of the drive.
In this way, pickup 172 is rotated into preferred
orientation to exit the top guide path.
Referring now to Figures 24, 25 and 25a, details
of the dampening action imparted to the apparatus is
described together with an improved locking device.
As a pan 16 (Fig. 1) traverses the top of the
conveyor 10, the shoes 98 (Fig. 1) are engaged in the
tracks 100 and 101 (Fig. 19) of the top transfer guide 102
(Fig. 1) and lift the transfer guide upward at the apex of
the travel and then returns as the shoes pass from the
apex of travel. The top transfer guide 102 (Fig. 17) is
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comprised of the sliding guide support 107 and transfer
guide 108. The center tube 109 of the sliding guide 107
is bolted 111 to the fixed tower 22. In fig. 24 the
vertical weight of the transfer is counter balanced by the
four shock absorbers 113 which also provide a dampening
motion for the guide movement. Inside the center tube 109
is a ground tube 114 (Fig. 25) that provides a vertical
guide for the sliding guide 107. At the bottom end of the
round tube 114 is round bar that engages a friction bar
115 and is restrained by a captive bar 116. Bellville
washers 117 provide friction between a friction plate 118
and the captive bar 116. The friction connection is then
established between the fixed tower 22 and the sliding
guide 107 and still allow a downward movement of the
transfer guide as the compression chain shortens during
the life of the conveyor.
The bottom transfer guide 130 floats down and up
as a pan 16 (Fig. 1) traverses the bottom of the conveyor
10 (Fig. 1). The vertical weight of the bottom transfer
guide 130 is transferred through the two shock absorbers
131 (Fig. 20) and two die springs 132 (Fig. 20) to the
header 28. The shock absorbers 131 provide the dampening
of the vertical motion of the bottom transfer guide 130.
The upward motion of the guide 130 is restricted by die
spring 133 and is mounted such that it comes in contact
with the under side of header 28 (Fig. 1) during excessive
upward movements. This series of die springs and shock
absorbers keep the bottom transfer guide at a prescribed
reference point and still allow vertical motion with a
d~Pening effect.
When a pan 16 (Fig. 1) is at the bottom of the
conveyor 10 the lock link system 140 (Fig. 4 and 23) is in
its extended position. The height of the lock link bar
141 (Fig. 4) is such that the top of the bar 141 is 1/8
(0-125) of an inch below a bearing roller 238 (Fig. 3) of
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a
a compression link. Normally a service brake 156 (Fig.
2) provides the holding power to resist any unbalanced
load. If one or both of these brakes 156 fail then the
compression chain 78 could move in the direction of the
unbalanced load. The lock link bars 141 are extended and
retracted by the cam motion of the actuator 143 (Fig. 23).
In Fig. 23 the lock link bars 141 are shown extended to
engage the compression chain. When the bar 141 is rotated
clockwise 180 degrees, the lock link bar will retract and
allow the compression chain 78 to move.
It should be understood that the foregoing
description of the invention is intended merely to be
illustrative thereof, and that other embodiments,
modifications, and equivalents may be apparent to those
skilled in the art without departing from its spirit.
Referring now to Figs. 26 and 27, a vertical
conveyor 10 according to a presently preferred embodiment
is depicted. The conveyor 10 has a skeletal frame 12. A
compression chain vertical conveyor system 14 (Figs. 26
and 55) includes a left subsystem 14a and a substantially
identical right subsystem 14b. A plurality of platform
cells or pans 16 are hung from the conveyor system 14 and
are rotated in either direction in an endless racetrack
(looped) path (Figures 26, 27 and 55).
The illustrated conveyor 10 has fourteen pans
16. Each pan 16 is designed to carry a static load of up
to 5,000 pounds, and thus can carry a full size
manufactured automobile. In this illustrated embodiment,
the conveyor 10 has an overall height of about 52 feet, an
overall width of about 20 feet, and an overall length of
about 25 feet. The conveyor 10 can be designed to have
more than thirty pans 16 and have a height of about 103
feet. The zoning laws in a particular location where the
conveyor is installed will sometimes dictate height
requirements.
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Frame 12 (Figs. 26 and 27), is a fixed support
structure and is substantially transversely symmetrical
about a central plane 18 as depicted in Fig. 27 and is
substantially longitudinally symmetrical about a central
plane 20. A top guide strut brace 52 is at the top. As
shown in Figs. 27 and 45, the frame 12 includes a front
vertical frame section 22 (shown in substantial elevation
in Fig. 26) and a substantially identical rear vertical
frame section 24 mounted on a rectangular base section 26.
The base section 26 has two transverse headers: 1) a front
transverse header 28 and 2) a rear transverse header 30
connected at substantially similar top cornices 32 to two
longitudinal side headers (not shown). The front, rear
and side headers define an annular rectangle. The base
section 26 also includes four legs (three shown) located
at and connected to each cornice 32.
As shown in Fig. 27, the front header 28 has a
rotated "G" shaped cross-section and rests above the
automobile entrance. The "G" shaped cross-section forms a
stronger, lighter and more economically manufactured
member which can be easily installed and removed. In
addition, other conveyor equipment can be mounted inside
the G-shaped header frame including operating equipment
for a gate (not shown) used to block the entrance to the
conveyor 10.
As shown in Fig. 27, a plurality of internal
braces on each side of the vertical conveyor 10 connect
the frame sections 22 and 24 together and provide
structural rigidity, equalizing the loading between the
frame sections. The internal bracing includes horizontal
struts 34, 54, 56, 58 (Fig. 27), each of which is rigidly
mounted at respective ends to frame sections 22 and 24.
Lateral stability is provided by diagonal bracing 60, 62
and 64. The bracing for the top transfer guide 102 Figs.
26, 44 and 45 is shown in section 50 and includes a top
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guide strut brace 52, two top guide spacing struts 51 and
57, and four top guide braces 53, 55, 59 and 61 bolted
together to form an "X" configuration.
As shown in Fig. 26, the frame section 22 has
substantially the form of an A-frame. The frame section
22 has a base formed by header 28 and legs 38 and 40, and
has an upper section formed by diagonal columns 66 and 68.
The diagonal columns 66 and 68 are bolted at their lower
ends to respective cornices 32 of the A-frame base, and
are bolted at their upper ends to each other and to a
transverse midpoint of front column 70.
A substantially similar rear column 70 (Fig. 27)
is provided for the frame section 24. The column 70
includes a lower section 72 and an upper section 74 that
are spliced together with bolts at a vertical mid-portion
joint 76 (described below). The height of the mid-portion
joint 76 above the foundation 11 depends upon the total
number of conveyor pans and the overall height of conveyor
10. The lower column section 72 includes a solid one-
Piece weldment.
The columns 70 and 70' form a fixed tower
structure and provide a conveyor housing and a track 77
for a secondary conveyor assembly that includes a rolling
compression chain 78 (Figs. 41 and 54).
Further details of the compression chain 78 are
described below. Other details of the compression chain
78 and of columns 70 and 70' can be obtained by referring
to United States Patent Nos. 3,424,321, 3,547,281, and
3,656,608 to Lichti, the disclosure of which are hereby
incorporated by reference.
Each column 70 and 70' serves as part of a main
frame extending upwardly from the front header 28 (or the
rear header for rear frame section 24) through a joint
adjacent the top of conveyor 10 where it supports the
upper end of endless compression chain 78 located at the
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point where chain 78 crosses over from one side to the
other.
Each platform pan 16 has a slightly, upwardly
curved, rectangularly configured bottom plate 80. The
bottom plate 80 is supported at each corner by a vertical
pan hanger or post 83. Those posts 83 are located on the
same side of the bottom plate 80 and connected at the tops
thereof to a horizontal, V-shaped top pan header 84 (Fig.
41). A horizontal, tubular top strut 85 connects the
apices of each header 84 and, with two braces 86, are
welded thereto.
Referring to Figure 41, each platform pan 16 is
mounted and stabilized during its travel around conveyor
10 through a mounting assembly 87. A stub shaft 88
connects the mounting assembly 87 to the pan 16. The stub
shaft 88 extends outwardly from the other side of the apex
of each header 84 and is welded thereto. A bearing
housing 89 is mounted on the stub shaft 83. The apex of a
"v" shaped link hanger 90 (Figure 57) is pivotally mounted
to the bearing housing 89. The link hanger 90 has two
mounting coplanar arms (arm 92 shown in Fig. 41, 55 and
57), which are pivotally mounted at their respective free
ends to a compression link of the endless compression
chain 78. As shown in greater detail in Figure 57, a
bracket arm 78a extends from the compression chain 78.
The bracket arm 78g slides within a respective arm 92 and
is held thereto by a clevis pin 93 and cotter pin 93a.
Thus, a pan 16 is cantilever mounted at each end
to the corresponding conveyor subsystem 14a and 14b by a
link hanger 90.
As shown in Figs. 26, 41 and 57, the apex of a
V-shaped stabilizer 96 is also mounted to the stub shaft
88. The stabilizer 96 pivotally mounts guide shoes 98.
The stabilizer 98 stabilizes the pan 16 as it is conveyed
around the top and bottom of the conveyor 10. Mounted to
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a
the top and bottom of front and rear conveyor housing 70
and 72 are a top guide 102 and a bottom guide 104 which
contain crossing channels 100 and 102 (see also Fig. 46).
Guide shoes 98 of each pan 16 are received in the channels
100 and 101 as a pan 16 is conveyed.
In general, the vertical conveyor 10 includes a
motor means 120, a pickup drive chain assembly 122 rotated
by the motor, and a compression drive chain assembly 124,
driven by the pickup drive assembly 122. The compression
chain assembly 124 includes a compression chain 78 that
carries pans 16.
In the present invention and as shown in greater
detail of Figure 58, the motor means includes a motor 130
which is a double ended, reversible, three phase 460 AC
volt input, 500 volt DC output, regenerative electric
motor. The motor is connected to the primary drive chain
assembly 122 or each frame section 22 and 24 through drive
subassemblies 146 and 148 (Fig. 27). Each drive
subassembly 146 and 148 comprises a commercially available
universal joint 150 which connects a drive shaft 152 to
motor 130. A second, distal universal joint 154 is
connected to the distal end of the drive shaft 152.
Connected to the other end of the distal universal joint,
through a keyed fitting (not shown) is a conventional,
hydraulically actuated electrically operated friction
brake 156, which is connected and mounted to a speed
reduction gearing 158 with a splice fitting (not shown).
The housing containing the reduction gearing 158 is
mounted at the other end to the corresponding vertical
frame section 22 or 24. The reduction gearing 158 is
operatively connected to and drives the pickup drive chain
assembly 122. A hydraulic controller, indicated generally
at 159a, actuates the brake 156. The controller 159a
includes a motor 159b for driving a pump 159c for pumping
hydraulic fluid from the reservoir 159d. An accumulator
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159e, pressure switch 159f and valve 1598 are also
included.
Referring now to Figs. 26 through 31, each
pickup drive chain assembly 122 is mounted on a solid, one
piece weldment 160 which includes a lower frame section 72
of the frame portion 22. More particularly, the pickup
drive chain assembly 122 is mounted inside an interior
cavity 162 of the weldment 160.
The pickup drive chain assembly 122 (Figs. 28,
38 and 56) includes an upper toothed drive sprocket
subassembly 166 (Fig. 33), a lower toothed idler sprocket
subassembly 168 (Fig. 35), a dual drive chain subassembly
170 (Fig. 39) and five pickups arms (pickups) 172 (Fig.
36) attached to the drive chain subassembly 170 with a
through-pin 194 (Fig. 39) and rotated in a racetrack path.
In the illustrated embodiment, there are only five pickups
172. For explanation and clarity, one of the pickups 172
is shown in phantom (Fig. 28) in an advanced position at
the top of drive chain subassembly 170. In Figure 29 the
bottom-most pickup 172 has been omitted.
An upper toothed drive sprocket subassembly 166
is an integral, one-piece, molded element (Figs. 32 and
33) and includes an outside drive sprocket 176, a
substantially similar inside drive sprocket 178, and an
interconnecting, hollow tube 179. A solid shaft 180 (Fig.
31) is keyed to and mounted inside the tube 179 and
terminates on its inner end in a splice (not shown), which
in turn is mounted to and driven by reduction gearing 158.
The outer end of the shaft 180 is mounted in a bearing 183
(Fig. 31), which in turn is rigidly mounted to the
weldment 160. Each drive sprocket 176 and 178 has a mean
diameter of about 23 inches, a total of 18 standard teeth
181, and two sets of two reduced diameter teeth 181'
located 180 degrees apart. The teeth 181' terminate
inside the mean diameter circle 177. The radial size of
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0
the teeth is smaller so as to provide clearance for the
diameter of the through-pin 194.
The lower toothed idler sprocket subassembly 168
is shown in Figs. 29, 31, 34, 35, and 40 and includes an
outside idler sprocket 184, a substantially similar inside
idler sprocket (not shown), and coaxial, spaced apart
shaft 188 for respectively mounting inside and outside
idler sprockets. The 186 spacing between the adjacent
ends of shafts 188 is selected so that pickups 172 can
Pass therebetween. Idler sprocket 184 has a diameter of
about 12 1/4 inches and a total of nine teeth 185 and two
teeth 185'. The teeth 185' terminate inside the mean
diameter circle 187 and the pitch between them is deeper
so as to provide clearance for the larger diameter of the
through-pin 194.
The pickup drive chain subassembly 122 (Figs. 38
and 39) is comprised of a first roller chain 190 and a
second roller chain 192 each with five interconnected,
matched strands. The center lines of the roller chains
190 and 192 are spaced apart about 8 1/2 inches and the
two chains are interconnected with five through-pins 194.
Each of the five strands of each chain 190 and 192 is
about 34 1/4 inches long and terminates in a master link
195 which connects to the adjacent strand and which mounts
through-pin 194. In this particular embodiment, each
chain 190 and 192 has an average tensile strength of
150,000 pounds per strand. The center axis line of the
through-pins 194 is offset from a center line drawn from
chain link-pins 197 (Fig. 38).
As shown in Figs. 28, 29, 37, 38 and 39 a pickup
172 is pivotally mounted at the bottom section thereof on
each heat-treated through-pin 194.
The pickups 172 of the present invention have a
split body. Each pickup 172 includes an upper head
Portion 196 and a smaller, lower bifurcated tail portion
_ , , , ~ ...__. . __ . .
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198 that is mounted to upper head portion with bolts and
nuts (not shown). In a preferred embodiment, pickup 172
is almost 26 inches long and a little over 14 inches wide
at the top and tapers down to 7 inches wide at the bottom
of head portion 196 with a 10 inch radius curve. Each
pickup 172 is journalled onto the through-pin 194 and is
held centered thereon with snap rings 199 on either side.
A notch 200 (Fig. 36) on each side of the centerline of
pickup 172 in the upper head portion 196 engages with and
picks up a connecting pin assembly, shown at 210 (Fig 28),
in compression chain 78 (Fig. 41).
The mating ends of the head portion 196 and tail
portion are provided with mating half-circular cutouts.
The cutout in the head portion 196 has a nominal radius of
1.5 inches so it can receive a semi-circular bearing
insert 201 having integral end flanges. The cutout in the
tail portion 198 has a nominal radius of 1.25 inches,
which matches with the inner surface of insert 201. A
sleeve 202 has a thickened central portion with a central
circular slot therein for engaging the head portion. The
sleeve 202 has a reduced shoulder to support ball bearings
203 at each end. Each ball bearing supports 203 a metal
wheel 204, which has been heat treated to a surface
hardness of Rc 44/47. The wheels 203 have an outer
diameter of 4.625 inches in a preferred embodiment and
engage and ride on a bottom guard 205 (see Fig. 4), which
helps orient the pickup 172.
Located near the top of head portion 196 (Fig.
36) is a hole having a radius of 1 3/4 inches for mounting
a upper shaft 206. Mounted onto each end of shaft 206
(Fig. 37) are ball bearings 207 which in turn mount a top,
inner flanged wheel 208, which has an base outer diameter
of 4.5 inches and a flange outer diameter of 5.25 inches
in a preferred embodiment. Wheel 208 engages and is
guided by a plurality of track guides 209 (Fig. 29) and
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WO 95123266 ~ 18 41 a 9 PCTI~JS95I00934
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0
352 (Fig. 29). Mounted between upper wheel 208 and lower
wheel 204 on either side of pickup 172 is a somewhat
triangular safety lug 211 (Fig. 36) which restricts the
back fall of the pickup traversing the top guide 350 (Fig.
29) .
As shown in Figs. 28, 41 and 59 through 62, the
compression chain 78 includes a plurality of outer
compression links 212 and a plurality of inner compression
links 214, which are similar to and fit inside outer
compression links 212. The inner and outer compression
links are pivotally interconnected by connecting pin
assemblies 210. Also mounted to the inner link 214 are
two angled connecting lugs 228, only one of which is
depicted in Fig. 41, for connecting link hanger arms 91
and 92 of the pan 16.
As shown in Fig. 28, the bearing roller 238 is
engaged in one of the notches 200 of the pickups 172 as
the engaging pickup 172 lifts or pushes it and the
associated compression link upwards. Thus the weight of
the whole load on the side of the upwardly rotated
conveyor 10 is realized through bearing roller 238. The
compression chain also includes two roller 292, 294 which
fit within the formed channels 77 so that the compression
chain forms a roller chain with reduced friction as it
moves in a looped manner.
The guide and channel subassemblies for the
compression chain assembly 124 (Fig. 27) are integral
components with the other elements of the conveyor 10.
For the upper frame section 74 (Figs. 26 and 42), the
outwardmost components have spaced apart left hand guide
rails 252 and right hand guide rails 254 (Fig. 42). The
guide rails 252 include an inner guide channel 256 and an
outer guide channel 258 spaced apart to the plate 260.
The guide rails 254 are formed of an inner guide channel
262 and an outer channel 264 spaced apart to a plate 266.
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Each guide channel also serves as a vertical structural
component and has a bevelled U-shaped channel that is
welded to the upper frame section 74. The compression
chain rollers 292, 294 (Fig. 41) have a similar size,
shape and bevel to the slope of the guide channels. The
upper and lower ends of channels 252 and 254 are flared
inwardly to permit the compression links 214 to "bend
over" the top of frame sections 74 (Fig. 26) and 74s (Fig.
27) .
The guide and channel subassemblies for the
lower tower section are parts of the weldment 160 (shown
in Figs. 28, 29, 31 and 43). As shown in Fig. 43, the
weldment 160 is formed of a welded metal sheet base plate
270 having side plates 272 and 274 welded to each end to
form a somewhat rectangular box. In the middle section of
side plates 272 and 274 are slots 276 and 278 to
accommodate pickups 172 entering the channel area and
engaging connecting pin 210 of compression chain 78. The
weldment, 160, as shown in Fig. 43, also contains suitable
mounting plates, such as mounting plate 280, for mounting
the pickup dive chain assembly 122.
Directly welded to side plate 272 is a guide
rail 282. A guide rail 284 is welded to side plate 274.
The guide rail 282 has an inner guide channel 286 (Fig.
43) and an outer guide channel 288 spaced apart and
connected to side plate 274 by welding. Similarly, the
guide rail 284 has an inner guide channel 290 and an outer
channel 290 mounted spaced apart and connected to side
plate 274 by welding. Each guide channel 286, 288, 290
and 292 also serves as vertical structural component and
is a bevelled U-shaped channel that is connected to
weldment 160. Also, each U-shaped channel has the same
size and shape as channels 256, 258, 262 and 264.
The weldment 160 (Figs. 28, 29 and 31) has three
Pickup guides - the bottom guide 205, side guide 209, and
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a top guide 302. The bottom guide 205 is also shown in
Fig. 40 and has a mounting plate 304 rigidly attached at
the bottom to a square mounting tube 306. Two
substantially identical spaced guides 308 and 309 (not
g shown) are rigidly mounted at their respective bottoms to
the mounting tube 306. Each guide 308 and 309 is
comprised of a U-shaped guide plate 310 (Fig. 29) with
removably mounted tip portions 312 bolted thereto and
supporting side gusset plates 314. A flat polyurethane
guide bar 316 is mounted perpendicularly along the inner
edge of guide plate 310 (Fig. 29). The pivot pin 320 also
catches the tail portion of the pickup 172 as the pickup
172 is rotated in either direction to it. This holds the
bottom of the pickup 172 stationary, and permits the top
Portion, connected to chains 190 and 192, to be rotated
with respect to the bottom in the proper direction.
The side guides 209 have an outer guide plate
326 which extends out of the paper (Fig. 28) and an inner
guide plate 328 which is bolted to the primary drive
mounting plate 272 and 274 (Fig. 43).
The top guide 302 (Fig. 28) has a front upper
guide plate 340 rigidly mounted on the weldment 160 and a
lower guide plate 342 spaced below the upper guide plate
340. A similarly shaped rear upper guide (not shown) is
spaced 2~ inches behind the front guide. Together the
front and rear guides form a captive path 352 for the
upper wheel 208 of a pickup 196 to traverse the top of the
drive. A plurality of U-shaped jointing plates 344 are
perpendicular to the plates 340 and 342 and welded at its
respective feet to plates 340 and 342. As seen in Fig.
30, the upper guide plate 340 has a lower concave
curvilinear surface 346 with a circular upper mid-portion
cutout 348 which is symmetrical about the centerline. The
curvilinear surface 346 has a preferred lower circular
segment with a 4.75 inch radius and an upper circular
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segment with a 39.75 inch radius. The cutout 348 has a
2.25 inch radius. The bottom length of upper guide plate
is 27.5 inches. The lower guide plate 346 has a pentagon
shape with an upper convex curvilinear surface 350 that is
symmetrical about the centerline. Each half of surface
350 has a circular segment to produce a guide path 352
(Fig. 29).
As upper wheel 208 of pickup 172 enters either
end of guide path 352, it will cause pickup 172 to rotate
slightly in the direction of motion. When pickup upper
wheel 288 enters cutout 348, the top of pickup 172 is
prevented from rotating and the pickup tail will then
rotate in the direction through the center of the drive.
In this way, pickup 172 is rotated into preferred
orientation to exit the top guide path.
Referring now to Figures 51, 52 and 53, details
of the dampening action imparted to the apparatus is
described together with an improved locking device.
As a pan 16 (Fig. 26) traverses the top of the
conveyor 10, the shoes 98 (Fig. 26) are engaged in the
tracks 100 and 101 (Fig. 46) of the top transfer guide 102
(Fig. 26) and lift the transfer guide upward at the apex
of the travel and then returns as the shoes pass from the
apex of travel. The top transfer guide 102 (Fig. 44) is
comprised of the sliding guide support 107 and transfer
guide 108. The center tube 109 of the sliding guide 107
is bolted 111 to the fixed tower 22. In Fig. 51 the
vertical weight of the transfer is counter balanced by the
four shock absorbers 113 which also provide a dampening
motion for the guide movement. Inside the center tube 109
is a ground tube 114 (Fig. 52) that provides a vertical
guide for the sliding guide 107. At the bottom end of the
round tube 114 is round bar that engages a friction bar
115 and is restrained by a captive bar 116. Bellville
washers 117 provide friction between a friction plate 118
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and the captive bar 116. The friction connection is then
established between the fixed tower 22 and the sliding
guide 107 and still allow a downward movement of the
transfer guide as the compression chain shortens during
the life of the conveyor.
The bottom transfer guide 130 floats down and up
as a pan 16 (Fig. 26) traverses the bottom of the conveyor
(Fig. 26). The vertical weight of the bottom transfer
guide 130 is transferred through the two shock absorbers
10 131 (Fig. 47) and two die springs 132 (Fig. 47) to the
header 28. The shock absorbers 131 provide the dampening
of the vertical motion of the bottom transfer guide 130.
The upward motion of the guide 130 is restricted by die
spring 133 and is mounted such that it comes in contact
with the under side of header 28 (Fig. 26) during
excessive upward movements. This series of die springs
and shock absorbers keep the bottom transfer guide at a
prescribed reference point and still allow vertical motion
with a dampening effect.
when a pan 16 (Fig. 26) is at the bottom of the
conveyor 10 the lock link system 140 (Fig. 29 and 50) is
in its extended position. The height of the lock link bar
141 (Fig. 29) is such that the top of the bar 141 is 1/8
(0.125) of an inch below a bearing roller 238 (Fig. 28) of
a compression link. Normally a service brake 156 (Fig.
27) provides the holding power to resist any unbalanced
load. If one or both of these brakes 156 fail then the
compression chain 78 could move in the direction of the
unbalanced load. The lock link bars 141 are extended and
retracted by the cam motion of the actuator 143 (Fig. 50).
In Fig. 50 the lock link bars 141 are shown extended to
engage the compression chain. When the bar 141 is rotated
clockwise 180 degrees, the lock link bar will retract and
allow the compression chain 78 to move.
It should be understood that the foregoing
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20
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description of the invention is intended merely to be
illustrative thereof, and that other embodiments,
modifications, and equivalents may be apparent to those
skilled in the art without departing from its spirit.
