JP6650902B2 - Combine - Google Patents

Description

  The present invention relates to a combine equipped with a cutting unit for cutting uncut culms in a field and a threshing unit for threshing grains of the cut culms.

  A conventional combine employs a configuration in which the power of an engine mounted on a traveling body is transmitted to left and right traveling units such as traveling crawlers via a driving device. For example, the combine described in Patent Document 1 is a crawler type. The output of the drive device is adjusted according to the amount of operation of a main shift lever and a steering handle provided on the control unit. The main shift lever and the steering handle are interlockingly connected to the drive device via a steering case and a link member for converting the operation amount. By the action of the internal mechanism of the steering case, the combine disclosed in Patent Document 1 can be steered at the same operation interval as that of a four-wheeled vehicle, while being a crawler type.

JP 2012-085598 A

  However, in the self-combining combine disclosed in Patent Literature 1, the straight hydraulic continuously variable transmission and the swing hydraulic continuously variable transmission are arranged at positions away from the control section with the transmission case interposed therebetween. Further, an oil cooler for cooling hydraulic oil in the transmission case is provided, and the oil cooler is disposed at a position away from the transmission case. Therefore, when starting the combine in a low temperature environment, the viscosity of the hydraulic oil increases, making it difficult to circulate the hydraulic oil through the hydraulic piping including the oil cooler, causing oil leakage from the transmission case and lubrication to the transmission mechanism. Failure may occur.

  Therefore, the present invention seeks to provide a combine that has been improved by examining these conditions.

  In order to achieve the above object, a combine of the present invention has a drive device that changes the power of an engine mounted on a traveling machine body and transmits the power to a left and right traveling unit, and a cutting unit transports a cutting culm and threshing unit. An oil cooler is connected to a hydraulic pipe that circulates hydraulic oil in the drive device, and a bypass path that bypasses the oil cooler is provided in the hydraulic pipe. The bypass path is provided integrally with the driving device.

  In the above combine, a connection member having two communication ports is provided in the driving device, and one end of the bypass path is connected to one communication port of the connection member, and the other communication port of the connection member is connected to the other end of the bypass member. A hydraulic pipe communicating with the oil cooler may be connected to the opening, and a relief valve may be provided at a connection portion between the connecting member and the bypass passage.

  In the above combine, the connecting member may be protruded from an upper surface of the driving device, and the bypass may be fixedly arranged above the driving device.

  According to the present invention, by connecting the drive device and the oil cooler, the piping path for circulating the drive device becomes longer, but the length can be reduced by the bypass route. Therefore, when the engine is started in a cold region, the high-viscosity hydraulic oil can be circulated, and the lubricity in the drive device can be maintained satisfactorily. In addition, since the drive device can be incorporated together with the bypass pipe by integrally providing the drive device with the bypass passage, assemblability is improved and maintenance of the hydraulic device in the drive device is facilitated.

It is a left view of the combine showing the 1st embodiment of the present invention. It is a right view of the combine. It is a top view of the combine. It is a drive system diagram of a combine. It is the perspective view of the combine seen from diagonally forward. It is a partial plane sectional view of a threshing part. It is a drive system diagram of a transmission case. It is a plane sectional view showing composition around an engine room. FIG. 3 is a hydraulic circuit diagram showing a configuration of a working hydraulic circuit. FIG. 2 is a front view illustrating an arrangement configuration of hydraulic circuit components. 1 is an overall perspective view of a combine showing a piping configuration of a working hydraulic circuit. FIG. 2 is an enlarged perspective view illustrating a piping configuration of a traveling system hydraulic circuit. FIG. 2 is a hydraulic circuit diagram illustrating a configuration of a traveling system hydraulic circuit. It is a perspective view which shows the piping workability of the hydraulic piping on a transmission case. It is a perspective view which shows the relationship between the hydraulic piping on a transmission case, and a connection link body. It is the perspective view which looked at the front part of the traveling body from diagonally left front. It is the perspective view which looked at the driver's cab (operating part) periphery from diagonally left rear. It is a front view of a driver's cab (control part) periphery. It is a top view of a driver's cab (control part) periphery. It is the perspective view which looked at the driver's cab (operating part) periphery from diagonally right backward. It is the perspective view which looked around the driver's cab (operating part) from the front.

  An embodiment of the present invention will be described below with reference to the drawings (FIGS. 1 to 21) applied to a normal combine. 1 is a left side view of the combine, FIG. 2 is a right side view thereof, and FIG. 3 is a plan view thereof. First, a schematic structure of a combine will be described with reference to FIGS. In the following description, the left side of the traveling body 1 in the forward direction is simply referred to as the left side, and the right side in the forward direction is simply referred to as the right side.

  As shown in FIGS. 1 to 3, the ordinary combine in the embodiment includes a traveling machine body 1 supported by a pair of left and right crawler belts 2 made of rubber crawlers as a traveling unit. At the front of the traveling machine body 1, a cutting unit 3 for cutting and harvesting uncut culms such as rice (or wheat, soybean, or corn) while cutting is mounted with a single-acting lifting hydraulic cylinder 4 so as to be adjustable. ing.

  On the left side of the traveling machine body 1, a threshing unit 9 for threshing the harvested grain culm supplied from the mowing unit 3 is mounted. At the lower part of the threshing unit 9, a grain sorting mechanism 10 for performing rocking sorting and wind sorting is arranged. A driver's cab 5 as a control unit on which an operator rides is mounted on the front right side of the traveling body 1. The engine 7 as a power source is arranged in the cab 5 (below the driver's seat 42). Behind the cab 5 (on the right side of the traveling machine 1), a grain tank 6 for taking out the grain from the threshing unit 9 and a grain for discharging the grain in the grain tank 6 toward the truck bed (or container or the like). Discharge conveyor 8 is arranged. The grain discharge conveyor 8 is tilted outward, and the grains in the Glen tank 6 are carried out by the grain discharge conveyor 8.

  The reaping unit 3 includes a feeder house 11 communicating with a handle 9 a at a front part of the threshing unit 9, and a horizontally long bucket-shaped grain header 12 continuously provided at a front end of the feeder house 11. A scraping auger 13 (platform auger) is rotatably supported in the grain header 12. The rake bar with tine bar 14 is arranged above the front of the rake auger 13. A clipper-like cutting blade 15 is arranged at the front of the grain header 12. Left and right weeds 16 are protruded on both left and right sides of the front of the grain header 12. Further, a supply conveyor 17 is provided in the feeder house 11. A beater 18 (front rotor) for cutting culm input is provided on the feed end side (handle 9a) of the supply conveyor 17. Note that the lower surface of the feeder house 11 and the front end of the traveling machine body 1 are connected via a lifting hydraulic cylinder 4, and the reaping unit 3 uses a reaping input shaft 89 (feeder house conveyor shaft), which will be described later, as a lifting fulcrum. It is moved up and down by the lifting hydraulic cylinder 4.

  With the above configuration, the tip side of the uncut grain culm between the left and right weeds 16 is scraped by the raking reel 14, the culm base side of the uncut grain culm is cut by the cutting blade 15, and Due to the rotational drive, the harvested grain culm is collected near the entrance of the feeder house 11 near the center of the left and right width of the grain header 12. The entire amount of the harvested culm of the cereal header 12 is conveyed by the supply conveyor 17, and is fed into the handle 9 a of the threshing unit 9 by the beater 18. A horizontal control hydraulic cylinder (not shown) for rotating the grain header 12 around a horizontal control fulcrum axis is provided, and the horizontal inclination of the grain header 12 is adjusted by the horizontal control hydraulic cylinder to thereby control the grain header. It is also possible to support the 12, the cutting blade 15 and the raking reel 14 horizontally with respect to the field scene.

  As shown in FIGS. 1 and 3, a handling cylinder 21 is rotatably provided in a handling room of the threshing unit 9. A handle cylinder 21 is supported by a handle cylinder shaft 20 (see FIG. 4) extended in the front-rear direction of the traveling machine body 1. On the lower side of the handling cylinder 21, a receiving net 24 for letting the grains leak is provided. A spiral screw blade-like intake blade 25 is provided on the outer peripheral surface of the front part of the handling cylinder 21 so as to project radially outward.

  With the above configuration, the harvested grain culm thrown in from the handling port 9 a by the beater 18 is transported toward the rear of the traveling machine 1 by the rotation of the handling cylinder 21, and between the handling cylinder 21 and the receiving net 24. Kneaded and threshed. Threshing materials such as grains smaller than the mesh of the receiving net 24 leak from the receiving net 24. Straw and the like that do not leak from the receiving net 24 are discharged to the field from the dust outlet 23 at the rear of the threshing unit 9 by the transporting action of the handling cylinder 21.

  Note that a plurality of dust feed valves (not shown) that adjust the transport speed of thresh in the handling room are pivotably mounted on the upper side of the handling cylinder 21. By adjusting the angle of the dust valve, the transport speed (residence time) of thresh in the handling room can be adjusted according to the type and properties of the harvested grain culm. On the other hand, as the grain sorting mechanism 10 arranged below the threshing unit 9, a swing sorting machine 26 for specific gravity sorting having a grain pan, a chaff sheave, a grain sheave, a straw rack, and the like is provided.

  Further, as the grain sorting mechanism 10, there is provided a fan-like Karamin 29 or the like for supplying a sorting wind to the swing sorting board 26. The threshed by the threshing cylinder 21 and leaking from the receiving net 24 is subjected to the specific gravity of the rocking sorter 26 and the wind of the Karin 29 in the form of a blower fan. No. 2), a mixture of grains and straw (secondary grains such as grains with branch spikes), and straw scraps.

  A first conveyor mechanism 30 and a second conveyor mechanism 31 are provided below the swinging sorter 26 as the grain sorting mechanism 10. Grains (the first ones) dropped from the swinging sorter 26 by the swinging sorter 26 and the fan-shaped Karino 29 are collected in the Glen tank 6 by the first conveyor mechanism 30 and the deep-lifting conveyor 32. You. The mixture of grain and straw (second product) is returned to the sorting start end side of the swing sorting machine 26 via the second conveyor mechanism 31 and the second reduction conveyor 33, and is re-sorted by the swing sorting machine 26. You. Straw chips and the like are configured to be discharged to a field through a dust outlet 23 at a rear portion of the traveling body 1.

  Further, as shown in FIGS. 1 to 3, the cab 5 is provided with a control column 41 and a driver seat 42 on which an operator sits. The steering column 41 includes an accelerator lever 40 for adjusting the number of revolutions of the engine 7, a circular steering handle 43 for changing the course of the traveling body 1 by a rotation operation of an operator, and a main body for switching the traveling speed of the traveling body 1. A gearshift lever 44 and an auxiliary gearshift lever 45, a mowing clutch lever 46 for driving or stopping the mowing unit 3, and a threshing clutch lever 47 for driving or stopping the threshing unit 9 are arranged. A roof 49 for awning is attached to the front upper surface of the Glen tank 6 via a sun visor support 48, and the roof 49 for awning covers the upper side of the driver's cab 5.

  As shown in FIGS. 1 and 2, left and right track frames 50 are arranged on the lower surface side of the traveling body 1. The track frame 50 includes a drive sprocket 51 for transmitting the power of the engine 7 to the crawler belt 2, a tension roller 52 for maintaining the tension of the crawler belt 2, a plurality of track rollers 53 for holding the ground side of the crawler belt 2 in a ground state, An intermediate roller 54 for holding the non-ground side of the crawler belt 2 is provided. The front side of the crawler belt 2 is supported by the driving sprocket 51, the rear side of the crawler belt 2 is supported by the tension roller 52, the ground contact side of the crawler belt 2 is supported by the track roller 53, and the non-ground contact side of the crawler belt 2 is supported by the intermediate roller 54. It is configured so that

  Next, the drive structure of the combine will be described with reference to FIGS. As shown in FIGS. 4 and 7, the transmission case 63 is provided with a linear hydraulic continuously variable transmission 64 having a hydraulic linear pump 64a and a hydraulic linear motor 64b for traveling speed change. The engine 7 is mounted on the right upper surface of the front of the traveling body 1, and the transmission case 63 is arranged on the front of the traveling body 1 on the left side of the engine 7. An output shaft 65 projecting leftward from the engine 7 and a mission input shaft 66 projecting leftward from the transmission case 63 are connected via an engine output belt 67, an engine output pulley 68, and a transmission input pulley 69. I have. In addition, the working unit charge pump 59 and the cooling fan 149 that drive the lifting hydraulic cylinder 4 and the like are arranged in the engine 7, and the working unit charge pump 59 and the cooling fan 149 are driven by the engine 7.

  In addition, a steering rotary hydraulic continuously variable transmission 70 having a hydraulic rotary pump 70a and a hydraulic rotary motor 70b is provided in the transmission case 63, and a straight hydraulic hydraulic continuously variable transmission 64 and a rotary hydraulic While the output of the engine 7 is transmitted to the continuously variable transmission 70, the steering handle 43, the main transmission lever 44 and the auxiliary transmission lever 45 output the straight hydraulic continuously variable transmission 64 and the turning hydraulic continuously variable transmission 70. Under the control, the left and right crawler belts 2 are driven via the straight hydraulic continuously variable transmission 64 and the swing hydraulic continuously variable transmission 70 to travel and move in a field or the like. In the embodiment, the straight-moving and turning hydraulic continuously variable transmissions 64 and 70 are arranged at the upper right side of the transmission case 63. The drive device according to the present invention is constituted by the straight and turning hydraulic continuously variable transmissions 64 and 70 and the transmission case 63.

  Further, as shown in FIGS. 1 to 6, a handlebar driving case 71 that supports the front end side of the handlebar shaft 20 is provided. A handling drum drive case 71 is arranged on the front side of the threshing unit 9. A handlebar input shaft 72 for driving the reaper 3 and the handlebar 21 is supported by a handlebar drive case 71. In addition, a main counter shaft 76 is provided as a constant rotation shaft penetrating right and left of the threshing unit 9. A working unit input pulley 83 is provided at the right end of the main counter shaft 76. The right end of the main counter shaft 76 is connected to an engine output pulley 68 on an output shaft 65 of the engine 7 via a threshing clutch 84 also serving as a tension roller and a working unit drive belt 85.

  In front of the handling cylinder 21, a handling cylinder input shaft 72 extending in the horizontal direction of the traveling body 1, a beater 18 arranged in the horizontal direction of the traveling body 1, and a mowing input shaft extending in the horizontal direction of the traveling body 1. 89 are provided. As a handle cylinder input mechanism 90 for transmitting the driving force of the main counter shaft 76 to the handle cylinder input shaft 72, the handle cylinder drive pulleys 86 and 87 and the handle cylinder drive belt 88 are provided, and the drive force from the engine 7 is transmitted. A handle cylinder input mechanism 90 (handle cylinder drive pulleys 86 and 87 and a handle cylinder drive belt 88) is arranged at one end of the counter shaft 76 on the engine 7 side, and the handle cylinder 21 is driven to rotate at a constant rotational output of the engine 7. It is configured as follows.

  A beater drive mechanism and a mowing drive mechanism for transmitting the driving force of the main counter shaft 76 to the beater shaft 82 and the mowing input shaft 89 are provided on the other end side of the main counter shaft 76. A sub-counter shaft 104 is arranged between the beater shaft 82 and the main counter shaft 76, and a power relay belt 113 is wound around power relay pulleys 105 and 106 provided on the main counter shaft 76 and the sub-counter shaft 104. It is turned to constitute a power relay mechanism for transmitting power to the mowing drive mechanism.

  A cutting drive belt 114 is wound around cutting drive pulleys 107 and 108 provided on the sub-counter shaft 104 and the beater shaft 82, respectively, to constitute a beater driving mechanism. The mowing drive belt 114 is stretched by the mowing clutch 109 also serving as a tension roller, so that the rotational power transmitted from the engine 7 to the main counter shaft 76 is transmitted to the beater via the power relay mechanism and the beater driving mechanism. It is input to the axis 82. A mowing drive mechanism is configured to transmit the mowing drive force from the engine 7 to the mowing input shaft 89 via the mowing drive chain 115 and the sprockets 116 and 117 from the beater shaft 82 on which the beater 18 is supported. ing. As a result, the reaper 3 is driven to rotate at a constant rotational output of the engine 7 together with the beater 18.

  A Karamin shaft 100, which is a rotating shaft of the Karamin 29 in the form of a blower fan, has a hollow tube shape, and a main counter shaft 76 is inserted into a hollow portion of the Karamin shaft 100. That is, the main counter shaft 76 and the Karamin shaft 100 have a double shaft structure, and the main counter shaft 76 and the Karamin shaft 100 are rotatably supported relative to each other. Further, a Karamin drive belt 103 is wound around Karaino drive pulleys 101 and 102 provided on the sub-counter shaft 104 and Karaoke shaft 100, respectively, to constitute a Karamin drive mechanism. Therefore, the rotational power from the engine 7 transmitted to the main counter shaft 76 is input to the beater shaft 82 via the power relay mechanism and the Karamin drive mechanism, and the Karamin 29 is driven to rotate at a constant rotational output by the engine 7 at a constant rotational output.

  Further, the machine housing of the threshing unit 9 is provided with a mowing support frame 36 on the upper surface side of the front portion of the threshing machine support column 34 on the upper surface side of the traveling machine body 1. A cutting bearing 37 is mounted on the front right side of the cutting support frame 36, and a forward / reverse switching case 121 described later is mounted on the left front of the cutting support frame 36. A cutting input shaft 89 is rotatably supported on the front side of the cutting support frame 36 via the cutting bearing body 37 and the forward / reverse rotation switching case 121 so as to be rotatable left and right. A rotatable beater shaft 82 (beater 18) is rotatably supported via a beater bearing body 38 in the inside of the shaft. A handlebar drive case 71 is attached to the upper surface side of the mowing support frame 36, and the handlebar input shaft 72 is supported by the handlebar drive case 71.

  On the other hand, a cutting input shaft 89 for driving the supply conveyor 17 in the feeder house 11 is provided. The harvesting driving force transmitted from the engine 7 to one end of the main counter shaft 76 on the engine 7 side is transmitted from the other end of the main counter shaft 76 opposite to the engine 7 to the forward / reverse rotation of the harvesting forward / reverse switching case 121. The light is transmitted to the shaft 122. The reaping input shaft 89 is driven via the forward rotation bevel gear 124 or the reverse rotation bevel gear 125 of the reaping forward / reverse switching case 121.

  Further, a handle cylinder input shaft 72 facing left and right is provided in front of the threshing unit 9, and the driving force transmitted from the engine 7 to one end of the main counter shaft 76 on the engine 7 side is applied to one end of the handle cylinder input shaft 72 on the engine 7 side. Transmitted to the department. The handle cylinder input shaft 72 provided on the front side of the threshing unit 9 is disposed in the traveling machine body 1 left and right direction, while the handling cylinder 21 is supported by the handling cylinder shaft 20 disposed in the traveling machine body 1 front and rear direction. The front end of the handle cylinder shaft 20 is connected via a bevel gear mechanism 75 to the left and right other ends of the handle cylinder input shaft 72 opposite to the engine 7. The driving force of the engine 7 is transmitted from the other left and right ends of the main counter shaft 76 opposite to the engine 7 to the grain sorting mechanism 10 or the cutting unit 3 for sorting the grain after threshing. .

  That is, the right end of the handle input shaft 72 is connected to the right end of the main counter shaft 76 closer to the engine 7 via the handle drive pulleys 86 and 87 and the handle drive belt 88. The front end side of the handle cylinder shaft 20 is connected via a bevel gear mechanism 75 to the left end of the handle cylinder input shaft 72 extending in the left-right direction. The power of the engine 7 is transmitted from the right end of the main counter shaft 76 to the front end side of the handle cylinder shaft 20 via the handle cylinder input shaft 72, and the handle cylinder 21 is driven to rotate in one direction. On the other hand, the driving force of the engine 7 is transmitted from the left end of the main counter shaft 76 to the grain sorting mechanism 10 arranged below the threshing unit 9.

  Further, the left end of the first conveyor shaft 77 of the first conveyor mechanism 30 and the left end of the second conveyor shaft 78 of the second conveyor mechanism 31 are connected to the left side of the main counter shaft 76 via the conveyor drive belt 111. The ends are connected. The left end of the second conveyor shaft 78 is connected through a swing selection belt 112 to the left end of a crank-shaped swing drive shaft 79 that supports the rear part of the swing selection board 26. That is, the threshing clutch 84 is turned on and off by the operation of the threshing clutch lever 47 by the operator. Each part of the grain sorting mechanism 10 and the handling cylinder 21 are configured to be driven by the engagement operation of the threshing clutch 84.

  It should be noted that the grain conveyor 32 is driven via the first conveyor shaft 77, and the first selected grains of the first conveyor mechanism 30 are collected in the Glen tank 6. In addition, the second reduction conveyor 33 is driven via the second conveyor shaft 78, and the second selection kernel (second product), in which the straw waste of the second conveyor mechanism 31 is mixed, is on the upper surface side of the swinging sorter 26. Is returned to. Further, in a structure in which a spreader (not shown) for scattering waste is provided in the dust outlet 23, the spreader is driven by a spreader driving pulley (not shown) and a spreader driving belt (not shown) to the left side of the main counter shaft 76. Connect the ends.

  A cutting input shaft 89 is provided as a conveyor input shaft that supports the feed end side of the supply conveyor 17. A header drive shaft 91 is rotatably supported on the right side rear side of the grain header 12. The left end of the forward / reverse transmission shaft 122 is connected to the left end of the beater shaft 82 via the cutting drive chain 115 and the sprockets 116 and 117, and the cutting input shaft 89 is forward / reverse transmitted via the forward / reverse switching case 121. It is connected to the shaft 122. The right end of the cutting input shaft 89 is connected to the left end of the header drive shaft 91 extending in the left-right direction via the header drive chain 118 and the sprockets 119 and 120. A rake shaft 93 that supports the rake auger 13 is provided. The middle part of the header drive shaft 91 is connected to the right part of the raking shaft 93 via the raking drive chain 92.

  Further, a reel shaft 94 that supports the scraping reel 14 is provided. The right end of the raking shaft 93 is connected to the right end of the reel shaft 94 via an intermediate shaft 95 and reel drive chains 96 and 97. The cutting blade 15 is connected to the right end of the header driving shaft 91 via a cutting blade drive crank mechanism 98. The feeding conveyor 17, the scraping auger 13, the scraping reel 14, and the cutting blade 15 are driven and controlled by the on / off operation of the cutting clutch 109, so that the tip side of the uncut culm in the field is continuously cut. It is composed.

  A forward bevel gear 124 integrally formed with the forward / reverse transmission shaft 122, a reverse bevel gear 125 rotatably supported on the cutting input shaft 89, and an intermediate bevel gear 126 for connecting the reverse bevel gear 125 to the forward bevel gear 124. , Inside the forward / reverse switching case 121. The intermediate bevel gear 126 is always meshed with the forward rotation bevel gear 124 and the reverse rotation bevel gear 125. On the other hand, a spline engagement shaft is slidably supported on the cutting input shaft 89 by a slider 127. The slider 127 is configured to be removably engageable with the forward rotation bevel gear 124 via a pawl clutch-shaped forward rotation clutch 128, and the slider 127 is engaged with the reverse rotation bevel gear 125 via a claw clutch-shaped reverse rotation clutch 129. It is configured to be detachably engageable.

  Further, a forward / reverse switching shaft 123 for sliding operation of the slider 127 is provided, and a forward / reverse switching arm 130 is provided on the forward / reverse switching shaft 123, and the forward / reverse switching arm 130 is operated by a forward / reverse switching lever (forward / reverse operation tool). By swinging, the forward / reverse switching shaft 123 is rotated to bring the slider 127 into and out of contact with the forward rotation bevel gear 124 or the reverse rotation bevel gear 125, and through the forward rotation clutch 128 or the reverse rotation clutch 129, the forward rotation bevel gear 124 or the reverse rotation The slider 127 is alternatively locked to the bevel gear 125, and the cutting input shaft 89 is connected to the forward / reverse transmission shaft 122 in the forward or reverse rotation.

  The structure includes a forward / reverse rotation switching case 121 as a forward / reverse rotation switching mechanism for driving the supply conveyor 17 to rotate forward or backward. The supply conveyor 17 is connected to the beater shaft 82 via the forward / reverse rotation switching case 121. Therefore, the supply conveyor 17 and the like of the feeder house 11 can be reversed by the reverse switching operation of the forward / reverse switching case 121, and the clogged straw in the feeder house 11 can be quickly removed.

  The right end of the auger drive shaft 158 is connected to the output shaft 65 of the engine 7 via an auger clutch 156 and an auger drive belt 157 in the form of a tension pulley. The front end of the lateral feed auger 160 at the bottom of the Glen tank 6 is connected to the left end of the auger drive shaft 158 via a bevel gear mechanism 159. A vertical feed auger 162 of the grain discharge conveyor 8 is connected to a rear end side of the horizontal feed auger 160 via a bevel gear mechanism 161, and a grain of the grain discharge conveyor 8 is connected to an upper end side of the vertical feed auger 162 via a bevel gear mechanism 163. The grain discharge auger 164 is connected. In addition, a grain discharge lever 155 for turning on and off the auger clutch 156 is provided. A grain discharge lever 155 is attached to the rear of the driver seat 42 and in front of the Glen tank 6 so that an operator can operate the grain discharge lever 155 from the driver seat 42 side.

  Next, a power transmission structure such as the transmission case 63 will be described with reference to FIGS. As shown in FIG. 4 and FIG. 7, etc., a transmission case 63 includes a pair of linear pumps 64a and a linear motor 64b. And a turning hydraulic continuously variable transmission 70 having a turning motor 70b. The transmission input shaft 66 of the transmission case 63 is gear-coupled to each of the pump shafts 258 and 259 of the rectilinear pump 64a and the revolving pump 70a to be driven. An engine output belt 67 is wound around a transmission input pulley 69 on a transmission input shaft 66. The output of the engine 7 is transmitted to the transmission input pulley 69 via the engine output belt 67, and drives the linear pump 64a and the revolving pump 70a.

  The driving force output from the output shaft 65 of the engine 7 is transmitted to the pump shaft 258 of the rectilinear pump 64a and the pump shaft 259 of the swing pump 70a via the engine output belt 67 and the transmission input shaft 66, respectively. In the linearly traveling hydraulic continuously variable transmission 64, hydraulic oil is appropriately fed from the linearly traveling pump 64a to the linearly traveling motor 64b by the power transmitted to the pump shaft 258. Similarly, in the swing hydraulic continuously variable transmission 70, hydraulic oil is appropriately fed from the swing pump 70a toward the swing motor 70b by the power transmitted to the pump shaft 259.

  The transmission input shaft 66 protrudes from the upper portion of the left side of the transmission case 63 toward the feeder house 11, and a transmission input pulley 69 is pivotally mounted on a protruding end (left end) of the transmission input shaft 66 so as not to rotate relatively. The transmission input shaft 66 is rotatably supported by a bearing fixed to the transmission case 63, and a power distribution gear 262 is fitted in the middle of the transmission input shaft 66 so as to be relatively non-rotatable. The pump shaft 258 of the rectilinear pump 64a and the pump shaft 259 of the revolving pump 70a are respectively arranged before and after the transmission input shaft 66 in plan view, and are disposed below the transmission input shaft 66 in side view.

  A linear input gear 263 meshing with a power distribution gear 262 fixed to the transmission input shaft 66 is relatively rotated at a protruding end (left end) of the pump shaft 258 protruding from the continuously variable transmission case 323 into the transmission case 63. It is fitted to impossible. Similarly, a projecting end (left end) of a pump shaft 259 projecting from the continuously variable transmission case 323 into the transmission case 63 has a turning input gear 264 meshed with a power distribution gear 262 fixed to the transmission input shaft 66. Are fitted so that they cannot rotate relative to each other.

  When the driving force output from the output shaft 65 of the engine 7 is transmitted to the transmission input pulley 69, the transmission input shaft 66 and the power distribution gear 262 rotate together with the transmission input pulley 69, and through the linear input gear 263, While rotating the pump shaft 258 of the rectilinear pump 64a, the pump shaft 259 of the swing pump 70a is rotated via the swing input gear 264. In other words, the power input gear 262 of the transmission input shaft 66 disposed between the pump shafts 258 and 259 is meshed with the rectilinear input gear 263 and the turning input gear 264 of the pump shafts 258 and 259, respectively. The driving force can be efficiently transmitted to each of the straight hydraulic continuously variable transmission 64 and the swing hydraulic continuously variable transmission 70.

  A transmission charge pump 151 for supplying hydraulic oil to the hydraulic pumps 64a and 70a and the hydraulic motors 64b and 70b is attached to the pump shaft 259. The linearly moving hydraulic continuously variable transmission 64 changes and adjusts the inclination angle of the rotary swash plate in the linearly moving pump 64 a in accordance with the operation amount of the main transmission lever 44 and the steering handle 43 arranged on the steering column 41, and The rotation direction and the number of rotations of the linear motor shaft 260 projecting from the linear motor 64b are arbitrarily adjusted by changing the discharge direction and the discharge amount of the hydraulic oil to the linear motor 64b.

  Rotational power of the linear motor shaft 260 is transmitted from the linear transmission gear mechanism 250 to the auxiliary transmission gear mechanism 251. The sub-transmission gear mechanism 251 includes a sub-transmission low-speed gear 254, a sub-transmission medium-speed gear 255, and an auxiliary transmission high-speed gear 256 that are switched by the sub-transmission shifters 252 and 253. By operating the auxiliary transmission lever 45 disposed on the steering column 41, the output rotation speed of the linear motor shaft 260 is selectively switched to three stages of low speed, middle speed or high speed. . It should be noted that a neutral position (a position at which the output of the subtransmission becomes zero) is provided between the low speed of the subtransmission and the middle speed and the high speed.

  A parking brake shaft 265 (sub-transmission output shaft) provided on the output side of the sub-transmission gear mechanism 251 is provided with a drum type parking brake 266. The rotational power from the auxiliary transmission gear mechanism 251 is transmitted to the left and right differential mechanisms 257 from an auxiliary transmission output gear 267 fixed to the parking brake shaft 265. The left and right differential mechanisms 257 each include a planetary gear mechanism 268. Further, a straight-running pulse generating rotary body 292 is provided on the parking brake shaft 265, and the rotation speed of the straight-running output (straight-running vehicle speed = shift output of the auxiliary shift output gear 267) is detected by a straight-running vehicle speed sensor (not shown). are doing.

  Each of the left and right planetary gear mechanisms 268 can rotate one sun gear 271, a plurality of planet gears 272 meshing with the sun gear 271, a ring gear 273 meshing with the planet gear 272, and a plurality of planet gears 272 on the same circumference. And a carrier 274 to be arranged. The carriers 274 of the left and right planetary gear mechanisms 268 are arranged opposite to each other at appropriate intervals on the same axis. A center gear 276 is fixed to a sun gear shaft 275 provided with left and right sun gears 271.

  Each of the left and right ring gears 273 is arranged concentrically on the sun gear shaft 275 in a state in which the internal teeth of the inner peripheral surface of the ring gear 273 mesh with the plurality of planetary gears 272. The external teeth on the outer peripheral surface of each of the left and right ring gears 273 are connected to a steering output shaft 285 via intermediate gears 287 and 288 for right and left turning output described later. Each ring gear 273 is rotatably supported by left and right forced differential output shafts 277 projecting left and right outward from the outer surface of the carrier 274. The left and right axle shafts 278 are connected to the left and right forced differential output shafts 277 via final gears 278a and 278b. Left and right drive sprockets 51 are attached to the left and right axles 278. Therefore, the rotational power transmitted from the auxiliary transmission gear mechanism 251 to the left and right planetary gear mechanisms 268 is transmitted from the left and right axles 278 to the respective drive sprockets 51 at the same rotational speed in the same direction, and causes the left and right crawler belts 2 to travel in the same direction. And the traveling body 1 is moved straight ahead (forward, backward).

  The swing hydraulic continuously variable transmission 70 changes and adjusts the inclination angle of the rotary swash plate in the swing pump 70a in accordance with the amount of rotation of the main shift lever 44 and the steering handle 43 disposed on the steering column 41. The rotation direction and the number of rotations of the turning motor shaft 261 projecting from the turning motor 70b are arbitrarily adjusted by changing the discharge direction and the discharge amount of the working oil to the turning motor 70b. Further, a turning pulse generating rotary wheel 294 is provided on a steering counter shaft 280 described later, and a turning speed (turning vehicle speed) of a steering output of the turning motor 70b is detected by a turning rotation sensor (turning vehicle speed sensor) (not shown). Is configured to be detected.

  Also, in the transmission case 63, a wet multi-plate type turning brake 279 (steering brake) provided on the turning motor shaft 261 (steering input shaft), and the turning motor shaft 261 via the reduction gear 281. A steering counter shaft 280 to be connected, a steering output shaft 285 connected to the steering counter shaft 280 via a reduction gear 286, and a left input connecting the steering output shaft 285 to the left ring gear 273 via a reverse gear 284. A gear mechanism 282 and a right input gear mechanism 283 that connects the steering output shaft 285 to the right ring gear 273 are provided. The rotational power of the turning motor shaft 261 is transmitted to the steering counter shaft 280. The rotational power transmitted to the steering counter shaft 280 is transmitted to the left ring gear 273 as reverse rotational power via the left intermediate gear 287 and the reverse gear 284 on the steering output shaft 285 in the left input gear mechanism 282. On the other hand, the power is transmitted to the right ring gear 273 as forward rotation power via the right intermediate gear 288 on the steering output shaft 285 in the right input gear mechanism 283.

  When the auxiliary transmission gear mechanism 251 is neutralized, power transmission from the linear motor 64b to the left and right planetary gear mechanisms 268 is blocked. When the auxiliary transmission gear mechanism 251 outputs a non-neutral auxiliary transmission, power is transmitted from the straight motor 64b to the left and right planetary gear mechanisms 268 via the auxiliary low-speed gear 254, the intermediate sub-speed gear 255, or the auxiliary high-speed gear 256. . On the other hand, when the output of the slewing pump 70a is in the neutral state and the slewing brake 279 is in the on state, power transmission from the slewing motor 70b to the left and right planetary gear mechanisms 268 is blocked. When the output of the swing pump 70a is set to a state other than neutral and the swing brake 279 is turned off, the rotational power of the swing motor 70b is transmitted to the left ring gear 273 via the left input gear mechanism 282 and the reverse gear 284. Meanwhile, the power is transmitted to the right ring gear 273 via the right input gear mechanism 283.

  As a result, at the time of forward rotation (reverse rotation) of the rotation motor 70b, the left ring gear 273 rotates reversely (forward rotation) and the right ring gear 273 rotates forward (reverse rotation) at the same rotational speed in the opposite directions. That is, the shift output from each of the motor shafts 260 and 261 is transmitted to the drive sprockets 51 of the left and right crawler belts 2 via the sub-transmission gear mechanism 251 or the differential mechanism 257, respectively, and the vehicle speed (running speed) of the traveling body 1 Speed) and direction of travel are determined.

  That is, when the rectilinear motor 64b is driven in a state where the turning motor 70b is stopped and the left and right ring gears 273 are stationary, the rotation output from the rectilinear motor shaft 260 is transmitted to the left and right sun gears 271 at the same left and right rotational speeds, and The right and left crawler belts 2 are driven at the same rotational speed in the same direction via the gear 272 and the carrier 274, and the traveling body 1 travels straight.

  Conversely, when the turning motor 70b is driven in a state in which the straight motor 64b is stopped and the left and right sun gears 271 are stationary, the left ring gear 273 is rotated forward (reverse rotation) by the rotation power from the turning motor shaft 261. Rotation), and the right ring gear 273 rotates in the reverse direction (forward rotation). As a result, one of the drive sprockets 51 of the left and right crawler belts 2 rotates forward and the other rotates reversely, and the traveling body 1 is turned on the spot (radical turning spin turn).

  Further, by driving the left and right ring gears 273 by the turning motor 70b while driving the left and right sun gears 271 by the rectilinear motor 64b, a difference occurs in the speeds of the left and right crawler belts 2. Make a left or right turn (U-turn) with a turning radius larger than the radius. The turning radius at this time is determined according to the speed difference between the left and right crawler belts 2. The vehicle 7 turns left or right while the traveling driving force of the engine 7 is constantly transmitted to the left and right crawler belts 2.

  Next, the working hydraulic circuit 180 and the traveling hydraulic circuit 200 in the ordinary combine according to the present embodiment will be described with reference to FIGS. As shown in FIGS. 8 to 12, the working hydraulic circuit 180 includes, as hydraulic actuators, a hydraulic cylinder 4 for raising and lowering the mowing, hydraulic cylinders 27L and 27R for raising and lowering the left and right reels that support the scraping reel 14 so as to be able to move up and down. An auger lifting hydraulic cylinder 55 that supports the grain discharge auger 164 so as to be able to move up and down, left and right machine lifting hydraulic cylinders 56L and 56R that move the traveling machine 1 up and down, a working oil tank 57 that stores working oil, and a working oil. A work part charge pump 59 connected to the tank 57 via a strainer 58, hydraulic valves 60A to 60E for switching the flow of hydraulic oil, and an oil cooler provided on a return pipe from the hydraulic valves 50A to 60E to the hydraulic oil tank 57 62. The hydraulic valves 60A to 60E are incorporated in a hydraulic valve unit 60 mounted on the traveling machine body 1.

  The work unit charge pump 59 is hydraulically connected to the hydraulic cylinder 4 for raising and lowering the cutting via the hydraulic valve 60A for raising and lowering the cutting. The hydraulic cylinder 4 for raising and lowering the cutting is operated by tilting a cutting posture lever (not shown) in the driving operation unit (cab) 5 in the front-rear direction, so that the operator can raise the cutting unit 3 to an arbitrary height (for example, the cutting work height). Or it is configured to be moved up and down to a non-working height. On the other hand, the working unit charge pump 59 is hydraulically connected to the reel elevating hydraulic cylinders 27L and 27R via the reel elevating hydraulic valve 60B. The operator operates the hydraulic cylinders 27L and 27R for lifting and lowering the reel by operating the tilting lever (not shown) in the left and right directions, and the operator raises and lowers the raking reel 14 to an arbitrary height, so that the uncut kernels in the field can be obtained. It is configured to cut culms.

  The work unit charge pump 59 is hydraulically connected to the auger lifting hydraulic cylinder 55 via the auger lifting hydraulic valve 60C. The auger lifting hydraulic cylinder 55 is operated by tilting the grain discharge lever 155 in the driving operation unit (cab) 5 in the front-rear direction, and the operator throws the grain discharge auger 164 of the grain discharge auger 164 in the grain discharge conveyor 8. Is moved up and down to an arbitrary height. In addition, the grain discharge auger 164 is horizontally rotated by the electric motor 165 together with the vertical feed auger 162 and the bevel gear mechanism 163, and the paddy throw is moved laterally. That is, the grain throwing port is located above the truck bed or container, and the grains in the Glen tank 6 are discharged into the truck bed or container.

  The hydraulic oil tank 57 and the work unit charge pump 59 are hydraulically connected to the left body lifting hydraulic cylinder 56L via the left body lifting hydraulic valve 60D. On the other hand, the hydraulic oil tank 57 and the working unit charge pump 59 are hydraulically connected to the right body lifting hydraulic cylinder 56R via the right body lifting hydraulic valve 60E. The right and left body lifting hydraulic cylinders 56L, 56R operate independently of each other to independently raise and lower the left and right of the traveling body 1.

  Therefore, when the right and left body frame lifting hydraulic cylinders 56L, 56R are simultaneously operated to lower the left and right track frames 50, 50 with respect to the traveling body 1, the traveling body 1 is moved to the right and left crawler tracks 2, 2 grounding portion. , And the relative height (vehicle height) of the traveling body 1 with respect to the crawler belts 2 and 2 is increased. Conversely, when the left and right track frames 50, 50 are simultaneously raised with respect to the traveling body 1, the traveling body 1 approaches the crawler belts 2 on both left and right sides (down), and the crawler belt 2 of the traveling body 1 , 2 relative to the ground contact portion (vehicle height) is reduced.

  Then, the left body frame lifting hydraulic cylinder 56L is operated to lower the left track frame 50 with respect to the traveling body 1, or the right body lifting hydraulic cylinder 56R is operated to raise the right track frame 50 with respect to the traveling body 1. (Or even if both operations are performed simultaneously), the traveling body 1 inclines to the lower right. Conversely, the right body frame lifting hydraulic cylinder 56R is operated to lower the right track frame 50 with respect to the traveling body 1, or the left body body lifting hydraulic cylinder 56L is operated to move the right track frame 50 to the traveling body 1. When the vehicle is raised (or both of the operations are performed simultaneously), the traveling body 1 tilts to the left.

  The hydraulic oil tank 57, the working unit charge pump 59, and the hydraulic valve unit 60 are mounted on the traveling machine body 1 and connected to each other via hydraulic piping 181 to 183. On the traveling body 1, a hydraulic oil tank 57 is installed on the front left side, while a working unit charge pump 59 is fixed to the front of the engine 7 mounted on the front right side, and a strainer 58 provided in the hydraulic oil tank 57 is provided. The working unit charge pump 59 is connected by a hydraulic pipe 181. A hydraulic valve unit 60 is disposed on the traveling body 1 at a position behind the engine 7, and the discharge side of the working unit charge pump 59 is connected to the hydraulic valve unit 60 via a hydraulic pipe 182. Further, the hydraulic valve unit 60 is connected to the hydraulic oil tank 57 via a hydraulic pipe 183 serving as a hydraulic oil return pipe and an oil cooler 62.

  The hydraulic oil tank 57 is installed on the traveling body 1 at a space position surrounded by the feeder house 11 and the beater 18, and the engine 7 and the hydraulic oil tank 57 are arranged side by side in front of the traveling body 1. I have. That is, the hydraulic oil tank 57 is disposed in a space surrounded by the feeder house 11 and the machine housing of the threshing unit 9, and it is possible to suppress the accumulation of dust from the reaping unit 3 on the hydraulic oil tank 57, It is also possible to prevent contamination of the hydraulic oil due to intrusion of dust from the oil supply port 184 and the like. Further, since the cooling air from the engine 7 flows into the installation space of the hydraulic oil tank 57, it is possible to suppress an increase in the hydraulic oil temperature without providing an oil cooler on the working hydraulic circuit 180, and to make each hydraulic member It can be driven properly.

  The hydraulic oil tank 57 has an oil supply port 184 protruding toward the left side (outside the machine) on the left side (the outside side of the machine), and has a strainer 58 that can be inserted and withdrawn from the left side. Therefore, by removing the threshing cover 185 provided on the left side (outside of the machine) of the threshing unit 9, the fuel supply port 184 and the strainer 58 can be easily accessed. Therefore, the work of refilling the hydraulic oil tank 57 and the work of replacing the oil filter in the strainer 58 can be easily performed, and the maintainability of the working hydraulic circuit 180 can be improved.

  The hydraulic pipes 181 and 183 connected to the hydraulic oil tank 57 extend right and left in front of the hydraulic oil tank 57 and the engine 7, and the hydraulic pipe 182 is disposed in front of the engine 7. And the strainer 58. That is, the hydraulic pipes 181 and 183 extend along the output shaft 65 of the engine 7 toward the hydraulic oil tank 57 bypassing the front of the engine 7. The hydraulic pipes 182 and 183 extend rearward below the cooling fan 149 provided on the right side of the engine 7 and are connected to the hydraulic valve unit 60. Therefore, the hydraulic pipes 181 to 183 are arranged so that the pipe length is shortened at a position where the hydraulic pipes 181 to 183 are not easily affected by the radiant heat from the engine 7, and the temperature of the hydraulic oil flowing through the hydraulic pipe is prevented from increasing. it can.

  As shown in FIGS. 7, 10 and 12 to 15, the traveling system hydraulic circuit 200 includes a linear pump 64 a, a linear motor 64 b, a slewing pump 70 a, a slewing motor 70 b, a transmission charge pump 151, an oil filter 152, and an oil A cooler 153 is provided. The rectilinear pump 64a and the rectilinear motor 64b in the rectilinear hydraulic continuously variable transmission 64 are connected in a closed loop by a rectilinear closed oil passage 201. On the other hand, the swing pump 70 a and the swing motor 70 b in the swing hydraulic continuously variable transmission 70 are connected in a closed loop by a swing closed oil passage 202. By driving the rectilinear pump 64a and the swirl pump 70a with the rotational power of the engine 7 and controlling the swash plate angle of the rectilinear pump 64a and the swirl pump 70a, the discharge direction and discharge of hydraulic oil to the rectilinear motor 64b and the swivel motor 70b are controlled. The amount is changed, and the rectilinear motor 64b and the turning motor 70b rotate forward and backward.

  The traveling system hydraulic circuit 200 includes a straight valve 203 that performs switching operation in response to a manual operation of the main shift lever 44, and a straight cylinder 204 connected to the transmission charge pump 151 via the straight valve 203. When the rectilinear valve 203 is switched, the rectilinear cylinder 204 operates to change the swash plate angle of the rectilinear pump 64a, and to change the rotational speed of the rectilinear motor shaft 260 of the rectilinear motor 64b in a stepless manner or to reverse the rotational speed. The operation is performed. Further, the traveling system hydraulic circuit 200 also includes a hydraulic servo mechanism 205 for straight-ahead shifting. The hydraulic servo mechanism 205 executes a feedback operation in which the rectilinear valve 203 returns to neutral by the swash plate angle control of the rectilinear pump 64a, and changes the swash plate angle of the rectilinear pump 64a in proportion to the manual operation amount of the main shift lever 44. The rotation speed of the straight motor shaft 260 of the straight motor 60b is changed.

  The traveling system hydraulic circuit 200 includes a swivel valve 206 that performs a switching operation in response to a manual operation of the steering handle 43, and a swivel cylinder 207 connected to the transmission charge pump 151 via the swivel valve 206. When the swivel valve 206 is switched, the swivel cylinder 207 operates to change the swash plate angle of the swivel pump 70a, and to continuously change or reverse the rotation speed of the swivel motor shaft 261 of the swivel motor 70b. A left-right turning operation is performed, and the traveling body 1 changes the traveling direction to the left and right to change the direction or correct the course on the field headland. Further, the traveling system hydraulic circuit 200 also includes a hydraulic servo mechanism 208 for turning gear. The hydraulic servo mechanism 208 performs a feedback operation in which the swivel valve 206 returns to the neutral position by the swash plate angle control of the swing pump 70a, and changes the swash plate angle of the swing pump 70a in proportion to the manual operation amount of the steering handle 43. The rotation speed of the swing motor shaft 261 of the swing motor 70b is changed.

  As shown in FIG. 13, a charge branch oil passage 219 (details will be described later) is connected to all the oil passages 201a, 201b, 202a, and 202b of both closed oil passages 201 and 202. A check valve 211 for the first straight oil passage 201a is provided between the charge branch oil passage 219 and the first straight oil passage 201a. A check valve 211 for the second straight oil passage 201b is provided between the charge branch oil passage 219 and the second straight oil passage 201b. Accordingly, the straight traveling oil passage 201 includes two check valves 211. A check valve 212 for the first swirl oil passage 202a is provided between the charge branch oil passage 219 and the first swirl oil passage 202a. A check valve 212 for the turning second oil passage 202b is provided between the charge branch oil passage 219 and the turning second oil passage 202b. Therefore, the turning closed oil passage 202 is also provided with two check valves 212.

  A straight traveling bypass oil passage 213 is connected to the straight traveling first oil passage 201a and the straight traveling second oil passage 201b. The rectilinear bypass oil passage 213 is provided with a rectilinear bidirectional relief valve 215. A turning bypass oil passage 214 is connected to the turning first oil passage 202a and the turning second oil passage 202b. The turning bypass oil passage 214 is provided with a turning-side bidirectional relief valve 216. Accordingly, each of the oil closing passages 201 and 202 has one bidirectional relief valve 215 and 216.

  The suction side of the transmission charge pump 151 is connected to a strainer 217 in the transmission case 63 via a hydraulic pipe 221. A charge introduction oil passage 218 is connected to the discharge side of the transmission charge pump 151 via a hydraulic pipe 222, and an oil filter 152 is provided on the hydraulic pipe 222. A charge branch oil passage 219 connected to both closed oil passages 201 and 202 is connected to the downstream side of the charge introduction oil passage 218. Therefore, while the engine 7 is operating, the hydraulic oil from the transmission charge pump 151 is constantly replenished to both the closed oil passages 201 and 202.

  Further, the charge branch oil passage 219 is connected to the rectilinear cylinder 204 via the rectilinear valve 203, and is connected to the turning cylinder 207 via the turning valve 206. Further, the charge branch oil passage 219 is connected to the transmission case 63 via the excess relief valve 220 and the hydraulic piping 223, and an oil cooler 153 is provided on the way of the hydraulic piping 223. Therefore, when the surplus hydraulic fluid from the transmission charge pump 151 is returned into the transmission case 63 via the surplus relief valve 220, it is cooled by the oil cooler 153.

  The hydraulic pipe 223 is connected by a bypass pipe 224 that bypasses the feed pipe 223a and the return pipes 223b to 223d. The bypass pipe 224 is fixed above the continuously variable transmission case 323 on the side of the transmission case 63. I have. By disposing the hydraulic pipe 223 and the bypass pipe 224 above the continuously variable transmission case 323, when the hydraulic oil temperature is low, for example, when the engine 7 is started, the hydraulic oil can be circulated without being sent to the oil cooler 153. it can. Therefore, even if the viscosity of the hydraulic oil is high in a state where the hydraulic oil temperature is low, the hydraulic oil can be smoothly circulated in the traveling system hydraulic circuit 200, and can be circulated in the transmission case 63 and the continuously variable transmission case 323. Lubricate each transmission mechanism.

  As described above, the oil cooler 153 is connected to the hydraulic pipes 221 to 223 that circulate the hydraulic oil in the transmission case 63 and the continuously variable transmission case 323 (drive device), and the bypass pipe (bypass) that bypasses the oil cooler 153. A path 224 is provided in the hydraulic pipe 223, and the bypass pipe 224 is provided integrally with the transmission case 63 and the continuously variable transmission case 323. Accordingly, by connecting the transmission case 63 and the continuously variable transmission case 323 to the oil cooler 153, the piping path for circulating the transmission case 63 and the continuously variable transmission case 323 becomes longer, but the length can be shortened by the bypass pipe 224.

  By providing a bypass pipe 224 in the hydraulic pipe 223 and bypassing the oil cooler 153, high-viscosity hydraulic oil can be circulated when the engine is started in a cold region, for example, and the transmission case 63 and the continuously variable transmission case 323 can be circulated. Can maintain good lubricity. Further, by providing the transmission case 63 and the continuously variable transmission case 323 integrally with the transmission case 63 and the continuously variable transmission case 323, the bypass pipe 224 can be incorporated into the transmission case 63, so that the assemblability is improved and the hydraulic device in the transmission case 63 is improved. Maintenance becomes easier.

  A connection member (connection joint) 225 having two communication ports 225a and 225b is provided in the continuously variable transmission case 323. One end of the bypass pipe 224 is connected to the communication port 225a of the connecting member 225, and the feed pipe 223a communicating with the oil cooler is connected to the communication port 225b of the connecting member 225. A connecting portion between the connecting member 225 and the bypass pipe 224 is provided with a bypass relief valve 226 (see FIG. 13). The connecting member 225 is provided on the straight hydraulic continuously variable transmission 64 side (front side) of the upper surface of the continuously variable transmission case 323, and the communication port 225a is disposed below the communication port 225b. Further, the communication ports 225a and 225b of the connecting member 225 are respectively provided so as to protrude rearward (toward the turning hydraulic continuously variable transmission 70).

  The return pipes 223b to 223d of the oil cooler 153 among the hydraulic pipes 223 are between the upstream return pipe 223b having one end connected to the oil cooler 153 and the downstream return pipe 223d having one end connected to the upper surface of the transmission case 63. Is provided with a metal relay pipe 223c. The metal relay pipe 223c is fixed to the turning hydraulic continuously variable transmission 70 side (rear side) of the upper surface of the continuously variable transmission case 323.

  A connecting plate (fixing member) 227 fixed to the side surface of the metal relay pipe 223c is fastened and fixed to the upper surface of the portion of the continuously variable transmission case 323 that accommodates the swivel valve 206 (the rear end side of the continuously variable transmission case 323). Thus, the metal relay pipe 223c is fixedly disposed above the continuously variable transmission case 323 so as to extend in a direction parallel to the pump shaft 259. Further, the metal relay pipe 223c has a T-shape in which a communication port (branch pipe) 223e protrudes forward from the middle part (toward the straight-travel hydraulic continuously variable transmission 64). That is, the communication port 223e in the middle of the metal relay pipe 223c is provided at the same height as the communication port 225a of the connecting member 225, and protrudes toward the communication port 225a of the connecting member 225.

  The bypass pipe 224 extends in the front-rear direction above the continuously variable transmission case 323 so as to connect the communication port 225a of the connecting member 225 arranged in front and rear with the communication port 223e of the metal relay pipe 223c. The bypass pipe 224 connects the metal pipe 224a having one end connected to the communication port 225a of the connecting member 225, and the hydraulic relay pipe (resin pipe) 224b having one end connected to the communication port 223e of the metal relay pipe 223c. It is configured. The metal pipe 224a is provided with a bypass relief valve 226 that opens and closes a connection portion of the connection member 225 with the communication port 225a.

  The bypass path for bypassing the oil cooler 153 is composed of a metal relay pipe 223c, a bypass pipe 224, and a connecting member 225 that are integrally assembled with the continuously variable transmission case 323. Therefore, hydraulic components other than the feed pipe 223a and the upstream return pipe 223b connected to the oil cooler 153 can be integrally assembled with the continuously variable transmission case 323, and the transmission case 63 to which the continuously variable transmission case 323 is assembled is assembled. Ease and maintainability can be improved.

  Hydraulic pipes 222 and 223 connected to the transmission case 63 and the continuously variable transmission case 323 are piped so as to go under the straight connecting link 345 and the turning connecting link 346 connected to the steering case 318. Therefore, not only can the straight connection link body 345 and the turning connection link body 346 be prevented from contacting the hydraulic pipes 222 and 223, but also the maintenance of each of the straight connection link body 345 and the rotation connection link body 346 becomes easy. Further, even when the hydraulic pipes 222 and 223 vibrate under the influence of the drive of the transmission case 63 or the like, it is possible to prevent the breakage due to the contact with the straight connecting link body 345 and the turning connecting link body 346.

  More specifically, a hydraulic pipe 222 connecting the charge pump 151 and the oil filter 152 is piped in the front-rear direction so as to pass below the rectilinear relay shaft 352 of the rectilinear connecting link 345. A hydraulic pipe 222 that connects the transmission case 63 with the transmission case 63 is provided in the front-rear direction so as to pass below the first relay rod of the turning connection link body 346. Further, the downstream return pipe 223 d connected to the transmission case 63 is bent so as to pass below the shaft support 366 in the turning connection link 346, and is connected to the metal relay pipe 223 c fixed to the continuously variable transmission case 323. Have been.

  Next, the engine room 146 in which the engine 7 is installed will be described with reference to FIG. As shown in FIG. 8 and the like, a pair of left and right engine room supports 147 is erected on the rear side of the cab 5 on the upper surface of the traveling body 1, and a rear plate 148 is stretched between the left and right engine room supports 147. It covers the rear of the engine room 146 below the seat 42. A box-shaped wind tunnel case 170 is provided upright on a right engine room support 147 provided at the right end of the cab 5 of the traveling body 1 via an opening / closing fulcrum shaft 171. A dust-removing net is provided on the outside opening on the right side of the wind tunnel case 170, and the presence of the dust-removing net prevents the ingress of straw chips and the like into the interior of the wind tunnel case 170 and thus the interior of the engine room 146. In the wind tunnel case 170, an oil cooler 153 in the traveling hydraulic circuit 200 and an oil cooler 62 in the working hydraulic circuit 180 are vertically arranged.

  A water-cooling radiator 154 is erected inside the wind tunnel case 170 on the upper surface side of the traveling machine body 1, and the radiator 154 faces the cooling fan 149 of the engine 7. A shroud 150 that covers the entire ventilation area of the radiator 154 is provided, and a cooling fan 149 is disposed in an opening formed in the shroud 150. An oil cooler 153 is provided in the wind tunnel case 170. By the rotation of the cooling fan 149, outside air (cooling air) is taken into the wind tunnel case 170 from the outside opening on the right side of the wind tunnel case 170, and the dust-removed cooling wind is fed into the engine room 146 from the inside opening on the left side of the wind tunnel case 170. Send to Thus, the oil cooler 153, the radiator 154, the engine 7, and the like are cooled by the cooling air flowing into the engine room 146.

  Next, a driving operation structure of the steering handle 43 and the like will be described with reference to FIGS. 8, 10, and 16 to 21. As shown in FIGS. 8, 10, and 16 to 21, the cab 5 includes a step frame 311 that constitutes a flat portion on which the operator mounts a foot. A plurality of support frames 312 are erected on the upper surface of the traveling body 1, and a step frame 311 is installed on the upper end of the support frame 312. A step 313 for getting on and off is fixed to the side surface of the supporting frame 312 on the right side of the outside of the step frame 311, and an oil filter 152 is attached to the front end of the step frame 311 on the upper surface of the traveling body 1.

  Further, a steering case 318 having a turning input shaft 316 and a main speed change input shaft 317 is provided. The both ends of the case supporting horizontal frame 319 are connected between the left and right support leg frames 312 on the front lower surface side of the step frame 311, and the steering case 318 is detachably fastened and fixed to the substantially horizontal case supporting horizontal frame 319. A turning input shaft 316 protrudes upward from the upper surface of the steering case 318, and the turning input shaft 316 is connected to the steering handle 43 via the steering shaft 321, and from the left side of the steering case 318 to the left. The main transmission input shaft 317 is protruded, and the main transmission input shaft 317 is connected to the main transmission lever 44 via the main transmission operation rod 322.

  As can be understood from the above description, the driver's cab 5 (control section) on the step frame 311 provided on the upper end side of the support leg frame 312 group is provided with the main shift lever 44 as a straight-ahead operating tool and a turning operation And a steering handle 43 which is a turning operation tool. A case support horizontal frame 319 is attached to the left and right support frames 312 at the front lower side of the step frame 311. The case support horizontal frame 319 is provided with a steering case 318 for interlocking the main transmission lever 44 and the steering handle 43 with the driving device (the continuously variable transmission case 323 and the transmission case 63). There are two case support horizontal frames 319 on the front and rear sides of the steering case 318. The steering case 318 is supported by two front and rear case supporting horizontal frames 319.

  An oil filter 152 fixed to a step frame 311 at a front end position is disposed on the left side of the steering case 318 in the front portion of the traveling body 1. The oil filter 152 is fixed to a portion protruding leftward from the left support frame 312 at the front of the step frame 311 so as to be disposed in front of the continuously variable transmission case 323. That is, the oil filter 152 is fixed to the left side of the front end of the step frame 311 via the filter fixing bracket 349, and thus is disposed in front of the continuously variable transmission case 323 fixed to the right side of the transmission case 63. Therefore, when connecting the transmission charge pump 151 and the charge introduction oil passage 218 to the hydraulic pipe 222 where the oil filter 152 is provided in the middle of the pipe, the hydraulic pipe 222 can be configured to be short.

  A case supporting horizontal frame 319 is bridged and attached between the left and right support frames 312 at the front lower side of the step frame 311. The main supporting lever 44, the steering handle 43, and the driving device (stepless speed changing) are mounted on the case supporting horizontal frame 319. Since the steering case 318 that connects the case 323 and the transmission case 63) is attached, the rigidity of the front portion of the traveling machine body 1 (particularly, the vicinity of the cab 5) can be improved by the presence of the case supporting horizontal frame 319. The steering case 318 can be supported with high rigidity by using the case supporting horizontal frame 319 that plays a role of reinforcing the front part of the traveling body 1. Therefore, there is no large deviation between the operation amounts of the main transmission lever 44 and the steering handle 43 and the outputs of the driving devices (the continuously variable transmission case 323 and the transmission case 63), and the traveling state is not expected by the operator. Can be eliminated. The case support horizontal frame 319 for reinforcement can also be used as a mounting portion of the steering case 318, and a dedicated mounting base for the steering case 318 is not required, which contributes to cost reduction.

  There is provided a continuously variable transmission case 323 in which the straight hydraulic continuously variable transmission 64 and the turning hydraulic continuously variable transmission 70 are assembled. A continuously variable transmission case 323 is fixed to the upper right side of the transmission case 63, and operation arms 355, 369 for straight traveling and turning are arranged on the front and rear surfaces of the continuously variable transmission case 323. That is, the straight hydraulic continuously variable transmission 64 and the turning hydraulic continuously variable transmission 70 are arranged in front and rear on the right side surface of the transmission case 63 opposite to the feeder house 11.

  Therefore, a space is created on the side (left side) of the transmission case 63 on the side of the feeder house 11, so that the degree of freedom of design in the reaping unit 3 is increased, and the wiping amount of the reaping unit 3 and the reaping width of the grain header 12 are increased. It can be configured with the optimum size. Further, since the installation width of the feeder house 11 in the left-right direction is increased, the feeder house 11 can be installed on a side close to the position of the center of gravity when the grain header 12 is moved up and down. Can be increased.

  On the front outer surface of the continuously variable transmission case 323, a straight operation shaft 325 as a straight output control unit is projected forward, and on the rear outer surface of the continuously variable transmission case 323, a turning operation shaft 326 as a rotation output control unit is directed rearward. To protrude. Although not shown in detail, an operation arm body 355 for straight traveling is connected to the straight operation shaft 325, and an operation arm body 369 for turning is connected to the turning operation shaft 326. Steering operation of the steering handle 43 and the main shift lever are performed by connecting operation arms 355 and 369 for straight traveling and turning, respectively, to a straight connecting link 345 and a turning connecting link 346 provided on the back side of the steering case 318. By the shift operation of 44, the linearly traveling hydraulic continuously variable transmission 64 and the turning hydraulic continuously variable transmission 70 are operated and controlled, so that the course and the moving speed of the left and right crawler belts 2 can be changed.

  A cab (control section) 5 provided in front of the traveling body 1 includes a main shift lever (straight operation tool) 44 for straight-ahead operation and a steering handle (slewing operation tool) 43 for turning operation. The steering column 41 is arranged on a side portion near the driving device (the transmission case 63 and the continuously variable transmission case 323). A steering case 318 for changing the output from the transmission case 63 in accordance with the amount of operation of the steering handle 43 and the main shift lever 44 at the front of the traveling body 1 below the cab 5 includes a straight-travel hydraulic continuously variable transmission. 64 and a continuously variable transmission case 323 provided with a swing hydraulic type continuously variable transmission 70.

  In this case, the steering handle 43 is disposed in the front center portion of the driver's cab 5 in front of the driver's seat 42, and the steering handle 43 is steered to the left side, which is a side portion closer to the driving device (the continuously variable transmission case 323 and the transmission case 63). The main speed change lever 44 is arranged on the column 41. That is, the steering case 318 is arranged below the steering handle 43, and the continuously variable transmission case 323 is arranged below the steering column 41 on which the main transmission lever 44 is installed. Thus, the respective components of the operation system mechanism connected from the steering handle 43 and the main transmission lever 44 to the continuously variable transmission case 323 via the steering case 318 can be arranged close to each other, and the respective components of the operation system mechanism can be connected. Each of the link mechanisms 321, 322, 345, and 346 is configured to be short, so that fluctuation and deformation thereof can be suppressed. Accordingly, a deviation between the operation amount of the main transmission lever 44 or the steering handle 43 and the output of the driving device (the continuously variable transmission case 323 and the transmission case 63) is suppressed, and a stable traveling state according to the operation of the operator is maintained. it can.

  A battery 230 that supplies power to the engine 7 is disposed below the cab 5 in the front part of the traveling body 1, behind the steering case 318 and beside the continuously variable transmission case 32. That is, the battery 230 that supplies power to the engine 7 and the like is arranged in a region surrounded by the steering case 318, the driving device (the continuously variable transmission case 323 and the transmission case 63), and the engine 7 on the lower side of the cab 5. . Thus, the dead space below the cab 5 can be effectively used not only as an arrangement space for the steering case 318 and the continuously variable transmission case 323 but also as an arrangement space for the battery 230. For this reason, the battery 230 can be arranged close to the engine 7 and the cab 5, and the electric system can be made compact. In addition, it is possible to avoid an increase in the size of the combine in order to secure an arrangement space for the battery 230.

  A driver's cab (control section) 5 is formed on a plurality of support frames 312 erected on the upper surface side of the traveling body 1. Then, the steering case is fixed to a case supporting horizontal frame (case supporting frame) 319 that is installed in the middle of the plurality of support leg frames 312, and is disposed above the continuously variable transmission case 323 and the battery 230. As described above, since the battery 230 and the steering case 318 are arranged in the upper and lower stages below the front portion of the step frame 311, the space formed in the area adjacent to the continuously variable transmission case 323 at the rear of the steering case 318 is used. As a result, the electric wiring for supplying power to the electric members of the various parts including the engine 7 and the cab 5 can be easily extended. In addition, it contributes to improvement in the workability of assembling and maintaining the steering case 318 and the battery 230.

  Further, since the oil filter 152 for filtering the hydraulic oil in the driving device (the continuously variable transmission case 323 and the transmission case 63) is disposed in the above-described region below the cab 5, the driving device (the continuously variable transmission case 323) is disposed. In addition, the length of the hydraulic pipe 222 connecting the transmission case 63) and the oil filter 152 can be shortened, and the hydraulic pipe 222 can be easily handled.

  In the upper part of the steering case 318, a lateral main transmission input shaft 317 is disposed on one of the front and rear sides of the turning input shaft 316, and a lateral straight output shaft 350 is disposed on the other. . The main transmission input shaft 317 and the straight traveling output shaft 350 extend left and right in parallel with each other in plan view, and are rotatably supported by the steering case 318. The main transmission input shaft 317 and the straight output shaft 350 are supported so as to project outward (leftward) from the left side surface of the steering case 318. A turning output shaft 164 extending in a direction orthogonal to the straight-moving output shaft 350 is supported on the back of the steering case 318 and below the straight-moving output shaft 350 so as to project outward (rearward) from the steering case 318. .

  The rectilinear connection link body 345 is connected to the rectilinear output shaft 350 by inserting the protruding end (left end) of the rectilinear output shaft 350 into one end (right end) of the cylindrical shaft connecting member 351. At the other end (left end) of the shaft coupling body 351, a straight traveling relay shaft 352 supported by a shift output support bracket 328 fixed to a support frame 312 at the left front position of the driver's cab 5 is inserted. By adjusting the left-right position of the rectilinear relay shaft 352 with respect to the shaft connection body 351, the installation position of the rectilinear connection link body 435 in the left-right direction is adjusted.

  One end (rear end) of a rectilinear relay arm body 353 extending in the front-rear direction is fixed to the other end of the rectilinear relay shaft 352. The other end (front end) of the relay arm body 353 is swung up and down. The other end (front end) of the rectilinear relay arm body 353 is connected to one end (upper end) of a vertically extending connecting rod 354 extending vertically. The operation arm body 355 is connected.

  The rectilinear connecting link body 345 connects the transit relay shaft 352 extending in the left-right direction to a position on the extension of the rectilinear output shaft 350 by a shaft connecting body 351, and the speed change output fixed to the support frame 312. It is supported by a support bracket 328. Accordingly, the rectilinear relay shaft 352 rotates together with the rectilinear output shaft 350, and swings the front end of the rectilinear relay arm body 353 fixed to the left end of the rectilinear relay shaft 352. Then, the connecting rod 354 for straight movement having both ends pivotally attached to the front end of the straight-forward relay arm body 353 and one end of the straight-forward operation arm body 355 moves up and down in response to the swing of the straight-forward relay arm body 353. Thus, the linear operation shaft 325 having the protruding end (front end) fixed to the other end of the operation arm body 355 is rotated.

  On the other hand, the turning connection link body 346 has a first end (a distal end) of an output arm body 362 having one end (a base end) fixed to a protruding end (a rear end) of the turning output shaft 361, and a first extending left and right side. One end (right end) of the relay rod 363 is connected. The first relay rod 363 extends left and right at a position rearward of the steering case 318 so as to straddle the front upper side of the continuously variable transmission case 323. It is connected to a first turning relay arm body 364 fixed to one end (front end) of the shaft 365. The turning relay shaft 365 is supported by being penetrated by a tubular shaft support 366.

  On the other hand, a second relay rod 368 extending left and right extends to the other end (distal end) of a turning operation arm body 369 having one end (base end) fixed to a protruding end (rear end) of the turning operation shaft 326. One end (right end) is connected. The second relay rod 368 extends left and right along the back of the transmission case 63 and the continuously variable transmission case 323, and the other end (left end) of the second relay rod 368 is connected to one end (rear end) of the turning relay shaft 365. (End) is connected to the second turning relay arm body 367 fixed to the end.

  The other end of the support plate 370 having one end fixed to the outer peripheral surface of the shaft support 366 is bolted to the upper surface of the transmission case 63 so that the shaft support 366 that supports the turning relay shaft 365 is bolted to the upper surface of the transmission case 63. And is fixed at the left side position of the continuously variable transmission case 323. A pipe fixing portion 372 for fixing the position by passing a hydraulic pipe 223 connected to the transmission case 63 is provided on the outer peripheral surface of the shaft support 366.

  The turning connection link body 346 includes a first relay rod extending in the left-right direction on an output arm body 362 whose tip swings left and right in accordance with rotation of a turning output shaft 361 protruding from the steering case 318. 363 The right end is pivoted. Therefore, the first relay rod 363 moves in the left-right direction in accordance with the swing of the output arm body 362, and the distal end of the first turning relay arm body 364 whose base end is fixed to the front end of the turning relay shaft 365 is moved left and right. Rock it. The swing of the tip of the first turning relay arm body 364 causes the turning relay shaft 365 pivotally supported by the shaft support 366 to rotate, and at the same time, the base end is fixed to the rear end of the turning relay shaft 365. The tip of the second turning relay arm 367 swings right and left. Then, a second relay rod 368 having both ends pivotally attached to the front end of the second turning relay arm body 367 and one end of the turning operation arm body 369, respectively, in accordance with the swing of the second turning relay arm body 367. , The turning operation shaft 326 having the protruding end (rear end) fixed to the other end of the operation arm body 369 is turned.

  The main transmission input shaft 317 protrudes from the steering case 318 toward the left and right central sides of the traveling machine body 1. A protruding end (left end) of the main transmission input shaft 317 is supported by a main transmission input support bracket 381 fixed to a step frame 311 on the left edge on the transmission case 63 side. One end (front end) of the main transmission arm body 382 is connected to a protruding end (left end) of the main transmission input shaft 317, and the other end (rear end) of the main transmission arm body 382 is connected to the main transmission lever 44. Is connected to the main speed change operation rod 322 connected to the main transmission.

  A straight hydraulic continuously variable transmission 64 and a turning hydraulic continuously variable transmission 70 for shifting the power of the engine 7 are arranged side by side on the cab (control section) 5 side of the left and right side surfaces of the transmission case 63. . A straight-moving operation shaft 325 of the straight-moving hydraulic continuously variable transmission 64 and a turning operation shaft 326 of the swing-hydraulic continuously-variable transmission 70 are disposed so as to be distributed back and forth. Since the straight hydraulic continuously variable transmission 64 and the turning hydraulic continuously variable transmission 70 are arranged side by side on the driver's cab 5 side, the connection structure with the steering case 318 can be shortened.

  Further, by arranging the straight-moving operation shaft 325 and the turning operation shaft 326 forward and backward, the same positional relationship as the straight-moving output shaft 350 and the turning output shaft 361 arranged front and rear in the steering case 318 can be obtained. Thus, the structure of the link mechanism from the steering case 318 to the straight hydraulic continuously variable transmission 64 and the swing hydraulic continuously variable transmission 70 can be simplified, and the continuously variable transmission case 323 and the steering case 318 can be arranged below the cab 5. And can be installed compactly.

  The steering case 318 is disposed below the cab (control section) 5 and above the driving devices (the continuously variable transmission case 323 and the transmission case 63), and the straight output shaft 350 and the turning output shaft 361 project from the steering case 318. It is established. The straight connecting link 345 connecting the straight output shaft 350 and the straight operating shaft 325 and the turning connecting link 346 connecting the turning output shaft 361 and the turning operating shaft 326 are each connected to the steering case 318 in plan view. It is installed between the step shifting cases 323. That is, since the straight connecting link body 345 and the turning connecting link body 346 are arranged on the cab 5 side together with the transmission case 63, the assembling property and the maintenance property are improved.

  A straight link member 345 for interlocking the steering case 318 and a straight operation shaft 325 as a straight output control unit is supported by a support frame 312 that supports the cab 5. The steering case 318 is fixed to a case support horizontal frame (case support frame) 319 that is installed in the middle of the left and right support frame 312 that supports the front position of the cab (control section) 5. Then, the straight connecting link body 345 is supported by the left support frame 312 on the side of the transmission case 63 (the continuously variable transmission case 323).

  A straight connection link body 345 for linking the steering case 318 and a straight operation shaft 325 (straight output control unit) provided on the drive unit (the continuously variable transmission case 323 and the transmission case 63) is connected to a support frame 312 for supporting the cab 5. Have been supported. Therefore, even if the bending of the straight connecting link body 345 is exerted on the straight connecting link body 345 due to the vibration of the driving device (the continuously variable transmission case 323 and the transmission case 63), the straight connecting link body 345 is highly rigid by the support frame 312 supporting the driver's cab 5. , And the fluctuation and deformation of the straight connecting link body 345 can be suppressed. Therefore, there is no large deviation between the operation amount of the main transmission lever 44 or the steering handle 43 and the output of the drive device (the continuously variable transmission case 323 and the transmission case 63), and the traveling state is not expected by the operator. Can be eliminated.

  A continuously variable transmission case 323 containing a straight hydraulic continuously variable transmission 64 and a swing hydraulic continuously variable transmission 70 is fixed above the right side surface of the transmission case 63. Then, the turning connection link body 346 is supported on the upper surface of the transmission case 63 and on the continuously variable transmission case 323 side. By utilizing the space between the feeder house 11 and the driver's cab 5, the revolving link body 346 can be compactly and highly rigidly supported on the transmission case 63 having the same vibration system as the continuously variable transmission case 323. Accordingly, the bending and pulling of the turning connection link body 346 due to the mechanical vibration is suppressed, and the operation amount of the main transmission lever 44 and the steering handle 43 and the output of the driving device (the continuously variable transmission case 323 and the transmission case 63) are output. There is no significant gap between them, and it is possible to eliminate the possibility of the traveling state not being assumed by the operator.

REFERENCE SIGNS LIST 1 traveling body 3 reaping section 5 cab 7 engine 9 threshing section 11 feeder house 17 supply conveyor 311 step frame 312 support frame 313 step-on / off step 314 hydraulic valve unit body 315 hydraulic oil tank 316 turning operation shaft 317 main transmission input shaft 318 steering Case 319 Case support horizontal frame 321 Steering shaft 322 Main transmission operation rod 323 Continuously variable transmission case 325 Straight operation shaft 326 Swing operation shaft 327 Vertical support 328 Support frame 329 Hydraulic piping 345 Straight connection link body 346 Swirl connection link body 349 Filter fixing bracket 350 Straight output shaft 351 Shaft connected body 352 Straight running relay shaft 353 Straight running relay arm body 354 Connecting rod 355 Operation arm body 361 Turning output shaft 362 Output arm body 363 First relay rod 364 First swiveling relay arm 365 Swiveling relay shaft 366 Shaft support 367 Second swiveling relay arm 368 Second relay rod 369 Operation arm 370 Support plate 371 Pipe fixing part

Claims (3)

In a combine having a drive unit that shifts the power of the engine mounted on the traveling body and transmits the power to the left and right traveling units, the harvesting unit includes a feeder house that transports the harvested culm and throws it into the threshing unit,
An oil cooler is connected to a hydraulic pipe that circulates hydraulic oil in the drive device, and a bypass path that bypasses the oil cooler is provided in the hydraulic pipe, and the bypass path is provided integrally with the drive device. A combine that is characterized by being done. A connection member having two communication ports is provided in the driving device, and one end of the bypass path is connected to one communication port of the connection member, and the oil is connected to the other communication port of the connection member. The hydraulic piping communicating with the cooler is connected,
The combine according to claim 1, wherein a relief valve is provided at a connection portion between the connection member and the bypass path.   The combine according to claim 2, wherein the connecting member protrudes from an upper surface of the driving device, and the bypass path is fixedly disposed above the driving device.

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