Abstract:
A novel drive system for a manure spreader is disclosed wherein an infinitely adjustable variable speed drive mechanism transfers power from the power input shaft to the apron assembly and a constant speed drive mechanism transfers power from the same power input shaft to the beater assembly. A bypass mechanism allows for an extension of the hydraulic cylinder controlling a cam device, used for varying the speed of the apron drive mechanism, without activation of the cam device when the power input shaft is not engaged for rotation of the drive system. A tensioning idler connected to the cam device through a lost motion linkage provides for disengagement of the beater drive system during the cleanout of the manure spreader by the apron assembly. A drive shaft to the beater assembly is included inside of a tubular drive shaft to the apron assembly, whereby a concentric drive line assembly transfers power rearwardly to the driven assemblies.

Description:
BACKGROUND OF THE INVENTION 
     The present invention relates generally to manure spreaders and, more particularly, to a drive system for providing rotational power to the moving components of a manure spreader, namely, the apron assembly and the widespread discharge means commonly referred to as the beater assembly. 
     Manure spreaders heretofore manufactured utilize a finitely variable drive system to transfer power to the rotatable components. One type of drive system is described in U.S. Pat. No. 3,722,306 granted to W. R. Campbell et al. and in U.S. Pat. No. 3,722,307 granted to W. R. Campbell, both of which issued Mar. 27, 1973. Typical of such spreaders, rotational power is delivered rearwardly from the tractor, from which the manure spreader trails, via a power input shaft. 
     A pulley attached to the power input shaft transfers the rotational power to a second pulley by means of a drive belt interconnecting the two pulleys. The second pulley is attached to a drive shaft running along the outside of the spreader. This drive shaft runs directly into a gearbox driving the beater assembly. The apron assembly is driven off this rotating drive shaft through a transmission mechanism and jaw clutch which is finitely variable via a control linkage extending to the front of the machine. 
     Another known drive system for a manure spreader is commonly referred to as a ratchet drive. An example of this ratchet drive system can be found in U.S. Pat. No. 2,699,337 granted to A. M. Best on Jan. 11, 1955. The speed of the apron assembly is finitely adjustable according to the number of notches (or ratchet teeth) the coacting pawl is allowed to engage in one stroke of the pitman arm. 
     These drives have been found to be difficult to shift while operating under loaded conditions. When shifting is accomplished, shock loads are imposed on the drive line. Also, the finitely adjustable apron seeds may not be optimum for certain operating conditions. Moreover, finite adjustments are usually accomplished through a mechanical linkage mechanism which requires frequent maintenance and is susceptible to being easily damaged. 
     In addition, most present day manure spreaders require cycling the drive system completely through to the cleanout position before returning to the neutral position. Another disadvantage to manure spreaders with beater drive jaw clutches is that the operator is required to remember to disengage the tractor&#39;s power takeoff before going into the neutral position in order to prevent damage to the jaw clutch. 
     Other types of manure spreader drive systems are described in U.S. Pat. Nos. 3,156,124 and in 3,448,930. The former reference reveals a drive system which is also only finitely adjustable among predetermined speeds, while the latter reference exemplifies a ground driven drive system. 
     SUMMARY OF THE INVENTION 
     It is an object of this invention to provide a manure spreader drive system which overcomes the aforementioned disadvantages of the prior art. 
     It is another object of this invention to provide a design which can be manufactured and utilized simply and inexpensively. 
     It is another object of this invention to provide a manure spreader drive system which allows the speed of the apron assembly to be infinitely adjustable along the entire range of speeds considered to be desirable for manure spreaders. 
     It is a feature of this invention to locate all control functions at the front of the manure spreader. 
     It is an advantage of this invention to eliminate the need for linkages or cables to extend to the rear of the manure spreader. 
     It is still another object of this invention to provide for a declutching of the drive to the beater assembly by the controlling belt tensions in the drive system. 
     It is another advantage of this invention to eliminate the need for jaw type clutches. 
     It is another feature of this invention to stop the rotation of the beater assembly during the cleanout phase. 
     It is a further object of this invention to synchronize the functions of the apron drive and the beater drive on a manure spreader. 
     It is still another feature of this invention that all control functions can be accomplished through a single hydraulic cylinder. 
     It is a further feature of this invention to provide an easily visible indicator displaying which mode of operation the manure spreader drive system is in. 
     It is a still further object of this invention to provide the capability of changing the position of operation without having to cycle through the entire sequence of positions. 
     It is still another advantage of this invention in providing a means to synchronize an automatic release of the fine material pan with the operation of the manure spreader drive system. 
     It is a further advantage of this invention to reduce the amount of adjustment and operator attention necessary for proper operation of a manure spreader drive system. 
     It is a still further object of this invention to provide a drive system for a manure spreader which is durable of construction, inexpensive of manufacture, carefree of maintenance and effective in use. 
     These and other objects, features and advantages are accomplished according to the instant invention by providing a novel drive system for a manure spreader wherein an infinitely adjustable variable speed drive mechanism transfers power from the power input shaft to the apron assembly and a constant drive mechanism transfers power from the same power input shaft to the beater assembly. A bypass mechanism allows for an extension of the hydraulic cylinder controlling the cam device, used for varying the speed of the apron drive mechanism, without activation of the cam device when the power input shaft is not engaged for rotation of the drive system. A tensioning idler connected to the cam device through a lost motion linkage provides for disengagement of the beater drive system during the cleanout of the manure spreader by the apron assembly. A drive shaft to the beater assembly is included inside of a tubular drive shaft to the apron assembly, whereby a concentric drive line assembly transfers power rearwardly to the driven assemblies. 
    
    
     BRIEF DESCRIPTION OF THE DRAWINGS 
     The advantages of this invention will become apparent upon consideration of the following detailed disclosure of the invention, especially when taken in conjunction with the accompanying drawings wherein: 
     FIG. 1 is a side elevational view of manure spreader incorporating the instant invention; 
     FIG. 2 is a partial front end view of the manure spreader of FIG. 1 as indicated by line 2--2, the power input shaft and hitch member being broken away; 
     FIG. 3 is a top plan view of the power transfer portion of the drive system located at the forward end of the manure spreader as shown in FIG. 2 being indicated by line 3--3; 
     FIG. 4 is an enlarged cross sectional view of the cam actuating mechanism shown in FIG. 3 taken along line 4--4; 
     FIG. 5 is an enlarged cross sectional view of the cam actuating mechanism shown in FIG. 3 taken along line 5--5, the maximum speed position, as effected by an extension of the hydraulic cylinder rod, being shown in phantom; 
     FIG. 6 is an enlarged partial top plan view showing the cam actuating mechanism, the maximum speed position being shown in phantom; 
     FIG. 7 is an enlarged partial top plan view of the mechanism of FIG. 6 showing a disengagement of the bypass mechanism from the cam device, the phantom lines indicating the initial position of the bypass mechanism; 
     FIG. 8 is an enlarged front end view of the tensioning mechanism, the phantom lines showing the normal operational movement responsive to the tension in the beater drive belt; 
     FIG. 9 is an enlarged front end view of the tensioning mechanism showing the declutching position effected by a rotation of the cam actuating mechanism, thereby removing the tension from the beater drive belt; and 
     FIG. 10 is an enlarged cross sectional view of the drive shaft assembly displaying the spacer between the beater and apron drive shafts shown in FIG. 1 indicated by line 10--10. 
    
    
     DETAILED DESCRIPTION OF THE INVENTION 
     Referring now to the drawings and particularly to FIG. 1, a side elevational view of a manure spreader can be seen. The manure spreader 10 is generally comprised of a mobile frame 12, a spreader box 20, a material conveying means 14, at least one beater assembly 16 and drive means 30. 
     GENERAL STRUCTURAL RELATIONSHIPS 
     The spreader box 20 is usually of the open ended type and, as such, is composed of a floor 22, a front endwall 24, two laterally spaced sidewalls 26 and an open rear discharge area 28. Normally, one or more beater assemblies 16 are rotatably journaled between the sidewalls 26 within the rear discharge area 28 for the widespread discharge and distribution of material from the spreader box 20. Some models are equipped with as many as three beater assemblies such as the manure spreaders shown in U.S. Pat. No. 4,026,476 issued to Ipnar et al. on May 31, 1977. As a matter of convenience, FIG. 1 displays a single beater assembly manure spreader. It should be realized by one skilled in the art that this invention is not limited by the number of beater assemblies disposed on the manure spreader. 
     Usually, the material conveying means 14 is a slatted apron assembly 40 which operates along the floor 22 to transport material rearwardly for engagement with the beater assembly 16. The material conveying means 14 is drivable by rotational forces applied to the apron shaft 42 through sprocket 47 which is interconnected with a reduction gearbox 45 via a chain 49. The reduction gearbox 45 reduces the speed of the rotational forces delivered thereto before transferring to sprocket 47 so that the apron assembly 40 will operate within an acceptable range of speeds. An idler shaft 43 adjacent the front endwall 24 enables the endless belt-like apron assembly 40 to make a circuitous route around the floor 22. 
     The beater assembly 16 is likewise driven by rotational forces delivered to gearbox 17 connected to the beater shaft 18. It should also be realized by one skilled in the art that the instant invention is not limited by the manner in which the rotational forces are applied to the beater and apron assemblies once delivered for application thereto. The use of the gearbox 17 and the reduction gearbox 45 in conjunction with the driving of the beater assembly 16 and apron assembly 40, respectively, is revealed in the aforementioned U.S. Pat. No. 3,722,307. 
     In general, the drive means 30 normally consists of a power input shaft 32 which provides an input of rotational power to the drive means 30, a power transfer mechanism 34 and a drive shaft assembly 35 which delivers rotational forces to the beater and apron assemblies 16, 40. The power transfer mechanism 34 includes two separately functional subdrive systems, a beater drive system 50 and an apron drive system 60. The drive shaft assembly 35 includes a beater drive shaft 36 extending from the beater drive system 50 and an apron drive shaft 37 extending from the apron drive system 60. 
     Support for the power transfer system 34, as seen best in FIG. 3, is provided by an L-shaped main support member 70 connected to the frame 12. A diagonal member 75 interconnecting the horizontal leg 72 and the vertical leg 73 of the main support member 70 adds further support and stability for the power transfer system 34. 
     APRON DRIVE SYSTEM 
     As can be best seen in a top plan view in FIG. 3, the apron drive system 60 is a variable speed drive system including a first variable diameter sheave 61 attached to the power input shaft 32, a second variable diameter sheave 62 attached to the apron drive shaft 37, and an apron drive belt 65 interconnecting the two variable diameter sheaves 61, 62. The effective diameter of the first variable diameter sheave 61 is controlled by a cam actuating mechanism 90. A spring 67, which reacts in opposition to the tension in the apron drive belt 65, controls the effective diameter of the second variable diameter sheave 62. 
     The hydraulic cylinder 95, connected to and activated by an external hydraulic system (not shown) through hydraulic hoses 98, operates the cam actuating mechanism 90 from a single external control (also not shown). The hydraulic cylinder rod 96 is connected to the cam actuating mechanism 90 by a pin 99 in such a manner that extension of rod 96 causes rotation of the cam actuating mechanism 90 about an axis 94 corresponding to cam shaft 92. 
     The cam actuating mechanism 90 includes a cam device 100, the cam shaft 92, a bypass mechanism 120 and a pivot arm 110. The pivot arm 110 is pivotally attached to the frame 12 at a predetermined point 115 along the length thereof, thereby allowing a pivotal movement of the pivot arm 110 about pivot point 115. The sheave end 113 of the pivot arm 110 has an engaging member 114 extending therefrom which contacts the first variable diameter sheave 61 to force movement of a mobile half 63 of sheave 61 towards the stationary half 64. A thrust bearing 66 allows the mobile half 63 to rotate during any movement relative to the stationary half 64. A roller 118, attached to the actuating end 117 of the pivot arm 110, contacts the cam device 100 and travels along the inclined ramp 102 upon rotation of the cam actuating mechanism 90 by the hydraulic cylinder 95. 
     The bypass mechanism 120 is a safety device for preventing damage to any of the components of the drive means 30 if the rod 96 is extended without the apron drive belt 65 being in motion. The bypass mechanism 120, as best seen in an enlarged cross sectional view in FIG. 4 and in the top plan view of FIG. 3, includes a bypass spring 125 which interconnects the base portion 122 and a ring-like collar 124. The base portion 122 is an extension of the cam device 100, thereby allowing a cancellation of the spring forces from the bypass spring 125. The collar 124, which has a rib 126 thereon to interfit a groove 106 formed in the base 101 of the cam device 100, is forced away from the base portion 122 and into engagement with the base 101 of the cam device 100 by the bypass spring 125. 
     In normal operation, when the apron drive belt 65 is rotating, the extending rod 96 rotates the collar 124 which in turn rotates the cam device 100. If the apron drive belt 65 is not rotating, the force required to rotate the cam device 100 (and thereby damage one or more of the components) is greater than the force exerted by the bypass spring 125. As can be seen in FIG. 7, the bypass spring 125 then yields allowing the rib 126 to slip out of the corresponding groove 106, which is to say, the collar 124 disengages from the cam device 100. Consequently, the collar 124 rotates harmlessly around the cam shaft 92. A retraction of the rod 96 permits the collar 124 to become re-engaged with the cam device 100 for subsequent operation thereof. It should be noted that the phantom lines of FIG. 7 indicate the initial position of the rod 96 prior to the aforementioned disengagement. 
     Referring now to FIG. 1, it can be seen that the apron drive shaft 37 is a hollow tube-like member extending to the apron assembly 40 from the apron drive system 60. As can be seen in FIG. 3, rotation of the apron drive shaft 37 is effected by rotation of the second variable diameter sheave 62. A base bracket 69 is attached to the mobile half 63 of the variable diameter sheave 62 by connecting bolts 68 which slide through the stationary half 64 such that the base bracket 69/mobile half 63 combination is moveable relative to the stationary half 64 which in turn is affixed to the apron drive shaft 37. The spring 67 forces the base bracket 69 away from the stationary half 64, thereby forcing the mobile half 63 of the variable diameter sheave 62 toward the stationary half 64. Tension forces in the apron drive belt 65, caused by an increase in the effective diameter of the first variable diameter sheave 61, cause the mobile half 63 of the second variable diameter sheave 62 to move away from the stationary half 64 against the force exerted by the resisting spring 67. 
     BEATER DRIVE SYSTEM 
     As can best be seen in a frontal view in FIG. 2 and in a top view in FIG. 3, the beater drive system 50 is a constant speed drive system including a first pulley 51 attached to the power input shaft 32, a second pulley 52 attached to the beater drive shaft 36, and a beater drive belt 55 interconnecting the two pulleys 51, 52. A tensioning mechanism 130 serves as a declutching device operable by reducing the tension in the beater drive belt 55. 
     The tensioning mechanism 130 includes an idler pulley 135 and a support bracket 136. The idler pulley 135 engages the beater drive belt 55 to control the tension therein, while the support bracket 136 extends from the idler pulley 135 to rotatably connect with the cam shaft 92. The support bracket 136 includes a semi-circular slot-shaped hole 137 concentric with the cam shaft 92 to serve as a lost motion mechanism. 
     A lost motion bracket 132 is affixed to the end 93 of cam shaft 92. An extension 133 protrudes from the lost motion bracket 132 through the slot-shaped hole 137 and is free to slide within the slot-shaped hole 137 without causing any movement of the support bracket 136. An elongate spring 139 interconnects the frame 12 and the support bracket 136 to provide a force for keeping the idler pulley 135 in a position to maintain tension in the beater drive belt 55. 
     Referring particularly to FIG. 3, it can be seen that the power input shaft 32 is rotatably journaled within a bearing 77 affixed to an L-shaped bracket 80 which has two slots 82 through which clamping bolts 83 attach the L-shaped bracket 80 to the main support member 70. An adjusting bolt 86, extending from a brace 89 projecting from the horizontal leg 72 of the main support member 70, interconnects the short vertical leg 81 of the L-shaped bracket 80. A nut 87 secures the adjusting bolt 86 to the L-shaped bracket 80. The cam shaft 92 and drive shaft assembly 35 are also rotatably journaled within bearings 78 and 79, respectively. 
     An adjustment of the first variable diameter sheave 61 and the first pulley 51 can be made toward or away from the second variable diameter sheave 62 and the second pulley 52 to maintain proper tension in the apron drive belt 65 through a loosening of the clamping bolts 83 and a proper adjustment of nut 87 on the adjusting bolt 88. 
     As best seen in FIGS. 1 and 10, the beater drive shaft 36 is set within the apron drive shaft 37 and rotates independently therefrom. Spacers 39, intermittently placed along the length of the drive shaft assembly 35, separate the beater drive shaft 36 from the apron drive shaft 37. Referring now to FIG. 3, two slack pins 58, one adjacent the first pulley 51 and the other adjacent the second pulley 52, keep the beater drive belt 55 on the respective pulleys 51 and 52 during the slack condition created by a disengagement of the tensioning mechanism 130 from the beater drive belt 55. 
     OPERATION 
     Prior to placing the drive means 30 into operation, the hydraulic cylinder 95 is fully retracted; the engaging member 124 of the bypass mechanism 120 is engaged with the cam device 100; the first variable diameter sheave 61 is at the smallest effective diameter with the mobile half 63 being at the most distant allowable position from the stationary half 64; the second variable diameter sheave 62 is at the largest possible effective diameter since there is not enough tension in the apron drive belt 65 to overcome the force exerted by the spring 67; and the idler pulley 135 is in engagement with the beater drive belt 65, thereby placing tension in the beater drive belt 65 and allowing the transfer of any rotational power from the first pulley 51 to the second pulley 52. The initial position of the cam device 100 is shown by solid lines in a frontal view in FIG. 5 and in a top view in FIG. 6, while the initial position of the tensioning mechanism 130 is shown in the frontal view of FIG. 8. 
     To initially engage the drive means 30, the power input shaft 32 is engaged for rotation. The power input shaft 32 rotates at a constant speed which, by means of the beater drive system 50, causes the beater assembly 16 to rotate at a constant speed. The apron assembly 40 is moving at the slowest speed possible since the first variable diameter sheave 61 is at the smallest possible effective diameter and the second variable diameter sheave 62 is at the largest possible effective diameter. 
     To increase the speed of the apron assembly 40, the operator manipulates the external hydraulic system to extend the rod 96 of the hydraulic cylinder 95, thereby causing the cam device 100 to rotate since it is engaged with the bypass mechanism 120. As the cam device 100 rotates, the roller 118 climbs the inclined ramp 102 forcing a pivotal motion of the pivot arm 110. The engaging member 114 then forces the mobile half 63 of the first variable diameter sheave 61 toward the stationary half 64. 
     As a result, the rotating apron drive belt 65 moves outward from the power input shaft 32, thereby increasing the effective diameter of the first variable diameter sheave 61. Simultaneously, the increasing tension exerted on the apron drive belt 65 forces the mobile half 63 of the second variable diameter sheave 62 away from the stationary half 64 by overcoming the force exerted by the spring 67. As will be readily realized by one skilled in the art, the speed of the apron assembly 40 is infinitely variable over the entire range of speeds permitted by the apron drive system 60 through controlling the amount of extension of rod 96. 
     As seen in phantom in FIGS. 5 and 6, when the roller 118 has been positioned at the top 103 of the inclined ramp 102, the operator may elect to effect a cleanout of the spreader box 20 by the apron assembly 40 without operation of the beater assembly 16. Further rotation of the cam device 100, by a greater extension of the rod 96, causes a corresponding rotation of the cam shaft 92 until the extension 133 of the lost motion bracket 132 has reached the end of the semi-circular slot-shaped hole 137 in the support bracket 136. Then, as shown in FIG. 9, an even further rotation of the cam device 100 and cam shaft 92 will cause a rotation of the tensioning mechanism 130, thereby disengaging the idler pulley 135 from the beater drive belt 55, at which time, the beater assembly 16 stops rotating and the apron assembly 40 effects a cleanout of the spreader box 20 at the greatest possible speed. 
     To return the drive means 30 to the initial position, the rod 96 is fully retracted, causing the cam device 100 and cam shaft 92 to rotate back to the starting position. As the extension 133 proceeds along the semi-circular slot-shaped hole 137, the elongate spring 139 returns the tensioning mechanism 130 into engagement with the beater drive belt 55. Also, as the cam device 100 rotates backwards, the roller 118 returns down the inclined ramp 102, thereby reducing the speed of the apron assembly 40 to the slowest desirable speed. 
     In addition, FIG. 8 shows the range of normal operating positions between the tensioning mechanism 130 and the beater drive belt 55. The phantom lines indicate the freedom of movement of the tensioning mechanism 130 in response to the tension forces in the beater drive belt 55. The tensioning mechanism 130 operates at an equilibrium between the forces exerted by the elongate spring 139 and the tension forces in the beater drive belt 55. The variety of loads which can be imposed on the beater drive belt 55 result in the varying positional relationships as depicted in phantom in FIG. 8; while the phantom lines in FIG. 9 indicate the approximate position of the beater drive belt 55 during normal operations. 
     Furthermore, as seen in FIGS. 2, 3, 5 and 6, it is possible to attach a rotation arm 107 to the cam device 100. A cable 108 leading from the rotation arm 107 activates an indicator device 109 which visually displays the speed of the apron assembly 40 and the phase of operation of the drive means 30. Another modification (not shown) of this drive means 30 is to connect another cable to the cam device 100 in such a manner as to effect an automatic opening of an optional fine material pan when entering the cleanout phase of operation. 
     It will be understood that various changes in the details, materials, steps and arrangements of parts which have been described and illustrated in order to explain the nature of the invention will occur to and may be made by those skilled in the art upon a reading of the disclosure within the principles and scope of the invention.