Abstract:
A baler having an improved hydraulically driven toggle mechanism for operating a baler pressing platen, improved bale ejector, and improved baler door latch. The toggle mechanism includes opposed pairs of first and second arms .Iadd.foldably joined together at their ends with their other respective ends joined to a pressing box and a pressing platen. The opposed sets of arms are mutually oriented so that as the platen is moved to a withdrawn position, the first and second arms of one set interfold compactly and without interference across the respective first and second arms of the opposed set .Iaddend. .[.and second arms, each first arm of which is a generally C-shaped bell crank arm. The first arms are connected.]. to provide a pressing mechanism which is compact but nonetheless has a long pressing stroke to facilitate production of a large bale in only a few pressing strokes. The bale ejector comprises a lifting plate having a hook which when engaged by a finger secured to the platen lifts the underside of a bale from the rear of the box as the platen is raised to cant the bale onto its forward edge permitting its easy removal from the baler. The lifting plate hook travels in a slot in the baler rear wall and is disengaged from the platen finger by a stop across the slot to drop the lifting plate to the bottom of the box in position for commencement of pressing of a new bale. And, the door latch comprises a rotatable pin and pivotal catch having arced and arcuate surfaces respectively which roll against each other during opening of the door latch to provide an easy opening door latch even when under heavy pressure from a compressed bale.

Description:
BACKGROUND AND FIELD OF THE INVENTION 
     The present invention relates in general to anti-pollution devices and in particular to refuse balers. 
     Air pollution has long been a problem. In large cities in particular the problems is especially acute. It is recognized that many deaths of the elderly and of those afflicted with respiratory diseases are attributable to air pollution. It has been noted that the death incidence of such people is markedly higher during high-pollution periods. 
     One source of air pollution is discharge from incinerators in which refuse, particularly paper and cardboard, is burned. Enormous quantities of shipping containers, alone, are disposed of daily by businesses of all types. Many food stores, for example, have long disposed of the cardboard boxes in which their canned and dry goods are delivered by burning them in incinerators. 
     Incineration as a form of disposal is objectionable on the further ground that it precludes recycling the material incinerated and is thus wasteful of natural resources. In the case of paper products disposed of by burning, new timber must be cut to product papers that could otherwise have come from the burned paper. An exploding population whose consumption per capita of combustible materials continues to rise, places an ever increasing demand on our natural resources. 
     An alternative to incineration which is nonpolluting and which permits recycling is baling. Devices which compact refuse such as paper and cardboard into a bale and secure the bale with some form of tie such as wire have long been known. 
     According to my invention I provide a baler which makes it economically practical to dispose of refuse by baling. I provide a baler which is inexpensive to construct and operate. It can be lightweight and small enough to be easily portable while nonetheless providing a large pressing force throughout a long pressing stroke to produce large, compact bales. My baler, besides being easy to operate, incorporates other labor and operating cost saving features including a specially designed, long-wearing door latch which operates with a minimum of friction to have a long life and require a minimum of maintenance. Another labor saving feature is a bale ejection mechanism which facilitates easy and quick removal of a completed bale. 
     BRIEF DESCRIPTION OF INVENTION 
     A baler having an improved hydraulically driven toggle mechanism for operating a baler pressing platen, improved bale ejector, and improved baler door latch. The toggle mechanism includes opposed pairs of first and second arms, each first arm of which is a generally C-shaped bell crank arm. The first arms are connected to provide a pressing mechanism which is compact but nonetheless has a long pressing stroke to facilitate production of a large bale in only a few pressing strokes. The bale ejector comprises a lifting plate having a hook which when engaged by a finger secured to the platen lifts the underside of a bale from the rear of the box as the platen is raised to cant the bale onto its formed edge permitting its easy removal from the baler. The lifting plate hook travels in a slot in the baler rear wall and is disengaged from the platen finger by a stop across the slot to drop the lifting plate to the bottom of the box in position for commencement of pressing of a new bale. Also, a part of my invention is a baler door latch which includes a rotatably mounted pin and a pivotally mounted catch for engaging the pin. The catch includes a concave arcuate surface which partially encircles and contacts an arced surface of the pin to latch the pin and catch. The pin also includes a projection which contacts the catch as the pin is rotated during opening of the door. As the pin is rotated, the pin arced surface rolls on the catch arcuate surface free or nearly free of sliding friction and the projection contacts the catch to pivot the catch out of engagement with the pin and unlatch the door. 
    
    
     BRIEF DESCRIPTION OF FIGURES 
     Having thus briefly described my invention, I will now describe how to make and use a preferred embodiment of the invention with reference to the accompanying drawings, wherein: 
     FIG. 1 is a front perspective view of a baler according to my invention; 
     FIG. 2 is a sectional view taken along line 2--2 of FIG. 1 illustrating the baler door latch; 
     FIG. 2A illustrates a door latch according to FIG. 2 but with the positions of the latch pin and catch reversed; 
     FIG. 3 is a front plan view of a first and of a second arm of the baler pressing mechanism shown in FIG. 1; and 
     FIG. 4 is a sectional view taken along line 4--4 of FIG. 1 illustrating the baler bale ejection mechanism and interconnection of the various components of the baler pressing mechanism. 
    
    
     DETAILED DESCRIPTION 
     Referring now to FIG. 1, a baler according to my invention is shown as 10. The baler is shown to comprise a pressing box 12 in which a pressing platen 14 is disposed for reciprocable movement along the vertical axis of the box. The box 12 has a pair of side walls 16 and 18, a rear wall 20, a bottom 22 and a charging door 24 and lower door 26. The box 12 tapers from front to back by having the rear wall 20 narrower than doors 24 and 26. The bottom 22 is provided with a pair of grooves 28 and rear wall 20 includes a pair of corresponding slots 30, one of which is hidden from view by side wall 18. Rear wall 20 is partially cut away to show a curved guideway 32 which runs from the bottom to the top of the lefthand slot 30; there is a similar guideway for the righthand slot. The grooves 28, slots 30, guideways 32, and grooves 34 (in the underside of platen 14) cooperate to facilitate securing ties around a completed bale held in a compressed state by platen 14. Platen 14 is provided on each side with a vertical combination of rollers, the lefthand combination of which is shown as 36. A similar combination of rollers is mounted in a like fashion to the righthand side of the platen but is hidden from view by side wall 18. Either the diameter of each of the rollers varies across the roller width at a rate corresponding to the taper of the wall against which it rolls, or the axis of rotation of the rollers are set parallel to the wall against which they roll. The features described thus far are not considered a part of the present invention. 
     What is considered to be my present invention, still referring to FIG. 1, are the door latch, bale ejection mechanism, and bale pressing mechanism shown generally as 38, 40, and 42, respectively. Three door latches are shown, they comprising a single elongate rotatably mounted pin 44 common to all three latches and three identical pivotably mounted catches 54. Throughout this detailed description it is to be understood that where specific dimensions, angles, shapes, or the like are recited, they are not given by way of limitation but instead are given to facilitate making and using a preferred embodiment of my invention and to illustrate the principles underlying my invention in general. For example, pin 44 in the preferred embodiment shown in FIG. 1 is a 5/8 inch diameter steel rod. However, it will be readily appreciated by one of ordinary skill in the art upon a reading of the following description of the door latch that pin 44 need not have a circular cross-section, but rather, need only have an arced surface in its circumference for rolling engagement with the catch. 
     Pin 44 is mounted for rotation to side wall 18 by mounting sockets, one of which sockets is designed 46. Pin 44 rests on a pad 50 which is welded to side wall 18. Also included in each door latch is a catch 54. Each catch is pivotably mounted by pivot 58 to a bracket 56 which in turn is secured to door 26. Bracket 56 is drilled and tapped for insertion of pivot 58 which is a 3/8 inch machine bolt; the bolt is screwed into the bracket and locked with a lock washer and nut. The center of the hole in bracket 56 for pivot 58 is about 1 inch outside the center of pin 44. 
     Further details of a door latch are evident from FIG. 2 wherein an engaged catch and pin as viewed along line 2--2 of FIG. 1 is shown. A view of the catch pivoted to a disengaged position is shown in dashed lines. Pin 44 is shown to be also provided with a projection 48 and to be connected to one end of a spring 68 which is connected at its other end to wall 18. Spring 68 acts as a pin positioning means in cooperation with the pin handle 67 and the side wall reinforcement tube 69. Spring 68 biases pin 44 in a &#34;latching&#34; position, and, although the spring alone could position the pin in latching position, the bend of handle 67 is made to even more precisely position the pin projection 48 just out of contact with the catch 54 when the pin and catch are engaged. 
     Turning now to consideration of catch 54, it is seen in FIG. 2 to have an indentation in its side which faces toward pin 44. The catch 54 is fabricated from a blank which is a 51/4 inch long piece of 1/2 inch mild-steel plate. The catch indentation includes a concave arcuate surface 60 which faces toward the catch pivot to partially encircle and contact the arced surface of pin 44. Surface 60 has the radius of a 3/4 inch diameter hole; this hole and the 3/8 inch diameter pivot hole are spaced about 21/2 inches center to center. The center of the concave surface radius and the 3/8 inch hole center are 3/16 and 3/4 inch from the side of the blank towards the pin. The foregoing dimensions and relationships insure positive engagement of the pin and catch. To further protect against the catch sliding off and disengaging from the pin, the catch pivot point is placed about one inch outside the pin center so that the catch angles back towards the pin. During opening of the latch, as pin 44 is rotated in a clockwise direction, the arced circumference of the pin rolls on the catch arcuate surface free or nearly free of sliding friction as the projection strikes against the catch strike surface 61 to pivot the catch out of engagement with the pin and unlatch the door. Also included in the catch is a spring 64 which biases the catch towards a closed position. The spring 64 is held in a hole drilled about 3/4 inch deep into bracket 56 by an L-shaped strip 66 secured to catch 54. In FIG. 2, catch 54 and bracket 56 are partially cut away to show the spring. Strip 66 in cooperation with a side and an end edge of bracket 56 limits pivoting of catch 54 to between, respectively, one position away from the pin slightly more than necessary to disengage the catch and pin and another position towards the pin slightly past the position at which the pin and catch are engaged. These positions are not critical, but are only selected to provide a freely operating door latch while avoiding excessive catch movement. With the door latch closed, spring 64 is under slight compression. As the catch is pivoted during opening or closing, spring 64 becomes progressively more compressed to provide a force for returning the catch to a closed position when the door reaches either an open or a closed position. Catch 54 is also provided with a beveled end formed by surface 62 which is a continuation of the arcuate surface and which angles away from both the side of the catch including the indentation and the catch pivot. During latching, the beveled end slidably contacts the pin to pivot the catch from the closed position towards the open position until the beveled end slides by and the indentation reaches the pin whereupon the spring 64 returns the catch to a closed position. In view 2A of FIG. 2 the pin 44 and catch 54 are shown in their alternate position; namely, with pin 44 mounted by mounting socket 46 to door 26 and catch 54 mounted by bracket 56 to side wall 18. 
     Returning now to FIG. 1, the baler pressing mechanism 42 shall now be described. The force producing means of the pressing mechanism comprises a hydraulic system which includes a hydraulic cylinder 70 and piston 72 which telescope in a conventional manner to produce a force in a direction always normal to the box vertical axis and along the two opposite directions of the piston travel. For the preferred embodiment shown, a 4 inch diameter cylinder with a 10 inch stroke which produces a force of 25,000 pounds is employed. 
     The remainder of the hydraulic system includes pumps, hoses connecting the pumps to the cylinder, and switches for controlling the fluid flow between the pumps and cylinder. These latter components of the system are mounted on the exterior of the box and may be constructed of commercially available, standard components in a well known manner. These components and their connection are incidental to the present invention. 
     A force translation means which converts at least a portion of a force produced by the hydraulic system to a re-directed force in a direction along the box vertical axis includes front and rear sets of opposed arms comprising a front pair of opposed first arms, 80 and 82, a rear pair of opposed first arms, 84 and 86, a front pair of opposed second arms, 88 and 90, and a rear pair of second arms, 92 and 94. These arms 80-94 are all of equal length; their construction shall be described later. The first arms 80-86 are each a bell crank arm .Iadd.and each is foldably and rotatably secured at its end to an end of a second arm with opposing first arms being thus secured to different ones of a pair of opposing second arms. The first arms .Iaddend..[.and.]. are each rotatably secured .Iadd.at their other ends .Iaddend.to one or the other of support members 96 and 98 which in turn are secured to the side walls of the pressing box. Support members 96 and 98 are formed of 2 by 3 inch rectangular box tubing. .[.The other end of each first arm is rotatably secured to an end of a second arm with opposing first arms being connected to different ones of a pair of opposing second arms..]. The other end of each second arm is rotatably secured to a leg of the pressing platen. The forward ones of these legs are visible in FIG. 1 and are designated as 100. All the axes about which the first and second arms 80-94 rotate are parallel to each other but normal to the box vertical axis. The legs 100 are secured to the channel irons which form the pressing platen and to front and rear reinforcement members 102 and 104 which span the width of the platen. The hydraulic system force producing means is coupled to the force translation means by a pair of cross-members each of which is pivotally connected between corresponding (front and rear) first arms .Iadd.adjacent the attachment of their other ends to the box through support members 96, 98.Iaddend.. The piston 72 is shown connected to one of the cross-members, designated 106. midway between the cross-member ends. The force translation means provides a large mechanical advantage to in turn permit use of a low pressure and thus inexpensive hydraulic system. The force translation means also permits of a wide and deep pressing box in addition to providing a long pressing stroke even through it also provides a highly compact pressing mechanism when the pressing platen is fully withdrawn. .Iadd.As shown in FIG. 1 and as will be evident from the exemplary dimensions given below, the arms 80-94 are of sufficient length and are mutually oriented so that when the platen is moved to its withdrawn position, the arms interfold to cross one another without interference, the first arms 80, 84 at one side of the box crossing and being received between the opposed first arms 82, 86 and the second arms 90, 94 at one side of the box crossing and being received between the opposed second arms 88, 92. In this collapsed, interfolded position, the arms take up little vertical space and are received in a relatively small area at the upper end of the pressing box. .Iaddend.The result is a large charging area which produces further economies as a large quantity of refuse can be loaded into the pressing box to produce a large bale in only a few pressing strokes. The compactness of the pressing mechanism is due in part to the bends in the first and second arms, particularly those of the first arms. Although the bend in each second arm may also contribute to a compact pressing mechanism, for reasons which will be explained later, for the embodiment shown, it is possible to achieve the same compactness with straight second arms. In FIG. 1, the end of arm 90 is partially cut away to illustrate that the end of arm 80 connected to the second arm is bent, as are all similar first arm ends; the cut away view makes it apparent that the first arms are folded between side pieces of the second arms as the arms approach a position parallel to the box vertical axis. For the embodiment shown, the degree of parallelity achieved is dependent upon the construction of the first arm in a manner to be described in greater detail hereinafter. 
     The shapes of a first and a second arm of the illustrated preferred embodiment of FIG. 1 are more clearly shown in FIG. 3 wherein a first and a second arm are shown drawn to scale. .Iadd.With reference to FIGS. 1 and 3, .Iaddend..[.A.]. .Iadd.a .Iaddend.first arm 150 is shown to have a first straight segment thereof, designated as dimension F.[.,.]. .Iadd.(FIG. 3). As shown in FIG. 1, this segment extends .Iaddend..[.extending.]. .Iadd.generally downwardly .Iaddend.between the end for connection with a side wall of the baler and the point for connection with a cross-member.Iadd., the arm thence extending obliquely inwardly of the box for attachment to the second arm and crossing the opposed first arm when the arms are in their folded position. .Iaddend.The other end segment is also straight and is dimensioned as G. Both segments F and G form angles, 25 and 15 degrees respectively, with the middle segment, which middle segment is likewise straight and is dimensioned E in FIG. 3. The end segments are approximately one-third and one-twelfth the length of the middle segment. The shorter segment and the bend angles are chosen to minimize the pressing mechanism heighth yet provide a lever arm, C, which will start the platen moving downward readily with the platen in a fully withdrawn position. The second arm 152 comprises only two segments which form a bend of about 58 degrees. The length of the shorter segment and the bend angle are chosen relative to the platen leg 100 heighth so that dimension B is as long as possible while dimension A approaches the heighth of platen leg 100. The first arm 150 is thus seen to have a generally C-shape and the second arm a generally L-shape. As shown in FIG. 1, the C-shapes face each other and conversely the L-shapes face away from each other when the platen is in an extended position. Each of the bends serves to improve the baler pressing mechanism heighth to stroke ratio. In the preferred embodiment of FIG. 1, for a box width of 36 inches, by utilizing curved arms having dimension as given below, a platen stroke of 40  inches for a linkage mechanism heighth of only 12 inches is provided. By contrast, the stroke and heighth for a mechanism with straight arms having lengths equal to dimensions B and D would be 30 and 22 inches respectively. 
     
         ______________________________________arm 150              arm 152C       23/4 in.     A         43/4 in.D       243/8&#34;       B         243/8 in.E       18 in.       H         6 in.F       61/8&#34;        R         58°G       11/2 in.S       15°T       25°______________________________________ 
    
     Because the first arms fold between the side pieces of the second arms, Dimension H should be as small as possible; the shorter this dimension, the closer the second arm approaches to normal to the box vertical axis when the platen is fully withdrawn. I have found that this H dimension can be reduced to 4 inches if the second arm 152 is straight instead of bent. However, no overall heighth eduction is realized as the additional amount which the first arm folds into the second arm is offset since the reinforcement members 102 and 104 are not brought above any part of the second arm. Nonetheless, some advantages are realized as when straight arms are used it is not longer necessary to cut away any of the vertical edges of the channel irons of platen 14. 
     The construction and interconnection of a first and second arm and their connection with the pressing box 12, platen 14, and cross-member 106 are shown in FIG. 4, a sectional view taken through the middle of rear wall 20 looking along line 4--4 of FIG. 1. As shown, the first arm 84 is of single piece construction and is connected to spacer pad 132 and support member 98 by a pin 134. First arm 84 is also connected to cross member 106 by a pin 108. Second arm 94 is of multi-piece construction, consisting of a pair of identical side pieces 136 and 138 which sandwich an end of the first arm 84 and a connecting member 140. A pin 133 connects first arm 84 and second arm 94, while the second arm is connected by its connecting member 140 with a pin 134 to leg 100 and reinforcement member 104. Although they have been omitted for the sake of clarity, it will be appreciated that each bearing surface of pins 108, 133, and 134 is supplied with a lubricant through grease fittings. An anti-seize and lubricating compound such as that sold under the Trade Name of Never-Seez by the Never-Seez Corporation of Broadview Illinois has been found to be an acceptable lubricant. 
     Returning again to FIG. 1, the bale ejection mechanism 40 shall now be described. It is shown to include a lifting plate 110 which normally rests flat on the bottom of the baler next to the rear wall. The depth of the plate 110 is important and should be about 1/8th the box depth. It has been found that when this dimension is increased to about 1/6th the box depth the plate tends to lift the entire bale instead of canting the bale onto its forward edge. Lifting plate 110 is secured by a spacer 111 to a bar 112. Spacer 111 is slightly thicker than the thickness of rear wall 20 to permit free vertical movement of plate 110 as well as a slight pivoting of bar 112 in a manner as will be explained later. The upper end of bar 112 terminates in a hook 114 which extends through a slot 116 in the baler rear wall and has a lower surface 117 and an upper surface 118 each of which slope from the rear wall towards the bottom of the box. The bar 112 is similarly sloped for about one-half on its width. A slot 120 in rear wall 20 permits vertical movement of plate 110. The remainder of the ejection mechanism includes a finger 122 secured to platen 14 and movable by a handle 124 into position for engagement by hook 114. Finger 122 and handle 124 are mounted to platen 14 by pipe 126 and are off-angle so that there are as a practical matter only two stable positions for the finger, one being an upright &#34;neutral&#34; position as shown in FIG. 1 wih the handle resting on the upright flange of the platen and the other being an &#34;engagement&#34; position with finger 122 lying horizontally on the platen. A stop 128 having the same slope as surface 118 is affixed across slot 116 at the point at which the hook and finger are to be disengaged. 
     The manner in which the bale ejection mechanism operates and further details of its construction shall now be described with reference to FIG. 4. It will be appreciated that during compensation of a bale, finger 122 is in the neutral position to permit platen 14 to descend below hook 114 by virtue of a cut-out in the platen which is wide enough to permit passage by hook 114 but narrow enough that finger 122 bridges the cut-out when in the engagement position. The far surface of the cut-out is shown in FIG. 4 as 121. With finger 122 in position for engagement, hook 114 is engaged by the finger as platen 14 is raised to in turn lift plate 110. Lifting of plate 110 continues until surface 118 slidably contacts stop 128 whereupon hook 114 is forced out of the slot to disengage the hook from the finger and drop the lifting plate to the bottom of the baler. As plate 110 drops, a wedge shaped projection 129 on bar 112 slides against a U-shaped strap 130 to force hook 114 into the box. During the next downward stroke of platen 14, finger 122 is still in the engagement position. As platen 14 moves downward past hook 114, finger 122 upon striking the upper surface 118 of the hook is rotated towards its neutral position. Because of the angle between handle 124 and finger 122, a finger 122 is rotated towards its neutral position, the center of gravity of the finger, handle and their connecting piece passes to the right of center whereupon the handle flips over against the platen to return the finger to its neutral position. 
     As is apparent in FIG. 4, the under surface 117 of hook 114 which contacts finger 122 slopes gradually from the rear wall downwards towards the bottom of the box. It has been found that without this slope, the hook tends to disengage prematurely. A slope for surface 117 of about 8° has been found acceptable when used with a surface 118 having a slope of about 60°. If this latter angle becomes appreciably less than 60°, such as about 50°, I have found that there is excessive friction between the stop 128 and hook surface 118. Returning to the description of lifting plate 110, it is shown to be joined by a spacer 111 to bar 112. For the embodiment shown, side and rear walls 16, 18 and 20 are 3/16 inch sheet steel. Spacer 111 is 1/4 inch thick; this thickness has been found sufficiently wide to permit pivoting of bar 112 as hook 114 is forced out of slot 116. 
     In a version of the foregoing described preferred embodiment used for compressing corrugated cardboard, the following was found suitable for producing bales weighing in excess of 150 pounds:side walls 16 &amp; 18          3/16 inch sheet steel,          80 inches high by 24          inches deep;rear wall 20   3/16 inch sheet steel,          80 inches high by 36          inches wide;pin 44         5/8 inch dia. hot rolled          steel rodmounting socket 46          1/2 by 11/2 inch bar stock          with a 5/8 inch dia. hole          for accepting pin 44;projection 48  21/2 inch long piece of 1/4          by 3/8 inch cold rolled          bar stock;bracket 56     1/2 by 11/2 inch bar stock;          0.055 in. dia. spring          wire would into 12 coils          11/4 in. long with an O.D.          of 0.295 in.;strip 66       1 inch length of 11/2 by          11/2 by 1/8 in. angle iron;hydraulics (70 &amp; 72)          an Energy Manufacturing          Inc. CTR series 4 in. dia.          and 10 in. stroke,          Monticello, Iowa;first arms 80-86          1 in. plate steel;supports 96 &amp; 98          7 gauge, 2 by 3 in. box          tubing;leg 100        5 in. piece of 1/2 by 21/2 in.          bar stock;members 102 &amp; 104          7 gauge, 11/2 by 3 in.          box tubing;cross-member 106          11/8 by 3 in. bar stock;pin 108        5 in. length of 11/2 in.          dia. cold rolled rod;plate 110      13 in. piece of 3 by 3 by          3/16 in. angle iron;bar 112        34 in. piece of 3/4 by          3/4 bar stock;hook 114       cut from 1/2 by 2 in.          bar stock;slot 116       3/4 in. wide by 11 in. long;slot 120       one in. wide by 15 in. long;finger 122     5/8 in. dia. hot rolled          steel rod;stop 128 and wedge 129          1 by 2 by 1/4 in. angle iron;strap 130      1/4 by 11/4 bar stockspacer 132     3 in. piece of 1/2 by 21/2 in.          bar stockpin 133        1 in. dia. cold rolled          steel rod;pin 134        11/4 in. dia. stress proof pin;side pieces 136 &amp; 138          1/2 by 21/2 in. bar stockconnector 140  1 by 3 in. bar stock 
     Having thus described a preferred embodiment of my invention, it will be readily apparent that numerous variations and modifications thereof are possible. For example, the hydraulic cylinder and piston are shown connected to the first arms to form a second class lever; connections which form first and third class levers are of course possible. Likewise, it would be possible to connect the force producing means between the second arms to form first, second, or third class levers. 
     Although my invention has been shown as having four first and four second arms connected as two sets of arms on each side of the box, a single set of arms on each side, preferably centered between the front and back of the platen, would suffice. Similarly within my invention is a baler having two additional sets of arms on each side of the piston and cylinder connected in tandem with the existing arms to cross-members connected to extensions of the piston and cylinder and to extensions of support members 96 and 98; such an arrangement would facilitate construction of a wider baler. 
     While the invention has been described with reference to a preferred embodiment, it is to be understood that the above modifications and variations and others not specifically mentioned are within the spirit and scope of the invention.