GB1593688A - Pull-type crop harvesting machines - Google Patents

Description

(54) IMPROVEMENTS IN OR RELATING TO PULGTYPE CROP HARVESTING MACHINES (71) We, SPERRY RAND CORPORATION a Corporation organised and existing under the laws of the State of Delaware, United States of America, of 1290 Avenue of the Americas, New York, New York 10019, United States of America do hereby declare the invention, for which we pray that a patent may be granted to us, and the method by which it is to be performed, to be particularly described in and by the following statement: The present invention relates to pull-type crop harvesting machines, such as mowerconditioners.

A conventional pull-type harvesting machine, such as a mower-conditioner, includes a mobile frame formed by a transverse main portion supported by a pair of ground-engaging wheels and a forwardly-extending side portion attached to an end of the main frame portion and having a tongue for attaching the machine to a towing tractor. Suspended from the transverse main frame portion is a subframe or header carrying a transverse cutterbar adapted to cut standing crop as the machine is advanced forwardly across a field, a transverse reel for directing the standing crop into the cutterbar and delivering the cut crop rearwardly, and upper and lower conditioner rolls positioned to receive the cut crop being delivered rearwardly and condition it before depositing it back onto the field. The header is commonly mounted on the mobile frame for vertical flotational movement in order that the header may clear field obstructions and surface irregularities when the latter are struck by the header, thereby avoiding structural damage to the header.

However, sub-frames or headers of the abovementioned type have considerable mass and therefore the reaction force required quickly to accelerate the header upwardly on stricking an obstruction is necessarily high.

Occasionally, the header is damaged due to its inability to rise rapidly enough and absorb direct impacts with obstacles. Also, the structure of the mobile frame of the machine which supports the header mst have considerable mass to support the header.

According to the present invention a pulltype crop harvesting machine comprises a mobile frame adapted to be moved across a field in a forward direction, the frame including a main portion extending transversely to the forward direction, a tongue extending generally in the forward direction and being adapted at its forward end for connection to a towing tractor and connected at its rear end to the mobile frame, an elongate header suspended from the mobile frame so as to be vertically movable relative to the transverse main frame portion and disposed in transverse relationship to the forward direction forwardly of the transverse main frame portion, the head including means for severing and rearwardly delivering crop from the field, upper and lower elongate conditioner rolls rotatably mounted on the transverse main frame portion rearwardly of the header, the rolls being operable to receive crop delivered rearwardly of the header and condition the crop, and drive means which are mounted on the mobile frame and which are adapted to be connected to and operated by a power source on the towing tractor for transmitting motive power to the crop severing and delivering means of the header and to the conditioner rolls on the mobile frame.

Thus, in a machine according to the invention the conditioner rolls are operatively mounted in the mobile frame of the machine rearwardly of and separate from the header.

The principal advantage achieved by this arrangement is that there is less mass in the vertically movable header than heretofore, permitting the header to elevate more by reacting more quickly to obstructions which it may encounter during movement of the machine across a field. As a result, the likelihood of damage to the header is substantially reduced. Additionally, with the rolls mounted in the frame instead of the header, much of the mass of the machine will be in its frame (which enhances its stability), rather in than the header where it constitutes "dead weight" which necessitates added frame structure to support the heavier header.

A pull-type crop harvesting machine according to the invention will now be described, by way of example, with reference to the accompanying drawings, in which: Figure 1 is a side elevation of the left-hand side of the machine, with parts cut away to show internal detail.

Figure 2 is an enlarged elevation of the righthand side of the machine, parts again being cut away to show internal detail, Figure 3 is a top plan view of the machine on a scale between that of Figures 1 and 2, parts again being cut away, Figure 4 is an enlarged fragmentary sectional view taken on the line 4--4 of Figure 3, Figure 5 is an enlarged fragmentary sectional view taken on the line 5--5 of Figure 3, Figure 6 is a side elevation of the structure shown in Figure 5, Figure 7 is an enlarged rear elevation taken on the line 7--7 of Figure 3, parts being cut away, Figure 8 is a fragmentary sectional view taken on the line 8-8 of Figure 7, Figure 9 is an enlarged fragmentary sectional view taken on the line 9--9 of Figure 8, Figure 10 is an enlarged fragmentary sec tional view taken on the line 10--10 of Figure 5, Figure 11 is a plan view of a frame piece, wheel arms, wheels, floor and cutterbar of a header of the machine, the lower links and the middle stabilizer link of the machine as seen from below the conditioner rolls, with the overall outline of the machine being shown in broken lines, Figure 12 is a view of the machine similar to that of Figure 1, but on a smaller scale than that of Figure 1 and with the machine being shown in a raised transport position instead of a lowered field operating position as shown in Figure 1, and Figure 13 is an enlarged fragmentary plan view, partly in section, of drive components for transmitting rotary power to the conditioner rolls, feel and cutterbar of the machine.

In the following description, references to "right-hand" and "left-hand" relates to an observer standing at the rear of the machine and facing in the direction of forward travel which is indicated by the arrow F in Figure 1.

In Figure 1, the machine 10, which is a mower-conditioner, is disposed in its normal harvesting position ready for movement across a field to perform a crop harvesting operation during which the machine is towed in a forward direction by a tractor. The harvesting machine 10 includes a mobile frame 12 which extends generally transversely with respect to the direction F of forward travel of the machine. A longitudinally extending tongue 14 is pivotally connected at its rear end to an inboard portion of the frame 12 and has a clevis 16 at its forward end adapted to be coupled to the drawbar (not shown) of the towing tractor (not shown).

An elongate header 18 is disposed forwardly of the frame 12 and extends generally transversely to the forward direction F of travel, the header 18 being generally parallel to the frame 12. The header 18 is suspended from the transverse mobile frome 12 so as to be able to float vertically relative to the frame 12 and thereby follow the field contours as the machine 10 is advanced across the field during harvesting operations.

For harvesting standing crop material from the field, the header 18 is provided with a reel 20 extending transversely between, and rotatably mounted at its opposite ends to, left-hand and right hand side panels 22, 24 of the header. The header 18 also has a cutterbar 26 mounted along the forward edge of an upwardly and rearwardly inclined floor 28 of the header 18.

The cutterbar 26 extends transversely and is spaced below the reel 20 and just above the field. The reel 20 comprises a central shaft 30 which adjacent its opposite ends respectively carries spiders 22, 34 which rotatably support between them a plurality of tine bars 35. The bars 36 each have s series a spaced tines 38 fixed therealong. As the reel 20 is rotated counterclockwise (when viewed in Figure 1), the tines 38 engage the incoming standing crop and sweep it rearwardly over the cutterbar 26 and move the crop, after it is severed from the field by the cutterbar 26, rearwardly over the floor 28.

Upper and lower intermeshing crop conditioner rolls 40, 42 are mounted in the frame 12 for rotation in mutually opposite directions (as indicated by the arrows in Figure 4). The rolls 40, 42 extend transversely of the forward directions F and are disposed generally rearwardly of, above and in close proximity to the rear edge of the header floor 28. The cut crop being swept over the floor 28 by the reel tines 38 is received between the rolls 40, 42. As the tines 38 approach the nip between the conditioner rolls 40, 42, the tine bars 36 are caused to rotate slightly colckwise (as seen in Figure 4) due to the path of movement of camrollers 44 attached to the left-hand ends of the respective bars 36. The rollers 44 follow a cam track plate 46 disposed adjacent the left-hand side panel 22 of the header 18. Such light clockwise rotation of the tine bars 36 effects optimum orientation of the tines 38 relative to the conditioner rolls 40, 42 so as to facilitate stripping of crop material from the tines 38 by the upper roll 40 which is disposed somewhat forwardly of the lower roll 42. The crop material is conditioned between the rolls 40, 42 in a known manner.

Then the conditioned crop is propelled rearwardly by the rotating rolls 40, 42, passes below a windrow forming structure 48 extending rearwardly from the frame 12 and is deposited back on the field.

For transmitting rotary power from a power take-off shaft of the towing tractor to the reel 20, cutterbar 26 and conditioner rolls 40,42, a drive line 50 extends along the tongue 14.

The mobile frame 12 of the machine 10 includes an upper hollow transverse or crossframe structure 52 (Figures 1 to 7 and 12), a transverse lower wheel frame assembly 54 (Figures 1 to 7, 11 and 12), and left-hand and right-hand spaced side members 56,58 (Figures 1 to 7) which extend vertically between the upper frame structure 52 and the lower frame assembly 54 and which rotatably support the conditioner rolls 40,42. The frame 12 also includes a box-like housing 60 (Figures 1, 3, 7, 11, 12 and 13) extending vertically between the left-hand end portions of the upper frame structure 52 and the lower frame structure 54, the housing 60 protruding forwardly for supporting components of the drive line 50 and for pivotally mounting the rear end of the tongue 14.

As seen in Figures 1 to 7 and 12, the upper hollow cross frame structure 52 is formed by an elongate plate-like top wall member 62 which spans the entire length of the transverse frame 12 and a channel member 64 which extends along and is fixed to the underside of the top wall member 62 so as to reinforce the latter.

As illustrated in Figures 1 to 7, 11 and 12, the lower wheel frame assembly 54 is formed by a cylindrical cross pipe 66 and a pair of left-hand and right-hand spaced wheel arms 68,70 which extend generally perpendicular to the pipe 66. As clearly seen in Figure 11, the arm 68 is fixed at its forward end to the pipe 66 at a location spaced inwardly from the left-hand end of the pipe 66, while the arm 70 is fixed at its forward end to the right-hand end of the pipe 66. Both of the arms 68,70 extend generally rearwardly in similar fashion from the piep 66 and have spindles 72,74 mounted on the rear ends thereof, The spindles 72,74 respectively rotatably support groundengaging wheels 76,78 (about a common horizontal axis defined by the spindles 72,74) and extend parallel to the horizontal axis of the pipe 66.

The members 56,58, as best seen in Figures 5 to 7, respectively extend in vertical, longitudinal planes which are parallel to the forward direction F of travel of the machine 10, are plate-like in construction, and have outwardly turned front, rear and bottom edge flanges 80, 82,84 and 86,88,90. The respective upper edges of the plate-like side members 56,58 engageable receive the channel member 64 and engage the underside of the top wall member 62 and are fixed to the latter (e.g. by welding) along the lines of engagement therewith. The frame side members 56,58 are thus fixed to and vertically depend from the upper cross frame structure 52 at a predetermined spacing.

Central portions of the flanges 84,90 are semicircular and concentric with the cylindrical shape of the lower cross pipe 66, such that the side members 56,58 seat upon the surface of the cross pipe 66 at respective locations inwardly of and adjacent the attachment points of the forward ends of the wheel arms 68,70 to the cross pipe 66. As seen in Figures 4, 5, 6, 7 and 11, left-hand and right-hand rigid straps 92,94 having respective semi-circular central portions concentric with the cylindrical shape of the cross pipe 66 surround the under surface of the latter and are fastened to the bottom flanges 84,90 by bolts 95 adjacent the front and rear sides of the pipe 66 so as to provide a bearing sleeve for the pipe 66.

Referring to Figures 1, 3, 7 and 13, the box-like housing 60 is formed by spaced outer and inner vertical side walls 96,98, a bottom wall 99 extending between and interconnecting the lower horizontal edges of the side walls 96, 98, and a lower upwardly and forwardly inclined front wall 100 adjoining the front horizontal edge of the bottom wall 99 and extending between and interconnecting the lower front upwardly inclined edges of the side walls 96,98. The housing 60 also includes an arcuate front plate 102 extending between and interconnecting the front vertical edges of the side walls 96,98 an upper downwardly and forwardly inclined front wall 104 extending between and interconnecting the upper front downwardly inclined edges of the side walls 96,98, and upper and lower horizontal cross braces 106,108 extending between and interconnecting intermediate portions of the side walls 96,98. The left-hand and portion of the upper hollow cross frame structure 52 is connected to the rear edge of the upper front wall 104 and extends between and interconnects the rear upper edges of the side walls 96,98. The box-like housing 60 is thus supported in depending fashion by the upper hollow cross frame structure 52. The box-like housing 60 is further supported from the left-hand side member 56 by a channel member 109 which is fixed at its right-hand end to the lower end of the left-hand side member 56 and extends parallel to and above the left-hand end portion of the cylindrical cross pipe 66. The member 109 extends through the inner vertical side wall 98 of the housing 60 for a short distance so as to overlie a portion of the housing bottom wall 99. The left-hand end portion of the channel member 109 is fixed to both the inner side wall 98 and the bottom wall 99 of the housing 60. Adjacent the housing 60, the left-hand end of the cross pipe 66 is rotatably mounted with respect to the channel member by a rigid semi-circular strap 110 fastened to the channel member 109.

The tongue 14 is formed by an elongate straight hollow main portion 112 which is rectangular in cross-section and a short front portion 114 which is fixed on the front end of the main portion 112 and extends downwardly and forwardly therefrom. The clevis 16 is attached to the front end of the front tongue portion 114. As seen in Figure 7, the tongue 14 is pivotably mounted about a vertical axis at the rear end of its straight main portion 112 by fasteners 116,118 which respectively couple the rear end of the portion 112 to the upper and lower spaced horizontal cross braces 106,108 located within the forward intermediate portion of the box-like housing 60.

The tongue 14 is laterally movable between limiting angular positions adjacent to and remote from the header 18 and may be held at any intermediate or limiting position by a releasable latch mechanism 120 mounted on the tongue 14 immediately forwardly of the arcuate front plate 102 of the box-like housing 60. The tongue 14 is shown in Figure 3 disposed in an intermediate position. The tongue 14 can be shifted to its remote position relative to the header 18 when setting up the machine 10 for field operation, while it is shifted to its adjacent position relative to the header 18 to set up the machine 10 for road transport.

When the tongue 14 is in its remote position, the header 18 is disposed in a position offset to the right of the towing tractor, whereby the tractor will not run over the standing crop to be harvested by the machine 10. When the tongue 14 is in its adjacent position, the machine 10 trails more or less directly behind the tractor.

The arcuate front plate 102 has holes (not shown) formed therethrough at the extreme left-hand and right-hand end portions thereof, the holes defining the respective remote and adjacent positions of the tongue 14 relative to the header 18. The arcuate curvature of the plate 102 coincides with the lateral path along which the adjacent portion of the tongue 14 moves when it is shifted laterally between the remote and adjacent positions.

The latch mechanism 120 is of a conventional construction and hence will not be described in great detail. Briefly, the mechanism 120 includes an upstanding bracket 122 mounted on the portion of the tongue 14 adjacent the front plate 102 which, in turn, supports a latch pin 124 which is spring biased towards the front plate 102. The pin 124 is supported for horizontal reciprocatory movement towards and away from the front plate 102 and is insertable through a chosen hole in the front plate 102 when the tongue 14 has been laterally shifted to bring the pin 124 into alignment with the chosen hole. A rope 126 which extends forwardly along the tongue 14 to be reachable by the tractor operator is connected at its rear end to the latch pin 124. Therefore, by merely pulling forwardly on the rope 126, the pin 124 is withdrawn from the hole in the front plate 102. By manoeuvring the tractor relative to the machine 10, the tongue 14 may be laterally shifted for a new position relative to the header 18. Once the tongue 14 has reached its new position, the rope 126 is released and the latch pin 124 passes into the hole in the front plate 102 corresponding to the new tongue position.

As mentioned hereinbefore, the header 18 is suspended from the transverse mobile frame 12 so as to be able to float vertically relative to the frame 12 and thereby follow the field contour as the machine 10 is advanced across the field during harvesting operations. The suspension system includes a pair of left-hand and righthand laterally spaced upper links 128,130 and a pair of left-hand and right-hand laterally spaced lower links 132,134. The upper and lower links comprise a generally parallel fourbar linkage system which pivotally connects the header 18 to the front of the mobile frame 12 such that the header 18 may be moved in a generally vertical direction toward and away from the field surface.

As shown in Figures 1,3 and 12, the lefthand upper link 128 is pivotally connected at its rear end at 136 to a left-hand forwardlyslanted bracket 138 which is attached to and depends from the channel member 64 of the frame structure 52 adjacent the outer side of the member 56 of the mobile frame 12. The front end of the upper link 128 is pivotally connected at 140 to the upper rear portion of the outer side of the panel 22 of the header 18.

As shown in Figures 2, 3, 4 and 6, the righthand upper link 130 is pivotally connected at its rear end at 142 to a right-hand forwardlyslanted bracket 144 which is attached to and depends from the channel member 64 of the frame structure 52 adjacent the outer side of the member 58 of the mobile frame 12. The front end of the upper link 130 is pivotally connected at 146 to the upper rear portion of the outer side of the panel 24 of the header 18.

As shown in Figures 1, 7, 11 and 12, the link 132 is pivotally connected at its rear end portion at 148 between a left-hand pair of spaced, forwardly-projecting mounting tabs 150 fixed on the front side of the left-hand end portion of the cylindrical cross pipe 66. The front end of the link 132 is pivotally connected at 152 to a left-hand bracket structure 154 which is fixed to and extends laterally outwardly from the lower central portion of the outer side of the panel 22 of the header 18.

By this arrangement, the pivotal connection 152 of the front end of the link 132 on the header 18 is located above and slightly forwardly of the left-hand end of the cutterbar 26.

As shown in Figures 2, 3, 4, 6, 7 and 11, the link 134 is pivotally connected at its rear end portion at 146 between a right-hand pair of spaced, forwardly-projecting mounting tabs 158 fixed on the front side of the right-hand end portion of the cylindrical cross pipe 66. The front end of the link 134 is pivotally connected at 160 to a right-hand bracket structure 162 which is fixed to and extends laterally outwardly from the lower central portion of the outer surfacethe panel 24 of the header 18. By this arrangement, the pivotal connection 160 of the front end of the link 134 on the header 18 is located above and slightly forwardly of the left-hand end of the cutterbar 26.

To facilitate flotation of the header 18, the suspension system also includes a pair of spaced tension springs 164,166 which support most of the weight of the header 18. The remaining weight of the header 18 is supported on the field by a pair of spaced groundengaging skid shoes 168,170 fixed on the lower central end portions of the respective side panels 22,24 of the header 18.

The left-hand spring 164, shown in Figures 1, 3 and 7, is disposed in a vertical plane above the link 132 and is pivotally connected at its rear end at 168 oetween a pair of spaced tabs 170 which are attached to and depend from the frame structure 52. The left-hand spring 164 is inclined downwardly and forwardly and is coupled at its forward end at 172 to an upstanding brace 174 on Lhe structure 154.

The right-hand flotation spring 166, shown in Figures 2, 4 and 7, is disposed in a vertical plane above the link 134 and is coupled at its rear end at 176 to a tab 178 fixed to and depending rearwardly and downwardly from the frame structure 53. The right-hand spring 166 is inclined downwardly and forwardly and is coupled at its forward end at 180 to the rear end of a horizontal brace 182 fixed on the outer side of the panel 24 of the header 18.

To facilitate raising and lowering the header 18 and the frame 12 relative to the field, a lift mechanism in the form of a hydraulic cylinder 184 is provided, as shown in Figures 1, 3, 5, 7 and 2. The hydraulic cylinder 184 is coupled between the frame structure 52 and the lefthand wheel arm 68. The upper anchor end of the cylinder 184 is pivotally connected at 186 to a tab 188 which is connected to and depends downwardly from the frame structure 52. The lower piston rod end of the cylinder 184 is pivotally connected at 190 to the rear end of a lever arm 192 pivotally connected at its forward end at 193 to a bracket 194 fixed on the outer side of the left-hand wheel arm 68.

When the hydraulic cylinder 184 is actuated (i.e. pressurized) by the operator through operation of suitable hydraulic controls (not shown) from its retracted position shown in Figure 1 to its extended position shown in Figure 12, relative movement occurs between the lower wheel frame assembly 54 and the remaining rigidly interconnected parts of the mobile frame 1, those parts being the structure 52, the side members 56,58 and the box-like housing 60. As the cylinder 184 extends, the assembly 54 of the mobile frame 12 is pivoted upwardly about the horizontal axis defined by the wheel spindles 72,74, with the cross pipe 66 of the assembly 54 rotating slightly in a clockwise direction (as viewed in Figures 1 and 12) within the rigid mounting straps 92,94 and 110 as the pipe 66 rises. The aforementioned rigidly interconnected parts of the frame 12 rise from the lower field operating position of Figure 1 (and broken line position of Figure 12) to the upper road transporting position s shown in solid lines in Figure 12. By relieving the hydraulic pressure within the cylinder 184, the latter is allowed to retract due to the weight of the above-mentioned rigidly interconnected parts of the mobile frame 12 and of the conditioner rolls 40,40 mounted therein whereby the rigidly interconnected frame parts move downwardly as a unit from the upper solid line position of Figure 12 to the lower position of Figure 1. When the cylinder 184 is fully extended, a transport lock link 196 pivotally mounted on the arm 68 adjacent the cylinder 184 may be moved into a lower notched portion 198 (Figure 5) of each of a pair of aligned slots 200 formed in a pair of spaced plates 220 fixed on and extending rearwardly from the member 56. The link 196 will then maintain the frame 12 in its raised position when the pressure in the cylinder 184 is relieved.

When the wheel frame assembly 54 is pivoted upwardly relative to the aforementioned remaining rigidly interconnected parts of the frame 12, header lift assist means come into operation. The header lift assist means comprise a pair of projections 204,206, each of which is provided on a rear end of one of the lower links 132,134, and become engaged with the bottom side of the rotating and elevating cross pipe 66 of the wheel frame assembly 54 and cause the header 18 to be elevated at the same time as the rigidly interconnected frame parts and the cross pipe 66.

Normally, when the frame 12 is in its lower position of Figure 1 each of the projections 204,206 is spaced slightly below the cross pipe 66. Once rotation and lifting of the pipe 66 is initiated to lift the remainder of frame 12, the respective tabs 150,158 begin ro totate and rise with the pipe 66, until the projections 204,206 come into contact with the lower side of the pipe 66. Until this happens, the header 18 does not rise with the frame 12.

However, once contact occurs between the arcuate top surfaces 208,210 of the projections 204,206, the wheel frame assembly 54 and the lower links 132,134 act as a single unit and the further rotation and elevation of the pipe 66 cause the lower links 132,134 to swing upwardly therewith and raise the header 18. The header 18 is raised upwardly at a greater rate than the rate at which the remaining rigidly interconnected parts of the frame 12 are raised.

As a result, at its fully raised position, the header 18 has been raised through a greater disctane than that of the cross pipe 66 of the wheel frame assembly 54 such that ground clearance between the header 18 and the field is maximised. It should be noted that when the header 18 is at its lower position of Figure 1, the locations of the projections 204, 206 relative to the cross pipe 66 do not interfere with the ability of the lower links 132,134 to swing upwardly or downwardly about the pivotal connections 148,156 when the header 18 moves vertically upon encountering an obstruction or depression in the field.

For stabilising the header 18 against the effect of any laterally directed forces which may impinge thereon, a telescope assembly 212 is provided at a central location between the cross pipe 66 and a lower portion of the header 18, as shown in Figures 2 to 7 and 11. A cross chamber member 214, shown in Figures 4 and 11, is fixedly mounted on and extends along the underside of the header floor 28. The telescopic assembly 212 comprises a front sleeve section 216 which telescopically receives a rear bar section 218. The front end of the front sleeve section 216 is pivotally connected at 220 between a pair of upstanding spaced tabs 222 fixed at a central location on an upper side of the cross channel member 214. The front end of the rear bar section 218 is received through the rear end of the front sleeve section 216.

The rear end of the rear bar section 218 is pivotally connected at 224 between a pair of forwardly projecting tabs 226 fixed at a central location on the cross pipe 66. The telescopic relationship between the sections 216, 218 accommodates the vertical movement of the header 18 relative to the frame 12 while still providing lateral stabilisation.

As described previously, the upper and lower intermeshing crop conditioner rolls 40,42 are mounted for counter-rotation relative to each other between the side members 56,58 of the mobile frame 12. Cut crop being swept over the header floor 28 by the reel tines 38 is received between the rolls 40,42. The crop material is conditioned between the rolls 40,42 in a known manner and then propelled by the rotating rolls 40,42 rearwardly below the windrow forming structure 48 and thence back onto the field. The construction of the rolls 40,42 is substantially the same as that illustrated and described in British Patent Specification No. 1143 066.

The lower conditioner roll 42 has a central shaft 228 opposite ends of which are rotatably mounted in left-hand and right-hand lower bearing assemblies 230,232, respectively. The bearing assemblies 230,232 are attached to lower portions of the side members 56,58 of the mobile frame 12, as shown in Figures 5 and 6.

The upper conditioner roll 40 has a central shaft 234 opposite each of which are rotatably mounted in left-hand and right-hand upper bearing assemblies 236,238, res shoulders 284,286 respectively fixed to the lower forward edges of the levers 240,242 abut and rest on rubber blocks 288,290 respectively attached to the outer sides of the side members 56,58. The levers 240,242 may pivot upwardly until upper shoulders 292,294, (which are respectively attached to the outer sides of the levers 240,242 and extend above the upper forward edges of the levers 240,242) abut the respective lower sides of the crank arms 258, 260.

The torsion adjusting assembly 252 is coupled to the adjacent inner ends of the torsion bars 254,256, these inner ends each being of hexagonal shape similar to that of the outer ends of the bars 254,256. The assembly 262 includes a pair of lever arms 296,298 carrying respective hubs 300,302 which have hexagonal central bores receiving the respective hexagonal inner ends of the torsion bars 254,265, as seen in Figures 4 and 7 to 9. The hubs 200,302 are axially aligned and received within and supported by a cylindrical sleeve 304 which is received through and secured to a pair of spaced gussets 306 fixed to and depending from the upper cross frame structure 52. By this arrangement, the inner end of the left-hand torsion bar 254, the left-hand hub 300 and the left-hand lever arm 296 are secured together as a unit which is rotatably journalled in theleft-hand half of the cylindrical sleeve 304. Similarly, the inner end of the right-hand torsion bar 286, the rignt-hand hub 302 and the right-hand lever arm 298 are rotatably journalled as a unit in the right-hand half of the sleeve 304.

The torsion adjusting assembly 262 further includes a bell crank lever 308 formed by two spaced, identical, generally L-shaped plates 310,312 which are rigidly interconnected by a sleeve 314. The bell crank lever 308 is mounted for pivotal movement about a generally longitudinal axis defined by a pin 316 which is received through the bell crank sleeve 314 and secured at its opposite ends to the first and rear vertical legs 318,320 of an inverted Ushaped bracket 322. The bracket 322 is fixed to and depends from the upper cross frame structure 52 rearwardly of the attachment of the gussets 306 to the frame structure 52. A device 324 having ball-and-socket joint assemblies 326,328 at its opposite ends pivotally connects the upper right-hand end of the bell crank lever 308 ta 330 to the rear ends of the lever arms 296,298 at 332. Thus, rotation of the lever arms 296,298 occurs about the coincident axes of the torsion bars 254,256 upon rotation of the bell crank lever 308 about the axis defined by the mounting pin 316. The lower left-hand end of the bell crank lever 308 pivotally supports an internally threaded sleeve 334 about an axis defined by the projections 336,338 fixed on opposite sides of the sleeve 334.

The torsion ajdusting assembly 262 also includes a transversely extending shaft 340 rotatably mounted near its right-hand end in the side member 58 and having a hand actuated crank 342 pivotally attached to its right-hand end. The opposite left-hand end of the transverse shaft 340 is threaded and received within the internally threaded sleeve 334. The hand crank 342 is normally retained in a stored position as seen in Figure 6 (and in solid lines in Figure 7) by a hook element 344 mounted on and projecitng rearwardly from the rear edge flange 88 of the member 58. When the hand crank 342 is moved to its operative position, as seen in broken lines in Figure 7, by turning the crank 342 in a predetermined direction the pressure imposed by the upper conditioner roll 40 upon the lower conditioner roll 42 may be regulated. In particular, when the hand crank 342 is turned clockwise, as viewed from the right-hand side of the machine 10, the sleeve 334 is moved along the rotating shaft 340 towards the hand crank 342 and correspondingly pivots the bell crank 308 counterclockwise, as viewed from the right-hand side of the machine 10. Clockwise rotation of the lever arms 296, 298 results in the inner ends of the torsion bars 254,256 rotating clockwise relative to the outer ends thereof and an increase in the torsional stress imposed on the torsion bars 254,256. This is converted into an increase in the downwardlydirected force imposed by the crank arms 258, 260 on the ends of the upper roll 40 through the interconnection provided by the link pairs 276,278 and the pivotal levers 240,242. When the hand crank 342 is turned countercloskwise the sleeve 334 is moved along the rotating shaft 340 away from the hand crank 342 and correspondingly pivots the bell crank lever 308 clockwise. This in turn rotates the lever arms 296, 298 counterclockwise, resulting in a decrease in the torsional stress imposed on the torsion bars 244,256. This is converted into a decrease in the magnitude of the downwardly-directed force imposed on the ends of the upper roll 40.

As briefly mentioned above, rotary driving power is transmitted from the power take-off shaft (not shown) or the towing tractor (not shown) to the reel 20, cutterbar 26 and conditioner rolls 40,42 of the harvesting machine 10 by the drive line 50, best illustrated in Figure 13 and partially seen in Figures 1, 3, 7 and 12.

The drive line 50 includes a rear input drive shaft 346 extending axially within the hollow interior of the elongate straight main portion 112 of the tongue 14 (the tongue being omitted in Figure 13 for purposes of clarity). The drive line 50 also includes a forward input telescopic drive shaft assembly 348 (only partially shown in Figures 1 and 12) having a forward universal joint (not shown) and a rear universal joint 350 for respectively coupling the front and rear ends of the assembly 348 to the tractor pto shaft and to the forward end of the rear input drive shaft 346 at the front open end of the main tongue portion 112. The forward telescopic drive shaft assembly 348 transmits the rotary motion of the tractor pto shaft to the rear input drive shaft 346.

The drive line 50 further includes a gearbox assembly 352 stationarily mounted within the box-like housing 50 of the mobile frame 12.

The assembly 352 includes a housing 354 mounted on the interior side of the innervertical side wall 98 of the box-like housing 60 by a bracket 356. The housing 354 contains and rotatably supports an input shaft 358 which extends outwardly from the forward side of the housing 354 and has a driving bevel gear 360 secured to the rear end of the shaft 358.

A transverse output shaft 362 is rotatably mounted in the housing 354 which extends laterally beyond the right-hand and left-hand sides of the housing 354. A driven bevel bear 364, which meshes with the driving bevel gear 360, is located within the housing 354 and is secured on the output shaft 362 near the right.

hand end of the shaft 362.

A universal joint assembly 366 extends through the rear open end of the main tongue portion 112 and interconnects at 368 (Figures 1 and 13) the rear end of the rear input drive shaft 346 and the forward end of the input shaft 358 of the gearbox assembly 352 so as to transmit rotary motion from the rear input drive shaft 346 to the driving bevel gear 360 in the housing 354. As shown in Figure 1, the connection 368 between the shfats 346,358 is vertically aligned with the fasteners 116,118. A slip clutch 370 is operatively interposed between the universal joint assembly 366 and the gearbox input shaft 358 to provide overload protection for the drive line.

The drive line 50 also includes various components, which will be described hereinafter, for transmitting rotary motion of the output shaft 362 of the gearbox assembly 352 to the reel 20, the cutterbar 26 and the conditioner rolls 40,42.

Rotary motion is transmitted from the righthand end of the gearbox output shaft 362 to the left-hand end of the central shaft 234 by a telescopic drive shaft assembly 372 which extends through an opening in the inner side wall 98 of the box-like housing 60. The assembly 372 has left-hand and right-hand uni versaljoints 374,376 for coupling the output shaft 362 and the upper roll shaft 234 so as to accommodate vertical movement of the upper roll 40.

Rotary motion is transmitted to the left-hand end of the central shaft 228 of the lower conditioner roll 42 from the left-hand end portion of the gearbox output shaft 362 through upper end lower geras 378,380 having a 1:1 ratio and a transverse drive shaft 382. The upper and lower rolls 40,42 are thereby rotated at the same peripheral speeds. The upper gear 378 is secured on the left-hand and portion of the gearbox output shaft 362 for rotation therewith and meshes with the lower gear 380 which is secured on the left-hand end of the transverse drive shaft 382. The gears 378,380 are both contained within a casing 384 which is secured to the left-hand side of the gearbox assembly housing 354 and also at 386 to a bracket 388 (Figure 1) fixed on and projecting upwardly from the bottom wall 99 of the box-like housing 60. The left-hand end portion of the transverse drive shaft 382 is rotatably mounted in a hub portion 390 of the casing 384 while its righthand end portion is coupled to the left-hand end of the shaft 228. A pair of couplers 392, 394 are interposed between sections of the transverse drive shaft 382.

Rotary motion is also transmitted to the reel 20 and the cutterbar 26 from the left-hand end portion of the gearbox output shaft 362. A first sheave 396 is mounted on the left-hand end of the gearbox output shaft 362 outwardly of the upper gear 378 for rotation with the shaft 362. A second sheave 398 is rotatably mounted, forwadrly of the first sheave 396, on a stub shaft 400 fixed to and extending inwardly from a plate 402 which is fastened by bolts 404 to the inner side of the outer side wall 96 of the box-like housing 60. An endless flexible belt 406 which transmits the rotary motion of the first sheave 396 to the second sheave 398 passes around the sheaves 396,398. The tension in the belt 406 may be adjusted oy loosening the bolts 404, moving the plate 402 in an appropriate direction generally fore-and-aft along a pair of slots 408 (Figure 1) formed through the outer side wall 96 and then retightening the bolts 404 when the desired level of tension in the belt 406 is reached. The rotary motion of the second sheave 398 is transmitted by a telescopie drive shaft assembly 410 to a flywheel 412 of an oscillating drive assembly 414 (Figure 13) mounted on the panel 22. The assembly 414 is operatively connected to and drives the cutterbar 26 with a reciprocating action in a conventional anner. The telesocpic drive shaft assembly 410 has lefthand and right-hand end universal joints 416, 418 for respectively coupling the inner side of the second sheave 398 and the left-hand end of a shaft 420, on which the flywheel 312 is secured, so as to accommodate vertical movement of the header 18 relative to the box-like housing 60.

The rotary motion of the central shaft 420 of the assembly 414 is not only translated into oscillatory motion of a drive arm 422 (which in turn drives the cutterbar 26), but also is transmitted to a large diameter sheave 424 secured on a stub shaft 426 which extends axially from the left-hand end of the central shaft 30 of the reel 20. A small diameter sprokket 428 is secured tn the right-hand end of the central shaft 402, this end extending outwadrly from the right-hand side of the assembly 414 as seen in Figure 14. A large diameter sprocket 430, which is rotatably mounted on a stub shaft 432 fixed on and extending outwardly towards the box-like housing 60 from the panel 22 of the header 18, is coupled to the small diameter sprocket 428 by a chain 434 which passes around the sprockets 428,430. An idler sprocket 436 (Figure 1) is mounted on the panel 22 adjacent the chain 434 and is adjustably movable towards and away from the chain 434 in order to take up the slack in the chain 434 or to permit its removal from the sprockets for servicing or repair purposes. The large diameter sprocket 430 is fixed to a small diameter sheave 438 by a hub 440 which extends between and interconnects the sprocket 430 and sheave 438, as seen in Figure 13, the latter thereby also being rotatably mounted on the stub shaft 432.

An endless belt 442 passes around the small diameter sheave 438 and the large diameter sheave 424. Also, the belt 442 passes around a pair of idler sheaves 444,446 (Figure 1) which are rotatably mounted on an arm 448 which is pivotally mounted on the panel 22 and movable to various angular positions for adjusting the tension in the belt 442.

It will be understood from the various diameter sizes of the sprockets and sheaves that transmit rotaty motion from the gearbox output shaft 362 to the shaft 30 that the peripheral speed of rotation of the reel 20 is substantially less than the reciprocatory speed of the cutterbar 26 and the peripheral speed or totation of the conditioner rolls 40,42.

Other aspects of the illustrated embodiment are described and claimed in co-pending Patent Application No. 52630/77, serial no. 1593689.

WHAT WE CLAIM IS: 1. A pull-type crop harvesting machine comprising a mobile frame adapted to be moved across a field in a forward direction, the frame including a main portion extending transversely to the forward direction, a tongue extending generally in the forward direction and being adapted to its forward end for connection to a towing tractor and connected at its rear end to the mobile frame, an elongate header suspended from the boimle frame so as to be vertically movable relative to the transverse main frame portion and disposed in transverse relationship to the forward direction forwardly of the transverse main frame portion, the header including means for severing and rearwardly delivering crop from the field, upper and lower elongate conditioner rolls rotatably mounted on the transverse main frame portion rearwardly of the header, the rolls being operable to receive crop delivered rearwardly of the header and condition the crop, and drive means which are mounted on the mobile frame and which are adapted to be connected to and operated by a power source on the towing tractor for transmitting motive power to the crop severing and delivering means of the header and to the conditioner rolls on the mobile frame.

2. A machine according to Claim 1, wherein the mobile frame includes a side portion fixed to an end of the transverse main frame portion and extending generally lognitudinally from and forwardly of said end of the transverse main frame portion, the rear end of the tongue being connected to the side portion of the mobile frame, the elongated header being disposed laterally adjacent the side portion and the tongue, the upper end and lower elongate conditioner rolls being generally horizontally disposed in transverse relationship to the forward direction, and the drive means being mounted on the side portion of the mobile frame.

3. A machine according to Claim 1, the transverse main frame portion of the mobile frame being an upper portion and the frame additionally having spaced right-hand and lefthand, as hereinbefore defined, portions fixed to the upper portion and extending downwardly therefrom, the header being disposed forwardly of the right-hand and left-hand portions of the mobile frame, the severing and delivering means comprising a cutterbar and a reel for severing and rearawrdly delivering the crop, with the upper and lower elongate conditioner rolls being rotatably mounted on and extending between the right-hand and left-hand frame portions and being disposed below the upper portion of the mobile frame.

4. A machine according to Claim 3, wherein the mobile frame additionally has a side portion fixed to and depending from an end of the upper portion laterally adajcent one of the righthand and left-hand frame portions and extending generally longitudinally from and forwardly of said end of the upper portion, the tongue being connected at its rear end to the side por tion of the mobile frame, the elongate header being disposed laterally adjacent the side por tion of said mobile frame and the tongue, and the drive means being mounted on the side portion of the mobile frame.

5. A pull-type crop harvesting machine constructed and arranged substantially as herein particularly described with reference to the accompanying drawings.

**WARNING** end of DESC field may overlap start of CLMS **.

Claims (5)

1. **WARNING** start of CLMS field may overlap end of DESC **.

   22 of the header 18, is coupled to the small diameter sprocket 428 by a chain 434 which passes around the sprockets 428,430. An idler sprocket 436 (Figure 1) is mounted on the panel 22 adjacent the chain 434 and is adjustably movable towards and away from the chain 434 in order to take up the slack in the chain 434 or to permit its removal from the sprockets for servicing or repair purposes. The large diameter sprocket 430 is fixed to a small diameter sheave 438 by a hub 440 which extends between and interconnects the sprocket 430 and sheave 438, as seen in Figure 13, the latter thereby also being rotatably mounted on the stub shaft 432.

   An endless belt 442 passes around the small diameter sheave 438 and the large diameter sheave 424. Also, the belt 442 passes around a pair of idler sheaves 444,446 (Figure 1) which are rotatably mounted on an arm 448 which is pivotally mounted on the panel 22 and movable to various angular positions for adjusting the tension in the belt 442.

   It will be understood from the various diameter sizes of the sprockets and sheaves that transmit rotaty motion from the gearbox output shaft 362 to the shaft 30 that the peripheral speed of rotation of the reel 20 is substantially less than the reciprocatory speed of the cutterbar 26 and the peripheral speed or totation of the conditioner rolls 40,42.

   Other aspects of the illustrated embodiment are described and claimed in co-pending Patent Application No. 52630/77, serial no. 1593689.

   WHAT WE CLAIM IS: 1. A pull-type crop harvesting machine comprising a mobile frame adapted to be moved across a field in a forward direction, the frame including a main portion extending transversely to the forward direction, a tongue extending generally in the forward direction and being adapted to its forward end for connection to a towing tractor and connected at its rear end to the mobile frame, an elongate header suspended from the boimle frame so as to be vertically movable relative to the transverse main frame portion and disposed in transverse relationship to the forward direction forwardly of the transverse main frame portion, the header including means for severing and rearwardly delivering crop from the field, upper and lower elongate conditioner rolls rotatably mounted on the transverse main frame portion rearwardly of the header, the rolls being operable to receive crop delivered rearwardly of the header and condition the crop, and drive means which are mounted on the mobile frame and which are adapted to be connected to and operated by a power source on the towing tractor for transmitting motive power to the crop severing and delivering means of the header and to the conditioner rolls on the mobile frame.
2. 2. A machine according to Claim 1, wherein the mobile frame includes a side portion fixed to an end of the transverse main frame portion and extending generally lognitudinally from and forwardly of said end of the transverse main frame portion, the rear end of the tongue being connected to the side portion of the mobile frame, the elongated header being disposed laterally adjacent the side portion and the tongue, the upper end and lower elongate conditioner rolls being generally horizontally disposed in transverse relationship to the forward direction, and the drive means being mounted on the side portion of the mobile frame.
3. 3. A machine according to Claim 1, the transverse main frame portion of the mobile frame being an upper portion and the frame additionally having spaced right-hand and lefthand, as hereinbefore defined, portions fixed to the upper portion and extending downwardly therefrom, the header being disposed forwardly of the right-hand and left-hand portions of the mobile frame, the severing and delivering means comprising a cutterbar and a reel for severing and rearawrdly delivering the crop, with the upper and lower elongate conditioner rolls being rotatably mounted on and extending between the right-hand and left-hand frame portions and being disposed below the upper portion of the mobile frame.
4. 4. A machine according to Claim 3, wherein the mobile frame additionally has a side portion fixed to and depending from an end of the upper portion laterally adajcent one of the righthand and left-hand frame portions and extending generally longitudinally from and forwardly of said end of the upper portion, the tongue being connected at its rear end to the side por tion of the mobile frame, the elongate header being disposed laterally adjacent the side por tion of said mobile frame and the tongue, and the drive means being mounted on the side portion of the mobile frame.
5. 5. A pull-type crop harvesting machine constructed and arranged substantially as herein particularly described with reference to the accompanying drawings.