GB2074537A

GB2074537A - Refuse compactor

Info

Publication number: GB2074537A
Application number: GB8111060A
Authority: GB
Original assignee: Sargent Industries Inc
Current assignee: Sargent Industries Inc
Priority date: 1978-02-10
Filing date: 1979-02-09
Publication date: 1981-11-04
Also published as: DE2905029C2; GB2017043A; FR2513224B1; PH18983A; DE2954626C2; FR2513224A1; BR7900789A; CA1127118A; JPS54113118A; DE2954627C2; ZA79585B; FR2424861A1; AU528399B2; DE2905029A1; IT7947955A0; SE7901154L; GB2074537B; AR225890A1; AU4386279A; DE2954625C2

Abstract

A refuse compactor has a loading hopper (34) in communication with a storage container (8) and a packer panel (44) mounted for movement through the loading hopper to sweep through the hopper in compacting refuse therein and in moving refuse from the loading hopper into the storage container. The loading hopper has a curved inner surface (36) with a sill (40) over which refuse is inserted into the hopper. The packer panel has an edge which is positioned adjacent to the curved surface (36) within the hopper as the packer panel sweeps through the hopper, there being at a pinch point 210 shortly beyond the sill at a minimum spacing between said edge and surface such as to prevent the trapping of fingers therebetween. <IMAGE>

Description

1 GB 2 074 537 A 1

SPECIFICATION Refuse compactor

The present invention relates to refuse compactors and provides a hopper having a curved bottom wall for 70 holding the refuse and having a rear wall and a first opening in the rear wall at an intermediate position along the rear wall in a downward direction for receiving the refuse and having a front wall and a second opening in the front wall for providing for removal of the refuse, a storage body constructed to hold the refuse and having an opening communicating with the second opening in the hopper for receiving the refuse passing through the second opening in the hopper, packer panel means initially positioned in a starting position and movable downwardly in the hopper from the starting position in spaced relationship to the rear wall and the first opening for moving into the hopper the refuse inserted into the hopper through the first opening, the packer panel means being movable in spaced relationship to the rear wall of the hopper past the first opening to a pinch point where the packer panel means is spaced from the hopper by a minimal distance providing for the safe insertion of human fingers through the first opening to the pinch point, the packer panel means being movable past the pinch point forwardly along the bottom wall to the second opening to direct the refuse into the storage body through the second opening in the hopper, the packer panel means being then movable rearwardly through the hopper to the starting position, and drive means operatively coupled to the packer panel means for moving the packer panel means downwardly to the pinch point in spaced relationship to the rear wall of the hopper and then along the bottom wall forwardly to the second 105 opening and then rearwardly to the starting position. It also provides a refuse compactor having a container for storing refuse under pressure, a loading hopper in communication with the storage container, a 110 packing panel mounted for movement through the loading hopper to sweep through the hopper in compacting refuse therein and in moving compacted refuse from the loading hopper into the storage container, a curved inner surface on said loading hopper; a sill on said hopper through which refuse may be inserted into the hopper; an edge on said packing panel, which is positioned adjacent said curved surface as the packing panel sweeps through the loading hopper, and means to maintain a minimum distance between said edge and the inner curved surface at a point adjacent the sill which distance is slightly 125 greater than the depth of a human finger and to increase slightly the distance between said edge and said inner curved surface as the packing panel sweeps through said hopper, whereby, the minimum between said edge and the inner surface at the sill reduces the forces applied to the sill while protecting the worker's fingers with the increased spacing between said edge and said inner surface as the panel sweeps through the hopper providing a gripping force on refuse caught between the edge and the curved inner surface that can pull refuse over the sill into the hopper as the panel sweeps through the hopper.

The means to maintain a minimum distance between the edge of the packing panel and the inner curved surface of the hopper may increase the minimum distance slightly as the packing panel sweeps past the sill and through the hopper.

The minimum spacing between the edge of the packing panel and the curved inner surface of the loading hopper of the sill may reduce forces applied to the sill during downward movement of the packing panel while also protecting the worker's fingers. The increased minimum spacing between the edge of the packing panel and the curved inner surface of the hopper as the panel sweeps through the loading hopper may provide a gripping force on refuse caught between the edge of the packing panel and the curved inner surface of the hopper which force may pull refuse over the sill and into the hopper as the panel sweeps through the hopper.

The invention and various preferred features thereof are illustrated, by way of example only, in the accompanying drawings, in which: Fig. 1 is a side elevational view of a garbage truck utilizing a refuse compactor according to the invention; 100 Fig. 2 is a side sectional view of the tailgate structure positioned at the rear of the storage container as shown in Fig. 1 with a side plate for the tailgate removed to illustrate the position of hydraulic cylinders therein for moving a packing panel through a loading hopper; Fig. 3 is an elevation detailed view of a packing panel and a portion of the drive mechanism for the panel, viewed from the rear of the tailgate as illustrated in Fig. 1; Fig. 4 is an end elevational view, partly in section, of the packing panel taken along line 4-4 of Fig. 3; Fig. 5 is a sectional view taken along line 5-5 of Fig. 3; 115 Fig. 6 is a sectional view taken along line 6-6 of Fig. 3; Fig. 7 is a sectional view taken along line 7-7 of Fig. 3; Fig. 8 is a side elevational view of the tailgate and drive mechanism, similar to Fig. 2, with the packing panel in a rest position and the retainer panel in a closed position; Fig. 9 is a side elevational view, similar to Fig. 8, illustrating the movement of the retainer panel in a working direction through the loading hopper; Fig. 10 is a side elevational view, similar to Figs. 8 and 9, illustrating the position of the packing panel at its pinch-point location after 2 GB 2 074 537 A 2 movement of the panel in a working direction until the lower edge of the packing panel is positioned closely adjacent to a curved inner surface of the loading hopper at a point adjacent to the sill of the loading hopper; Fig. 11 is a side elevational view, similar to Figs. 8 and 10, illustrating the position of the packing panel after movement of the packing panel in a working direction through the loading hopper to force refuse through a passage having a narrowed throat and then into the refuse storing container with very high pressures being exerted on the refuse as it passes through the throat; Fig. 12 is an elevational view taken along line 12-12 of Fig. 1 illustrating the appearance of the 80 tailgate as viewed from the rear; and Fig. 12a is a sectional view taken along line 12a-1 2a of Fig. 12.

Figure 1 illustrates a garbage truck 2 having a cab 4 and a frame 6. A storage body 8 for holding refuse under pressure is positioned on the truck frame 6 with a tailgate 10 being rotatably supported at the rear of the storage body. The tailgate is in its closed position is indicated in solid line drawing as 10 and is illustrated in phantom line drawing in a raised position as 10'. During the packing of storage body 8 with refuse under pressure, the tailgate is maintained in its lowered position 10 and is fixedly positioned against the storage body. However, when the storage body 8 is filled with refuse, the tailgate is then raised to its position 10' and refuse within the storage body may be ejected through the exposed opening at the rear of the storage body.

An ejection panel 12 may be slidably positioned 100 within the storage body 8 with movement of the ejection panel serving to vary the volume within the storage body which is available for storing refuse. To fill the storage body 8 with the maximum amount of refuse, it is important that refuse within the storage body be packed at a relatively uniform pressure. To accomplish this result, the ejection panel may be positioned as shown in solid line drawing 12 at a point adjacent the rear of the storage body 8 during the initial stage of packing refuse within the storage body.

As refuse is introduced into the storage body 8 from tailgate 10, the refuse may exert pressure against the ejection panel 12. When the pressure exerted by refuse against ejection panel 12 exceeds a predetermined pressure level, the ejection panel may then be moved a small incremental distance toward the front of the storage body 8. This reduces the pressure exerted by refuse against the ejection panel 12 and the 120 packing of refuse into the storage body 8 may then continue until the pressure exerted by refuse against the ejection panel again exceeds the predetermined pressure level with the ejection panel then being again moved a small incremental 125 distance, etc. Progressive filling of the storage body 8 with refuse may then be accomplished in a uniform manner with the refuse being packed within the storage body at a relatively uniform pressure. This results in filling the storage body 8 130 with the maximum amount of refuse which is beneficial in reducing the time which is lost in trips to a landfill or refuse transfer center to discharge refuse.

When the storage body 8 is full of refuse, the ejection panel may occupy the position shown in phantom line drawing as 12' adjacent to the forward end of the storage body. To move the ejection panel 12 within the storage body 8, a telescopic cylinder 14 may be connected to a pivot 16 at the forward end of the storage body with the other end of the cylinder connected to a pivot 18 on the frame for the ejection panel. WitW the ejection panel in its forward position 12, the telescopic cylinder 14 may be completely contracted and with the ejection panel in its rearward position 12', the cylinder may be completely extended. Slide rails 20 may be positioned along either side of the storage body 8 with slots in the frame for the ejection panel 12 engaging the slide rails. The upright position of the ejection panel 12 within the storage body 8 may, thus, be maintained during movement of the ejection panel.

As indicated, the storage body 8 may include a front frame 22 positioned adjacent to the cab 4 and a rear frame 24 which supports the tailgate and engages the tailgate in its closed position.

The construction of the storage body 8, as will be described, is strong and also surprisingly light as compared with prior constructions. Thus, the storage body 8 does not require support at points intermediate its ends. Only the front and rear frames 22 and 24 may be connected to the truck frame 6 in providing a lighter construction with savings in the energy required to power the truck 2 and a reduction in the wear and tear on the highways during usage of the truck.

A tailgate cylinder 26 may be employed for raising and lowering of the tailgate 10. The tailgate 10 may be connected to the rear frame 24 through pivots 28 positioned on either side of the rear frame. The tailgate cylinder 26 may be connected to the rear frame 24 through a pivot 30 with the other end of the tailgate cylinder being connected to the tailgate 10 through a pivot 32. The cylinder is illustrated in solid line drawing in an extended condition as 26 with the tailgate in [is raised position 10'. With the tailgate in its lowered position 10, the tailgate cylinder is shown in phantom line drawing in its contracted condition as 26'. A hopper denerally indicated as 34 may be formed in the lower portion of the tailgate 10 with the hopper including a curved bottom surface 36, a loading opening 38 to receive refuse, and a loading sill 40 beneath the loading opening. A passage shown in phantom line drawing as 42 may lead from the hopper 34 into the storage body 8 and a packing panel, generally indicated as 44, may be positioned within the hopper to move refuse from the hopper through the passage into the storage body.

The packing panel 44 may include a main panel indicated in phantom line drawing as 46 and a foldable panel in phantom line drawing as 48. As 3 GB 2 074 537 A 3 will be described, the foldable panel 48 may undergo limited rotational movement with respect to the main panel 46 with the foldable panel in an extended position adjacent the surface 36 as the packing panel 44 sweeps through the hopper 34 in a working direction to move refuse through the passage 42 into the storage body 8. However, when the packing panel 44 then moves in a return direction to return to its rest position adjacent the rear of the hopper 34, the foldable panel 48 may undergo rotational movement with respect to the main panel 47 to pass over refuse within the hopper.

In discussing the various positions of the packing panel 44, the packing panel will be referred to in its extended condition when the foldable panel 48 is extended to a position adjacent the bottom surface 36 during movement of the packing panel in a working direction. The packing panel 44 will be referred to in its collapsed or partially collapsed condition as the packing panel moves in a return direction to its rest position. To provide movement of the foldable panel 48 with respect to the main panel 46, friction pads indicated in phantom line drawing as 49 may be provided in either end of the foldable panel. The friction pads 49 may have an outer surface formed of plastic with the friction pads being spring biased in an outward direction into contact with the sidewalls of the hopper 34. The friction pads 49 may, thus, cause. rotational movement of the foldable panel 48 to an extended condition as the panel sweeps through the hopper 34 in a working direction. However, on movement of the packing panel 44 in a return direction to its rest position, the frictional contact of the friction pads 49 with the sidewalls of the hopper 34 may cause rotational movement of the foldable panel 48 to a collapsed or partially collapsed position such that the foldable panel 48 may ride over 105 refuse within the hopper.

In providing movement of the packing panel 44 within the hopper 34, a relatively large hydraulic drive cylinder 50 may be used to drive the packing panel in a working direction while a smaller hydraulic return cylinder 52 may be used to move the packing panel in a return direction to its rest position. As indicated, the drive cylinder 50 may transmit rotational movement to the packing panel 44 through a drive plate 53 which is operatively connected to the packing panel and functions as a lever in providing a mechanical advantage in transmitting power to the packing panel.

A retainer panel indicated in phantom line 120 drawing as 54 may be rotatably positioned adjacent the entrance into the passage 42 from the hopper 34. During movement of the packing panel 44 in a working direction through the hopper 34, the retainer panel 54 may positioned in its opened position as indicated in Figure 1 to permit movement of refuse from the hopper into the passage. With the retainer panel 54 in its opened position as indicated in Figure 1, the lower surface of the retainer panel, in effect, forms a continuation of the upper surface of the passage 42. This is advantageous in assisting the movement of refuse from the hopper 34 through the passage 42. However, on movement of the packing panel 44 in a return direction away from the passage 42, as will be described, the retainer panel may be rotated to its closed position to at least partially block the opening between the passage and the hopper 34. With the retainer panel 54 in its closed position, the flow of refuse from the passage 42 into the hopper 34 is impeded, which improves the overall efficiency of the packing mechanism in moving refuse from the loading hopper into the storage body 8.

With the packing panel 44 in its rest position in a raised location at the rear of the hopper 34, the packing panel may be in its collapsed condition. During movement of the packing panel 34 from its rest position in a working direction, contact of the friction pads 49 against the sidewalls of the hopper 34 cause the foldable panel 48 to undergo rotational movement with respect to the main panel 46. During this movement of the packing panel 44 in a working direction, it is desirable that the foldable panel 48 should not extend out of the hopper 34 through the loading opening 38 since this could present a safety hazard. Guide rails shown in phantom line drawing as 56 may be formed on the side walls of the hopper 34. The guide rails 56 may extend inwardly to engage the foldable panel 48 and to maintain the foldable panel within the confines of the hopper as the packing panel 44 moves from its rest position to a position adjacent the hopper sill 40.

Figure 2 is a side sectional view through the tailgate 10 to illustrate the mechanism for packing refuse and moving the refuse from the hopper 34 into the storage body 8. The pivot 30 for the tailgate cylinder 26, as illustrated, may be formed within a mounting ear 71 which is affixed to the rear frame 24. The hopper 34, as viewed from the left in Figure 3, may include a sidewall 73 which may be formed from several plates connected together in any suitable fashion, such as by welding. The sidewall 73 may be positioned between the packing panel 44 and the drive mechanism for the packing panel itself such that the drive mechanism is shielded from contact with refuse. The drive cylinder 50 may be rotatably connected at its upper end to a pivot 74 that is secured to the tailgate 10. Similarly, the relatively small return cylinder 52 may be connected at its upper end to a pivot 76 secured to the tailgate 10. The packing panel 44, as illustrated, has completed its movement in a working direction through the hopper 34 to move refuse from the hopper into the passage 42. At this point, the return cylinder 52 is completely extended, as indicated by the position of the piston rod 78.

Piston rod 78 may be connected to a drive chain 80 for transmitting movement to the packing panel 44 during its movement in a return direction to its rest position.

With the packing panel 44 positioned as illustrated, the drive cylinder 50 is completely 4 GB 2 074 537 A 4 contracted as indicated by the retracted position of piston rod 82. The piston rod 82 may be connected to a drive chain 84 whose lower end is secured to a connection 86 on the drive plate 53.

As described, the drive cylinder 50 and the return cylinder 52 may work together in unison because of their connection to the drive mechanism for the packing panel 44. Thus, as the drive cylinder 50 contracts, the return cylinder 52 expands during the movement of the packing panel 44 in a 75 working direction through the hopper 34.

Similarly, during movement of the packing panel 44 in a return direction to its rest position, the return cylinder 52 contracts while the drive cylinder 50 expands.

The retainer panel 54 may be rotatably secured to a pivot 88 for movement between its open and closed positions. The retainer panel 54 is illustrated in its opened position in Figure 3 as the packing panel is moved in a working direction through the hopper 34 to move refuse from the hopper into passage 42 and into the storage body 8.

With the tailgate 10 in its lowered position, the tailgate may be fixed with respect to the storage 90 body 8 by a tailgate latch generally referred to as 90. The tailgate latch 90 may be rotatably connected to the tailgate 10 through a piVOt 92 while a support member 94 on the rear frame 24 supports a keeper 96 which is engaged by the tailgate latch 90. The tailgate latch 90 may include a threaded rod 98 with a correspondingly threaded sleeve 100 being positioned about the rod. A handle 102 may be formed at the outer end of the sleeve 100 such that turning of the handle either threads or unthreads the sleeve with respect to the threaded rod 98. An enlargement 103 on the rod 98 may engage one side of the keeper 96 while the other side of the keeper may be engaged by the inner end of the sleeve 100 with the keeper, being tightly gripped between the enlargement and the end of the threaded sleeve.

The tailgate 10 may then be securely latched to the storage body 8.

Turning to Figure 3, which is a sectional view 1 taken along line 3-3 of Figure 2, the packing panel 44 may be rotatably mounted on a pa ' ir of shafts 104 and 106. In driving the packing panel 44, a torque tube 108 may be secured to the shaft 104 with a drive plate 110 being rigidly secured to 1 the outer end of the torque tube. As illustrated, the shaft 104, the torque tube 108, the drive plate 110 and the drive plate 53 move together in unison in imparting rotational movement to the packing panel 44. Moving inwardly along the shaft 104, a separator plate 112 is joined to the drive plate 53 and a stiffening plate 114 is joined to the plate 112 and to the torque tube 103. A stiffening plate 116 may then be joined to the inner end of the torque tube 108, to the shaft 104 and to the main panel 46.

At its undriven end, the main panel 46 may be connected to the shaft 106 by a stiffening plate 118 which is joined to the shaft and also to the main panel. A support member 120 may surround130 the shaft 106 and be connected to the main panel 46 with a stiffening plate 122 being joined to the other end of the support member, to the shaft and also to the main panel. A collar 124 may be positioned about the shaft 104 with the collar engaging the exterior surface of the drive plate and a collar 126 may be positioned about the shaft 106 with the collar engaging the exterior surface of stiffening plate 122.

To provide a strong and rigid connection between the torque tube 108, the shaft 104 and the main panel 46, a pair f side plate 128 may be secured to the torque tube and also to the main panel. The side plates 128 with the stiffening plates 114 and 116, joined to the end surfaces of the side plates, form a very rigid structure througW which torque is transmitted from the torque tube 108 to the main panel 46.

As illustrated, the drive chains 80 and 84 may each be connected to the drive plates 53 and 110 through which torque is imparted to the torque tube 108 and to the packing panel 44. In connecting the drive chain 80 to plates 53 and 110, a pin 130 may be secured to the drive plates through apertures therein with a clevis 132 positioned on the pin and having secured thereto the drive chain 80. A spacer element 134 may also be positioned on the pin 130 to maintain the position of the clevis 132 relative to the pin 130.

in securing the drive chain 84 to the drive plates 110 and 53, the pivot 86 may be secured to the drive plates through apertures therein with a mounting plate 136 secured to plate 110 to retain the outer end of the pivot relative to the plate 110. A clevis 138 may be rotatably positioned on the pivot 86 with the clevis secured to the drive chain 84. As indicated, the connection between the drive chain 84 and clevis 138 is positioned a greater distance from the axes of the shafts 104 and 106 than the connection between drive chain 80 and the clevis 130. Thus, forces transmitted to packing panel 44 through the drive chain 84 may act through a greater moment arm than the forces transmitted to the packing panel by the drive chain 80. This is advantageous in providing a mechanical advantage during movement of the packing panel 44 in a working direction by the drive chain 84.

The side wall 73 of the hopper 34, as illustrated in Figure 4, may extend into a space between the plates 53 and 114 such that the drive mechanisr-h for the packing pa'hel 44 is isolated from refuse within the loading hopper 34. A second sidewall 140 of loading hopper 34 may also be positioned in close proximity to the other end of the packing panel 44. The foldable panel 48 may be rotatably mounted with respect to the main panel 46 within slots 142 formed in the main panel. Tongue members 144 joined to the foldable panel 48 may be positioned within the slots 142 with the tongue members each being rotatably secured to pins 146 which extend between the sidewalls of the slots to engage apertures formed in the tongue members. Stop members 148 may be secured to the main panel 46 to permit limited rotational 1 GB 2 074 537 A 5 movement of the foldable panel 48 with respect to the main panel 46.

The rotational movement of panel 48, as discussed previously, may be provided by friction pads 49 positioned at either end of the foldable panel 48 in contact with the sidewalls 73 and 140. As the main panel 46 is moved, the frictional engagement of pads 49 with the sidewalls 73 and 140 causes rotational movement of the foldable panel 48 with respect to the main panel 46. Additionally, the movement of the foldable panel 48 is controlled to some extent by the guide rails 56 which may extend inwardly a short distance from the sidewalls 73 and 140 to engage guide members 150 on the foldable panel 48.

Figure 4 is a sectional view taken along line 4-4 of Figure 3 which illustrates the position of foldable panel 48 with respect to main panel 46 and the manner in which rotational movement of the foldable panel is limited with respect to the main panel. As indicated, support brackets 147 secured within the foldable panel 48 by bolts 149 may rotatably engage the pins 146 mounted to the main panel 46. The support brackets 147 may be secured to the foldable panel 48 by bolts 149. Stop members 148 secured to the main panel 46 may each provide stop surfaces 152 and 154 which are engageable by a stop member 156 secured to the foldable panel 48 by a support bracket 158. As indicated, contact between the stop member 156 and stop surfaces 152 and 154 effectively limits the rotational movement of the foldable panel between the limiting positions provided by the stop surfaces.

Figure 4 illustrates the foldable panel 48 in its 100 extended condition after rotation of the foldable panel in a clockwise direction with respect to the pin 146 to engage the stop member 156 with the stop surface 152. This is the position of the foldable panel 48 when the packing panel 44 rotates in a counter- clockwise direction from its direction shown in Figure 4 in moving in a working direction through the hopper 34 as shown in Figure 2. During rotational movement of the packing panel 44 in a return direction, i.e., clockwise from its position shown in Figure 4, the foldable panel 48 may undergo rotational movement in a counter-clockwise direction until the stop member 156 contacts the stop surface 154. At this point, the packing panel 44 is in a collapsed position such that the foldable panel 48 may pass over refuse within the hopper 34 during movement of the packing panel in its return direction.

Figure 5 is a sectional view taken along the line 5-5 of Figure 4 to illustrate the construction of the main panel 46 and that of the stop members 148 which control the degree of rotational movement of the foldable panel 48. As indicated, the torque tube 108 may be directly connected to the main panel 46 which may be displaced from the axis of the torque tube. Additionally, the side plates 128 may extend from the exterior surface of the torque tube 108 to the exterior surface of the main panel 46 to provide a very strong and rigid connection between the torque tube and main panel. In previous refuse compaction apparatus, it has been necessary to drive the packing mechanism through hydraulic cylinders positioned at either end of the packing panel. However, in the present apparatus, the main panel 46 may be driven from only one of its ends. This permits a great reduction in the weight of the drive mechanism and also simplification of the drive mechanism. To achieve these beneficial results, the main panel 46 has a generally elliptical crosssectional configuration which has great strength in resisting twisting moments and in transmitting torque. The cross-sectional configuration of the main panel 46 together with the strong and rigid connection between the torque tube 108 and the main panel permits driving the main panel from only one of its ends with the torque which is imparted to the main panel then being transmitted throughout the main panel.

As indicated in Figure 5 an aperture 160 may be formed in each of the stop members 148 to rotatably support the foldable panel 48 with respect to the main panel 46. Additionally, an aperture 162 may be formed in the stiffening plate 114 to engage the support shaft 104 as shown in Figure 3.

Figure 6 is a sectional view taken along the line 6-6 of Figure 3 which illustrates the internal construction of the main panel 46 through which the foldable panel 48 is supported. To provide strength within the main panel 46 to support the foldable panel 48, transverse baffle plates 164 may be positioned within the interior of the main panel with the baffleplates being secured to the inner surface of the main panel through any suitable means such as welding. Additionally, the baffle plates 164 may then extend through the exterior surface of the main panel 46 to be integrally connected to the stop members 148. A channel 166 (shown in phantom line drawing) may then be rigidly secured to the baffle plate and an angle 168 may be connected to the stop member 148 in providing additional strength for the stop members.

Figure 7 is a sectional view taken along the line 7-7 of Figure 3, which illustrates the crosssectional configuration of the main panel 46 at its undriven end. In securing the main panel 46 to the shaft 106, an aperture 170 may be formed in the stiffening plate 122 to engage the exterior surface of the shaft. During movement of refuse from the loading hopper 34 through the passage 42 into the storage body 8, as discussed in regard to Figures 1 and 2, the movement of the packing panel 44 and the retainer panel 54 may be precisely coordinated. Thus, as the packing panel 44 is driven in a working direction through the hopper 34, the retainer panel 54 may be positioned in an opened position so that there is unimpeded flow of refuse from the hopper 34 into the passage 42 and then into the storage body 8. However, with movement of the packing panel 44 in a return direction to return the packing panel to its rest position, the retainer panel 54 is moved to 6 GB 2 074 537 A 6 a closed position with the retainer panel at least partially blocking the opening between the loading hopper 34 and the passage 42. In its closed position, the retainer panel 54, thus, functions to impede the flow of refuse from the passage 42 into the hopper 34.

When the packing panel 44 has completed its movement in a working direction with the retainer panel 54 in an opened position (see Figure 2), the retainer panel is positioned closely adjacent to the exterior surface of the main panel 46. When the movement of the packing panel 44 is then reversed in moving the packing panel in a return direction, the retainer panel 54 may then be immediately moved to its closed position. During this movement of the retainer panel to a closed position, the retainer panel may move very close to the surface of the main panel to sweep refuse from the main panel which is forced into the passage 42 by the retainer panel 54. Returning to Figure 7, the main panel 46 may include an inwardly curved surface 172 which is expressly designed to accommodate the movement of the retainer panel 54 relative to the main panel 46 as the retainer panel is moved from its opened to its closed position. The retainer panel 54 may, thus, move along the inwardly curved surface 172 in sweeping refuse from the main panel 46 which is, thereby, forced from the main panel 46 into the passage 42.

The structure and operation of retainer panel 54 are described more fully in U.K. Specification

No. 2017043.A (with reference to Fig. 9 thereof) to which attentibn is directed.

Figure 8 is the first in a series of figures which illustrate the movement of the main panel 46 and the foldable panel 48 during their movements within the loading hopper 34. As illustrated, the passage 42 includes an enlarged opening 202 which leads into the storage body 8. The passage 42 also includes a narrowed throat 204 where the walls of the passage are converged. Throat 204 and its effects and advantages are discussed and explained in U.K. Specification No. 2017043.A, to which attention is directed for further detail.

In its position shown in Figure 8, the packing panel 44 is in its collapsed rest position with the foldable panel 48 folded with respect to the main panel 46 and the packing panel in an elevated location adjacent the rear of the hopper 34. Additionally, the retainer panel 54 is in its closed position to impede the flow of refuse from the passage 42 into the hopper 34. With the packing panel 44 in its rest position, the drive cylinder 50 is completely extended and the return cylinder 52 is completely contracted. To begin the movement of the packing panel 44 in a working direction from its rest position, control rods indicated in phantom line drawing as 206 and 207 may then be moved to initiate the flow of hydraulic fluid for contraction of the drive cylinder 50, extension of the return cylinder 52 and rotational movement of the retainer panel 54 from its closed position to its opened position.

Turning to Figure 9, with movement of the 130 control rods 206 and 207 to initiate movement of the packing panel 44 in a working direction, the first event to take place is the rotational movement of the retainer panel 54 from its closed position indicated in Figure 8 to its opened position shown in Figure 9. This provides an enlarged opening 208 from the hopper 34 into the passage 42. Moreover, as illustrated, the lower surface of the retainer panel 54 with the retainer panel in its opened position forms an extension of the adjacent surface of the passage 42 to cooperate in promoting the flow of refuse from the hopper 34 into the passage and in providing high localized pressures within the passage at the narrowed throat 204.

Proceeding to Figure 10, after movement of tHe retainer panel 54 to its opened position shown in Figure 9, the packing panel 44 moves downwardly from its rest position within the hopper 34. During downward movement of the packing panel 44, the foldable panel 48 undergoes rotational movement with respect to the main panel 46 to move the packing panel from its collapsed condition to its extended condition. As previously described, this takes place because of the frictional engagement of the friction pads 49 (see Figures 1, 2 and 3) with the sidewalls of the hopper 34. During movement of the packing panel from its collapsed to its extended position, the lower edge of the foldable panel 48 is guided through contact with the side rails 56 which may maintain the foldable panel 48 within the confines of the hopper 34.

With the packing panel 44 positioned as shown in Figure 10, the lower edge of the foldable panel 48 is brought into relatively close proximity with the curved bottom 36 at a point adjacent to sill 40, which is terr-fied the "pinch point" 210. At the pinch point 210, there is a spacing between the lower edge of the foldable panel 48 and the inner surface 36 which is sufficiently large to accommodate a worker's fingers. Thus, if the worker were careless and placed his fingers at the pinch point 210 as the packing panel was descending, the spacing at the pinch point would be sufficiently great to prevent the loss of the worker's fingers. Also, as indicated, a considerable distance is provided between the outer end of the sill 40 and the pinch point 210 (generally in the' order of a foot- and-a-half to two feet) which is a safety feature, since this distance would make it difficult for the worker to have his fingers at the' pinch point.

In addition to the safety reasons for maintaining the distance between the panel 44 and the surface 36 at the pinch point 210, the distance at the pinch point reduces the impact forces exerted on the metal at the sill 40 by the descending force of the packing panel against refuse at the pinch point. In previous refuse compaction apparatus, the packing panel was brought extremely close to the inner surface of the hopper at a point adjacent to the hopper sill. The refuse was then subjected to very high shearing forces exerted thereon by the downward edge of the packing panel. To resist these high shearing forces, it was generally 7 GB 2 074 537 A 7 necessary to provide heavy reinforcement within the tailgate structure at the sill at a point approximating the location of the pinch point 210. This had the effect of increasing the overall weight of the refuse compaction apparatus. However, by providing the present distance between the foldable panel 48 and the curved inner surface 36 at the pinch point 210, it is possible to reduce the weight of the structural members in the tailgate 10 in the vicinity of the pinch point 210. This results in making the overall apparatus lighter and cheaper.

During downward movement of the packing panel 44 from its rest position, shown in Figure 9, to its position shown in Figure 10, the drive cylinder 50 may contract, with force being transmitted from the piston rod 82 to the drive chain 84 and to the drive plate 53 and torque tube 108. As illustrated, with this movement of the packing panel 44, the drive chain 84 may contact 85 the exterior surface of the torque tube 108. Thus, torque which is transmitted to the packing panel 44 may be supplied through a constant moment arm determined by the radius of the torque tube 108. During this movement of the packing panel 44, the packing panel may be moved relatively rapidly and the force applied to the packing panel by the drive chain 84 may be relatively low. Also, during this movement of the packing panel 44, the panel does not encounter great resistance from refuse within the hopper 34 since the panel is merely moving from its collapsed rest position to a position where the foldable panel 48 is in an extended condition adjacent to curved inner surface 36 at the pinch point 210.

During movement of the packing panel 44 from its collapsed rest condition in Figure 11 to its extended condition shown in Figure 10, the return cylinder 52 may undergo expansion with the piston rod 78 being extended and the drive chain 80 being wrapped about the exterior surface of the torque tube 108. As indicated, the positioning of the drive chains 80 and 84 with respect to the torque tube 108 permits unwinding of the chain 84 from the torque tube while the drive chain 80 is being wound about the torque tube without interference between the two drive chains. Further, as illustrated, the movement of the cylinders 50 and 52 may be precisely coordinated due to their mechanical interconnection through drive chains 80 and 84 with the torque tube 108. In previous refuse compaction apparatus using several cylinders for driving a packing panel, it has been difficult to coordinate the movements of the various cylinders. This has resulted from the fact that the only interconnection between the various cylinders may have been a hydraulic interconnection which, through failure of some element in the hydraulic system, could permit the various cylinders to get out of balance. This cannot 125 occur in the functioning of the present apparatus, since the mechanical interconnection of cylinders 50 and 52 insures that these cylinders must work in unison. Additionally, as will be described, the cylinders 50 and 52 are hydraulically interconnected. However, the hydraulic interconnection of cylinders 50 and 52 is augmented by their mechanical interconnection which prevents the cylinders from being out of balance in moving the packing panel 44 within the hopper 34.

As discussed, during movement of the packing panel 44 from its position in Figure 9 to its position in Figure 10, the rotational force applied to the packing panel by the drive chain 84 may be applied through a constant moment arm determined by the radius of the torque tube 108. However, on continued rotational movement of the torque tube 108 and drive plate 53 from their position shown at the right of Figure 10, the connection point 86 moves to a point positioned to the left of the shaft 104. During this movement, the drive chain 84 is moved out of contact with the exterior surface of the torque tube 108 and the driving force from the cylinder 50 through drive chain 84 is applied directly to drive plate 53 at the connection point 86. This results in progressively increasing the moment arm through which the drive chain 84 acts in providing torque for rotational movement of the packing panel 44 with the applied force to the packing panel being progressively increased as the packing panel continues its movement through the hopper 34 in a working direction. During this movement of the packing panel 44, the resistance of refuse within the hopper is greatly increased as the refuse is compacted and forced into the passage 42 and through the narrowed throat 204. Accordingly, during this movement of the packing panel 44, it is essential that a large driving force be applied to the packing panel. Also, during this movement of the packing panel 44, the rotational speed of movement of the packing panel is progressively decreased as the moment arm between the drive chain and the axis of rotation of the panel is progressively increased.

Figure 11, which is similar to Figures 8 through 10, illustrates the position of the packing panel 44 after completion of its movement in a working direction through hopper 34. During movement of the packing panel 44 from its position in Figure 10 to that shown in Figure 11, the connection point 86 between the drive chain 84 and drive plate 53 is moved further and further away from the axis of the shaft 104. This progressively increases the torque applied to the packing panel 44 through contraction of the relatively large hydraulic drive cylinder 50. This progressive increase in torque provides a progressively increasing force to refuse within the loading hopper 34 as the refuse is forced into the passage 42 and through the narrowed throat 204 to exert very high localized pressures on the refuse. Also, during this movement of the packing panel 44, the drive chain 80 is wound about the outer surface of torque tube 108 as the return cylinder 52 continues its expansion.

As indicated, the inner surface of passage 42 includes a curved surface portion 212, whose curvature is directed toward the interior of the 8 GB 2 074 537 A 8 storage body 8, to exert a horizontal flow direction to refuse, indicated as 214, which is directed into the storage body. Thus, after subjecting the refuse to very high localized pressures within the narrowed throat 204, the refuse is discharged from passage 42 into storage body 8 with the movement of the refuse directed toward the ejection panel 12 as described in Figure 1. The force exerted on the ejection panel 12 by refuse in the storage body 8, even though much less than the pressures exerted on refuse at the narrowed throat 204, may be used in providing movement of the ejection panel away from the passage 42 as the storage body 8 becomes progressively filled with refuse. This permits uniform filling of the storage body 8 with refuse which has previously been uniformly compacted at relatively high pressures within the narrowed throat 204 with the refuse being stored at the lower pressures determined by the pressure of refuse against the ejection panel 12. The increased moment arm produced by the connection of the drive chain to the connection points 86 on the drive plate 53 is indicated as 216 at the right of Figure 11.

The various members effectively operate in a servo relationship to provide an optimum compaction of the refuse in the hopper 34, and particularly in the passage or opening 42. This will be seen from the discussion at page 14 line 103 et seq. of U.K. Specification No. 2017043.A, to which reference is directed.

Figure 12 is a rear view of the truck with the tailgate 10 in a closed position as indicated by the arrows 12-12 in Figure 1. The hopper opening is indicated by the distance of the bracket indicated 100 as 218 with a portion of the figure being broken away at the left to illustrate the support structure 220 for the shaft 104. As indicated, the drive mechanism, including the relatively large drive cylinder 50 may be positioned at the left side of tailgate 10 with the packing panel 44 being driven from only one side to provide a lighter and less complex drive mechanism. By providing the drive mechanism on only one side of the tailgate 10, there may be a weight imbalance, since the side of the tailgate 10 which houses the drive mechanism may be heavier than the other side. Also, re?ction forces which are transmitted from the drive members into the support structure of the tailgate 10 will be greater on the side of the tailgate which supports the drive mechanism. For these reasons, the construction of the tailgate 10 may be strengthened, as will be indicated, to absorb the greater weight and the greater reaction forces which may be imposed on the side which houses the drive mechanism.

The tailgate 10 may include an upper beam 222, an enlarged side beam 224 and a smaller side beam 226. Turning to Figure 12a which is a sectional view taken along lines 12a-1 2a of 125 Figure 12, the movement of the foldable panel 48 is illustrated in various states within the hopper 34. In moving from its rest position to its position at the pinch point 210, the lower end of the foldable panel 48 may move along a curved path 130 indicated by the arrow A with the guide members 150 contacting the guide rails 56. During this movement, contact of the friction pads 49 on foldable panel 48 with the sidewalls of the hopper causes rotational movement of the foldable panel about the pin 146 in the direction indicated by the arrow B. In moving in the direction of arrow B, the panel 48, thus, moves from a folded position relative to the main panel 46 to an extended condition relative to the main panel. During the movement of the foldable panel 48 in a reverse direction within the hopper 34 with the panel undergoing movement in a return direction, the frictional contact between friction pads 49 and the sidewalls of the hopper 34 produces rotational movement of the panel with respect to pin 146 which is opposite to that indicated by the arrow B. Thus, during return movement of the foldable panel 48, the panel is moved from its extended condition to its collapsed or folded condition.

As described, when the panel 48 is moved downwardly to a point adjacent the pinch point 210, there is a distance between the lower edge of the panel 48 and the inner curved surface 36 which may be in the order of 1 to 2 inches. This distance provides a margin of safety for the worker who may inadvertently place his fingers within the pinch point 210. Also, this distance reduces impact forces which may be transmitted from the panel 48 to the structure of the tailgate 10 at the pinch point 210.

In its position indicated as 48', the foldable panel is positioned adjacent to the pinch point 210 and this may be the closest point of approach of the panel to the curved inner surface 36 of hopper 34. After passing beyond the pinch point 210, the panel 48 has a path of movement indicated by the line 228. As illustrated, the line 228 is positioned further away from inner surface 36 than the distance between the foldable panel 48 and the curved inner surface at the pinch point 210. This increased distance, as indicated by the bracket 230, may be in the order of two and a half to four inches, which represents a distinct difference between the present apparatus as compared with compaction apparatus of the prior art. In previous refuse compaction apparatus, it. has been customary for the packing panel to pass in very close proximity to the wall of the loading hopper during packing of refuse within the loading hopper. By having the packing panel move in ver close proximity to the curved surface of the hopper, as has been done previously, the power requirements for driving the packing panel through the loading hopper may be greatly increased. With the panel positioned very close to the wall of the hopper, there is no provision for slippage through which refuse may be permitted to slip by the panel during its movement through the hopper.

However, with the path of movement of panel 48 as indicated by line 228 in Figure 12a there is provision for slippage such that refuse may be permitted to remain in the hopper 34 by slipping by the foldable panel 48 as it is moved through the hopper 34. By providing this degree of t 1 9 slippage, the power requirements for movement of the panel 48 through hopper 34 may be reduced.

Additionally, the spacing 230 between the path of movement 228 and the curved inner surface 36 provides a further advantage which has been lacking in refuse compaction apparatus of the prior art. For example, in loading refuse into a hopper, such as hopper 34, the refuse may frequently be of a bulky nature such as, for example a large cardboard box. Due to the size of

Claims

the object being placed within the hopper only a 75 CLAIMS small portion of the object may be capable of insertion into the hopper with the balance of the article extending out of the opening of the hopper and over the sill 40. In previous refuse compaction apparatus, the downward movement of the packing panel blade into close proximity to the surface of the loading hopper would provide a shearing force which would sever a large bulky article so that the severed portion would be packed within the hopper as the balance of the bulky article fell to the ground by reason of the weight of the article extending over the loading sill. This would make it necessary to again lift the article and to feed the remainder of the article sequentially into the hopper as each working movement of the packing panel would, in effect, take another bite out of the article. By providing a distance between the edge of the packing panel, such as the distance 230 between the foldable panel 48 and the curved inner surface 36, the panel may not completely shear bulky articles inserted into the hopper. Thus, the article, if it were a cardboard box, would merely be gripped between the lower edge of the panel 48 and the inner curved surface 36. As the 100 panel 48 continues its movement through the hopper 34, the bulky article may then be dragged into the hopper by the gripping force applied to the article by the movable panel. Following movement of the panel 48 through the hopper, 105 the movement of the panel in its collapsed position during return movement through the hopper may permit the panel to pass over the refuse which has been dragged into the hopper. In this manner, instead of the panel 48 taking bites 110 out of bulky article3 as they are inserted into the hopper 34, the panel may not only pack the bulky article within the hopper in a series of packing motions, but may also lighten the job of the worker by pulling the bulky article into the hopper 115 with each succeeding movement of the foldable panel in a working direction. The movement of the panel 48 through various positions within the hopper 34, as shown in phantom line drawing, is indicated as 48". A support plate 232 may be provided on the interior of the tailgate 10 with an aperture 234 to pivotally support an operating cylinder (not shown) for the retainer panel. Also, a pivot support 236 may be provided for rotatably supporting the retainer panel 54 at a point adjacent to passage 42. Additionally, a support member 238 may be provided for supporting the shaft 106 (see Figure 3) and a pivot support 240 may be GB 2 074 537 A 9 provided for the pivot 74 (see Figure 2) for support of the cylinder 50. Other features applicable to the apparatus illustrated herein are disclosed in Figs. 2, 9, 14b to 14c, 15,16,1 6a, 16b, 17, 17a, 18, 18a, 19,1 9a, 20, 21, 21 a to 21 c, and 22 to 24 and the accompanying description of U.K. Specification No. 2017043A to which attention is directed for further detail.

1. A refuse compactor comprising:

a hopper having a curved bottom wall for holding the refuse and having a rear wall and a first opening in the rear wall at an intermediate position along the rear wall in a downward direction for receiving the refuse and having a front wall and a second opening in the front wall for providing for removal of the refuse, a storage body constructed to hold the refuse and having an opening communicating with the second opening in the hopper for receiving the refuse passing through the second opening in the hopper, packer panel means initially positioned in a starting position and movable downwardly in the hopper from the starting position in spaced relationship to the rear wall and the first opening for moving into the hopper the refuse inserted into the hopper through the first opening, the packer panel means being movable in spaced relationship to the rear wall of the hopper past the first opening to a pinch point where the packer panel means is spaced from the hopper by a minimal distance providing for the safe insertion of human fingers through the first opening to the pinch point, the packer panel means being movable past the pinch point forwardly along the bottom wall to the second opening to direct the refuse into the storage body through the second opening in the hopper, the packer panel means being then movable rearwardly through the hopper to the starting position, and drive means operatively coupled to the packer panel means for moving the packer panel means downwardly to the pinch point in spaced relati,)nship to the rear wall of the hopper and then along the bottom wall forwardly to the second opening and then rearwardly to the starting position.

2. A refuse compactor according to claim 1 in which the packer panel means is movable forwardly toward the second opening in the hopper in spaced relationship to the bottom wall of the housing and the packer panel means is movable past the second opening to direct the refuse into the second opening and then rearwardly to the starting position.

3. A refuse compactor according to claim 1 or 2 wherein the packer panel means includes a first packer panel rotatable in the hopper and a second packer panel supported by the first packer panel and rotatable relative to the first packer panel between a collapsed position and an extended position, and means disposed on the hopper for providi6g a rotation of the second packer panel from the collapsed position toward the extended position during the movement of the packer panel means to the pinch point and a rotation of the second packer panel from the extended position to the collapsed position during the rearward movement of the packer panel means to the starting position.

4. A refuse compactor according to any of claims 1 to 3 wherein the drive means is constructed to provide a rotation of the first packer panel at a relatively high speed and with low power to substantially the pinch point and a rotation of the first packer panel at a progressively reduced speed and with relatively high power from substantially the pinch point to the second opening in the hopper.

5. A refuse compactor according to any of claims 1 to 4 wherein the drive means is constructed to drive the packer panel means from only one lateral end of the packer panel means.

6. A refuse compactor according to any of claims 1 to 5 wherein the second opening is provided with an opening of progressive constriction for passage of the refuse into the storage body and means for maintaining the pressure of the refuse in the second opening within particular limits.

7. A refuse compactor having a container for storing refuse under pressure, a loading hopper in communication with the storage container, a packing panel mounted for movement through the loading hopper to sweep through the hopper in compacting refuse therein and in moving compacted refuse from the loading hopper into the storage container, a curved inner surface on said loading hopper; a sill on said hopper through which refuse may be inserted into the hopper; an edge on said packing panel, which is positioned adjacent said curved surface as the packing panel sweeps through the loading hopper, and means to maintain a minimum distance between said edge and the inner curved surface at GB 2 074 537 A 10 a point adjacent the sill which distance is slightly greater than the depth of a human finger and to increase slightly the distance between said edge and said inner curved surface as the packing panel sweeps through said hopper, whereby, the minimum spacing between said edge and the inner surface at the sill reduces the forces applied to the sill while protecting the worker's fingers with the increased spacing between said edge and said inner surface as the panel sweeps through the hopper providing a gripping force on refuse caught between the edge and the curved inner surface that can pull refuse over the sill into the hopper as the panel sweeps through the hopper.

8. A refuse compactor according to claim 7 wherein said packing panel is collapsible; said panel being movable from a collapsed rest position to an extended condition to sweep refuse from said hopper into said container; said panel being movable in a partially collapsed condition in a direction away from said container in returning to said collapsed rest position, and said packing panel in its partially collapsed condition being capable of moving over refuse within said hopper.

9. A refuse compactor according to claim 8 including a loading opening in said hopper above said sill; a side surface on said hopper, and means to guide said packing panel in a downward path within said hopper as the panel moves from its collapsed rest position to an extended condition in which the edge of said panel is adjacent to said curved inner surface at a point adjacent the sill of the loading hopper.

10. A refuse compactor according to claim 1 substantially as hereinbefore described with reference to the accompanying drawings.

11. A refuse compactor according to claim 7 substantially as hereinbefore described with reference to the accompanying drawings.

Printed for Her Majesty's Stationery Office by the Courier Press, Leamington Spa, 1981. Published by the Patent Office, 25 Southampton Buildings, London, WC2A lAY, from which copies may be obtained.