Note : Les descriptions sont présentées dans la langue officielle dans laquelle elles ont été soumises.
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CROSS-REFERENCE TO RELATED APPLICATION
This application is related to my copending United States
Patent Application Serial No. .. ......, filed .. ......, entitled
"Mobile Machine Containing Displaceably Mounted Power Unit Or
Power Unit Components", United States Patent Application
Serial No. ....... , filed ....... , entitled "Mobile Material
Processing Machine With Tandem Axle", United States Patent
Application Serial No. ......... , filed ........ , entitled "Dual
Disintegration Shaft Comminuting Machine", and United States
Patent Application Serial No. .......... , filed ........ , and
entitled "Conveying System For Mobile Processing Machine".
BACKGROUND OF THE INVENTION
The present invention relates to a new and improved
construction of a control system for operating a comminuting
machine. The present invention also relates to a comminuting
machine including such control system.
In its more particular aspects, the present invention
relates to a new and improved construction of a control system
for operating a comminuting machine and a comminuting machine
containing such control system and which comminuting machine
generally includes comminuting means comprising two
cooperating disintegration shafts equipped with disintegrating
members acting upon material infed into the infeed hopper.
It is known in the art to drive the two cooperating
disintegrating shafts using a common drive motor and
mechanically coupling the two disintegration shafts. As a
result, the disintegration shafts always rotate in opposite
rotational directions and at the same rotational speed. In
such arrangement it is virtually impossible to vary the
rotational speed and the rotational speed of the two
disintegration shafts independent of each other.
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A further great disadvantage of the known comminuting
machine is caused by the fact that infed pieces of hard or
high-strength material which cannot be comminuted under the
action of the two disintegration shafts, tend to damage the
disintegration shafts or the disintegrating members with which
these shafts are equipped. Furthermore, the rotating movement
of the disintegration shafts may be blocked by infed material
pieces which assume a position in which their disintegration
can not be effected and further rotation of the disintegration
shafts is inhibited by these material pieces. In such events,
time and effort must be invested to repair the damage or
remove the blocking pieces of material, as the case may be,
which causes a highly undesirable interruption in the
operation of the machine.
SUMMARY OF THE INVENTION
Therefore, with the foregoing in mind, it is a primary
object of the present invention to provide a new and improved
construction of a control system for operating a comminuting
machine and a comminuting machine which includes such control
system and which is not afflicted with the drawbacks and
limitations of the prior art constructions heretofore
2S discussed.
Another and more specific object of the invention is
directed to providing a new and improved construction of a
control system for operating a comminuting machine and a
comminuting machine which includes such control system and
which permits readily adapting the operation of the
comminuting machine to diferent comminution requrements.
Another quite important object of the present invention
is directed to a new and improved construction of a control
system for operating a comminuting machine and a comminuting
machine which includes such control system and enables the
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comminuting machine to be operated at variable rotational
speed of the disintegration shafts.
It is a further important object of the present invention
to provide a new and improved construction of a control system
for operating a comminuting machine and a comminuting machine
which includes such control system and which renders possible
driving the two disintegration shafts independent of each
other and at different rotational speeds and even at opposite
rotational directions.
A further, highly significant object of the present
resides in providing a new and improved construction of a
control system for operating a comminuting machine and a
comminuting machine which includes such control system and
which very effective prevents damage to the disintegration
shafts of the comminuting machine during operation thereof.
It is another quite important object of the invention to
provide a new and improved construction of a control system
for operating a comminuting machine and a comminuting machine
which includes such control system and which permits ready
removal of blockage of the disintegration shafts during
operation of the comminuting machine.
Now, in order to implement these and still further
objects of the invention, which will become more apparent as
the description proceeds, the control system for operating a
comminuting machine and a comminuting machine which includes
such control system, of the present development is manifested
by the features that, among other things, the disintegration
shafts are drivlngly connected to respective pressure fluid
operated drive motors which, in turn, are powered by at least
one pressure fluid main pump. Preferably, the at least one
pressure fluid main pump can be adjusted with respect to the
amount and the direction of pressure fluid delivered to the
pressure fluid operated drive motors.
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Advantageously, two pressure fluid main pumps are
provided and each one of the pressure fluid operated drive
motors is powered by a respective one ot the two pressure
fluid main pumps.
In an advantageous further development of the inventive
control system for operating a comminuting machine and a
comminuting machine which includes such control system,
pressure sensing means are provided and subjected to the
operating fluid pressure which is effective at the pressure
fluid operated drive motors. The pressure sensing means are
designed such as to permit transient reversal of the pressure
fluid operated drive motor at the occurrence of an overload,
i.e. a working pressure which exceeds a predetermined
threshold value. Due to such transient reversal in the
rotational direction, any piece of material which offers
resistance against further rotation of the disintegration
shafts in the original rotational direction, will be
temporarily released from the disintegration shafts. Upon
return to the original rotational direction, the piece of
material will assume a different position with respect to the
disintegration shafts and thus become accessible for
comminution by the disintegrating members present at the
disintegration shafts.
The aforementioned pressure sensing means may include a
single pressure sensor which is connected to the working
pressure side of both pressure fluid operated drive motors via
a pressure sensitive switch valve by means of which the
highest existing working pressure is applied to the pressure
sensor.
In a still further development of the inventive control
system for operating a comminuting machine and a comminuting
machine which includes such control system, the aforementioned
reversals may be repeated a number of times. Corresponding
switching signals issue from the pressure sensing means and
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may be applied to counting and time control means which
produce an alarm signal whenever a predetermined number of
reversals, i.e. switching signals has occurred within a
predetermined time period. If the blockage continues in spite
of repeated reversals and returns of the disintegration shafts
to the original rotational direction, such occurrence provides
an indication that the piece of material present at the
comminuting means can not be comminuted. The alarm signal thus
produced may also result in shut-off of the drive means
driving the comminuting means.
BRIEF DESCRIPTION OF THE DRAWINGS
The invention will be better understood and objects other
than those set forth above will become apparent when
consideration is given to the following detailed description
thereof. Such description makes references to the annexed
drawings wherein the same or analogous components are
designated by the same reference characters and wherein:
Figure 1 is a side view of an exemplary embodiment of the
inventive comminuting machine;
Z5 Figure 2 i9 a partially sectional rear view of the
comminuting machine as shown in Figure 1;
Figure 3 is a side view illustrating the cooperation
between disintegrating discs mounted at cooperating
disintegration shafts of the comminuting machine as shown in
Figure 1;
Figure 4 is a detailed rear view of a first conveyor in
the comminuting machine as shown in Figure 2;
Figure 5 is a view into an open side of a pressing body
used in the comminuting machine as shown in Figure 1;
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Figure 6 is a front view of the pressing body as shown in
Figure 5;
Figure 7 is a view of a link connection provided between
conveyor sections of a second conveyor in the comminuting
machine as shown in Figure 1;
Figure 8 is a schematic top plan view of the comminuting
machine as shown in Figure 1; and
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Figure 9 is a schematic block circuit diagram showing a
control system controlling the operation of the comminuting ~
machine as shown in Figure 1. ~-
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS
Describing now the drawings, it is to be understood that
only enough of the construction of the control system for
operating a comminuting machine and a comminuting machine
which includes such control system, has been shown as needed
for those skilled in the art the readily understand the
underlying principles and concepts of the present development
while simplifying the showing of the drawing. While the
illustrated exemplary embodiment is concerned with a mobile
comminuting machine including a wheel-supported chassis, it
will be understood that the inventive construction is not
limited to mobile comminuting machines but can also be
realized in stationary comminuting machines.
Turning attention now to Figure 1, there ha~ been shown a
side view of an exemplary embodiment of the inventive
comminuting machine which is mounted at a wheel-supported
chassis 10. The chassis 10 defines a front end 11 which is
provided with coupling means 13 of conventional construction
for connection to a towing vehicle like a tractor or truck,
and a rear end 14 of the comminuting machine. During operation
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of the comminuting machine, the front end 11 of the chassis 10
is supported on ground by means of a standard 8 which is
removed for travel of the comminuting machine between
different working locations. For wheel support, a rear half of
the chassis 10 is connected to a tandem axle carriage 12,
preferably in a lengthwisely adjustable manner of the type as
described in the second initially cross-referenced United
States patent application the disclosure of which is herein
incorporated by reference.
The front end 11 of the chassis 10 carries a power unit 1
for driving the comminuting machine above the tandem axle
carriage 12. The power unit 1 is of conventional construction
and will be described further hereinbelow with reference to
Figure 8.
The actual comminuting means 15 is secured to a support
frame 16 which is mounted at the chassis 10. As will be
evident from Figure 2, which is a partially sectional view of
the comminuting machine from its rear end 14, the comminuting
means 15 encompasses two disintegration shafts 17 and 19 which
cooperate by defining respective overlapping cylindrical areas
18 and 20 of action. The disintegration shafts 17,19 are
driven by respective pressure fluid operated drive motors 21
and 22 which are drivingly connected to the aforementioned
power unit 1. In the illustrated exemplary embodiment, the
pressure fluid operated drive motors 21 and 22 are coupled to
opposite ends of the respective disintegration shafts 17,19,
however, in a preferred embodiment, the pressure fluid
operated drive motors 21 and 22 are arranged in juxtaposition
and coupled to respective front ends of the disintegration
shafts 17,19.
The comminuting means 15 specifically comprise a plural
number of disintegrating discs 23 exchangeably mounted at each
one of the disintegration shafts 17 and 19. The disintegrating
discs 23 are substantially identically constructed and,
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therefore, it will be sufficient to describe only one of the
disintegrating discs 23 shown in Figure 3. The disintegrating
disc 23 has as its base a wear resistant, high strength metal
disc which defines an aperture 24 of a contour corresponding
to that of the disintegration shaft for receiving the
respective disintegration shaft 17 or 19, as the case may be,
and a circumference 25. Protruding from the circumference 25
is a circumferential sequence of a multitude of disintegrating
members, namely at least one lacerating member 27 and a plural
number of protruding rounded bulges 26 in a sequence which
extends along a predetermined part of the circumference 25,
preferably in the range of one half to three quarters, i.e. in
the range of 180 to 270 degrees of the circumference 25. In
the illustrated exemplary embodiment, a single lacerating
member 27 is disposed between the ends of the bulge sequence,
preferably, as illustrated, close to one end of the sequence
of bulges 26. The lacerating member 27 has a base 28 which is
securely affixed such as by welding to the circumference 25,
and has a generally arcuate shape which protrudes from the
circumference 25 and ends in a sharp lacerating edge 29 from
which the lacerating member 27 recedes toward the
circumference 25 and defines a recess 30.
Each disintegrating shaft 17,19 is provided with a plural
number of such disintegrating discs 23 which are exchangeably
mounted thereat at a predetermined spacing by means of spacer
rings (not shown) between adjacent pairs of disintegrating
discs 23. The spacer rings are of substantially circular shape
and have a smaller diameter than the disintegrating discs 23
such that the spacer rings do not interfere with the
cooperation between the disintegrating discs 23 of the
ad~acent disintegration ~hafts 17,19. The thickness of the
~pacer rings which determines the number of disintegrating
discs 23 mounted at the disintegration shafts 17,19, is
dependent upon the type of material to be comminuted. For
example, for comminuting wood material the spacer rings may
have a thickness which is greater than that used in the case
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of plastic material. In the latter case, the disintegrating
discs 23 are mounted with less space therebetween and the
laterally overlapping lacerating members 27 and rounded bulges
26 of the adjacent disintegrating shafts 17,19 perform more of
a cutting action.
The plural number of disintegrating discs 23 is mounted
at the respective disintegration shafts 17,19 in a manner such
that the lacerating members 27 are circumferentially offset
from each other by by a predetermined angle, preferably by 30
degrees. As indicated in Figure 3, the disintegrating discs 23
are mounted at the adjacent disintegration shafts 17 and 19 in
a manner such that the disintegrating discs 23 on one of the
two shafts have a staggered relationship to the disintegrating
discs 23 mounted at the respective other one of the two
disintegrating shafts. In other words, the disintegrating
discs 23 mounted at one of the two shafts are aligned to the
spacer rings at the other one of the two shafts. This ensures
that the lacerating members 27 and the rounded bulges 26 do
not interfere with each other during rotation of the
disintegration shafts 17 and 19 but are arranged at a partial
lateral overlap of the type which is indicated in Figure 3 and
which ~esults in a further comminuting action.
The disintegrating discs 23 and the spacer rings are
exchangeably mounted at the disintegration shafts 17 and 19 in
conventional manner by placing the same in alternating manner
from one end onto the disintegration shafts which are
supported in position at the comminuting machine. After
placement of the disintegrating discs 23 and spacer rings, a
conventional shaft nut i9 threaded onto the free ends of the
disintegration shafts 17 and 19 whereby the disintegrating
discs and spacer rings are tlghtened together. The exact
alignment on the disintegration shafts 17,19 is favorably
affected by a polygonal, preferably hexagonal cross-section of
these shafts and the aperture 24 of the disintegrating discs
23.
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During operation of the comminuting machine, the
lacerating members 27 act upon coarse infed material or larger
pieces thereof to comminute the infed material by breaking off
pieces therefrom and thereby whittling the same down to
smaller size. The rounded bulges 26 actually fulfill two main
functions: (i) firstly, by acting upon the infed material
during rotation of the disintegration shafts 17,19, such
material is forced toward the nip which is defined by the two
disintegrating shafts 17,19. Thus, the infed material is very
effectively prevented from bouncing off the surface formed by
the substantially cylindrical areas 18 and 20 of action
defined by the disintegrating discs 23. (ii) Secondly, and due
to the partial latera~ overlap between axially adjacent ones
of the rounded bulges 26, the infed material and particularly
ths smaller pieces thereof and/or the smaller pieces present
as a result of the lacerating action of the lacerating members
27, are forced into the aforementioned nip and become crushed
or cut between the cooperating axially adjacent rounded bulges
26. This results in a highly effective further comminuting
process and, at the same time, assists in forcing the infed
material through the comminuting means 15.
Further supported at the support frame 16 is an infeed
hopper 31 which has a front wall 32, a rear wall 33 and two
opposite side walls 34 and 35. All of the aforenoted walls
extend at a non-vertical inclination toward the comminuting
means 15.
A first conveyor 36 is disposed below the comminuting
means 14 and extends in the lengthwise direction of the
chassis 10. The first conveyor 36 is constructed substantially
in the manner of a conventional band or belt conveyor of which
the conveying band or belt 37 and a deflection roll 38 are
schematically indicated in Figure 2. Both ends of the
deflection roll 38 are journalled in bearings 39. A drive roll
(not shown) is placed at the other end of the first conveyor
and drivingly connected to, for example, a pressure fluid
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operated drive motor which may be constructed as a
conventional flange motor and which is not shown in the
drawing for reasons of clarity. The drive motor is drivingly
connected to the aforementioned power unit 1. The first
conveyor 36 receives comminuted material which has passed
through the comminuting means 15, and conveys the
throughpassed material to a second or rear conveyor 59 to be
described further hereinbelow.
Instead of the the construction as a band or belt
conveyor, the first conveyor 36 may also be constructed in the
manner of a conventional scraper conveyor. Such scraper
conveyor receives the comminuted material and comprises a
plate extending the conveying length. A chain drive contains
two chains extending along opposite lateral sides of the plate
and carrying transverse ledges which extend across the plate
and scrape the comminuted material along the plate during
operation of the chain drive.
The first conveyor 36 is mounted at the chassis 10 by
means of frame members 40 which extend alongside the first
conveyor 36 and which have an inverted U-shape. The frame
members 40 are secured to the support frame 16 on an underside
thereof. The frame members 40 accommodate suspension spring
assemblies one of which is schematically indicated by the
block 41 and which bear at respective tandem axles of the
tandem axial carriage 12 by means of respective support blocks
42. The rear axle of the tandem axle carriage 12 is shown in
broken lines in Figure 2 of the drawing.
As schematically illu8trated in Figure 4, the first
conveyor 36 is part of an assembly including carrier3 43 which
extend along both opposite lateral sides of the first conveyor
36. Each one of the carriers 43 is provided with a bent-off
carrier member 44 which is slidably held between retainer
members 45 and 46 which protrude toward the carrier member 44.
The lower retainer member 45 is formed by a guide rail affixed
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to an inner leg 47 of the U-shaped frame member 40. The upper
retainer member 46 is in the form of a guide member mounted at
the support frame 16. The retainer member 46 also has a guide
surface 48 cooperating with a guide surface 49 at the carrier
43 in order to guide the comminuted material passing through
the comminuting means 15 toward the first conveyor 36. The
rear ends of the bent-off carrier members 44 are affixed to
the support frame 16 by conventional securing means such as
respective bolts and linchpins (not shown). After releasing
the linchpins and withdrawing the bolts, the first conveyor 36
can be removed from the support frame 16 by rearwardly sliding
the same between the retainer members 45 and 46. Thereby, the
underside of the comminuting machine as well as the first
conveyor 36 become readily accessible for inspection and, if
need be, maintenance and repair. Also, the arrangement of the
first conveyor 36 below the support frame 16 is a space and
height saving arrangement.
In the illustrated exemplary embodiment, the comminuting
machine further includes at least one pressing body which, if
required, can be pivoted to act upon infed material to be
comminuted and urge the same into comminuting contact with the
disintegration shafts 17,19.
The pressing body 50 is pivotably mounted by means of a
pivot shaft 51 which, in turn, is pivotably mounted in slide
bearing~ 52 provided at the upper part of the support frame
16, see Figure 1. Specifically, the rear slide bearing 52 has
a divided construction in which an upper part of the slide
bearing 52 can be removed, for example, by unscrewing a
fastening ~rew. After removal of this upper bearing part, the
entire pressing body 50 can be removed by sllding the same in
the rearward direction for relea~e from the front slide
bearing 52 and by laterally removing the same from the support
frame 16. The associated side wall 35 of the infeed hopper 31
is provided with an aperture 53 for receiving the pressing
body 50 in its inoperative or retracted position.
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The pressing body 50 is constructed from a plural number
of reinforcing discs 54 which are firmly secured such as by
welding to the pivot shaft 51, see Figure 5. In the
illustrated exemplary embodiment, six such reinforcing discs
53 are provided and have a substantially circular sector
shape. The reinforcing discs 54 are fixedly connected such as
by welding to a shell plate 55 substantially along their
entire circumference so that the pressing body 50 actually
assumes the shape of a hollow, substantially cylindrical
sector body. The entire side facing the comminuting means 15,
is covered by a cover or pressing plate 56 which is affixed
such as by welding to the respective edge of the shell plate
55, the edges of the reinforcing discs 54 and the pivot shaft
51. In this manner, there is formed the pressing body 50 which
is closed on the side facing the material to be comminuted and
which can be pressed thereupon.
The intermediate reinforcing discs 54 are pairwisely
arranged and provided with mounting means 57 for connection to
an actuator 58 as shown in Figure 2 and disposed between the
reinforcing discs 54 of the respective pair. The actuator 58
of the illustrated exemplary embodiment is constructed as a
conventional pressure fluid operated cylinder-piston unit
which is powered by means of the power unit 1. The cylinder is
linked to the support frame 16 whereas the piston is linked to
the mounting means 57 of the reinforcing discs 54.
Consequently, the pressing body 50 assumes an inoperative or
retracted position when the piston is retracted, and an
operative or pressing position when the piston is extended.
Power is stepwisely applied such that, at relatively low
power, the pivoting movement is carried out whereas, in the
operative position, relatively high power can be applied in
order to exert a pre~ing actlon on the infed materlal by
means of the pressing body 50. As will be apparent from Figure
5, the pressing body 50 is connected to two actuators 58.
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The pressing body 50 is constructed in adaptation to the
aperture 53 in the associated side wall 35 of the infeed
hopper 31. In particular, the pressing body 50 assumes an
inoperative or retracted position such that the pressing plate
56 extends in the plane of the side wall 35 and the aperture
53 is substantially completely closed. It is thereby ensured
that all of the material infed into the infeed hopper 31 will
be directed to the comminuting means 15 and no parts or pieces
of the material are allowed to exit from the infeed hopper 31
other than through the comminuting means 15.
In the illustrated preferred embodiment, two
substantially identical pressing bodies 50, which are of
basically the same construction as described hereinbefore, are
placed in a mirror-image relationship in respective apertures
53 in the opposite side walls 34 and 35 of the infeed hopper
31. As explained hereinbefore, the pressing plates 56 are
flush with the respective side walls 34 and 35 in the
inoperative or retracted position of the pressing bodies 50.
In the operative position, the pressing plates 56 extend
across the comminuting means 15 close toward each other, as
illustrated in Figure 2 of the drawing by broken lines.
A second conveyor 59 constituting, for example, likewise
a band or belt conveyor, is mounted at the rear end 14 of the
comminuting machine, see Figure 1. The arrangement is such
that the second conveyor 59 cooperates with the first conveyor
36 for receiving comminuted material therefrom and further
conveying the ~ame. The second conveyor 59 includes a first
conveyor section 60 and a second conveyor section 61 which are
interconnected by a link or hinge connection 62 which is
illustrated in detail in Figure 7 in an expanded condition.
The first conveyor section 60 is provided with bushes 63
at the four corners or along top and bottom rims of its end 64
which is remote from the rear end 14 of the comminuting
machine. The bushes 63 protrude from this end 64. The second
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conveyor section 61 has an end 65 facing the end 64 of the
first conveyor section 60. This end 65 is provided with a
substantially circular disc 66 on one of its lateral sides and
a disc 67 of substantially semicircular shape on the opposite
lateral side. The discs 66 and 67 are provided with aligned
throughbores 68. The ends 64,65 of the first and second
conveyor sections 60,61 are linked to each other by placing
the bushes 63 of the end 64 of the first conveyor section 60
in between the discs 66 and 67 of the end 65 of the second
conveyor section 61, particularly in a manner such that the
bushes 63 are aligned with the throughbores 68. Then,
conventional locking means such as, for example, bolts and
associated linchpins are employed to lock the first and second
conveyor sections 60,61 to each other. To this end, the bolts
are pas~ed through the bushes 63 and the aligned throughbores
68 and locked by the linchpins. In this condition, the
mutually facing ends 64,65 of the first and second conveyor
sections 60,61 are locked to each other in a manner such that
the second conveyor ~ection 61 extends substantially in
straight continuation of the first conveyor section 60. If the
linchpin is removed from the bolt which extends through the
upper bushes 63 and throughbores 68, and the bolt is also
removed, then, the two conveyor sections 60,61 remain linked
to each other merely by the bolt extending through the lower
bushes 63 and throughbores 68.
Furthermore, the second conveyor section 61 contains a
cable mount 69 from which a cable or rope 70 or the like
extends and is fixed to the rear end 14 of the comminuting
machine at a further cable mount 71. The cable or rope 70 is
guided along a guide surface provided at the circumference of
the circular disc 66. The cable or rope 70 exerts a pull on
the end 65 of the second conveyor section 61 so a~ to ensure,
in addition to the locked link connection 62, the
aforementioned position of this conveyor section 61 in
substantially straight continuation of the first conveyor
section.
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The receiving end 73 of the second conveyor 59 is mounted
at the bottom of the rear end 14 of the comminuting machine.
To this end, a link 74 is linked to a link carrier 75 at the
rear end 14. Actuator means 76 includes a pressure fluid
operated cylinder-piston unit. The cylinder of the actuator
means 76 is linked to a cylinder carrier 77 which is secured
to the bottom of the chassis 10. The piston of the actuator
means 76 is linked to the free end of the link 74. The purpose
of this arrangement is as follows:
During operation of the comminuting machine, the second
conveyor 59 assumes the operative or extended position which
is illustrated in Figure 1. In this position, the two conveyor
sections 60 and 61 follow each other and extend substantially
in ~traight continuation at an upward inclination from the
rear end 14 of the comminuting machine. It would be
undesirable to leave the second conveyor 59 in this operative,
extended position during travel of the comminuting machine
from one working location to another. Therefore, the second
conveyor 59 is constructed such that the conveyor sections 60
and 61 can be folded into an inoperative, folded position as
indicated by broken lines in Figure 1.
In order to place the second conveyor 59 into the
inoperative, folded condition, the upper bolt and linch pin of
are removed from the link connection 62. The second conveyor
section 61 is, then, subject to the action of gravity but held
in position due to the tensioned cable 70. When, now, the
actuator means 76 is actuated by extending the piston and
thereby pivoting the link 74 upwardly toward the position as
shown by broken lines, the tension of the cable 70 is reduced
and the second conveyor section 61 is permitted to pivot in a
downward direction. During further extension of the piston and
the resulting further pivoting movement, part of the cable 70
is "wound up" on the cable guide surface provided at the
circular disc 66 and the second conveyor section 61 is
permitted to pivot further downward while the first conveyor
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section 60 continues to be upwardly pivoted. At the end of the
movement, the two conveyor sections 60 and 61 of the second
conveyor 59 are located parallel to each other and the rear
end 14, i.e. depend substantially vertically in an arrangement
S in which the first conveyor section 60 extends upwardly and
the second conveyor section 61 extends downwardly. The
dimensions of the first and second conveyor sections 60,61 are
selected such that their extended length satisfies the
operating requirements while their folded condition satisfies
existing traffic regulations.
For returning the second conveyor 59 into the operating
condition, the aforenoted sequence of movements is reversed
which is effected by retracting the piston of the actuator
means 76.
According to the schematic top plan view of Figure 8, the
power unit 1 comprises a prime mover 78 like a diesel engine
or an electric motor, if the comminuting machine is
exclusively used in places where electric power is available,
and at least one pressure fluid main pump 79 like, for
example, an axial piston pump for powering the various
pres~ure fluid operated components of the comminuting machine.
The at least one pressure fluid main pump 79 is coupled to the
prime mover 78 by conventional coupling means (not shown)
capable of compensating for rotational and axial offsets. A
cooler 80 is pivotably connected to the prime mover 79 by
means of a hinge connection 81. More specifically, the power
unit 1 preferably may be constructed in the manner of the
power unit as disclosed in the first initially mentioned
cross-referenced United States Patent Application the
disclo~ure of which is incorporated herein by reference.
Furthermore, preferably two pres~ure fluid main pumps 79
of the same type, namely axial piston pumps, are drivingly
connected to respective pressure fluid operated drive motors
21 and 22 driving the front ends of the respective
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disintegration shafts 17 and 19. Also powered thereby are the
other pressure fluid operated drive motors which are present
in the comminuting machine and which drive the first and
second conveyors 36 and 59, and the actuator means 58 and 76
which are present in the comminuting machine and which
respectively act upon pressing bodies 50 and the second
conveyor 59. This arrangement has the advantage that the
pressure fluid main~ pumps 79, the pressure fluid operated
drive motors 21 and 22 and further pressure fluid pumps can be
arranged conjointly in a readily accessible part of the
comminuting machine.
It should be noted that in this arrangement the two
disintegration shafts 17 and 19 are independently driven and
thus may rotate at different rotational speeds and in
different rotational directions. If only one pressure fluid
main pump and an associated control valve are provided, both
of the pressure fluid operated drive motors are driven at the
same rotational speed but their rotational direction can still
be reversed. Also, in the case of an overload, one or both of
the two disintegration shafts 17,19 may even be reversed so as
to thereby clear the nip defined by the two disintegration
shafts 17,19 from infed material and subject the same to
comminution upon return of the disintegration shafts 17 and 19
to the original rotational directions.
Figure 9 shows, in the form of a schematic block circuit
diagram, a control sy~tem for controlling the operation of the
aforedescribed comminuting machine and its connection with the
various pressure fluid operated components which have been
described hereinbefore.
In Figure 9, there will recognized the prime mover 78 at
the bottom on the left. The prime mover 78, as explained
hereinbefore, is in driving connection through conventional
coupling means (not shown) with two pressure fluid main pumps,
namely 79a and 79b, which may be constructed as axial piston
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pumps. A common drive shaft 82 interconnects the pressure
fluid main pumps 79a, 79b with the associated pressure fluid
operated drive motors 21,22 and further pressure fluid pumps
210,216 and 222 for respectively powering pressure fluid
operated drive motors of the first and second conveyors
212,218 and the actuators 58 and 76 which respectively act
upon the pressing bodies 50 and the second conveyor 59. Leaked
pressure fluid from the pressure fluid operated drive motors
21,22 is passed to a pressure fluid reservoir 174 through
lines or conduits 184,182 and a pressure fluid cooler 172.
Starting with the control of the pressure fluid operated
drive motors 21 and 22 which are drivingly to the respective
front ends of the disintegration shafts 17 and 19, it will be
noted that the pressure fluid main pumps 79a,79b are
conventional axial piston pumps containing a swash plate which
is conventionally adjustable for varying the pressure fluid
flow and its direction.
The adjustment of the swash plates is effected by means
of respective actuators 126,128 which are constructed in the
manner of double-acting pressure fluid cylinders. In the
following, there will only be described the actuator 126 and
it will be understood that the actuator 128 is constructed and
oper-ated essentially in the same manner. The cylinder is
subdivided into two cylinder chambers by means of an adjusting
piston. Control pressure can be selectively applied either to
the left-hand or the right-hand cylinder chamber, as the case
may be, while correspondingly either the right-hand or the
left-hand cylinder chamber is connected to the pressure fluid
reservoir 174. As a result, such actuator may exert pressure
fluid forces in two opposlte directions.
The operation of the actuator 126 is governed by means of
an electromagnetically operable control valve 130. The control
valve 130 is conventionally constructed in the manner of a
4/3-way valve. Two connectors of the control valve 130 are
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21
connected to respective ones of the two cylinder chambers in
the actuator 126, a further connector receives the control
pressure and a still further connector leads to the reservoir
174.
The control valve is spring-loaded and normally held in a
neutral, central position in which all four of the connectors
are blocked. Two magnet coils are provided for adjusting the
control valve in basically two different limiting valve
positions. In a first limiting valve position, control
pressure is applied to the right-hand cylinder chamber of the
actuator 126 whereas the left-hand cylinder chamber of the
actuator 126 is connected to the reservoir 174. In a second
limiting valve position, control pressure is applied to the
left-hand cylinder chamber in the actuator 126 whereas the
right-hand cylinder chamber is connected to the reservoir 174.
A valve housing 132 of the control valve 126 is mechanically
coupled through a conventional and, therefore, only
schematically indicated mechanical connection 134 to the
adjusting piston of the actuator 126.
As a result, and in the aforementioned first limiting
valve position which the control valve 130 assumes upon
energization by the respective magnet coil, control pressure
is applied to the right-hand cylinder chamber whereas the
right-hand cylinder chamber will be connected to the reservoir
174. Consequently, the adjusting piston of the actuator 126
will move to a left limiting position in Figure 9. The valve
housing 132 will follow the movement of the adjusting piston,
i.e. the valve housing 132 will also move to the left until
the control valve again assumes the neutral, central position
and the connection to the cylinder chambers i8 blocked. To
acieve the second limiting valve position, opposite movements
occur in essentially the same manner with the result that the
adjusting piston is moved in the opposite direction into the
opposite limiting position. The application of control
pressure to the respective cylinder chambers and thus the
2~2~'3 ~
corresponding displacement of the respective adjusting pistons
may be continuously variable or in a preselected number of
steps in conventional manner.
Since the displacement of the adjusting piston in one or
the other direction causes corresponding tilting of the swash
plate in one or the other corresponding direction, pressure
fluid will flow in one or the other direction depending upon
the direction of displacement of the adjusting piston of the
actuator 126. The amount or extent of displacement will also
be governed by the electromagnetically controlled control
valve 130. The pressure fluid operated drive motor 22 which is
in driving connection with the disintegration shaft 19, is
connected to the pressure fluid main pump 79a through the
lines or conduits 136 and 138. Therefore, the drive motor 22
will rotate the disintegration shaft 19 in a rotational
direction determined by the direction of displacement of the
adjusting piston in the actuator 126 and at a rotational speed
determined by the amount of displacement of the adjusting
piston in the actuator 126.
Essentially corresponding movements occur upon
electromagnetic adjustment of the control valve 129 and
application of control pressure to the actuator 128. The valve
housing 129 likewise is mechanically coupled to the adjusting
piston of the actuator 128 by means of a mechanical connection
133. The pressure fluid operated drive motor 21 which is in
driving connection with the disintegration shaft 17, is
connected to the pressure fluid main pump 79b through the
lines or conduits 140 and 142. Therefore, the drive motor 21
will rotate the disintegration shaft 17 in a rotational
direction determined by the direction of displacement of the
adjusting piston in the actuator 128 and at a rotational speed
determined by the amount of displacement of the adjusting
piston in the actuator 128.
2~21~3~
23
It should be noted that the control valves 129 and 130 as
well as the actuators 126 and 128 are operated independently
of each other. As a consequence, the pressure fluid operated
drive motors 21 and 22 the respective disintegration shafts 17
and 19 are also operated independent of each other.
The control pressure effective at the actuator 126 and
the associated control valve 130 is supplied by means of a
control pressure pump 140 which likewise is driven by means of
the common drive shaft 82. A pressure limiter 146 limits the
control pressure to a predetermined value. A pressure
accumulator 150 is provided to maintain the control pressure.
Correspondingly, a control pressure pump 147, a control
pre~sure limiter 148 and a pressure accumulator 152 are
provided in conjunction with the actuator 128 and the control
valve 129.
A pressure limiter 154 is connected to both the lines or
conduits 136 and 138 interconnecting the pressure fluid main
pump 79a and the pressure fluid operated drive motor 22. The
pressure limiter 154 thus limits the working pressure
prevailing at the pressure fluid operated drive motor 22
independent of the feed direction of the pressure fluid main
pump 79a and the rotational direction of the drive motor 22
resulting therefrom. In corresponding manner, a pressure
limiter 158 is connected to both the lines or conduits 140 and
142 intercoonecting the pressure fluid main pump 79b and the
pressure fluid operated drive motor 21. The pressure limiter
15~ thus limits the working pressure prevailing at the
pres~ure fluid operated drive motor 21 independent of the feed
direction of the pressure ~luid main pump 79b and the
rotational direction of the drive motor 21 resulting
therefrom.
Furthermore, a pressure responsive switch 164 is
controlled by means of a pressure responsive switch valve 162
which interconnects the lines or conduits 136 and 140 which
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2~21~3~
24
respectively connect the pressure fluid main pump 79a with the
pressure operated drive motor 22 and the pressure fluid main
pump 79b with the pressure fluid operated drive motor 21. The
pressure responsive switch valve 162 provides connection
between the two lines or conduits 136 and 140 in the reversed
operating condition in which the disintegration shaft 19
rotates in clockwise direction and the disintegration shaft 17
in counterclockwise direction because under such condition the
working pressure exists in both lines or conduits 136 and 140.
The pressure responsive switch 164 reacts to the occurrence of
a predetermined excess pressure by causing emergency shut-off
of the comminuting machine.
A further pressure responsive switch valve 166 is
connected between lines or conduits 136 and 138. The purpose
of this pressure responsive switch valve 166 is to apply the
working pressure, i.e. the higher pressure of the pressures
prevailing in the lines or conduits 136 and 138 to a pressure
limiter 168. The pressure limiter 168 passes any pressure
fluid which is relieved as a result of a pressure limiting
action, to the pressure fluid reservoir 174 through a line or
conduit 170 and the pressure fluid cooler 172. In
corresponding manner, a further pressure responsive switch
valve 176 is connected between lines or conduits 140 and 142.
The purpose of this pressure responsive switch valve 176 is to
apply the working pressure, i.e. the higher pressure of the
pressures prevailing in the lines or conduits 140 and 142 to a
pressure limiter 178. The pressure limiter 178 passes any
pressure fluid which is relieved as a re~ult of a pressure
limiting action, to the pressure fluid reservoir 174 through a
line or conduit 180,182 and the pressure fluid cooler 172.
The two l~nes or conduits 138 and 142 are feed lines or
conduits in which the working pressure prevails when the
pressure fluid operated drive motor 22 rotates the
disintegration shaft 19 in counterclockwise direction and the
pressure fluid operated drive motor 21 rotates the
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2121-~3~
disintegration shaft 17 in clockwise direction. A pressure
responsive switch valve 190 is connected to the lines or
conduits 138 and 142 through respective lines or conduits 186
and 188. The pressure responsive switch valve 190 connects
that one of the two lines or conduits 138,142 which has the
higher pressure, with a pressure sensor 192. In the event that
the rotation of the disintegration shafts 17,19 is blocked by
a non-disintegrable piece of infed material, the working
pressure experiences a strong rise which is detected by the
pressure sensor 192. The pressure sensor 192 will respond if a
pressure threshold value is exceeded which is distinctly above
the standard operating pressure.
In the event of a response of the pressure sensor 192 to
an excessive pressure build-up above the working pressure in
the line or conduit 138, the control valve 130 is reversed for
a predetermined period of time T. As a consequence, the
displacement of the adjusting piston in the actuator 126 is
reversed and thus also the feed direction of the pressure
fluid main pump 79a. The working pressure now is applied to
the line or conduit 136 and also the rotational direction of
the pressure fluid operated drive motor 22 and the associated
disintegration shaft 19 is reversed. The clamped, blocking
piece of material is thereby released and, after the
predetermined time period T has elapsed, the control valve 130
and the adjusting piston of the actuator 126 are returned into
their original position. As a result, the pressure fluid main
pump 79a assumes the original feed direction and the drive
motor 22 and its disintegration shaft 19 are rotated in the
original rotational direction so that the comminuting
operation is restarted. The circuit producing this sequence of
events, is illustrated in the block diagram shown in the top
left-hand corner of Figure 4 where there are shown the
pressure sensor 192, the reversing switch 198 which receives
the output signal of the pressure sensor 192 via an input 194
and which produces at a first output 196 an output signal for
effecting reversal of the control valve 130.
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26
If the excessive pressure build-up occurs in the line or
conduit 142, the corresponding sequence of events is effected
at the pressure fluid main pump 79b and the associated
pressure fluid operated drive motor 21 and disintegration
shaft 17. In the event that the control means 130 ccontrols
both of the pressure fluid main pumps 79a,79b or a common
pressure fluid main pump is provided for both the pressure
fluid operated drive motors 21 and 22, both of the pressure
fluid operated drive motors 21,22 and the associated
disintegration shafts 17,19 will be temporarily reversed.
It may occur that even after repeated reversal the
comminuting means 15 remain blocked, for example, because the
clamped piece of material which produces the blockage, is not
released by repeated reversal, because the piece of material
can not be disintegrated at all even if repeatedly subjected
to the comminuting action, or because the piece of material
offers an unduely high resistance to the comminuting action.
Therefore, the aforedescribed operation would repeat itself
endlessly without producing any result if no countermeasures
are taken. For this reason, an alarm signal is triggered and
brings the comminuting machine to standstill, after multiple
repetitions of the transient reversal have occurred within a
pre~etermined period of time. Instead or additionally, the
alarm signal may be or may include an optical or acoustic
alarm indication.
The circuit for producing this sequence of events, is
shown by the block diagram at the top left-hand corner of
Figure 9. Thus, a second output 202 of the reversing switch
198 produces a signal which i~ applied to a counter 200 which
counts the number of switching or reversing operations and in
which a predetermined number of counts is pre~et. At the
occurrence of each reversing operation, a pulse appears at a
3s third output 204 of the reversing switch 198. This pulse will
set a timer 206 which is connected to a reset input of the
counter 200 and which may be, for example, a monostable
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212~ ~3~
27
multivibrator, which sets a predetermined counting period.
After this counting period has elapsed, the counter 200 will
be reset to zero. If during this counting period the preset
count nO is exceeded, the alarm signal will be produced at an
output 208 of the counter 200.
Each reversing ~aoperation will produce a pulse at the
third output 204. This pulse determines the start of the
predetermined counting period and sets the timer 206. Further
pulses will not affect the timer 206 as long as the timer 206
has not been rese~ to the original state or condition. If less
than nO pulses appear during the predetermined counting
period, the counter 200 will be reset to 0 and an alarm signal
will not occur. The alarm signal will only be triggered if the
number nO of pulses, which appear during the predetermined
counting period which is preset by the timer 206, is exceeded.
Furthermore, a pressure fluid pump 210 is connected to
the cGmmon drive shaft 82 and feeds pressure fluid to a
pressure fluid operated drive motor 212. A pressure limiter
214 is provided for limiting the pressure which is effective
at the drive motor 212. The pressure fluid operated drive
motor 212 i8 in driving connection with the drive roll of the
first conveyor 36 which is located below the comminuting means
15. A still further pressure fluid pump 214 is connected to
the common drive shaft 82 and feeds pressure fluid to a
pressure fluid operated drive motor 218. A pressure limiter
220 is provided for limiting the pres~ure which is effective
at the drive motor 218. The pressure fluid operated drive
motor 218 is in driving connection with the drive roll of the
second conveyor S9 which is located at the rear end 14 of the
comminuting machine.
Yet a further pressure fluid pump 222 is connected to the
common drive shaft 82 and feeds pressure fluid to the actuator
means 58 and 76 respectively operating upon the pressing
bodies 50 and the first conveyor section 60 of the second
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2121~
28
conveyor 59 for producing the desired pivoting movements
thereof. The pressure fluid is delivered to the respective
pressure fluid operated cylinder-piston units of the actuator
means 58 and 76. Such units include double acting cylinders as
schematically indicated in Figure 9. The pressure fluid feed
thereto is controlled by means of respective 4/3-way valves
224 and 230 via respective twin check valves 226,228 and
232,234. The 4/3-way valve 224 is mechanically switched in
correspondence with the pivoting movements of the pressing
10bodies 50. The 4/3-way valve 230 is mechanically switched in
correspondence with the pivoting movements of the first
conveyor section of the second conveyor 59.
A number of modifications are envisaged in the
aforedescribed control system. Thus, instead of providing
separate control valves 129 and 130 for each one of the
pressure fluid main pumps 79a and 79b, only one control valve
such as the control valve 130 may be provided as a common
control valve conjointly with additional lines or conduits
leading from the common control valve to the cylinder chambers
of the actuator 128. Also, in a simplified version, the
control valves 129,130 or the common control valve may just
apply control pressure to the cylinder chambers of the
respective actuators and thus displace the adjusting pistons
merely between the neutral, central position and the selected
one of the two limiting positions. In such arrangement, the
pressure fluid supply to the pressure fluid operated drive
motors 21 and 22 can only be varied between zero and a maximum
value in either rotational direction, i.e. the pressure fluid
operated drive motors 21 and 22 and their associated
disintegration shafts 19 and 17 can only be driven at the
~ame, namely the maxlmum rotational speed and in the selected
one of the two rotational directions.
35In a further variant, the circuitry for operating the
control valve and thereby the actuator for reversing the
pressure fluid main pump and thereby the pressure fluid
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2~21~
29
operated drive motor of the disintegration shafts may be
displaced by correspondingly operating mechanical devices.
Such mechanically operated devices may include, for example,
angle transmitters or cam members.
While there are shown and described present preferred
embodiments of the invention, it is to be distinctly
understood that the invention is not limited thereto, but may
be otherwise variously embodied and practiced within the scope
of the following claims. Accordingly,
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