Bale discharging pusher for baling machines

The present invention provides a bale bumper for use on a machine capable of forming cylindrical bales of crop stock. The invention comprises a pair of swingable legs pivoted off each side of the machine and actuated by the tractor hydraulic system to engage a cylindrical bale during the bale discharge sequence and to push it rearwardly of the bale forming machine, thereby reducing the danger of machine damage from engagement with the bale following discharge and increasing baling efficiency by reducing the number of maneuvers normally associated with a bale discharge.

The present invention relates in general to machinery for forming 
cylindrical bales of crop stock, commonly known as round bales, and in 
particular to apparatus for discharging the bale from such a machine. 
BACKGROUND OF THE PRESENT INVENTION 
Machinery for forming bales of crop stock, e.g., of clover or alfalfa hay, 
are long known in the art. In a representative operation, the crop stock 
would be mowed and then gathered into a windrow. A baler, either 
self-propelled or pulled by some other machine such as a farm tractor, 
would then be driven down the windrow from which it would gather the crop 
stock, form a bale in a bale-forming chamber, and then discharge the bale 
from the baler. Typically such machines form bales having either a 
cylindrical configuration or a rectangular configuration. 
Balers for forming cylindrical bales were at one time designed and 
constructed to form bales capable of being easily handled manually by an 
adult. Such bales would typically be approximately two feet long, have a 
maximum diameter of about three feet, and weigh at most 100 lbs. With the 
reduction of available farm labor, as well as its increasing costs, 
however, in the last two decades there has been a move to produce 
cylindrical bales of a larger size to make a baling operation less labor 
intensive. These bales typically have a length of about five feet, a 
maximum diameter of about five feet, and weigh approximately 1,500 lbs. 
Obviously a single farmer with the appropriate mechanical bale-handling 
apparatus is capable of handling a large quantity of crop when in such a 
form. 
Each bale shape had its advocates and its particular advantages and 
disadvantages. One of the disadvantages that round balers suffer in 
comparison to square balers is that a square baler is capable of a 
continuous baling operation. That is, unlike the round baler, a square 
baler is able to continue baling while discharging a tied-up bale of crop 
stock. With a round baler it is necessary to discontinue pick up of the 
crop from the windrow while the baler finishes forming the bale, ties the 
bale with wire or twine, and discharges the bale from the rear of the 
baler to the ground. Additionally, it is usually necessary to back the 
round baler up prior to discharging the bale so that no crop stock would 
be passed over by the baler. These extra movements increase baling time or 
if not performed resulted in un-baled crop stock being left in the field. 
These problems were further exacerbated with the movement to the larger 
balers 
The large round balers typically include front and rear portions forming a 
bale formation chamber therebetween. These portions are often pivotally 
attached at the tops thereof such that the rear portion or gate may be 
moved apart from the front portion for discharging of a bale in a manner 
similar to the opening of a clam shell. Because it is necessary that the 
rear portion of the baler be closed before baling recommences, when 
discharging a bale with the present large apparatus it is necessary to 
stop the forward movement of the baler, reverse directions, back up a 
predetermined distance, discharge the bale, move forward, close the rear 
portion, and then begin baling again. Failure to perform such a maneuver 
would result in the necessity of discharging a bale and then pulling ahead 
a sufficient distance to close the rear portion of the baler, resulting in 
unbaled crop stock being left on the ground. A further disadvantage of 
such balers is that on occasion the rear portion of the baler can strike a 
discharged bale when closing and can suffer damage thereto. 
Prior art attempts addressing these problems have taken several approaches, 
namely, the ramp, the conveyor, the pusher, and the kicker. Typical of the 
ramp approach are U.S. Pat. No. 3,974,632 to VanderLely, U.S. Pat. No. 
4,559,770 to Mast, and U.S. Pat. No. 4,566,380 to Clostermeyer et al. The 
VanderLely patent discloses a ramp that extends rearwardly and 
groundwardly of the baler for bale discharge. The ramp is formed by a 
lower portion of the rear wall of the baler. The Mast patent discloses a 
ramp that is pivotally connected to the baler frame so that the bales may 
be rolled to the ground upon bale discharge. Similarly, Clostermeyer 
teaches a ramp attached to the rear of the baler and down which a bale 
rolls upon discharge. 
U.S. Pat. No. 4,683,815 to Van Ryswyk teaches the attachment of a 
chain-driven conveyor system to the rear of the baler. Upon discharge of a 
bale from the rear of the baler the conveying system moves the bale 
rearwardly of the baler to a discharge position on the ground. The 
conveyor system is pivotally mounted to the baler and projects rearwardly 
therefrom. Upon opening of the rear portion of the baler, the conveyor 
pivots downwardly in response to the weight of the bale such that its 
rearwardmost position contacts the ground. 
Representative of the pusher-type solution are U.S. Pat. Nos. 4,779,527 to 
Ardueser et al, and 4,483,247 to Coeffic. These patents teach the use of a 
U-shaped pusher mechanism pivotally attached to the front section of the 
baler that is used to push a discharged bale away from the baler after 
discharge and to retain the bale in such a position while the rear gate of 
the baler closes. 
Representative bale kickers are found in U.S. Pat. Nos. 4,458,587 to 
Jennings, 4,406,221 to Parrish et al, and 4,206,587 to Freimuth et al. 
Each of the three referenced patents teaches a bale kicker comprised of a 
U-shaped structure attached to the rear portion of the baler. The U-shaped 
structure is spring loaded such that as a discharged bale rolls over the 
crossbar portion of the "U," the coil spring is stretched thereby allowing 
the U-shaped kicker to pivot towards the ground. As the center of gravity 
of the bale passes over the bar rearwardly of the baler, the spring begins 
to retract, pivoting the U-shaped member upwardly and providing additional 
impetus to the bale as it is discharged from the baler. This additional 
rearward impetus is referred to as a kick and results in the bale being 
discharged slightly further rearwardly from the baler than it otherwise 
would. 
Each of the prior art attempts just described fail to completely solve the 
problems of bale discharge. For example, while basically a simple device, 
the kicker mechanisms require springs of great strength in order to 
provide a rolling impetus to a bale which may weigh as much as 1,500 lbs., 
and thus they may fail to move the bale far enough away from the baler. In 
addition, as the kicker returns to its position, it does so with a force 
directly proportional to the spring constant of the springs used. This can 
result in loud clanging noises as the kicker returns to its position as 
well as in jarring motions and structural damage to the baler. The ramps 
also provide a simple solution, however they can fail to produce the 
desired results when baling is carried on in terrain that is not flat. The 
more complicated solutions of the conveyor and the pusher present 
additional mechanical breakdown problems. For example, the conveyor system 
described relies upon a chain-driven conveyance system to move a bale away 
from the gate. The pusher of the referenced patent utilizes a shock 
absorbing system to work against the energy of the spring assembly 
utilized in the mechanism taught there. 
Thus there is a need for a bale discharge apparatus which performs several 
desirable functions. First, such an apparatus should ultimately deposit a 
bale on the ground at a desired position rearward of where it would be if 
it simply fell from the rear of the baler. Second, it should retain the 
discharged bale at the desired discharge position while the rear portion 
of the baler closes, thereby preventing the rear portion of the baler from 
coming in contact with a discharged bale. Third, such an apparatus should 
retain a discharged bale at the desired position so that the operator can 
stop the baler, discharge a bale therefrom, and then continue onward with 
no back up maneuvering necessary, and therefore no unbaled crop left in 
the field. Fourth, such an apparatus should be mechanically simple and 
impart minimal reaction forces to the baler from the bale discharge. 
BRIEF SUMMARY OF THE PRESENT INVENTION 
It is a principal object of the present invention to provide new and 
improved bale discharge apparatus that is not subject to the foregoing 
disadvantages. 
It is another object of the present invention to provide new and improved 
apparatus useful on a cylindrical baler that reduces the amount of baler 
maneuvering that an operator must perform. 
It is a further object of the present invention to provide new and improved 
apparatus useful on a cylindrical baler that reduces the possibility of 
damage to the baler during bale discharge. 
It is yet another object of the present invention to provide new and 
improved apparatus useful on a baler forming cylindrical bales that 
reduces the amount of unbaled crop stock left in the field. 
According to the present invention there is provided a bale discharge 
apparatus for deposition of a bale at a position a predetermined distance 
behind the baler and for keeping the bale in its said position, said 
apparatus being movable between retracted and extended positions during 
bale discharge. The bale discharge apparatus of the present invention 
includes a pair of stanchions pivotally attached to a baler, one on each 
lateral side thereof, boom means pivotally attached to the free end of 
each stanchion, a bumper comprising a bale-engaging cross-member extending 
between the free ends of the boom means, and actuation means for extending 
and retracting said apparatus at desired intervals. 
Each boom means of the apparatus may include a boom and a restraining and 
supporting means pivotally attached between the baler and each boom. In a 
preferred embodiment of the present invention, each stanchion includes a 
pair of elongated bars pivotally attached to the front section. The 
actuation means includes an hydraulic cylinder attached at one end to a 
stationary position of the baler and attached at the other end to a pivot 
point on the boom means. In one embodiment the actuation means may be 
attached to the boom and in another to the restraining and supporting 
means. The restraining and supporting means are pivotally attached at one 
end at a pivot point on the boom and to the front section of the baler at 
the other end. The bumper includes a crossbar and a pair of arms attached 
at each end thereof, the free ends of the arms being attached to the 
booms. In a preferred embodiment the crossbar includes at least one freely 
rotating roller means. 
In operation, as the rear portion or gate of the baler opens following bale 
formation and tying for discharge of the bale, the actuation means extends 
the bumper rearwardly of the baler. As the bale is discharged from the 
baler it passes over the bumper to a discharge position more distant from 
the rear of the baler than it would had it fallen simply onto the ground. 
The bumper extends and rolls the bale rearwardly of the baler. The bumper 
acts to hold the bale at the discharge position while the rear portion of 
the baler begins to close. When the rear portion of the baler has closed 
sufficiently so as to avoid damaging contact with the bale, the actuation 
means retracts the bumper back to its rest position. 
There is also provided in accordance with the present invention an 
hydraulic system including a valve useful in the operation of the just 
described bale discharge apparatus and other such apparatus of the pusher 
type. The hydraulic system interconnects the actuation means for the bale 
discharge apparatus and the rear gate portion of the baler to provide a 
single system capable of coordinated movement of the bale discharge 
apparatus and the baler gate. The hydraulic circuit includes a reservoir, 
a hydraulic pump for pumping hydraulic fluid into and out of the 
reservoir, and a valve means connected to the pump and in parallel to the 
gate and bumper actuation means, the valve means allowing uninterrupted 
flow between the reservoir and the gate actuation means and allowing 
selective flow to the bumper actuation means. 
An embodiment of the valve means includes a valve housing having a fluid 
flow path therethrough providing uninterrupted flow of hydraulic fluid to 
the gate actuation means from the reservoir. The housing further includes 
a valve biased in a closed position on a valve seat by a biasing means 
such as a coil spring, the valve being operative by a plunger in response 
to the movement of the rear gate and being actuated when the rear gate 
reaches a desired open position. When actuated, the valve unseats from the 
valve seat allowing hydraulic fluid to flow through a branch passage into 
the bumper actuation means, which will preferably comprise an hydraulic 
cylinder. 
The foregoing delineated objects of the invention as well as others will 
become apparent to those skilled in the art when the following detailed 
description of the invention is read in conjunction with the accompanying 
drawings. Throughout the drawings like numerals refer to similar or 
identical parts.

DETAILED DESCRIPTION OF THE PRESENT INVENTION 
FIG. 1 illustrates in phantom a baler 10 of the type used for forming 
cylindrical bales of crop stock. Baler 10 includes a pair of side walls 12 
only one of which is shown and a rear gate portion 14 forming a bale 
forming chamber interiorly thereof. Baler 10 is supported by a pair of 
ground engaging wheels 16 that are each attached to a hub plate 18, only 
one of which is shown. Each wheel 16 is mounted for rotation on a stub 
axle 20, which is an individual axle portion of short length that does not 
extend from one side of the baler 10 to the other. 
Baler 10 is drawn through a field by a tractor attached to a hitch portion 
21. Baler 10 picks up windrowed crop stock and forms it into a cylindrical 
bale in a known manner. After a bale has formed within the bale forming 
chamber of baler 10, an operating means such as dual action hydraulic 
cylinder 22 (shown in phantom) is actuated to open rear gate portion 14 
such that the formed bale of crop stock may be discharged therefrom. As 
best seen in FIG. 3, cylinder 22 is comprised of a cylinder 22b attached 
at one end thereof to a gate cylinder pivot 23 along side wall 12 and a 
reciprocally extensible piston 22a attached at the other end of cylinder 
22 to rear gate 14 at a gate cylinder pivot point 24. Preferably, a pair 
of such gate actuation cylinders are mounted in such a manner on the 
opposite sides of the baler. 
Also shown in FIG. 1 is an embodiment of a bale discharge apparatus or bale 
bumper 50 in accordance with the present invention. Apparatus 50 is shown 
in a retracted position as it would be mounted on baler 10. In describing 
apparatus 50 it will be understood that bumper 50 is substantially 
symmetrically configured with respect to left and right sides thereof and 
that the description of one side will also be descriptive of the other 
side. 
Referring principally now to FIGS. 1 and 2, bale bumper 50 will be 
described in detail. In FIG. 2, bale bumper 50 is shown in its retracted 
position where it is positioned during bale forming operations and in 
phantom in its fully extended position following discharge of a formed 
bale from the baler. Bumper 50 includes a pair of stanchions 51 pivotally 
connected to baler 10 on opposite sides thereof. Each stanchion 51 may 
include a pair of stanchion bars 52, as best seen in FIG. 1, that are each 
attached at a lower end 53 to a first pivot point 54 disposed on baler 10. 
At an upper stanchion end 55 each stanchion is pivotally attached to boom 
means 45 comprising a boom 62 at a boom end 63. The attachment between 
boom end 63 and upper stanchion end 55 forms a second pivot point 64 
providing a pair of swingable legs having a knee joint defined by second 
pivot point 64. When bumper 50 is retracted, the stanchions 51 and boom 62 
are oriented generally vertically but are angularly disposed with respect 
to each other. When bumper 50 is in an extended position, stanchions 51 
and boom 62 have a generally horizontal orientation and are substantially 
aligned with each other, as shown in phantom lines in FIG. 2. 
The other end 65 of boom 62 terminates at an arm 66 at an arm end 67 
thereof. Arm 66 may be welded to boom 62 or formed integrally therewith. 
The other end 68 of arm 66 is attached to a cross member 70, as best seen 
in FIG. 1, that extends between the ends of the arms disposed on opposite 
sides of the baler and that engages the bales during discharge from the 
baler. Arms 66 are attached to booms 62 such that when bumper 50 is in its 
retracted position, arms 66 extend generally forwardly beneath the body of 
baler 10. In a preferred embodiment, cross member 70 comprises a roller 
rotatably supported between booms 62. When the swingable legs are 
retracted, cross-member 70 may be disposed beneath side walls 12 such that 
each bale will strike it as the bale is discharged downwardly and will 
move rearwardly of the baler in response to such contact. As shown in FIG. 
1, cross-member 70 may be disposed at a level below that of wheel hub 18 
when the bumper 50 is in a retracted position. 
Extension and retraction of bale bumper 50 is provided by a bale discharge 
operating means 71 that is supported at one end 74 thereof by an 
attachment to baler 10 at a pivot point 76. The other end 78 of operating 
means 71 is attached to boom 62 at a pivot point 80. Operating means 71 
operates to move the swingable legs between their retracted or collapsed 
position during bale formation and their extended position during bale 
discharge. Preferably, operating means 71 is also a dual action hydraulic 
cylinder comprised of a cylinder 71B and a reciprocally extensible piston 
71A. In any event, it is desirable that both operating means 22 and 
operating means 71 be of the same type such that the systems for actuating 
rear gate 14 and bumper 50 may be tied together into one system. 
In a preferred embodiment, the boom means 45 of bale discharge apparatus of 
the present invention also includes a restraining and supporting means 82. 
As best seen in FIG. 1, restraining and supporting means 82 includes a 
pair of closely spaced, parallel bars 83 and is attached at an end 84 to 
baler 10 at a pivot 85 and at the other end 86 to a pivot 87 disposed on 
boom 62. Means 82 provide vertical support to bumper 50 during extension 
and retraction of bumper 50. Means 82 may also prevent overextension of 
booms 62 thereby inhibiting movement of second pivot point 64 to a point 
on or below a line drawn between first pivot point 54 and boom end 65. 
Should such an overextension occur, bumper 50 may not retract properly and 
may be damaged. 
As further shown in FIG. 2, the discharge apparatus of the present 
invention may be attached to the lower portion of baler 10. Thus, 
discharge apparatus or bale bumper 50 may include a vertical support 
member 56 attached at an end 57 thereof to the tubular housing of axle 20 
and attached at the other end 58 to a horizontal support member 59 at an 
end 60 thereof Members 56 and 59 may be joined by welding and braced as 
shown to provide a mounting support structure for the bale bumper assembly 
50. In this configuration pivot point 54 for stanchion 51 is disposed at 
and attached to end 61 of horizontal member 59. Attachment of bumper 50 to 
baler 10 close to the ground is preferable because of better leverage 
obtainable with such an attachment but the present invention also 
contemplates its attachment anywhere on front sidewalls 12. In the 
configuration shown in FIGS. 1 and 2, operating means 71 is attached to 
the forward end 61 of horizontal support member 59. 
FIG. 11 shows an alternate embodiment of apparatus 50. In this embodiment, 
bumper 50 is mounted on a fender 46, which is in turn rigidly attached to 
stub axle 20. Fender 46 includes a vertically disposed member 46a, and a 
horizontal member 46b and a diagonal member 46c, the latter two members 
46b and 46c being attached to member 46a so as to extend in a direction 
outwardly from the body of baler 10 and over wheel 16. Actuation means 71 
and stanchion 51 are attached to member 46b while restricting and 
supporting means 82 is attached to member 46c. The pivoting arc of 
stanchions 51 is therefore substantially parallel to the plane of rotation 
of wheel 16 and, in fact, is in substantial alignment therewith. This 
manner of mounting bumper 50 to baler 10 has the advantage of eliminating 
the extension of stub axles 20, which may be necessary when bumper 50 is 
mounted as shown in FIGS. 1 and 2. The extension of stub axles 20 in turn 
makes baler 10 wider and thus may complicate the cross-country 
transportation of some models of baler 10 from manufacturer to distributor 
because of roadway width restrictions. 
The embodiment shown in FIG. 11 further shows an alternate location for 
attaching actuation means 71 to boom means 45. Thus, as shown in the 
Figure, actuation means 71 is attached to restraining and supporting means 
82 at a pivot point 82a. This attachment presents mechanical advantages 
over the attachment shown in FIGS. 1 and 2 in that the cylinder of 
actuation means 71 is directed substantially horizontally. Thus comparing 
FIG. 2 with FIG. 11, it can be seen that in FIG. 2 actuation means 71 is 
initially disposed in a generally upright position and extends and pivots 
to a substantially horizontal position. In FIG. 11, however, actuation 
means begins and ends in a substantially horizontal position. Since it is 
desired to exert a substantially horizontal, rearwardly directed force, 
attachment of actuation means 71 to pivot point 82a on restraining means 
82 rather than to pivot point 80 on boom means 41, as shown in FIGS. 11 
and 2 respectively, provides an additional mechanical advantage to the 
bumper 50 and therefore facilitates the rearward extension of the bale 
bumper and, most importantly, the rearward movement of a discharged bale. 
The embodiments shown in FIGS. 1, 2 and 11 may form a retrofit kit for 
attachment to existing balers or it may be utilized on newly manufactured 
models. In either situation those skilled in the art will recognize 
variations, modifications, or substitutions that may be made in the manner 
in which the present invention is attached to the baler, without departing 
from the spirit and scope thereof. 
OPERATION OF THE PRESENT INVENTION 
A typical discharge sequence illustrating the operation of the bale 
discharge apparatus is shown in FIGS. 3, 4 and 5. In all three figures, 
wheel 16 is shown in phantom to more fully illustrate the operation of the 
bale discharge apparatus. Arrow 90 in FIG. 3 indicates the direction of 
baler movement. As indicated in FIG. 3, a bale 88 has been formed in the 
bale formation chamber of baler 10 in a manner well known in the art, and 
rear gate portion 14 of baler 10 has begun to open by swinging in an 
upward arc indicated by arrow 91. Bale 88 begins to drop from baler 10 to 
the ground as indicated by arrow 92. Bale 88 is shown in a discharge 
position 88a wherein the bottom of the bale has dropped to a position 
below the stub axles 20 such that it may, if desired, contact cross member 
70 of bale discharge apparatus 50. Operating means 71 acts to move bumper 
50 from its retracted position as indicated by letter A in FIG. 3 to its 
fully extended position as shown in phantom in FIG. 2 and in solid lines 
in FIG. 5. Thus in FIG. 4, as bale 88 continues to fall rearwardly of 
baler 10 to a position 88b, bumper 50 may extend to a position B along an 
arc indicated by arrow 93. As bale 88 drops from baler 10 the extension of 
bumper 50 and the consequent contact between bale 88 and cross member 70 
results in a lifting force as well as a rearwardly directed pushing force 
being applied to the bale as it falls as indicated by arrow 93. That is, 
because this arc has an upward direction, cross member 70, which is in 
contact with bale 88 in position 88b, is exerting a lifting force on bale 
88 as indicated by arrow 94. Force 93 slows the fall of bale 88 to the 
ground while imparting a rearward velocity to bale 88. This has the 
advantageous result of depositing bale 88 on the ground rearwardly of 
where it would land without the use of the bale discharge apparatus of the 
present invention. 
Bale 88 continues to fall rearwardly until, as shown in FIG. 4, it lands on 
the ground in position 88c. As further shown in FIG. 4, as bale bumper 50 
continues to extend rearwardly to a position as indicated by the letter C, 
cross member 70 is still in contact with bale 88 as it moves to a position 
88d and is continuing to exert an upward lifting force as indicated by 
arrow 95 on bale 88. As the bale bumper 50 moves to its fully extended 
position as indicated by the letter D in FIG. 5 bale 88 has moved to a 
position 88e rearward of the opening and closing arc of rear gate portion 
14. Bale 88 has been moved away from baler 10 a sufficient distance such 
that rear gate portion 14 may close without interference from bale 88. The 
added length given to bale bumper 50 by the knee joint assembly comprised 
of pivotal stanchion 51 and boom 62 permits the contact of the bale bumper 
50 with the bale for a greater distance behind the baler, thus assuring 
that the discharged bale will be moved rearwardly out of the closing path 
of rear gate 14. 
It should be noted that up until a full extension as indicated by letter D, 
the bale bumper of the present invention has been exerting an upward force 
on bale 88 throughout the entire discharge sequence. Furthermore, it 
should be noted that cross member 70 through which the lifting force is 
exerted on bale 88 is disposed at a position below the rolling axis 89 of 
the bale 88. In addition to the benefit previously noted of the more 
rearwardly discharged position of bale 88 on the ground, this lifting 
action below the rolling axis of the bale has a further advantage in that 
it facilitates the rearward rolling of the bale. This lifting action is 
advantageously pivoted off the lower portion of baler 10, which is 
structurally the strongest part of baler 10, through booms 62 and 
stanchions 51, rather than from the upper central gate portions as in 
prior art bale ejector designs This distinctly different pivot location 
reduces wear and tear on the baler and makes a bale discharge a smoother 
operation In other words, with the present invention there are less 
forward and rearward reaction forces imparted to the tractor-baler 
combination than occurred with prior art U-shaped pusher-ejectors because 
of the continuous lifting action of bale bumper 50 on bale 88 as it rolls 
rearwardly of the baler. 
In the retraction sequence, bumper 50 will hold bale 88 in the position 
shown in FIG. 5 while gate 14 begins to close. When the rear gate 14 has 
reached a predetermined position of closing, actuation means 71 will 
retract bumper 50. Gate 14 may thus be safely closed without contacting 
bale 88 and the entire bale discharge sequence can be accomplished without 
any movement of the tractor/baler combination and without the loss of 
unbaled crop stock. 
FIG. 6 illustrates a hydraulic system that may be advantageously employed 
in a bale discharge apparatus of the present type. There is shown in the 
Figure a hydraulic circuit 30 that jointly controls the operation of rear 
gate cylinders 22 and bale bumper cylinders 71. It will be understood that 
the hydraulic system of the baler, which is included in hydraulic circuit 
30, is essentially a mirror image system. Thus while a single numeral was 
used to reference to FIGS. 1-5 to describe the components of the baler 10 
and the bumper 50, many of the components shown in those figures have an 
identical component on the other side of the baler. Therefore, the two 
components of the hydraulic system comprising the rear gate cylinders and 
the bale bumper cylinders will be referred to with respect to the left and 
right side of the baler. Thus, by way of example, while numeral 22 is used 
to refer to the gate cylinder of baler 10 generally, with reference to 
FIG. 6, numeral 22R refers to the gate cylinder on the right side of the 
baler and numeral 22L refers to the gate cylinder on the left side of the 
baler. Because the operation of the left and right sides of baler circuit 
31 are identical, only the operation of the right side will be described. 
It will be understood that an action or event occurring on the right side 
will be occurring substantially simultaneously on the left side. 
Referring still to FIG. 6, hydraulic system 30 comprises a baler circuit 31 
and a tractor circuit 39. Tractor circuit 39 is a typical hydraulic 
circuit including a pump 40, an hydraulic oil reservoir 41, and a main 
control valve 42. Tractor circuit 39 is connected to baler circuit 31 by 
means of lines 25 and 26 as indicated in FIGS. 3 and 6. During extension 
of gate cylinders 22R and 22L, valve 42 is switched to the lower side as 
shown and oil is pumped by pump 40 from reservoir 41 through line 25 to a 
branch line 25R and a branch line 25L. 
Line 25R connects line 25 to a special valve 32R which will be discussed 
more fully below. Oil passes substantially unimpeded through valve 32R 
into a connecting line 27R that connects valve 32R to gate cylinder 22R. 
When gate cylinder 22R is substantially extended valve 32R shunts oil into 
line 72R, which connects bumper cylinder 71R with valve 32R. Valve 32 is 
activated by means of an actuation means 33, such as a chain or cable 
attached to valve 32 and to rear gate 14 at a connection point 36 as best 
seen in FIG. 3. Connection point 36 may be disposed where desired on rear 
gate portion 14 and may be located at pivot point 24. When rear gate 14 
reaches a desired degree of opening, activation means 33 will be pulled 
tight, thereby activating valve 32 to begin shunting oil into line 72R. 
Pressure supplied through line 72R extends cylinder 71R thereby causing 
bumper 50 to extend as previously described. During extension of gate 
cylinder 22R, oil is returned to reservoir 41 via line 28R, which connects 
cylinder 22R with a line 26R, and by line 26 which connects line 26R with 
tractor system 39. Similarly, during the extension of bumper cylinder 71R, 
oil is returned via a line 73R, which connects cylinder 71R to line 26R, 
and via line 26 which, as previously noted, connects line 26R with tractor 
system 39. 
Following the discharge of a bale, the retraction of the gate and the bale 
bumper begins. Control valve 42 is switched into the upper position shown 
in FIG. 6 and oil is pumped via line 26 into a pair of branch lines 26R 
and 26L. Again, since the operation of the right and left sides are 
identical, the gate closure operation will be described with reference to 
the right side only, it again being understood that the actions and events 
occurring on the right side are occurring substantially simultaneously on 
the left. Thus, oil is transmitted to cylinder 22R from tractor system 39 
via lines 26, 26R and 28R. Oil pressure operating on cylinder 22R, as well 
as the weight of the open gate, forces cylinder 22R to retract thereby 
closing rear gate portion 14. Oil is returned to reservoir 41 of tractor 
system 39 from cylinder 22R via lines 27R, 25R and 25. 
During retraction of cylinder 22R, a back pressure is exerted on bumper 
cylinder 71R through line 72R because of the weight of rear gate portion 
14. This back pressure prevents cylinder 71R from beginning to retract 
even though pressure is exerted on cylinders 22R and 71R simultaneously 
through lines 28R and 73R, respectively, until rear gate 14 is 
substantially closed. Thus as gate portion 14 reaches a position of 
substantial closure, the back pressure exerted on cylinder 71R due to the 
weight of gate 14 will substantially diminish, thereby reducing the back 
pressure exerted on cylinder 71R through line 72R. This will allow 
cylinder 71R to begin to retract and so retract bumper 50. Baler circuit 
31 may include flow restrictors 29R and 29L disposed in lines 28R and 28L 
respectively to sequence the closing of rear gate 14 and bumper 50 as 
desired. That is, by controlling the oil flow through lines 73R and 28R so 
that a pressure is exerted on cylinder 71R sufficient to overcome the back 
pressure exerted by the weight of gate 14, bumper 50 may be retracted at a 
desired time. For example, in the preferred embodiment, the flow passage 
through restrictor 29R is so sized that bumper cylinder 71R will start the 
retraction strike of its piston 71A from the fully extended position shown 
in FIGS. 2 and 5 to begin the retraction and collapsing of bumper 50 
before gate 14 is fully closed. This has the benefit of reducing the time 
required for the complete bale discharge cycle. 
FIGS. 7, 8 and 9 illustrate alternative hydraulic circuit interconnections 
in which only a single valve means is used to actuate the bumper cylinders 
71R and 71L. Thus, in FIG. 7, an embodiment 30a is shown wherein valve 32L 
and, consequently, line 27L have been eliminated. Valve means 32R is 
operatively connected to a line 74 through which hydraulic oil flows into 
lines 72R and 72L for actuating bumper cylinders 71R and 71L respectively. 
Thus, when valve means 32R is actuated by linking means 33R in response to 
the opening motion of gate 14, oil will flow from the reservoir through 
line 25 into line 25R, then into valve means 32R and out thereof through 
line 74. In all other respects, the hydraulic circuit illustrated in FIG. 
7 functions the same as that illustrated in FIG. 6. 
FIG. 8 shows again a single valve circuit embodiment 30b of the present 
invention. In this embodiment, however, valve 32 is disposed in hydraulic 
circuit 30b before line 25 branches into lines 25R and 25L. Once again 
when valve means 32 is actuated by linking means 33, oil flows through 
line 74 into line 72R and 72L to actuate gate cylinders 71R and 71L 
respectively. As with FIG. 7, FIG. 8 illustrates an hydraulic circuit 30b 
which functions in all respects the same as hydraulic circuit 30 of FIG. 
6. 
FIG. 9 illustrates an hydraulic circuit 30c that utilizes a valve means 32A 
similar to valve means 32 illustrated in FIGS. 6, 7 and 8 with the 
following difference noted. Valve means 32A of FIG. 9 is connected 
directly into line 25 after lines 25R and 25L branch off. Because of this 
positioning in the circuit 30c, valve means 32A need not have an 
uninterrupted flow passage for oil as do valve means 32 as shown in FIGS. 
6, 7 and 8. Thus with the embodiment shown in FIG. 9, valve means 32A will 
allow oil passage through the valve means only when actuated by linking 
means 33. Upon that occurrence, oil will flow through the valve into lines 
72R and 72L to actuate bumper cylinders 71R and 71L. Other than the 
difference noted, hydraulic circuit 30c functions identically to that of 
hydraulic circuits 30, 30a, and 30b illustrated in FIGS. 6, 7 and 8 
respectively While FIGS. 7 and 8 teach positioning of the single valve 
means in the right side of the hydraulic circuit, it will be understood 
that the valve means could be positioned as well on the left side of the 
circuit. 
FIG. 10 shows a valve 32R that may find application in the present 
invention. As previously noted in the discussion of the other components 
of the hydraulic system, valve 32L is identical to valve 32R and it will 
be understood that the components of valve 32R will also be found in valve 
32L. As shown in the Figure, valve 32R includes a casing 100R having a 
first flow passage 102R, a second flow passage 104R, a third flow passage 
106R, and a chamber 108R. First, second and third passages 102R, 104R, and 
106R are respectively connected to lines 25R, 27R, and 72R (or 74), by 
means known to the art, such as crimping or screwing. A plunger 110R is 
slidably received within chamber 108R. 
Plunger 110R is attached at one end to chain 33R and has a valve 112R 
disposed at the other end for seating on a valve seat 114R disposed within 
housing 100R. As shown, this valve seat 114R may be directly at the end of 
line 72R. Plunger 110R includes a collar or shoulder 116R that is rigidly 
fixed thereto. A biasing means such as coil spring 118R is disposed around 
plunger 110R. Spring 118R extends between collar 116R and a recessed 
shoulder 120R formed in fitting 121R on one end of housing 100R. Fitting 
121R, which may be screwed into chamber 108R, is disposed within the 
opening of chamber 108R to define the upper limit of movement of plunger 
110R. A fitting 124R closes the end of housing 100R to which line 72R is 
connected. The internal end of fitting 124 is formed to include a tubular 
extension 126R, the top of which serves as a stop for collar 116R and thus 
for plunger 110R. Spring 118R normally biases plunger 110R to the position 
shown in FIG. 10 wherein valve 112R is urged against valve seat 114R to 
close flow passage 106R, thus blocking flow through line 72R. 
Plunger 110R is configured to provide a substantially uninterrupted flow 
between lines 25R and 27R through passages 102R and 104R, thereby allowing 
a substantially unimpeded flow at all times between these lines. During a 
bale discharge, when valve 32R is activated as previously referred to by 
the opening movement of gate 14 as indicated in FIG. 3, plunger 110R is 
pulled upward by the tightening of chain 33R and thereby valve 112R is 
unseated from valve seat 114R. Upward movement of plunger 110R is resisted 
by biasing means 118R. As valve 112R unseats, oil from line 25R begins to 
flow through passage 106R into line 72R, thereby extending cylinder 71R 
and beginning the extension of bumper 50. 
During the closing operation of gate 14, chain 33R will slacken due to the 
downward movement of its upper attached end, thus relieving the 
compression force on spring 118R and permitting it to extend, forcing 
plunger 110R downward and seating valve 112R on valve seat 114R. This 
seating action is initially prevented by the back hydraulic pressure 
exerted on valve 112R through line 27R. Thus, during the closing 
operation, pressure will be exerted through lines 26, 26R, and 73R on 
cylinder 71R. Oil will return to the oil reservoir 41 through line 72R and 
valve 32R. This backward flow of oil will hold valve 112R open. When gate 
14 has substantially closed, oil will flow through line 72R, through valve 
32R and into line 25R. This back flow of hydraulic oil will have 
sufficient pressure to prevent biasing means 118R from seating valve 112R, 
thereby providing an open flow path for oil to return to reservoir 41 from 
cylinder 71R. 
Biasing means 118R acts to keep valve 112R seated on valve seat 114R until 
plunger 110R is pulled upwardly by chain 33R. If desired, biasing means 
118R may be disposed externally of housing 100R. By selectively 
determining the amount of slack disposed in chain 33R, valve 32R can be 
selectively activated at a predetermined position of gate 14 during its 
opening movement to begin extension of bumper 50. That is, by reducing the 
amount of slack in chain 33R, valve 32R will be opened more quickly in the 
gate opening sequence, and by increasing the amount of slack valve 32R 
will be opened later in the sequence. 
Valve means 32A which is used in the hydraulic circuit embodiment of FIG. 9 
has a slightly different configuration than that shown in FIG. 10. Valve 
means 32A would not include second branch 104R for attachment to line 27R 
as illustrated in FIG. 10. Thus, no oil will flow through valve means 32A 
until valve 112 is unseated from valve seat 114. When the valve is opened, 
oil will flow directly from line 25 and valve outlet line 74 into lines 
72R and 72L. This valve construction requires only two connections to be 
operable rather than the three of the previous version since oil does not 
need to flow unimpeded through the valve housing to actuate the rear gate 
cylinders. In all other respects, the valve means 32A shown in FIG. 9 
functions identically to that described with respect to FIG. 10. 
It is contemplated that means other than chain 33 may be utilized to 
actuate valve plunger 110R. Any type of lost motion mechanical connection 
between plunger 110R and gate 14 would be satisfactory. Also, actuating 
means for plunger 110R other than a mechanical connection could be used. 
For example, valve 32 could be of the solenoid type with plunger 110R 
being reciprocally disposed within a solenoid coil connected in an 
electrical control circuit. A limit switch would be mounted at an 
appropriate position in the path of movement of gate 14, to be tripped by 
gate 14 during its opening movement The limit switch actuation would 
complete a circuit through the solenoid coil, the energization of which 
would pull plunger 110R to its open position, unseating valve 114R. 
It is contemplated that numerous alterations, modifications, and 
substitutions will suggest themselves to those skilled in the art all of 
which fall within the spirit and scope of the present invention. 
Accordingly it is intended that the scope of the present invention be 
limited only by the scope of the appended claims.