WO2018179584A1 - Combine - Google Patents

Abstract

In this combine, a cutter assembly 3 is installed on the front section of a travel chassis 1 mounted with an engine 7 thereon, a thresher assembly 9 is mounted behind the cutter assembly 3 on the travel chassis 1, a steering assembly 7 is disposed laterally and to the front of the thresher assembly 9, and the engine 7 is mounted below and to the rear of a step part 400 of the steering assembly 5. An ECU 401 for controlling the operation of the combine is disposed on a section to the front of the step part 400. The ECU 401 is positioned to the front of the step part 400 with a space therebetween, and the engine 7 is positioned to the rear of the step part 400.

Description

Combine

The present invention relates to a combine equipped with a reaping section for reaping uncut grain stalks in a field and a threshing section for shredding grains of the reaped grain stalk.

Conventionally, in the combine, generally, an ECU for controlling the operation of the combine is often arranged around a control unit mounted on a traveling vehicle (see, for example, Patent Documents 1 and 2).

Japanese Patent Application Laid-Open No. 10-295152 JP 2014-14333 A

However, in the case of a combine equipped with an engine at the rear of the control unit, the exhaust heat from the engine may affect the ECU. In recent years, it is desirable that the thermal effects from the periphery be as small as possible for an ECU that is particularly responsible for complicated control.

This invention makes it a technical subject to provide the combine which improved and examined the above present condition.

In the present invention, a reaper is mounted on the front of a traveling machine body mounted with an engine, a threshing unit is mounted on the rear of the reaper of the traveling machine body, and a control unit is disposed on the front side of the threshing unit In the combine mounted with the engine on the lower rear side of the step portion in the steering unit, an ECU for controlling the operation of the combine is disposed on the front side of the step portion.

In the combine of the present invention, a shielding plate may be disposed on the front side of the step portion, and the ECU may be attached to the front side of the shielding plate.

In the combine of the present invention, the shielding plate may be supported by the step portion.

In the combine of the present invention, a battery for supplying power may be mounted on the step portion, and the ECU may be positioned higher than the battery.

According to the present invention, the reaper is mounted on the front of a traveling machine body having an engine mounted thereon, the threshing unit is mounted on the rear of the reaper of the traveling machine body, and the steering unit is on the front side of the threshing unit. In the combine that arranges and mounts the engine on the lower rear side of the step portion in the control unit, since the ECU for controlling the operation of the combine is arranged on the lower front portion of the step portion, the control unit In the periphery, the ECU is disposed as far as possible from the engine, and the thermal influence of the engine on the ECU can be reduced. Control stabilization and long life of the ECU can be achieved.

It is a left side view of the combine concerning the present invention. It is a right view of the combine. It is a top view of the combine. It is a drive systematic diagram of a combine. It is a 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 mission case. It is a plane sectional view showing the composition around an engine room. FIG. 2 is a hydraulic circuit diagram showing a configuration of a working hydraulic circuit. It is a front view which shows the arrangement configuration of hydraulic circuit components. It is a whole perspective view of the combine which shows the piping structure of a working system hydraulic circuit. It is an expansion perspective view showing piping composition of a traveling system hydraulic circuit. FIG. 2 is a hydraulic circuit diagram showing a configuration of a traveling system hydraulic circuit. It is a perspective view which shows the plumbing property of hydraulic piping on a transmission case. It is a perspective view which shows the relationship between hydraulic piping on a transmission case, and a connection link body. It is the perspective view which looked at a traveling body front part from diagonally left front. It is the perspective view which looked at a driver's cab (manipulation part) periphery from diagonally left backward. It is a front view around a driver's cab (control part). It is a top view around a driver's cab (control part). FIG. 5 is a perspective view of the area around the driver's cab (steering unit) viewed obliquely from the rear right; It is the perspective view which looked at a driver's cab (control part) periphery from the front. It is the perspective view which looked at the attachment position of ECU from diagonally left front of a traveling body. It is a front view around a driver's cab (control part) which shows the attachment position of ECU. It is a top view of a driver's cab (control part) periphery which shows the attachment position of ECU. FIG. 3 is a perspective view of the positional relationship between an ECU and a steering case as viewed obliquely from the front right. It is the perspective view which looked at the attachment position of ECU from the diagonally right front.

Hereinafter, an embodiment of the present invention will be described based on the drawings (FIGS. 1 to 26) applied to a common type combine. First, the schematic structure of the combine will be described with reference to FIGS. 1 to 3. In the following description, the left side in the forward direction of the traveling vehicle 1 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 according to the embodiment includes a traveling machine body 1 supported by a pair of left and right crawler belts 2 made of rubber crawlers as traveling units. At the front of the traveling vehicle 1, a reaper 3 to be taken in while harvesting uncut grain cran such as rice (or wheat or soybean or corn) is mounted so that it can be moved up and down by a single acting hydraulic cylinder 4 for elevating ing.

On the left side of the traveling vehicle 1, a threshing unit 9 for carrying out a threshing process on the reaping grain fed from the reaping section 3 is mounted. In the lower part of the threshing unit 9, a grain sorting mechanism 10 for swinging sorting and wind sorting is disposed. On the front right side of the traveling vehicle 1, a driver's cab 5 as a control unit on which the operator gets is mounted. An engine 7 as a power source is disposed in a cab 5 (below the driver's seat 42). Behind the cab 5 (right side of the traveling vehicle 1), a grain tank 6 for taking grains from the threshing part 9 and a grain for discharging grains in the grain tank 6 toward a truck bed (or a container etc.) The discharge conveyor 8 is arranged. The grain discharging conveyor 8 is inclined outward, and the grains in the gren tank 6 are carried out by the grain discharging conveyor 8.

The reaper 3 includes a feeder house 11 in communication with a throttling opening 9 a at the front of the threshing part 9 and a grain header 12 in the form of a horizontally long bucket connected to the front end of the feeder house 11. The scraping auger 13 (platform auger) is rotatably supported in the grain header 12. A take-in reel 14 with a tine bar is disposed above the front of the take-in auger 13. A clipper-like cutting blade 15 is placed on the front of the grain header 12. The left and right side branch bodies 16 are protrusively provided on the left and right sides of the front of the grain header 12. Further, the feed conveyor 17 is installed in the feeder house 11. A beater 18 (front rotor) for feeding a reaping grain is provided on the feed end side (the throttling port 9a) of the feed conveyor 17. The lower surface portion of the feeder house 11 and the front end portion of the traveling machine body 1 are connected via the elevating hydraulic cylinder 4, and the reaper 3 reaps using the reaper input shaft 89 (feeder house conveyor shaft) described later as a elevating fulcrum It is moved up and down by the lifting hydraulic cylinder 4.

According to the above configuration, the tip end side of the uncut grain weir between the left and right weeds 16 is scratched by the scratching reel 14, the weir side of the uncut grain weir is cut away by the cutting blade 15, and the scratching auger 13 By the rotational drive, the reaper is collected near the entrance of the feeder house 11 near the center of the lateral width of the grain header 12. The entire amount of the reaper of the grain header 12 is conveyed by the feed conveyor 17 and is introduced into the sip 9 a of the threshing part 9 by the beater 18. A grain control hydraulic cylinder (not shown) for rotating the grain header 12 about the horizontal control fulcrum axis is provided, and the inclination of the grain header 12 in the left-right direction is adjusted by the above-mentioned hydraulic cylinder for horizontal control. It is also possible to horizontally support the cutting blade 12 and the take-up reel 14 with respect to the scoop scene.

Further, as shown in FIG. 1 and FIG. 3, the threshing drum 21 is rotatably provided in the throttling chamber of the threshing unit 9. The threshing drum 21 is supported by a threshing drum shaft 20 (see FIG. 4) extended in the front-rear direction of the traveling vehicle 1. Under the threshing drum 21, a net 24 for leaking kernels is stretched. In addition, on the outer peripheral surface of the front portion of the threshing drum 21, a spiral screw blade intake blade 25 is provided to project radially outward.

According to the above-described configuration, the reaping grain hopper inserted from the throttling port 9a by the beater 18 is transported toward the rear of the traveling airframe 1 by the rotation of the threshing drum 21, and between the throttling drum 21 and the net 24 It is kneaded and threshed. De-graining such as grains smaller than the mesh of the receiving net 24 leaks from the receiving net 24. Scales 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 part 9 by the transport action of the threshing drum 21.

A plurality of dust transfer valves (not shown) pivotally connected to the upper side of the threshing cylinder 21 are provided to adjust the speed at which the grain is removed from the throttling chamber. By adjusting the angle of the dust transfer valve, it is possible to adjust the transport speed (residence time) of the grain removal in the throttling chamber according to the type and characteristics of the reaper. On the other hand, as a grain sorting mechanism 10 disposed below the threshing part 9, a swing sorting board 26 for sorting with a specific gravity is provided which has a grain pan, chaff sieve, grain sieve, straw rack and the like.

Further, as the grain sorting mechanism 10, a blast fan-like carp 29 or the like for supplying sorting air to the swinging sorting board 26 is provided. The degrained threshed by the threshing drum 21 and leaked from the net 24 is a grain (one of the fine grains, etc.) by the specific gravity sorting action of the swing sorting disc 26 and the wind sorting action of the blast fan-like tangerine 29. It is configured to be sorted out and taken out as a batch), a mixture of grain and straw (a second thing such as a grain with a stem), and scale.

As the grain sorting mechanism 10, the first conveyor mechanism 30 and the second conveyor mechanism 31 are provided on the lower side of the rocking sorting board 26. Grains dropped from the rocking sorting board 26 (first ones) are first collected by the conveyor mechanism 30 and the grain harvesting conveyor 32 in the grain tank 6 by the sorting of the rocking sorting board 26 and the fan-shaped fan gutter 29. Ru. The mixture of grain and straw (secondary material) is returned to the sorting start end side of the rocking sorting disc 26 via the No. 2 conveyor mechanism 31 and the No. 2 reducing conveyor 33 etc. and resorted by the rocking sorting disc 26 Ru. Scales and the like are configured to be discharged to the field from the dust outlet 23 at the rear of the traveling airframe 1.

Further, as shown in FIG. 1 to FIG. 3, the driver's cab 5 is provided with a control column 41 and a driver's seat 42 on which an operator sits. The control column 41 includes an accelerator lever 40 for adjusting the number of revolutions of the engine 7, a round control handle 43 for changing the course of the traveling vehicle 1 by the rotation operation of the operator, and a main for switching the moving speed of the traveling vehicle 1 A shift lever 44 and an auxiliary shift lever 45, a reaper clutch lever 46 for driving or stopping the reaper 3 and a threshing clutch lever 47 for driving or stopping the threshing portion 9 are disposed. In addition, a roof 49 for sun protection is attached to a front upper surface side of the glen tank 6 via a sun visor support 48, and the roof 49 for sun protection is configured to cover the upper side of the driver's cab 5.

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

Next, the drive structure of the combine will be described with reference to FIGS. 4 to 8. As shown in FIGS. 4 and 7, a transmission case is provided with a linear hydraulic continuously variable transmission 64 for traveling shift having a hydraulic linear movement pump 64a and a hydraulic linear movement motor 64b. The engine 7 is mounted on the upper right side of the front of the traveling vehicle 1, and the transmission case 63 is disposed on the front of the traveling vehicle 1 on the left of the engine 7. An output shaft 65 protruding leftward from the engine 7 and a transmission input shaft 66 protruding 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. There is. In addition, a work unit charge pump 59 for driving the lifting hydraulic cylinder 4 and the like and a cooling fan 149 are disposed in the engine 7, and the work unit charge pump 59 and the cooling fan 149 are driven by the engine 7.

In addition, a turning hydraulic stepless transmission 70 for steering having a hydraulic turning pump 70a and a hydraulic turning motor 70b is provided in a transmission case 63, and a linear hydraulic stepless transmission 64 and a turning hydraulic type via a transmission input shaft 66. The output of the engine 7 is transmitted to the continuously variable transmission 70, while the straight steering hydraulic continuously variable transmission 64 and the swing hydraulic continuously variable transmission 70 are output by the steering handle 43 and the main shift lever 44 and the sub shift lever 45. The crawler belts 2 are controlled to drive the crawler belts 2 on the left and right through the linear hydraulic continuously variable transmission 64 and the swing hydraulic continuously variable transmission 70 so as to travel and move in a field or the like. In the embodiment, the straight and swing hydraulic continuously variable transmissions 64 and 70 are disposed on the upper right side of the transmission case 63. The driving device of 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 threshing drum drive case 71 is provided which pivotally supports the front end side of the threshing drum shaft 20. A threshing drum drive case 71 is disposed on the front side of the threshing unit 9. A threshing cylinder input shaft 72 for driving the reaper 3 and the throttling cylinder 21 is pivotally supported by the threshing cylinder drive case 71. Moreover, the main counter shaft 76 as a fixed rotating shaft which penetrates the right and left of the threshing part 9 is provided. A work 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 which also serves as a tension roller and a working unit drive belt 85.

In front of the threshing drum 21, a threshing drum input shaft 72 extended in the lateral direction of the traveling machine body 1, a beater 18 disposed in the lateral direction of the traveling vehicle body 1, and a mowing input shaft extended in the lateral direction of the traveling vehicle body 1 89 is provided. A threshing drum drive pulley 86, 87 and a threshing drum drive belt 88 are provided as a threshing drum input mechanism 90 for transmitting the driving force of the main counter shaft 76 to the threshing drum input shaft 72, and the driving force from the engine 7 is transmitted A threshing drum input mechanism 90 (threshing drum drive pulleys 86 and 87 and a threshing drum drive belt 88) is disposed at one end of the counter shaft 76 on the engine 7 side, and the throttling drum 21 is rotationally driven at a constant rotation output of the engine 7 It is configured as follows.

A beater drive mechanism and a reaper drive mechanism for transmitting the driving force of the main counter shaft 76 to the beater shaft 82 and the reaper input shaft 89 are provided on the other end side of the main counter shaft 76. Further, the sub counter shaft 104 is disposed between the beater shaft 82 and the main counter shaft 76, and the 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. The power relay mechanism is configured to transmit power to the reaper drive mechanism by being rotated.

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

The limp shaft 100, which is the rotational shaft of the fan-shaped fan-shaped limp 29, has a hollow tubular shape, and a main counter shaft 76 is inserted in the hollow portion of the limp shaft 100. That is, the main counter shaft 76 and the tang shaft 100 have a double shaft structure, and the main counter shaft 76 and the tang shaft 100 are rotatably supported relative to each other. In addition, the Karasu drive belt 103 is wound around the Karasu drive pulleys 101 and 102 provided on the sub-countershaft 104 and the Karasu shaft 100, respectively, to constitute a Karasu drive mechanism. Therefore, the rotational power from the engine 7 transmitted to the main counter shaft 76 is input to the beater shaft 82 through the power relay mechanism and the tang mechanism, and the tang 29 is rotationally driven at a constant rotational output of the engine 7.

Furthermore, the machine housing of the threshing part 9 has installed the cutting support frame body 36 in the upper surface side of the front part of the threshing machine case support | pillar 34 among the traveling machine body 1 upper surface sides. A cutting bearing body 37 is attached to the front right side of the cutting support frame 36, and a forward / reverse switching case 121 described later is attached to the front left side of the cutting support frame 36. Then, the cutting input shaft 89 is pivotally supported on the front side of the cutting support frame 36 so as to be able to rotate in the lateral direction of the traveling body 1 via the cutting bearing body 37 and the forward / reverse switching case 121, and the cutting support frame 36 The beater shaft 82 (beater 18), which is directed leftward and rightward, is rotatably supported via a beater bearing body 38 inside. Further, the threshing cylinder drive case 71 is mounted on the upper surface side of the cutting support frame 36, and the threshing cylinder input shaft 72 is axially supported by the threshing cylinder drive case 71.

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

In addition, a threshing cylinder input shaft 72 is provided on the front side of the threshing portion 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 one end of the threshing cylinder input shaft 72 It is transmitted to the department. The threshing drum input shaft 72 provided on the front side of the threshing portion 9 is disposed in the left-right direction of the traveling machine body 1, and the threshing cylinder 21 is pivotally supported by the threshing barrel shaft 20 disposed in the front-rear direction of the traveling machine body 1. The front end side of the threshing drum shaft 20 is connected to the left and right other end portions of the threshing drum input shaft 72 opposite to the engine 7 via a bevel gear mechanism 75. The driving force of the engine 7 is transmitted to the grain sorting mechanism 10 or the reaper 3 for sorting grains after threshing from the left and right other ends opposite to the engine 7 in the main counter shaft 76. .

That is, the right end of the threshing drum input shaft 72 is connected to the right end of the main counter shaft 76 closer to the engine 7 via the threshing drum drive pulleys 86 and 87 and the threshing drum drive belt 88. The front end side of the threshing drum shaft 20 is connected via the bevel gear mechanism 75 to the left end of the threshing drum input shaft 72 extended 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 threshing drum shaft 20 via the threshing drum input shaft 72, and the throttling drum 21 is rotationally driven 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 disposed below the threshing unit 9.

Furthermore, 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 via the conveyor drive belt 111 to the left of the main counter shaft 76 The ends are connected. The left end of the second conveyor shaft 78 is connected to the left end of a crank-like swinging drive shaft 79 pivotally supported at the rear of the swing sorting disc 26 via a swing sorting belt 112. That is, the operation of the threshing clutch 84 is controlled by the operation of the threshing clutch lever 47 of the operator. Each part of the grain sorting mechanism 10 and the threshing drum 21 are driven by the entry operation of the threshing clutch 84.

In addition, the grain conveyor 32 is driven via the conveyor shaft 77 first, and the grain sorted first of the conveyor mechanism 30 is collected in the grain tank 6. Further, the No. 2 reduction conveyor 33 is driven via the No. 2 conveyor shaft 78, and the No. 2 sorted grain (the second thing) in which the scale waste of the No. 2 conveyor mechanism 31 is mixed is the upper surface side of the rocking sorting board 26 Will be returned to Moreover, in the structure which provides the spreader (not shown) for scattering of scraps in the dust outlet 23, the left side of the main counter shaft 76 to the said spreader via a spreader drive pulley (not shown) and a spreader drive belt (not shown). Connect the ends.

A reaper input shaft 89 is provided as a conveyor input shaft for pivotally supporting the feed end side of the supply conveyor 17. A header drive shaft 91 is rotatably supported on the back side of the right 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 reaper drive chain 115 and the sprockets 116 and 117, and the reaper input shaft 89 is forward / reverse transmission via the forward / reverse switching case 121 It is connected with the shaft 122. The right end of the reaper 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. The pick-up shaft 93 is provided to support the pick-up auger 13. An intermediate portion of the header drive shaft 91 is connected to the right side portion of the scratching shaft 93 via the scratching drive chain 92.

In addition, a reel shaft 94 for supporting the take-in reel 14 is provided. The right end of the take-in shaft 93 is connected to the right end of the reel shaft 94 via the intermediate shaft 95 and the reel drive chains 96 and 97. The cutting blade 15 is connected to the right end of the header drive shaft 91 via a cutting blade driving crank mechanism 98. The feed conveyor 17, the take-in auger 13, the take-in reel 14, and the cutting blade 15 are driven and controlled by the on / off operation of the reaper clutch 109 so that the tip side of the uncut grain weirs of the field is continuously cut off It is composed of

The normal rotation bevel gear 124 integrally formed on the forward / reverse transmission shaft 122, the reverse rotation bevel gear 125 rotatably supported on the reaper input shaft 89, and the intermediate bevel gear 126 connecting the reverse rotation bevel gear 125 to the normal rotation bevel gear 124. , Installed in the forward / reverse switching case 121. The intermediate bevel gear 126 is always meshed with the forward bevel gear 124 and the reverse bevel gear 125. On the other hand, the slider 127 is slidably supported by spline engagement on the reaper input shaft 89 in a slidable manner. The slider 127 is configured to be engageable with the bevel gear 124 for forward rotation via the claw clutch shaped forward rotation clutch 128, and the slider 127 is engaged with the reverse rotation bevel gear 125 via the claw reverse clutch 129. It is configured to be releasably engageable.

In addition, a forward / reverse switching shaft 123 for sliding operation of the slider 127 is provided, 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 forward / reverse switching lever (forward / reverse operation tool) operation. It is swung to rotate the forward / reverse switching shaft 123, and the slider 127 is brought into contact with or separated from the forward rotation bevel gear 124 or the reverse rotation bevel gear 125, and the forward rotation bevel gear 124 or the reverse rotation via the forward clutch 128 or the reverse clutch 129 The slider 127 is selectively locked to the bevel gear 125, and the reaper input shaft 89 is connected to the forward and reverse transmission shaft 122 in a forward or reverse connection.

The structure includes the forward / reverse switching case 121 as a forward / reverse switching mechanism that drives the feed conveyor 17 forward or backward. The feed conveyor 17 is connected to the beater shaft 82 via the forward / reverse switching case 121. Therefore, the feed conveyor 17 or the like of the feeder house 11 can be reversed by the reverse switching operation of the forward / reverse switching case 121, and clogging debris in the feeder house 11 or the like 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 the tension pulley pulley auger clutch 156 and the auger drive belt 157. The front end side 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. The vertical feed auger 162 of the grain discharging conveyor 8 is connected to the rear end side of the cross feed auger 160 via the bevel gear mechanism 161, and the grain of the grain discharge conveyor 8 is loaded on the upper end side of the vertical feed auger 162 via the bevel gear mechanism 163. The particle discharge auger 164 is connected. In addition, a grain discharging lever 155 for turning on and off the auger clutch 156 is provided. A grain discharging lever 155 is attached to the rear of the driver's seat 42 and in front of the grain tank 6, and the operator can operate the grain discharging lever 155 from the driver's seat 42 side.

Next, the power transmission structure of the transmission case 63 and the like will be described with reference to FIGS. 4 and 7 and the like. As shown in FIG. 4 and FIG. 7 etc., the transmission case 63 includes a hydraulic stepless transmission 64 for straight running (traveling main shift) having a pair of straight running pumps 64a and a straight running motor 64b, and a pair of turning pumps 70a. And a hydraulic continuously variable transmission 70 for turning having a turning motor 70b. The transmission input shaft 66 of the transmission case 63 is configured to be gear-connected to drive the respective pump shafts 258 and 259 of the linear movement pump 64a and the turning pump 70a. 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 to drive the linear pump 64a and the swing pump 70a.

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

The mission input shaft 66 protrudes from the upper portion of the left side surface of the transmission case 63 toward the feeder house 11, and the transmission input pulley 69 is axially fixed to the projecting end (left end) of the transmission input shaft 66 without relative rotation. The transmission input shaft 66 is rotatably supported by a bearing fixed to the transmission case 63, and the power distribution gear 262 is non-rotatably fitted in the middle of the transmission input shaft 66. The pump shaft 258 of the rectilinear pump 64a and the pump shaft 259 of the swing pump 70a are separately disposed before and after the transmission input shaft 66 in a plan view, and are disposed below the transmission input shaft 66 in a side view.

At the projecting end (left end) of the pump shaft 258 protruding from the continuously variable transmission case 323 into the transmission case 63, a relative rotation input gear 263 engaged with the power distribution gear 262 fixed to the transmission input shaft 66 is relatively rotated. Impossible to fit. Similarly, at the projecting end (left end) of the pump shaft 259 projected from the continuously variable transmission case 323 into the transmission case 63, a turning input gear 264 engaged with the power distribution gear 262 fixed to the transmission input shaft 66. Is fitted non-rotatably.

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 the straight input gear 263 The pump shaft 258 of the linear pump 64 a is rotated, while the pump shaft 259 of the rotary pump 70 a is rotated via the rotary input gear 264. That is, the straight drive input gear 263 and the swing input gear 264 of each of the pump shafts 258, 259 mesh with the power distribution gear 262 of the transmission input shaft 66 disposed between the pump shafts 258, 259, The driving force can be efficiently transmitted to the linear hydraulic continuously variable transmission 64 and the turning hydraulic continuously variable transmission 70, respectively.

The pump shaft 259 is attached with a transmission charge pump 151 for supplying hydraulic oil to the hydraulic pumps 64a, 70a and the hydraulic motors 64b, 70b. The straight forward hydraulic type continuously variable transmission 64 changes and adjusts the inclination angle of the rotary swash plate in the straight forward pump 64a according to the operation amount of the main transmission lever 44 and the steering handle 43 disposed on the control column 41, By changing the discharge direction and the discharge amount of the hydraulic oil to 64b, the rotation direction and the number of rotations of the straight advance motor shaft 260 protruding from the straight advance motor 64b are arbitrarily adjusted.

The rotational power of the rectilinear motor shaft 260 is transmitted from the rectilinear transmission gear mechanism 250 to the auxiliary transmission gear mechanism 251. The auxiliary transmission gear mechanism 251 has an auxiliary transmission low speed gear 254, an auxiliary transmission middle speed gear 255, and an auxiliary transmission high speed gear 256 switched by the auxiliary shift shifters 252 and 253. By operating the sub shift lever 45 disposed on the control column 41, the output rotational speed of the motor shaft 260 for going straight is configured to be alternatively switched to the three speed stages of low speed, medium speed or high speed. . A neutral position (a position at which the output of the auxiliary shift is zero) is provided between the low speed, the medium speed and the high speed of the auxiliary shift.

A parking brake 266 of a drum type is provided on a parking brake shaft 265 (sub transmission output shaft) provided on the output side of the sub transmission gear mechanism 251. The rotational power from the auxiliary transmission gear mechanism 251 is transmitted from the auxiliary transmission output gear 267 fixed to the parking brake shaft 265 to the left and right differential mechanisms 257. The left and right differential mechanisms 257 are each provided with a planetary gear mechanism 268. In addition, a pulse generation rotary wheel body 292 for going straight on is provided on the parking brake shaft 265, and it is configured to detect the number of revolutions of straight output (go straight vehicle speed = shift output of the sub shift output gear 267) by a straight vehicle speed sensor (not shown). doing.

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 gears 272, and a plurality of planet gears 272 on the same circumference. The respective carriers 274 to be arranged are provided. The carriers 274 of the left and right planetary gear mechanisms 268 are disposed 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.

The left and right ring gears 273 are disposed concentrically with the sun gear shaft 275 in a state in which the internal teeth of the inner circumferential surface thereof are meshed 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 the steering output shaft 285 via intermediate gears 287 and 288 for left and right turning output described later. Each ring gear 273 is rotatably supported by left and right forced differential output shafts 277 protruding outward from the outer surface of the carrier 274 in the left and right direction. The left and right axles 278 are connected to the left and right forced differential output shafts 277 via final gears 278 a and 278 b. 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 rotation speed in the same direction. The traveling body 1 is moved straight (forward, backward) by driving at the same number of revolutions.

The turning hydraulic continuously variable transmission 70 changes and adjusts the inclination angle of the rotary swash plate in the turning pump 70a according to the amount of turning operation of the main transmission lever 44 and the steering handle 43 disposed on the steering column 41, By changing the discharge direction and the discharge amount of the hydraulic fluid to the swing motor 70b, the rotation direction and the number of rotations of the swing motor shaft 261 protruding from the swing motor 70b are arbitrarily adjusted. In addition, a pulse generation rotating wheel body 294 for turning is provided on a steering counter shaft 280 described later, and the number of rotations (steering vehicle speed) of steering output of the turning motor 70b by a turning rotation sensor (turning vehicle speed sensor) not shown. Configured to detect

Also, in the transmission case 63, a wet multi-plate type swing brake 279 (steering brake) provided on the swing motor shaft 261 (steering input shaft), and the swing motor shaft 261 via the reduction gear 281 A steering counter shaft 280 to be coupled, a steering output shaft 285 coupled to the steering counter shaft 280 via a reduction gear 286, and a left input to couple the steering output shaft 285 to the left ring gear 273 via a reverse gear A gear mechanism 282 and a right input gear mechanism 283 connecting 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 through the left intermediate gear 287 and the reverse gear 284 on the steering output shaft 285 of the left input gear mechanism 282. On the other hand, it is transmitted to the right ring gear 273 as forward rotational 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 made neutral, power transmission from the linear motor 64b to the left and right planetary gear mechanisms 268 is blocked. Power is transmitted from the linear motor 64b to the left and right planetary gear mechanisms 268 via the auxiliary low speed gear 254, the auxiliary intermediate speed gear 255, or the auxiliary high speed gear 256 when the auxiliary speed is output from the auxiliary speed change gear mechanism 251. . On the other hand, when the output of the swing pump 70a is in the neutral state and the swing brake 279 is in the on state, power transmission from the swing motor 70b to the left and right planetary gear mechanisms 268 is blocked. When the output of the swing pump 70a is in 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. And 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 swing motor 70b, the left ring gear 273 reverses (forwards) and the right ring gear 273 rotates forward (reverses) 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 crawler belt 2 on the left and right through the auxiliary transmission gear mechanism 251 or the differential mechanism 257, respectively. The speed) and the direction of travel are determined.

That is, when the linear motor 64b is driven in a state where the swing motor 70b is stopped and the left and right ring gears 273 are fixed stationary, the rotational output from the straight drive motor shaft 260 is transmitted to the left and right sun gears 271 at the same number of rotations on the left and right. 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 linear motor 64b is stopped and the left and right sun gears 271 are stationary fixed and the turning motor 70b is driven, the rotational power from the turning motor shaft 261 causes the left ring gear 273 to rotate forward (reverse 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 is forwardly rotated, and the other is backwardly rotated, and the traveling airframe 1 is turned on the spot (spin turn spin turn).

Further, by driving the left and right ring gears 273 by the swing motor 70b while driving the left and right sun gears 271 by the straight drive motor 64b, a difference occurs in the speeds of the crawler belts 2 and the traveling machine body 1 moves forward or backward while turning. Turn to the left or right (U-turn) with a turning radius greater 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 traveling driving force of the engine 7 is constantly transmitted to the left and right crawler belts 2 and the vehicle is turned to the left or right.

Next, with reference to FIGS. 8 to 15, the working hydraulic circuit 180 and the traveling hydraulic circuit 200 in the ordinary combine according to the present embodiment will be described. As shown in FIGS. 8 to 12, the working system hydraulic circuit 180 includes, as hydraulic actuators, a reaper raising and lowering hydraulic cylinder 4 and left and right reel raising and lowering hydraulic cylinders 27L and 27R for supporting the take-up reel 14 so as to be able to move up and down. The auger lifting hydraulic cylinder 55 supporting the grain discharge auger 164 so as to be able to move up and down, the left and right body lifting hydraulic cylinders 56L and 56R for raising and lowering the traveling machine body 1, the hydraulic oil tank 57 storing hydraulic oil, hydraulic oil A working unit charge pump 59 connected via a tank 57 and a strainer 58, hydraulic valves 60A to 60E for switching the flow of hydraulic fluid, and an oil cooler provided on the way of return piping from hydraulic valves 50A to 60E to hydraulic fluid tank 57 And 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 reaper lifting and lowering hydraulic cylinder 4 via the reaper lifting and lowering hydraulic valve 60A. The operator lifts and lowers the reaper lifting hydraulic cylinder 4 by tilting the reaper posture lever (not shown) in the drive operation unit (cab) 5 in the front-rear direction, and the operator can adjust the reaper 3 to an arbitrary height (for example, reaper height) Or, it is configured to move up and down to a non-working height or the like. On the other hand, the work unit charge pump 59 is hydraulically connected to the reel raising and lowering hydraulic cylinders 27L and 27R via the reel raising and lowering hydraulic valve 60B. The reel raising and lowering hydraulic cylinders 27L and 27R are operated by an operation such as tilting the harvesting posture lever (not shown) in the left and right direction, and the operator raises and lowers the take-up reel 14 to an arbitrary height, and the uncut grain of the field It is configured to reap bushes.

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 the operation of tilting the grain discharging lever 155 in the operation operation unit (cab) 5 in the front-rear direction, and the operator throws the grit opening of the grain discharging auger 164 in the grain discharging conveyor 8 Up and down to any height. In addition, the grain discharging 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 javelin is moved in the lateral direction. That is, the gutter is positioned above the truck bed or container, and the grains in the gren tank 6 are discharged into the truck bed or container.

The hydraulic fluid tank 57 and the work unit charge pump 59 are hydraulically connected to the left machine lifting hydraulic cylinder 56L via the left machine lifting hydraulic valve 60D. On the other hand, the hydraulic fluid tank 57 and the work unit charge pump 59 are hydraulically connected to the right machine lifting hydraulic cylinder 56R via the right machine lifting hydraulic valve 60E. The left and right hydraulic cylinders 56L and 56R for raising and lowering the machine independently move the left and right of the traveling body 1 independently.

Therefore, when the left and right hydraulic cylinders 56L and 56R are simultaneously actuated to lower the left and right track frames 50, 50 simultaneously with respect to the traveling body 1, the traveling body 1 is in contact with the crawler belts 2, 2 and the ground , The relative height (vehicle height) of the traveling airframe 1 with respect to the crawler belts 2, 2 and the contact portion becomes high. Conversely, when the left and right track frames 50, 50 are simultaneously raised with respect to the traveling airframe 1, the traveling airframe 1 approaches (drops) to the crawler belts 2, 2 and the ground contact portions on both left and right The relative height (vehicle height) with respect to the two contact portions decreases.

Then, the left airframe lifting hydraulic cylinder 56L is operated to lower the left track frame 50 relative to the traveling airframe 1, or the right airframe lifting hydraulic cylinder 56R is operated to raise the right track frame 50 relative to the airframe 1 And (or both actions are performed simultaneously), the traveling body 1 tilts downward to the right. Conversely, the right aircraft lifting hydraulic cylinder 56R is operated to lower the right track frame 50 relative to the traveling vehicle 1 or the left aircraft lifting hydraulic cylinder 56L is operated to place the right track frame 50 relative to the traveling aircraft 1 When raised (or when both operations are performed simultaneously), the traveling vehicle 1 tilts to the left.

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

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 the front of the traveling body 1 There is. That is, the hydraulic oil tank 57 is disposed in the 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 reaper 3 on the hydraulic oil tank 57, It is also possible to prevent the contamination of the hydraulic oil due to the entry of dust from the filler port 184 or the like. Further, since the cooling air from the engine 7 flows into the installation space of the hydraulic oil tank 57, the hydraulic oil temperature can be suppressed from rising without providing the oil cooler on the working hydraulic circuit 180, and each hydraulic member can be It can drive properly.

The hydraulic oil tank 57 has an oil supply port 184 protruding toward the left side (outer side) on the left side (outer side), and incorporates a strainer 58 which can be inserted and removed from the left side. Therefore, by removing the threshing cover 185 provided on the left side (outboard side) of the threshing portion 9, the access to the filler port 184 and the strainer 58 can be easily achieved. As a result, the operation of refueling the hydraulic oil tank 57 and the operation of replacing the oil filter in the strainer 58 become easy, and the maintainability of the working hydraulic circuit 180 can be improved.

Also, hydraulic pipes 181 and 183 connected to the hydraulic oil tank 57 are extended with the hydraulic oil tank 57 and the engine 7 extended to the left and right, and the hydraulic pipe 182 is disposed at the front of the engine 7. And the strainer 58 are in communication. That is, the hydraulic pipes 181 and 183 extend along the output shaft 65 of the engine 7 toward the hydraulic oil tank 57 by bypassing the front of the engine 7. The hydraulic pipes 182 and 183 are extended rearward through the lower side of 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 becomes short at a position 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 rising. it can.

As shown in FIG. 7, FIG. 10 and FIG. 12 to FIG. 15, the traveling system hydraulic circuit 200 includes a straight drive pump 64a, a straight drive motor 64b, a swing pump 70a, a swing motor 70b, a transmission charge pump 151, an oil filter 152, and oil A cooler 153 is provided. The straight drive pump 64 a and the straight drive motor 64 b of the straight hydraulic continuously variable transmission 64 are connected in a closed loop by the straight 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. The rotational power of the engine 7 drives the straight drive pump 64a and the swing pump 70a, and controls the swash plate angle of the straight drive pump 64a and the swing pump 70a to discharge hydraulic oil to the straight drive motor 64b and the swing motor 70b. The amount is changed, and the linear movement motor 64b and the turning motor 70b operate in the forward and reverse directions.

The traveling system hydraulic circuit 200 includes a straight movement valve 203 which is switched in response to the manual operation of the main shift lever 44 and a straight movement cylinder 204 connected to the transmission charge pump 151 via the straight movement valve 203. When the straight movement valve 203 is switched and operated, the straight movement cylinder 204 is operated to change the swash plate angle of the straight movement pump 64a and change the rotation number of the straight movement motor shaft 260 of the straight movement motor 64b steplessly or reversely The action is performed. The traveling system hydraulic circuit 200 also includes a hydraulic servo mechanism 205 for linear shift. The hydraulic servo mechanism 205 executes a feedback operation in which the straight drive valve 203 returns to neutral by the swash plate angle control of the straight drive pump 64a, and changes the swash plate angle of the straight drive pump 64a in proportion to the manual operation amount of the main shift lever 44, The linear motor shaft 260 rotation speed of the linear motor 60b is changed.

The traveling system hydraulic circuit 200 includes a swing valve 206 which is switched in response to the manual operation of the steering handle 43, and a swing cylinder 207 connected to the transmission charge pump 151 via the swing valve 206. When the turning valve 206 is switched, the turning cylinder 207 operates to change the swash plate angle of the turning pump 70a, and the rotation speed of the turning motor shaft 261 of the turning motor 70b is continuously changed or reversed. The left and right turning motion is executed, and the traveling body 1 changes the traveling direction to the left and right to change the direction or correct the course in the field headland. The traveling system hydraulic circuit 200 also includes a hydraulic servo mechanism 208 for turning and shifting. The hydraulic servo mechanism 208 performs feedback operation in which the swing valve 206 returns to neutral 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 motor shaft 261 rotation speed of the rotation 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, 202b of the both closed oil passages 201, 202. A check valve 211 for the straight first oil passage 201a is provided between the charge branch oil passage 219 and the straight first oil passage 201a. A check valve 211 for the straight second oil passage 201b is provided between the charge branch oil passage 219 and the straight second oil passage 201b. Therefore, the straight closing oil passage 201 is provided with two check valves 211. Further, a check valve 212 for the swirling first oil passage 202a is provided between the charge branch oil passage 219 and the swirling first oil passage 202a. Between the charge branch oil passage 219 and the turning second oil passage 202b, a check valve 212 for the turning second oil passage 202b is provided. Therefore, the swing closed oil passage 202 is also provided with two check valves 212.

A straight bypass oil passage 213 is connected to the straight first oil passage 201a and the straight second oil passage 201b. A straight forward bi-directional relief valve 215 is provided in the straight bypass oil passage 213. A swirl bypass oil passage 214 is connected to the swirl first oil passage 202a and the swirl second oil passage 202b. A turning side bidirectional relief valve 216 is provided in the turning bypass oil passage 214. Therefore, each closed oil passage 201, 202 is provided with one bidirectional relief valve 215, 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 installed in the middle of the hydraulic pipe 222. A charge branch oil passage 219 connected to the both closing oil passages 201 and 202 is connected to the downstream side of the charge introduction oil passage 218. Therefore, while the engine 7 is in operation, hydraulic oil from the transmission charge pump 151 is constantly replenished in both the closed oil passages 201 and 202.

Further, the charge branch oil passage 219 is connected to the straight movement cylinder 204 via the straight movement valve 203 and is connected to the turning cylinder 207 via the turning valve 206. Furthermore, the charge branch oil passage 219 is connected to the transmission case 63 via the excess relief valve 220 and the hydraulic pipe 223, and the oil cooler 153 is installed in the hydraulic pipe 223. Therefore, when the surplus of the hydraulic oil from the transmission charge pump 151 is returned to the inside of the transmission case 63 via the surplus relief valve 220, it is cooled by the oil cooler 153.

The hydraulic piping 223 is connected by a bypass pipe 224 that bypasses the feed piping 223a and the return piping 223b to 223d, and the bypass pipe 224 is fixed above the continuously variable transmission case 323 on the side of the transmission case 63. There is. By arranging the hydraulic piping 223 and the bypass pipe 224 above the continuously variable transmission case 323, it is possible to circulate without sending the hydraulic oil to the oil cooler 153 when the temperature of the hydraulic oil is low at the time of starting the engine 7 or the like. it can. Therefore, even when the viscosity of the hydraulic fluid is high when the temperature of the hydraulic fluid is low, the hydraulic fluid can be circulated smoothly in the traveling system hydraulic circuit 200, and the transmission case 63 and the continuously variable transmission case 323 can be Lubricate each power transmission mechanism.

As described above, the oil cooler 153 is connected to the hydraulic pipes 221 to 223 for circulating the hydraulic oil in the transmission case 63 and the continuously variable transmission case 323 (drive device), and the bypass pipe for bypassing the oil cooler 153 A road) 224 is provided in the hydraulic piping 223, and the bypass pipe 224 is provided integrally with the transmission case 63 and the continuously variable transmission case 323. Therefore, by connecting the transmission case 63 and the continuously variable transmission case 323 to the oil cooler 153, although the piping route for circulating the transmission case 63 and the continuously variable transmission case 323 becomes long, the bypass pipe 224 can shorten the length.

By providing the bypass pipe 224 in the hydraulic pipe 223 and bypassing the oil cooler 153, hydraulic oil with high viscosity can be circulated when the engine is started in a cold region, etc., and the transmission case 63 and the continuously variable transmission case 323 can be Maintain good lubricity. Further, by integrally providing the transmission case 63 and the continuously variable transmission case 323 in 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 improves and the hydraulic system in the transmission case 63 is improved. Maintenance of is easy.

A continuously variable transmission case 323 is provided with a connection member (connection joint) 225 provided with two communication ports 225a and 225b. One end of the bypass pipe 224 is connected to the communication port 225a of the connection member 225, and a feed pipe 223a in communication with the oil cooler is connected to the communication port 225b of the connection member 225. Further, a relief valve for bypass 226 (see FIG. 13) is provided at a connection portion between the connecting member 225 and the bypass pipe 224. The connecting member 225 is provided on the upper surface of the continuously variable transmission case 323 on the side of the hydraulic hydraulic continuously variable transmission 64 for forward travel (the front side), 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 provided to project rearward (to the side of the turning hydraulic CVT 70).

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

A connection 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 housing portion (the rear end side of the continuously variable transmission case 323) of the turning valve 206 in the continuously variable transmission case 323. Thus, the metal relay pipe 223 c is fixedly disposed above the continuously variable transmission case 323 so as to be parallel to the pump shaft 259. Further, the metal relay pipe 223c has a T-shape in which a communication port (branch pipe) 223e is provided to project forward (on the side of the linear hydraulic continuously variable transmission 64) from the middle part. That is, the communication port 223 e in the middle of the metal relay pipe 223 c is provided at the same height as the communication port 225 a of the connection member 225 and is protruded toward the communication port 225 a of the connection member 225.

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

The bypass passage for bypassing the oil cooler 153 is constituted by the metal relay pipe 223 c, the bypass pipe 224, and the connecting member 225 which are assembled integrally 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 assembly of the transmission case 63 to which the continuously variable transmission case 323 is assembled. Easy and maintainability can be improved.

The hydraulic pipes 222 and 223 connected to the transmission case 63 and the continuously variable transmission case 323 are arranged below the straight connection link 345 and the swing connection link 346 connected to the steering case 318. Therefore, not only the contact between the rectilinear connection link body 345 and the swing connection link body 346 and the hydraulic piping 222 and 223 can be prevented, but maintenance of the rectilinear connection link body 345 and the swing connection link body 346 is facilitated. Further, even if the hydraulic pipes 222 and 223 vibrate due to the drive of the transmission case 63 or the like, damage due to contact with the rectilinear connection link body 345 and the turning connection link body 346 can be prevented.

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 relay shaft 352 for rectilinear movement of the rectilinear connection link body 345. The hydraulic piping 222 which connects the transmission case 63 and the transmission case 63 is arranged in the front-rear direction so as to pass below the first relay rod of the swing direct connection link 346. Further, the downstream side return pipe 223b connected to the transmission case 63 is bent so as to pass below the shaft support 366 in the swing direct connection link 346, and is connected to the metal relay pipe 223c fixed to the continuously variable transmission case 323. It is done.

Next, an engine room 146 in which the engine 7 is installed will be described with reference to FIG. 8 and the like. As shown in FIG. 8 and the like, a pair of left and right engine room support columns 147 are erected on the rear side of the driver's cab 5 on the upper surface of the traveling machine body 1, and a back plate 148 is stretched between the left and right engine room support columns 147 It covers the rear of the engine room 146 below the seat 42. Further, a box-like wind tunnel case 170 is provided upright on the right engine room support column 147 provided at the right end of the driver's cab 5 in the traveling airframe 1 via the open / close fulcrum shaft 171. A dust removal net is stretched over the outer side opening of the right side surface of the wind tunnel case 170, and the presence of the dust removal net prevents intrusion of scraps and the like inside the wind tunnel case 170 and further into the engine room 146. Further, in the wind tunnel case 170, the oil cooler 153 in the traveling system hydraulic circuit 200 and the oil cooler 62 in the working system hydraulic circuit 180 are arranged vertically.

A water cooling radiator 154 is provided upright inside the wind tunnel case 170 on the upper surface side of the traveling airframe 1, and the radiator 154 is opposed to the cooling fan 149 of the engine 7. Then, a shroud 150 is installed in such a manner as to cover the entire ventilation range of the radiator 154, and the cooling fan 149 is disposed in an opening formed in the shroud 150. Further, an oil cooler 153 is installed in the wind tunnel case 170. By the rotation of the cooling fan 149, the outside air (cooling air) is introduced into the wind tunnel case 170 from the air duct opening on the right side of the wind tunnel case 170, and the dust air is removed from the air vent 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, with reference to FIG. 8, FIG. 10, and FIG. 16 to FIG. 21, the driving operation structure of the steering handle 43 and the like will be described. As shown in FIG. 8, FIG. 10, and FIG. 16 to FIG. A plurality of leg frames 312 are erected on the upper surface side of the traveling machine body 1, and a step frame 311 is erected on the upper end side of the leg frames 312. A landing step 313 is fixed to the side surface of the leg frame 312 on the right side outer side 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 machine body 1.

In addition, a steering case 318 having a turning input shaft 316 and a main transmission input shaft 317 is provided. Both ends of the case support horizontal frame 319 are connected between the left and right 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 support horizontal frame 319. A turning input shaft 316 is projected upward from the upper surface of the steering case 318, and the steering input shaft 316 is connected to the steering handle 43 via the steering shaft 321, and from the left side surface of the steering case 318 toward the left side. The main shift input shaft 317 is protruded, and the main shift input shaft 317 is connected to the main shift lever 44 via the main shift operating rod 322.

As can be understood from the above description, in the driver's cab 5 (steering unit) on the step frame 311 provided on the upper end side of the leg frame 312 group, the main shift lever 44 which is a straight operating tool for straight driving and And a steering handle 43 which is a turning operation tool of the present invention. The case support horizontal frame 319 is mounted by being bridged between the left and right leg frames 312 on the lower side of the front of the step frame 311. The case support horizontal frame 319 is attached with a steering case 318 that interlocks and links the main transmission lever 44 and the steering handle 43 with the drive (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 support horizontal frames 319.

Further, an oil filter 152 fixed to the step frame 311 at the 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 of the front portion of the step frame 311 protruding leftward from the left support leg frame 312 so as to be disposed in front of the continuously variable transmission case 323. That is, the oil filter 152 is fixed on the left side of the front end of the step frame 311 via the filter fixing bracket 349, and thus, the oil filter 152 is disposed in front of the continuously variable transmission case 323 fixed on the right side of the transmission case 63. Therefore, when connecting the transmission charge pump 151 and the charge introduction oil passage 218, the hydraulic piping 222 can be configured to have a short length.

The case support horizontal frame 319 is bridged and attached between the left and right leg frames 312 at the front lower side of the step frame 311, and the case support horizontal frame 319 includes the main shift lever 44, the steering handle 43 and the drive (stepless Since the steering case 318 for interlockingly connecting the case 323 and the transmission case 63) is attached, the rigidity of the front portion of the traveling vehicle body 1 (especially, near the driver's cab 5) can be improved by the presence of the case support horizontal frame 319. The steering case 318 can be supported with high rigidity by utilizing a case support horizontal frame 319 that plays a role of reinforcing the front of the traveling airframe 1. Therefore, there is no significant shift between the operation amount of the main shift lever 44 and the steering handle 43 and the output of the drive unit (the continuously variable shift case 323 and the transmission case 63), and the traveling condition is not expected by the operator. Eliminate the possibility of The reinforcing case support horizontal frame 319 can also be used as a mounting portion of the steering case 318, and a mounting base dedicated to the steering case 318 is unnecessary, which contributes to cost reduction.

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

Therefore, since there is space on the side (left side) on the feeder house 11 side in the mission case 63, the degree of freedom in design of the mowing part 3 is increased, and the mowing quantity of the mowing part 3 and the mowing width of the grain header 12 are increased. Can be configured in the most suitable size. Moreover, since the installation width of the feeder house 11 in the left-right direction is expanded, the feeder house 11 can be installed on the side close to the center of gravity position when moving up and down the grain header 12, and the support strength by the feeder house 11 of the reaper 3 Can be enhanced.

A straight operating shaft 325 as a straight output control unit is projected forward on the outer front surface of the continuously variable transmission case 323, and a rear operating surface 326 as a turning output control unit is directed backward on the rear outer surface of the continuously variable transmission case 323. It is projected to Although detailed illustration is omitted, a linear movement operation arm 355 is connected to the straight movement operation shaft 325, and a turning operation arm 369 is connected to the turning operation shaft 326. The operation arm 355 and 369 for going straight and turning are respectively connected to the rectilinear connection link body 345 and the turning connection link body 346 provided on the back side of the steering case 318, and the steering operation of the steering handle 43 and the main shift lever The linear hydraulic continuously variable transmission 64 and the turning hydraulic continuously variable transmission 70 are operationally controlled by the speed change operation 44, and the path and the moving speed of the left and right crawler belts 2 can be changed.

A driver's seat (manipulation unit) 5 provided at the front of the traveling machine body 1 includes a main shift lever (straight operation tool) 44 for straight operation and a steering handle (turn operation tool) 43 for turning operation. The control column 41 is disposed on the side near the drive 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 according to the operation amount of the steering handle 43 and the main shift lever 44 in the lower part of the cab 5 in the front portion of the traveling body 1 is a linear hydraulic continuously variable transmission It is disposed on the side of the continuously variable transmission case 323 provided with the V. 64 and the turning hydraulic CVT 70.

In this case, the steering handle 43 is disposed in the front center portion of the driver's seat 5 in front of the driver's seat 42, and the steering wheel 43 is disposed on the left side which is a side portion closer to the drive device (the continuously variable transmission case 323 and the transmission case 63). A main shift lever 44 is disposed on the column 41. That is, the steering case 313 is disposed below the steering handle 43, and the continuously variable transmission case 323 is disposed below the steering column 41 where the main transmission lever 44 is installed. As a result, from steering wheel 43 and main shift lever 44, the components of the operation system mechanism coupled to stepless transmission case 323 with steering case 313 interposed therebetween can be disposed close to each other, and the components of the operation system mechanism are coupled. Each link mechanism 321, 322, 345, 346 can be configured to be short to suppress its variation and deformation. Therefore, the shift between the operation amount of the main shift lever 44 and the steering handle 43 and the output of the drive device (the continuously variable shift case 323 and the transmission case 63) is suppressed, and the stable traveling state according to the operator's operation is maintained. it can.

A battery 230 for supplying power to the engine 7 is disposed behind the steering case 318 and on the side of the continuously variable transmission case 32 below the driver's seat 5 in the front portion of the traveling machine body 1. That is, the battery 230 for supplying power to the engine 7 and the like is disposed in the area surrounded by the steering case 318, the drive 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 driver's 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 disposed close to the engine 7 and the cab 5, and the electric system can be made compact. In addition, it is possible to avoid increasing the size of the combine in order to secure the arrangement space of the battery 230.

A cab (steering unit) 5 is configured on a plurality of leg frames 312 erected on the upper surface side of the traveling vehicle body 1. A steering case 318 is fixed to a case support horizontal frame (case support frame) 319 provided in the middle of the plurality of leg frames 312 and arranged above the continuously variable transmission case 323 and the battery 230. As described above, since the battery 230 and the steering case 318 are disposed in the upper and lower stages in the lower part of the front of the step frame 311, a space formed in the area adjacent to the continuously variable transmission case 323 at the rear of the steering case 318 is utilized. Thus, it is possible to easily extend the electric wiring for supplying electric power to the electric members of the engine 7 and the cab 5 and other parts. In addition, it contributes to the improvement of the assembling workability and the maintenance workability of the steering case 318 and the battery 230.

Further, since the oil filter 152 for filtering the hydraulic oil in the drive unit (the continuously variable transmission case 323 and the transmission case 63) is disposed in the above-mentioned region below the driver's cab 5, the drive unit (the continuously variable transmission case 323) And, the length of the hydraulic piping 222 connecting the transmission case 63) and the oil filter 152 can be shortened, and the management of the hydraulic piping 222 is simplified.

At the upper part in the steering case 318, the main transmission input shaft 317 facing sideways is disposed on one of the front and rear sides sandwiching the turning input shaft 316, and the rectilinear output shaft 350 going sideways is disposed on the other . The main shift input shaft 317 and the rectilinear output shaft 350 extend parallel to each other in a plan view in a left-right direction, and are pivotally supported by a steering case 318 so as to be rotatable. The main shift input shaft 317 and the rectilinear output shaft 350 are supported so as to protrude outward (leftward direction) from the left side surface of the steering case 318. A turning output shaft 164 extending in a direction orthogonal to the straight advance output shaft 350 is supported so as to protrude outward (rearward) from the steering case 318 at the back of the steering case 318 and below the straight advance output shaft 350 .

The straight connection link 345 is connected to the straight output shaft 350 by inserting the protruding end (left end) of the straight output shaft 350 at one end (right end) of the cylindrical shaft coupling body 351. At the other end (left end) of the shaft coupling body 351, a straight relay shaft 352 supported by a shift output support bracket 328 fixed to the leg frame 312 at the left front position of the cab 5 is inserted. By adjusting the left and right position of the relay shaft 352 for rectilinear movement relative to the shaft connector 351, the installation position of the rectilinear connection link body 435 in the left and right direction is adjusted.

One end (rear end) of a relay arm 353 for straight movement extending in the front-rear direction is fixed to the other end of the relay shaft 352 for straight movement, and for straight movement according to the rotation of the relay shaft 352 for straight movement The other end (front end) of the relay arm body 353 is swung up and down. The other end (front end) of the relay arm for straight movement 353 is connected to one end (upper end) of a connection rod 354 for straight movement extended vertically, and the other end (lower end) of the connection rod 354 is for straight movement It is connected with the operation arm 355 of.

The straight connection link body 345 connects the relay shaft 352 for straight movement extended in the left and right direction to a position on the extension line of the straight movement output shaft 350 by the shaft connection body 351 and the shift output fixed to the leg frame 312 It is pivotally supported by a support bracket 328. As a result, the rectilinear relay shaft 352 rotates 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 whose both ends are pivotally attached to the front end of the relay arm for straight movement 353 and one end of the operation arm 355 for straight movement moves up and down according to the swing of the relay arm for straight movement 353. As a result, the linear movement operation shaft 325 having the projecting end (the front end) fixed to the other end of the operation arm body 355 is rotated.

On the other hand, the swing connection link body 346 is extended in the left and right to the other end (tip) of the output arm 362 whose one end (base end) is fixed to the projecting end (rear end) of the swing output shaft 361. One end (right end) of the relay rod 363 is connected. The first relay rod 363 extends leftward and rightward over the front upper side of the continuously variable transmission case 323 at the rear position of the steering case 318, and the other end (left end) of the first relay rod 363 is a relay for turning It is connected to a first pivoting relay arm 364 fixed to one end (front end) of the shaft 365. The pivoting relay shaft 365 is supported by being penetrated by the tubular shaft support 366.

On the other hand, a second relay rod 368 extending laterally to the other end (tip) of the turning operation arm 369 whose one end (base end) is fixed to the protruding end (rear end) of the turning operation shaft 326 One end (right end) is connected. The second relay rod 368 extends laterally along the rear 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 one end of the turning relay shaft 365 (rear It connects with the 2nd relay arm body 367 fixed to the end.

The shaft support 366 that pivotally supports the turning relay shaft 365 is bolted to the upper surface of the transmission case 63 by bolting the other end of the support plate 370 whose one end is fixed to the outer peripheral surface of the shaft support 366. And fixed to the left side position of the continuously variable transmission case 323. Further, on the outer peripheral surface of the shaft support 366, a pipe fixing portion 372 is provided which is fixed in position by passing the hydraulic pipe 223 connected to the transmission case 63.

A first relay rod is provided extending in the left and right direction to an output arm 362 whose tip is pivoted to the left and right in accordance with the rotation of a pivot output shaft 361 provided to project rearward of the steering case 318. The right end of 363 is pivotally attached. Therefore, the first relay rod 363 moves in the left-right direction in accordance with the swinging of the output arm body 362, and the base end is fixed to the front end of the first turning relay arm 364 fixed to the front end of the turning relay shaft 365 Swing it. The swinging relay shaft 365 pivotally supported by the shaft support 366 is rotated by the swinging of the tip of the first swinging relay arm 364, and at the same time, the base end is fixed to the rear end of the swinging relay shaft 365. The tip of the second pivoting relay arm 364 swings to the left and right. Then, the second relay rod 368 whose both ends are pivotally attached to the front end of the second turning relay arm 367 and one end of the turning operation arm 369 is the right and left according to the swing of the second turning relay arm 367. As a result, the pivoting operation shaft 326 having the projecting end (rear end) fixed to the other end of the operation arm 369 is turned.

A main transmission input shaft 317 protrudes from the steering case 318 toward the center side of the traveling body 1 in the left and right direction. The projecting end (left end) of the main transmission input shaft 317 is pivotally supported by a main transmission input support bracket 381 fixed to the step frame 311 at the left edge on the transmission case 63 side. Further, one end (front end) of the main transmission arm body 382 is connected to the projecting end (left end) of the main transmission input shaft 317, and the other end (rear end) of the main transmission arm body 382 is the main transmission lever 44 Is connected to the main shift operating rod 322 connected to the.

A straight forward hydraulic continuously variable transmission 64 and a turning hydraulic continuously variable transmission 70 for shifting the power of the engine 7 are juxtaposed on the front and rear sides of the transmission case 63 on the side of the cab 5 (control unit). . A straight operation shaft 325 of the straight hydraulic hydraulic continuously variable transmission 64 and a turning operation shaft 326 of the turning hydraulic continuously variable transmission 70 are separately protrusively protrusively. Since the linear hydraulic continuously variable transmission 64 and the turning hydraulic continuously variable transmission 70 are arranged side by side on the cab 5 side, the connection structure with the steering case 318 can be configured to be short.

Further, by disposing the rectilinear operation shaft 325 and the turning operation shaft 326 in the front-rear direction, the same positional relationship as the rectilinear output shaft 350 and the turning output shaft 361 disposed in the front and rear in the steering case 318 can be obtained. As a result, the structure of the link mechanism from the steering case 318 to the linear hydraulic continuously variable transmission 64 and the turning hydraulic continuously variable transmission 70 can be simplified, and the continuously variable transmission case 323 and the steering case 318 below the cab 5. Can be placed close to each other for compact installation.

The steering case 318 is disposed below the driver's cab (steering unit) 5 and above the driving device (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 set up. The straight connection link body 345 connecting the straight movement output shaft 350 and the straight movement operation shaft 325, and the turn connection link body 346 connecting the turning output shaft 361 and the turn operation shaft 326 do not have the steering case 318 in plan view. It is installed between the speed change case 323. That is, since the rectilinear connection link body 345 and the turning connection link body 346 are disposed together with the transmission case 63 on the driver's cab 5 side, assemblability and maintainability are improved.

A straight link link body 345, which interlocks and links the steering case 318 and the straight operation shaft 325 which is a straight output control unit, is supported by a leg frame 312 supporting the cab 5. A steering case 318 is fixed to a case support horizontal frame (case support frame) 319 built in the middle of the left and right leg frames 312 that support the front position of the driver's cab (pilot unit) 5. Then, the rectilinear connection link body 345 is supported by the left support leg frame 312 on the transmission case 63 (continuously variable transmission case 323) side.

A leg frame 312 for supporting the driver's cab 5, a rectilinear connection link body 345 for interlockingly connecting the steering case 318 and the rectilinear operation shaft 325 (straight output control unit) provided in the drive device (the continuously variable transmission case 323 and the transmission case 63). It is supported by Therefore, even if bending or tension acts on the rectilinear connection link body 345 by the vibration of the drive unit (the continuously variable transmission case 323 and the transmission case 63), the rectilinear connection link body 345 has high rigidity by the leg frame 312 supporting the cab 5 Can be supported, and fluctuation and deformation of the rectilinear connection link body 345 can be suppressed. Therefore, there is no significant shift between the operation amount of the main shift lever 44 and the steering handle 43 and the output of the drive unit (the continuously variable shift case 323 and the transmission case 63). Eliminate the possibility of

A continuously variable transmission case 323 in which the linear hydraulic continuously variable transmission 64 and the turning hydraulic continuously variable transmission 70 are installed is fixed at an upper position on the right side surface of the transmission case 63. The swing connection link body 346 is supported on the upper surface of the transmission case 63 and on the side of the continuously variable transmission case 323. By utilizing the space between the feeder house 11 and the cab 5, the swing connecting link 346 can be compactly and highly rigidly supported on the transmission case 63 where the continuously variable transmission case 323 and the vibration system are the same. Therefore, bending or tension of the swing connection link body 346 due to mechanical vibration is suppressed, and the amount of operation 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) There will not be a large gap between them, and there is no risk of running conditions that the operator does not expect.

The mounting structure of the ECU 401 that controls the operation of the combine will be described with reference to FIGS. 22 to 26. As can be understood from the above description, in the embodiment, the step portion 400 which is a space surrounded by the traveling airframe 2 front portion, the leg frame 312 group, and the step frame 311 group is a dead space. A steering case 318, a continuously variable transmission case 323 and a battery 230 are disposed.

On the front side of the step unit 400, an ECU 401 that controls the operation of the combine is disposed. In the embodiment, the shielding plate 402 is arranged to bridge over the front side of the step portion 400, that is, the front center side of the step frame 311 and the front center side of the case support horizontal frame 319. The upper end side of the shielding plate 402 is welded and fixed to the front center side of the step frame 311. The lower end side of the shielding plate 402 is welded and fixed to the front center side of the case support horizontal frame 319. That is, the shielding plate 402 is supported by the step portion 400 (the step frame 311 and the case support horizontal frame 319). The ECU 401 is fastened to the front side of the shielding plate 402.

Therefore, the ECU 401 is positioned on the front side across the space of the step portion 400, and the engine 7 is positioned on the rear side. Moreover, the steering case 318 and the shielding plate 402 are located between the ECU 401 and the engine 7, and both the steering case 318 and the shielding plate 402 serve as a shield against the exhaust heat from the engine 7. With this configuration, the ECU 401 is disposed as far as possible from the engine 7 around the cab 5 (steering unit), and the thermal influence of the engine 7 on the ECU 401 can be reduced. Control stabilization and long life of the ECU 401 can be achieved. In particular, since the exhaust heat from the engine can be shut off by the shielding plate 402, the effect of reducing the thermal influence of the engine 7 on the ECU 401 is high.

The outer shape of the shielding plate 402 is larger than the outer shape of the ECU 401. For this reason, the peripheral portion of the shielding plate 402 protrudes from the outer periphery of the ECU 401. Exhaust heat from the engine 7 is less likely to flow to the front side of the ECU 401 due to the presence of the peripheral portion of the shielding plate 402. In the embodiment, the lower center side of the shielding plate 402 is cut out, and the shielding plate 402 is substantially U-shaped downward. The notched portion 403 is provided for the purpose of thinning the shielding plate 402 and for the purpose of applying the outside air to the rear side of the ECU 401 or releasing the heat of the ECU 401.

The front side of the ECU 401 is covered by a front cover 404 of the cab 5. The battery 230 for power supply disposed in the step portion 400 is located below the steering case 318 and the case support horizontal frame 319. Therefore, the ECU 401 is at a higher position than the battery 230. The battery 230 is placed at a position where the traveling airframe 1 is not affected by, for example, muddy water or rain water in a field (no muddy water or the like is applied). Since the ECU 401 is also disposed at a high position in such a battery 230, there is also an advantage that the influence of mud water or the like on the ECU 401 can be more reliably eliminated. Further, since the ECU 401 and the battery 230 are disposed close to each other, the electric system can be made compact.

The configuration of each part in the present invention is not limited to the illustrated embodiment, and various changes can be made without departing from the spirit of the present invention.

Reference Signs List 1 traveling body 3 reaper 5 cab 7 engine 9 threshing part 11 feeder house 311 step frame 312 leg frame 318 steering case 319 case support horizontal frame 400 step part 401 ECU
402 shielding plate 403 notched portion 404 front cover

Claims (4)

1. A reaper is attached to the front of a traveling unit equipped with an engine, a threshing unit is mounted behind the reaper of the traveling unit, and a control unit is disposed on the side of the front of the threshing unit. In the combine that mounts the engine on the lower rear side of the step part in the part,
   An ECU that controls the operation of the combine is disposed on the front side of the step portion.
   Combine.
2. A shielding plate is disposed on the front side of the step portion, and the ECU is attached to the front side of the shielding plate.
   The combine according to claim 1.
3. The shielding plate is supported by the step portion,
   The combine according to claim 2.
4. A battery for supplying power is mounted on the step portion, and the ECU is positioned higher than the battery.
   The combine according to claim 1.

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