JP7569293B2 - combine - Google Patents

Description

The present invention relates to a combine harvester equipped with a cutting unit that cuts uncut stalks in a farm field and a threshing unit that threshes grains from the cut stalks.

Conventionally, in combine harvesters, an ECU that controls the operation of the combine harvester has generally been disposed around a control unit mounted on the traveling body (see, for example, Patent Documents 1 and 2, etc.).

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

However, in the case of combine harvesters that have an engine mounted behind the control unit, the ECU may be affected by exhaust heat from the engine. In recent years, it is desirable for ECUs, which often handle complex controls, to be as unaffected by heat as possible from their surroundings.

The technical object of the present invention is to provide a combine harvester which has been improved based on the above-mentioned current situation.

The present invention relates to a combine harvester having a cutting unit attached to the front of a running body on which an engine is mounted, a threshing unit mounted on the running body rear of the cutting unit, a control unit disposed to the front side of the threshing unit, and an engine mounted below the rear of the control unit, in which a battery for supplying power is mounted below the control unit, and an ECU for controlling the operation of the combine is attached to a support frame below the front of the control unit , and the battery is positioned between the engine and the ECU .

According to the present invention, in a combine harvester having a reaping unit mounted on the front of a traveling body equipped with an engine, a threshing unit mounted on the traveling body behind the reaping unit, a control unit disposed on the front side of the threshing unit, and an engine mounted on the rear side below the control unit, a battery for supplying power is mounted below the control unit, and an ECU for controlling the operation of the combine harvester is attached to a support frame on the front side below the control unit , and the battery is disposed between the engine and the ECU , so that the ECU is disposed as far away from the engine as possible around the control unit, thereby reducing the thermal effect from the engine to the ECU, and stabilizing the control and extending the life of the ECU.

FIG. 2 is a left side view of the combine harvester according to the present invention. FIG. FIG. FIG. 1 is a diagram showing the drive system of a combine harvester. This is a perspective view of the combine harvester as seen diagonally from the front. A partial cross-sectional plan view of the threshing section. FIG. 4 is a drive system diagram of the transmission case. FIG. 2 is a plan cross-sectional view showing the configuration of the engine room and its surroundings. FIG. 2 is a hydraulic circuit diagram showing a configuration of a working hydraulic circuit. FIG. 2 is a front view showing the arrangement of hydraulic circuit components. FIG. 2 is an overall perspective view of a combine harvester showing a piping configuration of a work hydraulic circuit. FIG. 4 is an enlarged perspective view showing a piping configuration of a traveling hydraulic circuit. FIG. 2 is a hydraulic circuit diagram showing a configuration of a traveling hydraulic circuit. FIG. 4 is a perspective view showing the piping construction of hydraulic piping on a transmission case. FIG. 4 is a perspective view showing the relationship between hydraulic piping on a transmission case and a connecting link body. This is an oblique view of the front part of the traveling body as seen diagonally from the front left. This is an oblique view of the driver's seat (control section) and its surroundings seen diagonally from the rear left. This is a front view of the area around the driver's seat (control section). This is a plan view of the area around the driver's seat (control section). This is an oblique view of the driver's seat (control section) and its surroundings seen from diagonally rear right. This is an oblique view of the driver's seat (control section) and its surroundings from the front. 1 is a perspective view of the mounting position of the ECU as viewed from diagonally forward left of the traveling body. FIG. 2 is a front view of the driver's seat (control section) and its surroundings, showing the mounting position of the ECU. FIG. 2 is a plan view of the driver's seat (control section) and its surroundings, showing the mounting position of the ECU. 4 is a perspective view showing the positional relationship between the ECU and the steering case as viewed from diagonally forward right. FIG. 2 is a perspective view of the mounting position of the ECU as viewed from diagonally forward right. FIG.

The following is a detailed description of an embodiment of the present invention applied to a normal type combine harvester, with reference to the drawings (FIGS. 1 to 4).
The following description will be made based on the drawings (FIG. 26). First, the general structure of the combine will be described with reference to FIGS. 1 to 3. In the following description, the left side facing the forward direction of the traveling body 1 will be simply referred to as the left side, and the right side facing the forward direction will be simply referred to as the right side.

As shown in Figures 1 to 3, the conventional combine harvester in the embodiment includes a traveling body 1 supported by a pair of left and right tracks 2 made of rubber crawlers as a traveling part. At the front of the traveling body 1, there is a reaping part 3 that harvests and collects unharvested stalks such as rice (or wheat, soybeans, or corn).
is mounted so that its elevation can be adjusted by a single-acting lifting hydraulic cylinder 4.

A threshing unit 9 for threshing the harvested stalks supplied from the harvesting unit 3 is mounted on the left side of the traveling machine body 1. A grain sorting mechanism 10 for performing rocking sorting and wind sorting is mounted on the lower part of the threshing unit 9.
On the right front part of the traveling body 1, a driver's seat 5 is arranged as a control section where an operator sits.
The engine 7 as a power source is disposed in the cab 5 (below the cab 42). A grain tank 6 for removing grains from the threshing section 9 is disposed behind the cab 5 (to the right of the traveling machine body 1).
A grain discharge conveyor 8 is disposed to discharge the grains in the grain tank 6 toward the truck bed (or a container, etc.). The grain discharge conveyor 8 is tilted toward the outside of the machine so that the grains in the grain tank 6 are carried out by the grain discharge conveyor 8.

The reaping section 3 comprises a feeder house 11 connected to the handling port 9a at the front of the threshing section 9, and a horizontally long bucket-shaped grain header 12 connected to the front end of the feeder house 11. A raking auger 13 (platform auger) is rotatably supported within the grain header 12. A tine bar-equipped raking reel 14 is disposed above the front of the raking auger 13. A clipper-shaped cutting blade 15 is disposed at the front of the grain header 12. Left and right grass division bodies 16 protrude from both the left and right sides of the front of the grain header 12. A supply conveyor 17 is also provided inside the feeder house 11. A beater 18 (front rotor) for feeding harvested stalks is provided at the feed end side (handling port 9a) of the supply conveyor 17. The underside of the feeder house 11 and the front end of the running body 1 are connected via a lifting hydraulic cylinder 4, and the cutting unit 3 is raised and lowered by the cutting input shaft 89 (feeder house conveyor shaft) described later, which serves as a lifting fulcrum.

With the above configuration, the tips of the uncut stalks between the left and right grass segments 16 are raked in by the raking reel 14, the bases of the uncut stalks are cut by the cutting blade 15, and the raking auger 13 is driven to rotate, collecting the cut stalks near the entrance to the feeder house 11 near the center of the left and right width of the grain header 12. The entire amount of cut stalks in the grain header 12 is transported by the supply conveyor 17, and is configured to be fed into the handling opening 9a of the threshing section 9 by the beater 18.
It is also possible to provide a horizontal control hydraulic cylinder (not shown) that rotates the grain header 12 around the horizontal control fulcrum axis, and to adjust the left-right inclination of the grain header 12 with the horizontal control hydraulic cylinder, thereby supporting the grain header 12, the cutting blade 15, and the raking reel 14 horizontally relative to the field surface.

As shown in Figs. 1 and 3, a threshing drum 21 is rotatably provided in the threshing chamber of the threshing section 9. The threshing drum 21 is supported by a threshing drum shaft 20 (see Fig. 4) extending in the front-rear direction of the traveling machine body 1.
A receiving net 24 is stretched below the threshing drum 21 to allow grains to fall through. A helical screw-blade-like intake blade 25 is provided on the outer circumferential surface of the front part of the threshing drum 21 so as to protrude radially outward.

With the above-mentioned configuration, the harvested stalks fed from the threshing opening 9a by the beater 18 are conveyed to the threshing drum 21.
The grains are conveyed toward the rear of the traveling machine body 1 by the rotation of the threshing drum 21 and are mixed and threshed between the threshing drum 21 and the receiving net 24. Grains smaller than the mesh size of the receiving net 24 will fall through the receiving net 24. Straw chips that do not fall through the receiving net 24 will be conveyed to the threshing section 9 by the conveying action of the threshing drum 21.
The dust is discharged into the field through the dust outlet 23 at the rear.

In addition, a number of dust-transport valves (not shown) for adjusting the transport speed of the removed grains in the threshing chamber are rotatably attached to the upper side of the threshing drum 21. By adjusting the angle of the dust-transport valves, the transport speed (retention time) of the removed grains in the threshing chamber can be adjusted according to the variety and properties of the harvested stalks. Meanwhile, a oscillating sorting plate 26 for specific gravity sorting having a grain pan, chaff sieve, grain sieve, straw rack, etc. is provided as the grain sorting mechanism 10 arranged below the threshing section 9.

The grain sorting mechanism 10 is also provided with a fan-type winnower 29 that supplies sorting air to the oscillating sorting plate 26. The threshed grains that have been threshed by the threshing drum 21 and dropped through the receiving net 24 are sorted by the gravity sorting action of the oscillating sorting plate 26 and the wind sorting action of the fan-type winnower 29 into grains (first grains such as refined grains), a mixture of grains and straw (second grains such as grains with stalks), and straw chips, etc., and are removed.

Below the oscillating sorting plate 26, a first conveyor mechanism 30 and a second conveyor mechanism 31 are provided as the grain sorting mechanism 10. Grains (first grains) that fall from the oscillating sorting plate 26 due to sorting by the oscillating sorting plate 26 and the fan-like winnower 29 are collected in the grain tank 6 by the first conveyor mechanism 30 and the grain lifting conveyor 32. A mixture of grains and straw (second grains) is returned to the sorting start end of the oscillating sorting plate 26 via the second conveyor mechanism 31 and the second return conveyor 33, etc., and is sorted again by the oscillating sorting plate 26. Straw chips and the like are configured to be discharged into the field from the dust outlet 23 at the rear of the traveling body 1.

1 to 3, the cab 5 is provided with a steering column 41 and a driver's seat 42 on which an operator sits. The steering column 41 is provided with an accelerator lever 40 for adjusting the RPM of the engine 7, a round steering wheel 43 for changing the course of the traveling body 1 by the operator's rotation, a main speed change lever 44 and a sub-speed change lever 45 for changing the moving speed of the traveling body 1, a reaping clutch lever 46 for driving or stopping the reaping unit 3, and a threshing clutch lever 47 for driving or stopping the threshing unit 9. A sunshade roof body 49 is attached to the front upper surface side of the grain tank 6 via a sun visor support 48, and the sunshade roof body 49 is configured to cover the upper side of the cab 5.

As shown in Figures 1 and 2, left and right track frames 50 are disposed on the underside of the traveling vehicle body 1. The track frames 50 are provided with a drive sprocket 51 for transmitting the power of the engine 7 to the crawler belt 2, a tension roller 52 for maintaining the tension of the crawler belt 2, a plurality of track rollers 53 for keeping the grounded side of the crawler belt 2 in a grounded state, and intermediate rollers 54 for holding the non-grounded side of the crawler belt 2.
The front side of the crawler belt 2 is supported by a drive sprocket 51, the rear side of the crawler belt 2 is supported by a tension roller 52, the ground contact side of the crawler belt 2 is supported by a track roller 53, and the non-ground contact side of the crawler belt 2 is supported by an intermediate roller 54.

Next, the drive structure of the combine harvester will be described with reference to Figures 4 to 8. As shown in Figures 4 and 7, a hydraulic linear pump 64a and a hydraulic linear motor 64b are provided in a transmission case 63. The engine 7 is mounted on the upper right side of the front part of the traveling body 1.
and a transmission case 63 is disposed in front of the traveling body 1 on the left side 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. In addition, a working section charge pump 59 and a cooling fan 149 that drive the lifting hydraulic cylinder 4 and the like are disposed on the engine 7, and the working section charge pump 59 and the cooling fan 149 are driven by the engine 7.

A hydraulic swing pump 70a and a hydraulic swing motor 70b are provided in the transmission case 63. The output of the engine 7 is transmitted to the linear hydraulic continuously variable transmission 64 and the swing hydraulic continuously variable transmission 70 via the transmission input shaft 66. The steering handle 43, the main shift lever 44, and the sub shift lever 45 are used to control the linear hydraulic continuously variable transmission 64.
and the swing hydraulic continuously variable transmission 70 to drive the left and right crawlers 2 via the linear hydraulic continuously variable transmission 64 and the swing hydraulic continuously variable transmission 70, thereby traveling within a farm field, etc. In this embodiment, the linear and swing hydraulic continuously variable transmissions 64, 70 are disposed on the upper right side of the transmission case 63. The linear and swing hydraulic continuously variable transmissions 64, 70 and the transmission case 63 constitute the drive device of the present invention.

1 to 6, a threshing drum drive case 71 is provided which supports the front end of the threshing drum shaft 20. The threshing drum drive case 71 is disposed on the front side of the threshing unit 9. A threshing drum input shaft 72 for driving the reaping unit 3 and the threshing drum 21 is supported by the threshing drum drive case 71. A main counter shaft 76 is provided as a constant rotation shaft which passes through the threshing unit 9 from left to right. A working unit input pulley 83 is provided on the right end of the main counter shaft 76. The right end of the main counter shaft 76 is connected to the engine output pulley 68 on the 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.

Provided in front of the threshing drum 21 are a threshing drum input shaft 72 extending left and right from the traveling body 1, a beater 18 arranged left and right from the traveling body 1, and a reaping input shaft 89 extending left and right from the traveling body 1. As a threshing drum input mechanism 90 that transmits the driving force of the main counter shaft 76 to the threshing drum input shaft 72, threshing drum drive pulleys 86, 87 and a threshing drum drive belt 88 are provided, and the threshing drum input mechanism 90 (threshing drum drive pulleys 86, 87 and threshing drum drive belt 88) is arranged at one end of the main counter shaft 76 on the engine 7 side to which the driving force from the engine 7 is transmitted, so that the threshing drum 21 is driven to rotate at a constant speed by the constant rotation output of the engine 7.

A beater drive mechanism and a reaping drive mechanism that transmit the driving force of the main counter shaft 76 to the beater shaft 82 and the reaping input shaft 89 are provided on the other end side of the main counter shaft 76. In addition, a sub-counter shaft 104 is disposed between the beater shaft 82 and the main counter shaft 76.
The power relay belt 1 is connected to the power relay pulleys 105 and 106 provided on the counter shaft 104 and the power relay pulleys 106 and 106 provided on the counter shaft 104.
13 is wound around the winding to form a power relay mechanism that transmits power to the reaping drive mechanism.

The counter shaft 104 and the beater shaft 82 are provided with driving pulleys 107 and 10
A mowing drive belt 114 is wound around the main counter shaft 76 and constitutes a beater drive mechanism. The mowing drive belt 114 is tensioned by a mowing clutch 109 which also serves as a tension roller, so that the rotational power from the engine 7 transmitted to the main counter shaft 76 is input to the beater shaft 82 via the power relay mechanism and the beater drive mechanism. The mowing drive mechanism is configured so that the mowing drive force from the engine 7 is transmitted from the beater shaft 82, on which the beater 18 is journalled, to the mowing input shaft 89 via the mowing drive chain 115 and sprockets 116, 117. As a result, the mowing unit 3, together with the beater 18, is driven to rotate at a constant speed by the constant rotational output of the engine 7.

The winnowing shaft 100, which is the rotating shaft of the fan-shaped winnowing machine 29, has a hollow tubular shape.
The main counter shaft 76 is inserted into the hollow portion of the winnowing shaft 100. In other words, the main counter shaft 76 and the winnowing shaft 100 form a double shaft structure, and the main counter shaft 76 and the winnowing shaft 100 are supported so as to be rotatable relative to each other. A winnowing drive belt 103 is wound around winnowing drive pulleys 101, 102 provided on the sub-counter shaft 104 and the winnowing shaft 100, respectively, to form a winnowing drive mechanism. Therefore, the rotational power from the engine 7 transmitted to the main counter shaft 76 is input to the beater shaft 82 via the power relay mechanism and the winnowing drive mechanism, and the winnower 29 is driven to rotate at a constant speed by the constant rotational output of the engine 7.

Furthermore, the machine housing of the threshing section 9 has a reaping support frame 36 installed on the top surface of the front part of the threshing machine housing support pillar 34, among the upper surface side of the traveling machine body 1. A reaping bearing body 37 is attached to the front right side of the reaping support frame 36, and a forward/reverse rotation changeover case 121, which will be described later, is attached to the front left side of the reaping support frame 36. The reaping input shaft 89 is journaled on the front side of the reaping support frame 36 via the reaping bearing body 37 and the forward/reverse rotation changeover case 121 so as to be rotatable left and right on the traveling machine body 1, and the left and right beater shaft 82 (beater 1) is connected to the inside of the reaping support frame 36 via the beater bearing body 38.
8) is rotatably supported.
1 is attached, and a threshing drum input shaft 72 is journalled on the threshing drum drive case 71.

On the other hand, the left-right reaping input shaft 89 which drives the supply conveyor 17 in the feeder house 11
The mowing drive force transmitted from the engine 7 to one end of the main counter shaft 76 on the engine 7 side is transmitted from the other end of the main counter shaft 76 opposite the engine 7 to a forward/reverse transmission shaft 122 of a mowing forward/reverse rotation switching case 121. The mowing input shaft 89 is driven via a forward rotation bevel gear 124 or a reverse rotation bevel gear 125 of the mowing forward/reverse rotation switching case 121.

A threshing drum input shaft 72 facing left and right is provided on the front side of the threshing section 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 transmitted to one end of the threshing drum input shaft 72 on the engine 7 side. The threshing drum input shaft 72 provided on the front side of the threshing section 9 is arranged facing left and right with respect to the traveling body 1, while the threshing drum 21 is journaled on a threshing drum shaft 20 arranged in the front-rear direction of the traveling body 1. The front end of the threshing drum shaft 20 is connected via a bevel gear mechanism 75 to the other left and right end of the threshing drum input shaft 72 opposite the engine 7. The main counter shaft 76
The driving force of the engine 7 is transmitted from the other left and right ends, which are opposite the engine 7, to a grain sorting mechanism 10 that sorts grains after threshing or to the reaping unit 3.

That is, the right end of the main counter shaft 76 on the side close to the engine 7 is provided with a throttling drum drive pulley 86, 87.
The right end of the threshing drum input shaft 72 is connected via the engine 7 and a threshing drum drive belt 88. The front end of the threshing drum shaft 20 is connected via a bevel gear mechanism 75 to the left end of the threshing drum input shaft 72, which extends 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 of the threshing drum shaft 20 via the threshing drum input shaft 72, so as to drive the threshing drum 21 to rotate in one direction. Meanwhile, the driving force of the engine 7 is transmitted from the left end of the main counter shaft 76 to a grain sorting mechanism 10 disposed below the threshing section 9.

Furthermore, the left end of the main counter shaft 76 is connected to 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 a conveyor drive belt 111. The left end of the second conveyor shaft 78 is connected to the left end of a crank-shaped oscillating drive shaft 79 that supports the rear part of the oscillating sorting board 26 via an oscillating sorting belt 112. That is, the threshing clutch 8 is engaged by operating the threshing clutch lever 47 by the operator.
The threshing clutch 84 is controlled to be turned on and off. By turning on the threshing clutch 84, each part of the grain sorting mechanism 10 and the threshing drum 21 are driven.

The grain lifting conveyor 32 is driven via the first conveyor shaft 77, and the first sorted grains from the first conveyor mechanism 30 are collected in the grain tank 6. The second return conveyor 33 is driven via the second conveyor shaft 78, and the second sorted grains (second grains) mixed with straw dust from the second conveyor mechanism 31 are returned to the upper surface side of the oscillating sorting plate 26. In a structure in which a spreader (not shown) for scattering straw dust is provided at the dust outlet 23, the left end of the main counter shaft 76 is connected to the spreader via a spreader drive pulley (not shown) and a spreader drive belt (not shown).

The grain header 12 includes a reaping input shaft 89 that serves as a conveyor input shaft and supports the feeding end side of the supply conveyor 17. A header drive shaft 91 is rotatably supported on the rear side of the right side of the grain header 12. The left end of a forward/reverse rotation transmission shaft 122 is connected to the left end of the beater shaft 82 via a reaping drive chain 115 and sprockets 116, 117, and the reaping input shaft 89 is connected to the forward/reverse rotation transmission shaft 122 via a forward/reverse switching case 121. The left end of the header drive shaft 91, which extends in the left-right direction, is connected to the left end of the header drive shaft 91 via a header drive chain 118 and sprockets 119, 120.
The right end of the harvesting input shaft 89 is connected to the rear end of the harvesting input shaft 89. A raking shaft 93 is provided for supporting the raking auger 13. The middle portion of the header drive shaft 91 is connected to the right portion of the raking shaft 93 via a raking drive chain 92.

The header drive shaft 91 also includes a reel shaft 94 that supports the pick-up reel 14. The right end of the reel shaft 94 is connected to the right end of the pick-up shaft 93 via an intermediate shaft 95 and reel drive chains 96, 97. The right end of the header drive shaft 91 is connected to the blade 1 via a blade drive crank mechanism 98.
5 is connected to the reaping clutch 109. By turning the reaping clutch 109 on and off, the supply conveyor 17, the raking auger 13, the raking reel 14, and the cutting blade 15 are driven and controlled to continuously reap the tips of the uncut stalks in the field.

In addition, the forward rotation bevel gear 124 formed integrally with the forward/reverse rotation transmission shaft 122 and the reaping input shaft 89
A reverse rotation bevel gear 125 rotatably supported on the forward rotation bevel gear 124, and an intermediate bevel gear 126 for connecting the reverse rotation bevel gear 125 to the forward rotation bevel gear 124 are disposed inside the forward/reverse rotation changeover case 121. The intermediate bevel gear 126 is always meshed with the forward rotation bevel gear 124 and the reverse rotation bevel gear 125. Meanwhile, a slider 127 is slidably supported on the reaping input shaft 89 by spline engagement. The slider 127 is connected to the forward rotation bevel gear 124 via a forward clutch 128 in the form of a claw clutch.
The slider 127 is configured to be releasably engageable with the reverse rotation bevel gear 125 via a reverse rotation clutch 129 in the form of a pawl clutch.

In addition, a forward/reverse rotation switching shaft 123 that slides the slider 127 is provided.
A forward/reverse switching arm 130 is provided on the forward/reverse transmission shaft 122, and the forward/reverse switching arm 130 is swung by operating a forward/reverse switching lever (forward/reverse operating device) to rotate the forward/reverse switching shaft 123 and move the slider 127 closer to or away from the forward bevel gear 124 or the reverse bevel gear 125. The slider 127 is selectively engaged with the forward bevel gear 124 or the reverse bevel gear 125 via a forward clutch 128 or a reverse clutch 129, and the mowing input shaft 89 is connected in forward or reverse direction to the forward/reverse transmission shaft 122.

The structure includes a forward/reverse switching case 121 as a forward/reverse switching mechanism for driving the supply conveyor 17 in the forward or reverse direction, and the supply conveyor 17 is connected to the beater shaft 82 via the forward/reverse switching case 121. Therefore, the supply conveyor 17 of the feeder house 11 and the like can be reversed by the reverse switching operation of the forward/reverse switching case 121, and the feeder house 1
It can quickly remove any clogged straw inside the drain.

The right end of the auger drive shaft 158 is connected to the output shaft 65 of the engine 7 via a tension pulley-shaped auger clutch 156 and an auger drive belt 157.
The front end of a lateral feed auger 160 at the bottom of the grain tank 6 is connected to the left end of the lateral feed auger 160 via a bevel gear mechanism 159. A vertical feed auger 162 of the grain discharge conveyor 8 is connected to the rear end of the lateral feed auger 160 via a bevel gear mechanism 161, and a grain discharge auger 164 of the grain discharge conveyor 8 is connected to the upper end of the vertical feed auger 162 via a bevel gear mechanism 163. Also, a grain discharge lever 155 is provided for turning the auger clutch 156 on and off. The grain discharge lever 155 is attached to the front of the grain tank 6 behind the driver's seat 42, so that the operator can operate the grain discharge 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, 7, etc. As shown in Figs. 4, 7, etc., the transmission case 63 is provided with a hydraulic continuously variable transmission 64 for straight travel (main travel speed change) having a pair of straight pumps 64a and straight motors 64b, and a hydraulic continuously variable transmission 70 for swinging having a pair of swing pumps 70a and swing motors 70b. The transmission input shaft 66 of the transmission case 63 is gear-coupled to each of the pump shafts 258, 259 of the straight pumps 64a and the swing pumps 70a, respectively, to drive them. An engine output belt 67 is wound around a mission input pulley 69 on the mission input shaft 66. The output of the engine 7 is transmitted to the mission input pulley 69 via the engine output belt 67 to drive the straight pump 64a and the swing pump 70a.

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

The transmission input shaft 66 protrudes from the upper left side surface of the transmission case 63 toward the feeder house 11, and a transmission input pulley 69 is axially attached to the protruding end (left end) of the transmission input shaft 66 so as not to rotate relative to the transmission input pulley 69. The transmission input shaft 66 is rotatably supported by a bearing fixed to the transmission case 63, and a power distribution gear 262 is fitted to the middle portion of the transmission input shaft 66 so as not to rotate relative to the transmission input pulley 69. A pump shaft 258 of the linear pump 64a and a pump shaft 259 of the rotary pump 70a are respectively arranged in front of and behind the transmission input shaft 66 in a plan view, and are arranged below the mission input shaft 66 in a side view.

The pump shaft 25 protrudes from the continuously variable transmission case 323 toward the inside of the transmission case 63.
A linear input gear 263 that meshes with a power distribution gear 262 fixed to the transmission input shaft 66 is fitted to the protruding end (left end) of the continuously variable transmission case 32 so as not to rotate relative to the transmission input shaft 66.
The pump shaft 259 is protruded from the transmission case 63 into the transmission case 63 at its protruding end (left end) thereof. The protruding end (left end) of the pump shaft 259 is fitted with a rotation input gear 262 which is engaged with a power distribution gear 262 fixed to the transmission input shaft 66.
4 are fitted to each other so as not to rotate relative to each other.

When the driving force output from the output shaft 65 of the engine 7 is transmitted to the transmission input pulley 69, the transmission input shaft 66 and the power distribution gear 262 rotate together with the transmission input pulley 69, rotating the pump shaft 258 of the linear pump 64a via the linear input gear 263, while rotating the pump shaft 259 of the swirl pump 70a via the swirl input gear 264. That is, the power distribution gear 262 of the transmission input shaft 66, which is disposed between the pump shafts 258, 259, is connected to the linear input gears 263 and the swirl input gears 264 of the pump shafts 258, 259.
By meshing the gears 4, the driving force from the engine 7 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 connected to the hydraulic pumps 64a, 70a and the hydraulic motors 64b, 7
The linear hydraulic continuously variable transmission 64 is operated by the main speed change lever 44 and the steering handle 46 disposed in the steering column 41.
The inclination angle of the swash plate in the linear pump 64a is changed and adjusted in accordance with the amount of operation of the linear motor 64.3, thereby changing the discharge direction and discharge amount of the hydraulic oil to the linear motor 64b.
The rotation direction and rotation speed of the linear motion motor shaft 260 protruding from b can be arbitrarily adjusted.

The rotational power of the linear motor shaft 260 is transmitted from the linear transmission gear mechanism 250 to the sub-transmission gear mechanism 25
The auxiliary transmission gear mechanism 251 has an auxiliary low speed gear 254, an auxiliary medium speed gear 255, and an auxiliary high speed gear 256 which are switched by auxiliary transmission shifters 252, 253.
The output speed of the straight-travel motor shaft 260 is selectively switched to one of three speed stages, low speed, medium speed, or high speed, by operating the auxiliary speed change lever 45 disposed on the steering column 41. Note that the auxiliary speed change has a neutral position (a position where the output of the auxiliary speed change is zero) between low speed, medium speed, and high speed.

A parking brake shaft 265 (sub-transmission output shaft) provided on the output side of the sub-transmission gear mechanism 251 is provided with a drum-type parking brake 266. The rotational power from the sub-transmission gear mechanism 251 is transmitted from a sub-transmission output gear 267 fixed to the parking brake shaft 265 to the left and right differential mechanisms 2.
The right and left differential mechanisms 257 are each equipped with a planetary gear mechanism 268. In addition, a straight-line pulse generating rotating wheel 292 is provided on the parking brake shaft 265, and a straight-line output rotation speed (straight-line vehicle speed = shift output of the sub-transmission output gear 267) is detected by a straight-line vehicle speed sensor (not shown).

Each of the left and right planetary gear mechanisms 268 includes a sun gear 271, a plurality of planetary gears 272 meshing with the sun gear 271, a ring gear 273 meshing with the planetary gears 272, and a plurality of planetary gears 273.
The carriers 274 of the left and right planetary gear mechanisms 268 are disposed facing each other on the same axis with an appropriate gap provided.
76 is fixed.

Each of the left and right ring gears 273 is disposed concentrically about the sun gear shaft 275 with the inner teeth of the inner peripheral surface of the ring gear 273 meshing with the planetary gears 272.
The external teeth on the outer circumferential surface are connected to a steering output shaft 285 via intermediate gears 287, 288 for left and right turning output, which will be described later. Each ring gear 273 is rotatably supported by left and right forced differential output shafts 277 protruding outwardly to the left and right from the outer surface of the carrier 274. Left and right axles 278 are connected to the left and right forced differential output shafts 277 via final gears 278a, 278b. Left and right drive sprockets 51 are attached to the left and right axles 278. Therefore, the rotational power transmitted from the auxiliary transmission gear mechanism 251 to the left and right planetary gear mechanisms 268 is transmitted from the left and right axles 278 to the respective drive sprockets 51 at the same rotational speed in the same direction, driving the left and right crawlers 2 at the same rotational speed in the same direction, and moving the traveling body 1 straight (forward, backward).

The swing hydraulic continuously variable transmission 70 is configured to arbitrarily adjust the rotation direction and rotation speed of the swing motor shaft 261 protruding from the swing motor 70b by changing and adjusting the inclination angle of the rotating swash plate in the swing pump 70a in accordance with the amount of rotation of the main speed change lever 44 and the steering handle 43 arranged on the steering column 41, thereby changing the discharge direction and discharge amount of hydraulic oil to the swing motor 70b. In addition, a swing pulse generating rotating wheel 294 is provided on the steering counter shaft 280 described later, and a swing rotation sensor (swing vehicle speed sensor) not shown is configured to detect the rotation speed (swing vehicle speed) of the steering output of the swing motor 70b.

Also, within the transmission case 63, there are disposed a wet-type multi-plate swing brake 279 (steering brake) provided on the swing motor shaft 261 (steering input shaft), a steering counter shaft 280 connected to the swing motor shaft 261 via a reduction gear 281, and a reduction gear 282 connected to the steering counter shaft 280.
6, a left input gear mechanism 282 which connects the steering output shaft 285 to the left ring gear 273 via a reverse gear 284, and a right input gear mechanism 283 which connects the steering output shaft 285 to the right ring gear 273. The rotational power of the turning motor shaft 261 is transmitted to a steering countershaft 280. The rotational power transmitted to the steering countershaft 280 is transmitted to the left ring gear 273 as reverse rotational power via a left intermediate gear 287 on the steering output shaft 285 in the left input gear mechanism 282 and a reverse gear 284, and is transmitted to the right ring gear 273 as forward rotational power via a right intermediate gear 288 on the steering output shaft 285 in the right input gear mechanism 283.

When the sub-transmission gear mechanism 251 is in neutral, power transmission from the linear motor 64b to the left and right planetary gear mechanisms 268 is blocked. When the sub-transmission gear mechanism 251 outputs a sub-transmission output other than neutral, power is transmitted from the linear motor 64b to the left and right planetary gear mechanisms 268 via the sub-transmission low speed gear 254, the sub-transmission medium speed gear 255, or the sub-transmission high speed gear 256. On the other hand, the swing pump 70
When the output of the swing pump 7 a is in a neutral state and the swing brake 279 is in an on state, the power transmission from the swing motor 70 b to the left and right planetary gear mechanisms 268 is blocked.
When the output of the swing motor 70a is in a state other than neutral and the swing brake 279 is in an off state, 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, while the rotational power of the swing motor 70b is transmitted to the right ring gear 273 via the right input gear mechanism 283.
This will be transmitted to 73.

As a result, when the swing motor 70b rotates forward (reversely), the rotation speeds are the same but in opposite directions.
The left ring gear 273 rotates in the reverse direction (forward rotation), and the right ring gear 273 rotates in the forward direction (reverse rotation).
The speed change output from each motor shaft 260, 261 is sent to the sub-speed change gear mechanism 251 or the differential mechanism 257.
The signal is then transmitted to the drive sprockets 51 of the left and right crawlers 2 via the drive shafts 51 and 52, respectively, to determine the vehicle speed (traveling speed) and direction of travel of the traveling machine body 1.

In other words, when the slewing motor 70b is stopped and the left and right ring gears 273 are fixed stationary, when the straight-line motor 64b is driven, the rotational output from the straight-line motor shaft 260 is transmitted to the left and right sun gears 271 at the same rotation speed on the left and right, and via the planetary gears 272 and carrier 274, the left and right tracks 2 are driven at the same rotation speed in the same direction, causing the running body 1 to run in a straight line.

Conversely, when the slewing motor 70b is driven with the linear motor 64b stopped and the left and right sun gears 271 fixed stationary, the left ring gear 273 rotates forward (reverse) and the right ring gear 273 rotates reverse (forward) due to the rotational power from the slewing motor shaft 261. As a result, one of the drive sprockets 51 of the left and right tracks 2 rotates forward and the other rotates backward, causing the running body 1 to change direction on the spot (spin turn).

In addition, the left and right sun gears 271 are driven by the linear motor 64b, while the swing motor 70
By driving the left and right ring gears 273 by b, a difference in speed occurs between the left and right crawlers 2, and the traveling body 1 turns left or right (makes a U-turn) with a turning radius larger than the pivot turning radius while moving forward or backward. The turning radius at this time is determined according to the speed difference between the left and right crawlers 2.
The vehicle turns left or right while the driving force of the engine 7 is constantly transmitted to the left and right crawlers 2 .

Next, a working hydraulic circuit 180 and a traveling hydraulic circuit 200 in the normal type combine harvester of this embodiment will be described with reference to Figures 8 to 15. As shown in Figures 8 to 12, the working hydraulic circuit 180 includes, as hydraulic actuators, a reaping lifting hydraulic cylinder 4, left and right reel lifting hydraulic cylinders 27L, 27R that support the raking reel 14 so that it can be raised and lowered, an auger lifting hydraulic cylinder 55 that supports the grain discharge auger 164 so that it can be raised and lowered, and a traveling machine body 1
a hydraulic oil tank 57 for storing hydraulic oil; a working section charge pump 59 connected to the hydraulic oil tank 57 via a strainer 58; hydraulic valves 60A to 60E for switching the flow of hydraulic oil; and hydraulic valves 50A to
The hydraulic valves 60A to 60E are provided with an oil cooler 62 provided in the return pipe from the hydraulic valve unit 60A to the hydraulic oil tank 57.
It is built into 0.

A working unit charge pump 59 is hydraulically connected to the hydraulic cylinder 4 for lifting and lowering the reaper via a hydraulic valve 60A for lifting and lowering the reaper. A reaping position lever (not shown) in the driving operation unit (driver's seat) 5
The operator is configured to raise and lower the cutting unit 3 to a desired height (e.g., cutting work height or non-work height) by tilting the cutting position lever (not shown) forward and backward, thereby operating the cutting lifting hydraulic cylinder 4, and the operator is configured to raise and lower the cutting unit 3 to a desired height (e.g., cutting work height or non-work height, etc.). Meanwhile, a working unit charge pump 59 is hydraulically connected to the reel lifting hydraulic cylinders 27L, 27R via a reel lifting hydraulic valve 60B. The reel lifting hydraulic cylinders 27L, 27R are operated by tilting the cutting position lever (not shown) forward and backward, etc.
By operating the reel 27L, 27R, the operator can raise and lower the raking reel 14 to the desired height to harvest the uncut stalks in the field.

A working section charge pump 59 is hydraulically connected to the auger lifting hydraulic cylinder 55 via the auger lifting hydraulic valve 60C.
The operator operates the hydraulic cylinder 55 for lifting and lowering the auger by tilting the auger 164 forward and backward, and raises and lowers the rice-throwing opening of the grain discharge auger 164 on the grain discharge conveyor 8 to a desired height.
The grain discharge auger 164 is rotated horizontally together with the grain tank 6 to move the rice throwing opening laterally. That is, the rice throwing opening is positioned above the truck bed or container, and the grains in the grain tank 6 are discharged into the truck bed or container.

The hydraulic oil tank 57 and the working unit charge pump 59 are hydraulically connected to the left machine body lifting hydraulic cylinder 56L via the left machine body lifting hydraulic valve 60D. Meanwhile, the hydraulic oil tank 57 and the working unit charge pump 59 are hydraulically connected to the right machine body lifting hydraulic cylinder 56R via the right machine body lifting hydraulic valve 60E. The left and right machine body lifting hydraulic cylinders 56L, 56R are operated independently of each other to lift and lower the left and right running machine body 1 independently.

Therefore, when the left and right vehicle body lifting hydraulic cylinders 56L, 56R are simultaneously operated to simultaneously lower the left and right track frames 50, 50 relative to the traveling vehicle body 1, the traveling vehicle body 1 moves away (rises) from the ground contact portions of the left and right tracks 2, 2, and the relative height (vehicle height) of the traveling vehicle body 1 to the ground contact portions of the tracks 2, 2 becomes higher. Conversely, when the left and right track frames 50, 50 are simultaneously raised relative to the traveling vehicle body 1, the traveling vehicle body 1 moves closer (descends) to the ground contact portions of the left and right tracks 2, 2, and the relative height (vehicle height) of the traveling vehicle body 1 to the ground contact portions of the tracks 2, 2 becomes lower.

Then, the left vehicle body lifting hydraulic cylinder 56L is operated to lower the left track frame 50 relative to the traveling vehicle body 1, or the right vehicle body lifting hydraulic cylinder 56R is operated to raise the right track frame 50 relative to the traveling vehicle body 1 (or both of these operations can be performed simultaneously).
Conversely, when the right body lifting hydraulic cylinder 56R is operated to lower the right track frame 50 relative to the traveling body 1, or when the left body lifting hydraulic cylinder 56L is operated to raise the right track frame 50 relative to the traveling body 1 (or when both of these operations are performed simultaneously), the traveling body 1 is tilted downward to the left.

The hydraulic oil tank 57, the working section charge pump 59, and the hydraulic valve unit 60 are mounted on the traveling machine body 1, and are connected to each other via hydraulic piping 181 to 183. On the traveling machine body 1, the hydraulic oil tank 57 is installed on the front left side, while the working section charge pump 59 is fixed to the front of the engine 7 mounted on the front right side, and the strainer 58 built in the hydraulic oil tank 57 and the working section charge pump 59 are connected by hydraulic piping 181. In addition, 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 working section charge pump 59 is connected to the hydraulic valve unit 60 via hydraulic piping 182. Furthermore, the hydraulic valve unit 60 is connected to the hydraulic oil tank 57 via hydraulic piping 183, which serves as a hydraulic oil return pipe, and an oil cooler 62.

The hydraulic oil tank 57 is installed on the traveling body 1 in a space 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 on the left and right in front of the traveling body 1. In other words, the hydraulic oil tank 57 is arranged in the space surrounded by the feeder house 11 and the machine housing of the threshing section 9, and dust from the reaping section 3 is trapped in the hydraulic oil tank 57.
This can prevent contamination of the hydraulic oil due to dust entering through the fuel filler port 184, etc. In addition, since the cooling air from the engine 7 flows into the installation space of the hydraulic oil tank 57, an increase in the hydraulic oil temperature can be suppressed without providing an oil cooler on the working hydraulic circuit 180, and each hydraulic member can be driven appropriately.

The hydraulic oil tank 57 has a fuel filler port 184 protruding toward the left side (outside the aircraft) on the left side (
The strainer 58 is mounted on the outer side of the engine and can be inserted and removed from the left side.
Therefore, by removing the threshing cover 185 provided on the left side (outside the machine) of the threshing section 9, the oil supply port 184 and the strainer 58 can be easily accessed.
This facilitates the oil supply operation of the oil supply unit 7 and the oil filter replacement operation of the strainer 58, and also improves the ease of maintenance of the work system hydraulic circuit 180.

Hydraulic pipes 181, 183 connected to the hydraulic tank 57 are extended to the left and right in front of the hydraulic tank 57 and the engine 7, and hydraulic pipe 182 connects the working section charge pump 59 disposed in front of the engine 7 to the strainer 58.
Hydraulic pipes 181, 183 are extended along the output shaft 65 of the engine 7, bypassing the front of the engine 7 toward the hydraulic oil tank 57. Hydraulic pipes 182, 183 are extended rearward, passing below a 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 in positions that are unlikely to be affected by radiant heat from the engine 7, with short pipe lengths, and the temperature of the hydraulic oil flowing through the hydraulic pipes can be prevented from becoming too high.

As shown in FIGS. 7, 10, and 12 to 15, the traveling hydraulic circuit 200 includes a linear pump 6
The straight-line pump 64a and the straight-line motor 64b in the straight-line hydraulic continuously variable transmission 64 are connected in a closed loop by a straight-line closed oil passage 201. On the other hand, the swing pump 70 in the swing hydraulic continuously variable transmission 70
The straight pump 64a and the swing motor 70b are connected in a closed loop by a swing closed oil passage 202. The straight pump 64a and the swing pump 70a are driven by the rotational power of the engine 7, and the straight pump 64
By controlling the swash plate angles of the linear motor 64b and the swing motor 70a, the discharge direction and discharge amount of the hydraulic oil to the linear motor 64b and the swing motor 70b are changed.
b operates in forward and reverse directions.

The traveling system hydraulic circuit 200 includes a linear valve 203 that is switched in response to manual operation of the main shift lever 44, and a linear cylinder 204 that is connected to the transmission charge pump 151 via the linear valve 203. When the linear valve 203 is switched, the linear cylinder 204 operates to change the swash plate angle of the linear pump 64a, thereby executing a linear speed change operation in which the rotation speed of the linear motor shaft 260 of the linear motor 64b is changed steplessly or reversed. The traveling system hydraulic circuit 200 also includes a hydraulic servo mechanism 205 for linear speed change.
A hydraulic servo mechanism 205 executes a feedback operation in which the linear valve 203 returns to neutral by controlling the swash plate angle of the linear pump 64a, and changes the swash plate angle of the linear pump 64a in proportion to the amount of manual operation of the main shift lever 44, thereby changing the rotation speed of the linear motor shaft 260 of the linear motor 60b.

The traveling hydraulic circuit 200 is equipped with a swing valve 206 which is switched in response to manual operation of the control handle 43, and a swing cylinder 207 which is connected to the transmission charge pump 151 via the swing valve 206. When the swing valve 206 is switched, the swing cylinder 207 operates to change the swash plate angle of the swing pump 70a, and a left/right swing operation is performed in which the rotation speed of the swing motor shaft 261 of the swing motor 70b is changed steplessly or reversed, and the traveling machine body 1 changes the traveling direction left/right to change direction or correct the course in the headland of the farm field. The traveling hydraulic circuit 200 also includes a hydraulic servo mechanism 208 for swing speed change. The hydraulic servo mechanism 208 performs a feedback operation in which the swing valve 206 returns to neutral by controlling the swash plate angle of the swing pump 70a, changing the swash plate angle of the swing pump 70a in proportion to the amount of manual operation of the control handle 43, and changing the rotation speed of the swing motor shaft 261 of the swing motor 70b.

As shown in FIG. 13, all of the oil passages 201a, 201b, 201c of the closed oil passages 201 and 202 are
A charge branch oil passage 219 (details will be described later) is connected to the straight first oil passage 201a. A check valve 211 for the straight first oil passage 201a is provided between the charge branch oil passage 219 and the straight second oil passage 201b. 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. Thus, the straight closed oil passage 201 has two check valves 211. Furthermore, a check valve 212 for the swing first oil passage 202a is provided between the charge branch oil passage 219 and the swing first oil passage 202a. A check valve 212 for the swing second oil passage 202b is provided between the charge branch oil passage 219 and the swing second oil passage 202b. Thus, the swing closed oil passage 202 also has two check valves 211.
It is equipped with 12.

The straight first oil passage 201a and the straight second oil passage 201b are connected to a straight bypass oil passage 213. A straight side bidirectional relief valve 215 is provided in the straight bypass oil passage 213. The swing first oil passage 202a and the swing second oil passage 202b are connected to a swing bypass oil passage 214. A swing side bidirectional relief valve 216 is provided in the swing bypass oil passage 214. Thus, each of the closed oil passages 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 2 in the transmission case 63.
17 via hydraulic piping 221. A charge introduction oil passage 218 is connected to the discharge side of the transmission charge pump 151 via hydraulic piping 222, and an oil filter 152 is installed midway through the hydraulic piping 222. A charge branch oil passage 219 connected to both closed oil passages 201, 202 is connected to the downstream side of the charge introduction oil passage 218. Therefore, while the engine 7 is running, hydraulic oil from the transmission charge pump 151 is constantly replenished to both closed oil passages 201, 202.

Furthermore, the charge branch oil passage 219 is connected to the linear cylinder 204 via the linear valve 203, and is also connected to the swing cylinder 207 via the swing valve 206. Furthermore, the charge branch oil passage 219 is connected to the transmission case 63 via an excess relief valve 220 and a hydraulic pipe 223, and the oil cooler 153 is installed midway through the hydraulic pipe 223. Therefore, when the excess hydraulic oil from the transmission charge pump 151 is returned to the transmission case 63 via the excess relief valve 220, it is cooled by the oil cooler 153.

The hydraulic pipes 223 are connected to a bypass pipe 224 that bypasses the feed pipe 223a and the return pipes 223b to 223d. The bypass pipe 224 is connected to the transmission case 6.
The hydraulic piping 223 and the bypass pipe 224 are fixed above the continuously variable transmission case 323 on the side of the hydraulic piping 223.
By disposing the oil cooler 24 above the continuously variable transmission case 323, when the hydraulic oil temperature is low, such as when the engine 7 is started, the hydraulic oil can be circulated without being sent to the oil cooler 153. Therefore, even when the hydraulic oil temperature is low and the viscosity of the hydraulic oil is high, the hydraulic oil can be smoothly circulated within the traveling system hydraulic circuit 200, and the various transmission mechanisms within the transmission case 63 and the continuously variable transmission case 323 are lubricated.

As described above, the oil cooler 153 is connected to the hydraulic pipes 221 to 223 that circulate the hydraulic oil in the transmission case 63 and the continuously variable transmission case 323 (drive device), and the bypass pipe (bypass path) 224 that bypasses the oil cooler 153 is provided in the hydraulic pipe 223. The bypass pipe 224 is connected to the transmission case 63 and the continuously variable transmission case 32
3. Therefore, although the piping path for circulating oil through the transmission case 63 and the continuously variable transmission case 323 becomes longer by connecting the transmission case 63 and the continuously variable transmission case 323 to the oil cooler 153, the bypass pipe 224 can shorten the length.

By providing a bypass pipe 224 in the hydraulic piping 223 to bypass the oil cooler 153, it is possible to circulate highly viscous hydraulic oil, for example when starting the engine in cold regions, and to maintain good lubrication within the transmission case 63 and the continuously variable transmission case 323.
In addition, by integrating the transmission case 63 and the continuously variable transmission case 323 into one body, the bypass pipe 224 can be incorporated into the transmission case 63, improving assembly and facilitating maintenance of the hydraulic device in the transmission case 63.

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

Of the hydraulic piping 223, the return piping 223b to 223d of the oil cooler 153 is configured by providing a metal relay pipe 223c between the upstream return piping 223b, one end of which is connected to the oil cooler 153, and the downstream return piping 223d, one end of which is connected to the top surface of the transmission case 63. The metal relay pipe 223c is fixed to the top surface of the continuously variable transmission case 323 on the swing hydraulic continuously variable transmission 70 side (rear side).

A connecting plate (fixing member) 227 fixed to the side surface of the metal relay pipe 223c is fastened and fixed to the upper surface of the accommodation portion (rear end side of the continuously variable transmission case 323) of the swing valve 206 in the continuously variable transmission case 323. As a result, the metal relay pipe 223c is fixed and disposed above the continuously variable transmission case 323 so as to be parallel to the pump shaft 259.
has a T-shape with a communication port (branch pipe) 223e protruding forward (toward the linear hydraulic continuously variable transmission 64) from its midsection. That is, the communication port 223e of the midsection of the metal relay pipe 223c is provided at the same height as the communication port 225a of the connecting member 225 and protrudes toward the communication port 225a of the connecting member 225.

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

The bypass passage that bypasses the oil cooler 153 is composed of a metal relay pipe 223c that is integrally assembled with the continuously variable transmission case 323, a bypass pipe 224, and a connecting member 225.
Hydraulic components other than 23b can be assembled integrally with the continuously variable transmission case 323, and the ease of assembly and maintainability of the transmission case 63 to which the continuously variable transmission case 323 is assembled can be improved.

The hydraulic pipes 222, 223 connecting the transmission case 63 and the continuously variable transmission case 323 are connected to a straight-line connecting link body 345 and a turning connecting link body 346 which are connected to the steering case 318.
46. This not only prevents the linear connection link body 345 and the revolving connection link body 346 from coming into contact with the hydraulic pipes 222, 223, but also facilitates maintenance of the linear connection link body 345 and the revolving connection link body 346. Furthermore, even if the hydraulic pipes 222, 223 vibrate due to the influence of the driving of the transmission case 63 or the like, damage due to contact with the linear connection link body 345 and the revolving connection link body 346 can be prevented.

More specifically, a hydraulic pipe 2 that connects a charge pump 151 and an oil filter 152
The hydraulic pipe 222 connecting the oil filter 152 and the transmission case 63 is arranged in the front-rear direction so as to pass below the first relay rod 366 of the turning direct-connection link body 346. The downstream return pipe 223b connected to the transmission case 63 is bent so as to pass below the shaft support 366 of the turning direct-connection link body 346, and is connected to a metal relay pipe 223c fixed to the continuously variable transmission case 323.

Next, the engine room 146 in which the engine 7 is installed will be described with reference to Fig. 8 and other figures. As shown in Fig. 8 and other figures, a pair of left and right engine room supports 147 are erected on the rear side of the driver's seat 5 on the upper surface of the traveling body 1, and a back plate 14 is disposed between the left and right engine room supports 147.
A dust net is stretched over the right side of the wind tunnel case 170, covering the rear of the engine room 146 below the driver's seat 42. A box-shaped wind tunnel case 170 is erected via an opening/closing fulcrum shaft 171 on a right engine room support pillar 147 provided at the right end of the driver's seat 5 of the traveling vehicle body 1. A dust net is stretched over the outer opening on the right side of the wind tunnel case 170, preventing the intrusion of straw and other debris into the wind tunnel case 170 and, ultimately, the engine room 146.
In the hydraulic circuit 180, the oil cooler 153 in the traveling system hydraulic circuit 200 and the oil cooler 62 in the working system hydraulic circuit 180 are disposed above and below each other.

A water-cooling radiator 154 is erected on the inside of the air tunnel case 170 on the upper surface side of the traveling vehicle body 1, and the radiator 154 faces the cooling fan 149 of the engine 7. A shroud 150 is installed in a manner that covers the entire ventilation range of the radiator 154, and the cooling fan 149 is disposed in an opening formed in this shroud 150. An oil cooler 153 is also installed inside the air tunnel case 170. By rotating the cooling fan 149, outside air (cooling air) is taken into the air tunnel case 170 from an opening on the outside of the air tunnel case 170 on the right side, and dust-free cooling air is discharged from an opening on the inside of the air tunnel case 170 on the left side to the engine room 146.
As a result, the cooling air flowing into the engine compartment 146 cools the oil cooler 153, the radiator 154, the engine 7, etc.

Next, the driving operation structure of the control handle 43 and the like will be described with reference to Figures 8, 10, 16 to 21. As shown in Figures 8, 10, 16 to 21, the vehicle is equipped with a step frame 311 that constitutes a flat footrest section for the operator to place on the driver's seat 5. A plurality of support frames 312 are erected on the upper surface of the running vehicle body 1, and a step frame 312 is provided on the upper end of the support frame 312.
11 is erected. The step frame 311 and the support frame 312 constitute a support frame. A boarding/disembarking step 313 is fixed to the side of the support frame 312 on the right 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 top surface of the traveling body 1.

In addition, a steering case 318 is provided having a turning input shaft 316 and a main speed change input shaft 317. Both ends of a case support horizontal frame 319 are connected between the left and right support leg frames 312 on the underside of the front part of the step frame 311, and the steering case 318 is detachably fastened to the approximately horizontal case support horizontal frame 319. The turning input shaft 316 protrudes upward from the top surface of the steering case 318 and is connected to the operation handle 43 via a steering shaft 321, and the main speed change input shaft 317 protrudes leftward from the left side surface of the steering case 318 and is connected to the main speed change lever 44 via a main speed change operating rod 322.

As can be seen from the above description, the driver's seat 5 (operating section) on the step frame 311 provided on the upper end side of the support frame group 312 is provided with the main speed change lever 4, which is a straight-line operation tool for straight-line operation.
The step frame 311 is provided with a steering wheel 43 which is a turning operation tool and a steering handle 43 which is a turning operation tool. A case support horizontal frame 319 is attached between the left and right support frames 312 located under the front of the step frame 311. A steering case 318 which interlocks and connects the main speed change lever 44 and the steering handle 43 with the drive unit (stepless speed change case 323 and transmission case 63) is attached to the case support horizontal frame 319. There are two case support horizontal frames 319, one at the front and one at the back of the steering case 318. The steering case 318 is supported by the two case support horizontal frames 319, one at the front and one at the back.

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 part of the traveling body 1. The oil filter 152 is fixed to the step frame 311 so as to be disposed in front of the continuously variable transmission case 323.
The oil filter 152 is fixed to a portion protruding leftward from the front left support frame 312. That is, the oil filter 152 is fixed to the left side of the front end of the step frame 311 via a filter fixing bracket 349, and is thereby disposed in front of the continuously variable transmission case 323 fixed to the right side of the transmission case 63. Therefore, when the hydraulic pipe 222, in which the oil filter 152 is provided midway, is connected between the transmission charge pump 151 and the charge introduction oil passage 218, the hydraulic pipe 222 can be configured to be short.

A case support horizontal frame 319 is installed between the left and right support frames 312 on the lower front side of the step frame 311. The case support horizontal frame 319 is provided with the main speed change lever 44, the steering handle 43, and the drive mechanism (the continuously variable speed change case 323 and the transmission case 63).
) is attached, the presence of the case support horizontal frame 319 improves the rigidity of the front part of the traveling body 1 (particularly near the driver's cab 5). The case support horizontal frame 319, which serves to reinforce the front part of the traveling body 1, can support the steering case 318 with high rigidity. Therefore, there is no significant difference between the amount of operation of the main speed change lever 44 and the operating handle 43 and the output of the drive unit (the continuously variable transmission case 323 and the transmission case 63), eliminating the risk of the operator being in a driving state that he or she does not expect. The reinforcing case support horizontal frame 319 can also be used as the mounting part for the steering case 318, and a dedicated mounting stand for the steering case 318 is not required, which contributes to cost reduction.

A continuously variable transmission case 3 in which the linear hydraulic continuously variable transmission 64 and the turning hydraulic continuously variable transmission 70 are assembled.
23. A continuously variable transmission case 323 is fixed to the upper right side of the transmission case 63, and each of the straight-line and turning operation arm bodies 355, 369 is disposed on the front and rear sides of the continuously variable transmission case 323. That is, the straight-line hydraulic continuously variable transmission 64 and the turning hydraulic continuously variable transmission 70 are disposed side by side in the front and rear on the right side of the transmission case 63, which is the side opposite the feeder house 11.

Therefore, since space is created on the side (left side) of the feeder house 11 in the transmission case 63, the degree of freedom in designing the reaping unit 3 is increased, and the feeder house 11 can be easily mounted on the reaping unit 3.
The feeder house 11 can be configured to have an optimal size for the reaping amount and the reaping width of the grain header 12. In addition, because the installation width of the feeder house 11 in the left-right direction is increased, the feeder house 11 can be installed on the side closer to the center of gravity position when the grain header 12 is raised and lowered, and the support strength of the feeder house 11 for the reaping unit 3 can be increased.

A linear operation shaft 325 as a linear output control section protrudes forward from the front outer surface of the continuously variable transmission case 323, and a turning operation shaft 326 as a turning output control section protrudes backward from the rear outer surface of the continuously variable transmission case 323. Although detailed illustration is omitted, a linear operation arm body 355 is connected to the linear operation shaft 325, and a turning operation arm body 369 is connected to the turning operation shaft 326. The linear and turning operation arm bodies 355, 369 are respectively connected to a linear connection link body 345 and a turning connection link body 346 provided on the rear side of the steering case 318, and the linear hydraulic continuously variable transmission 64 and the turning hydraulic continuously variable transmission 70 are operated and controlled by the steering operation of the steering handle 43 and the speed change operation of the main speed change lever 44, so that the course and moving speed of the left and right crawlers 2 can be changed.

A cab (operating section) 5 provided at the front of the traveling body 1 is equipped with a main speed change lever (straight-line operation tool) 44 for straight-line operation and a control handle (turning operation tool) 43 for turning operation, and a control column 41 is disposed on the side of the cab near the drive unit (transmission case 63 and continuously variable transmission case 323). Below the cab 5 at the front of the traveling body 1, a steering case 318 that changes the output from the transmission case 63 according to the amount of operation of the control handle 43 and the main speed change lever 44 is disposed to the side of the continuously variable transmission case 323 equipped with the straight-line hydraulic continuously variable transmission 64 and the turning hydraulic continuously variable transmission 70.

In this case, the steering handle 43 is disposed in the front center portion of the driver's seat 42 of the driver's cab 5, and the main shift lever 44 is disposed on the steering column 41 on the left side, which is the side portion closer to the drive unit (the continuously variable transmission case 323 and the transmission case 63).
The continuously variable transmission case 323 is disposed below the steering column 41 on which the steering wheel 43 and the main shift lever 44 are mounted. This allows the various parts of the operation system mechanism that connect the operation handle 43 and the main shift lever 44 to the continuously variable transmission case 323 via the steering case 313 to be disposed close to each other, and each of the link mechanisms 321, 322, 345, 346 that connect the various parts of the operation system mechanism can be made short, thereby suppressing their fluctuation and deformation. This suppresses the discrepancy between the amount of operation of the main shift lever 44 or the operation handle 43 and the output of the drive device (the continuously variable transmission case 323 and the transmission case 63),
A stable driving condition can be maintained according to the operator's operation.

A battery 230 that supplies power to the engine 7 is disposed below the cab 5 in the front part of the traveling vehicle body 1, behind the steering case 318 and to the side of the continuously variable transmission case 32.
A battery 230 that supplies power to the engine 7 and the like is disposed in an area surrounded by the steering case 318 and the transmission case 63 and the engine 7. This allows the dead space under the cab 5 to be effectively utilized 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.
Since the battery 230 can be disposed close to the engine 7 and the cab 5, the electrical system can be made compact. In addition, it is possible to avoid making the combine larger in size in order to secure a space for disposing the battery 230.

A cab (operating section) 5 is configured on a plurality of support 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 erected on the middle part of the plurality of support frames 312, and is disposed above the continuously variable transmission case 323 and the battery 230. In this way, the battery 230 and the steering case 318 are disposed in multiple vertical stages below the front part of the step frame 311, so that electrical wiring for supplying power to electrical members of each part including the engine 7 and the cab 5 can be easily extended by utilizing the space formed in the area adjacent to the continuously variable transmission case 323 at the rear of the steering case 318. This also contributes to improving the ease of assembly and maintenance of the steering case 318 and the battery 230.

In addition, since an oil filter 152 for filtering the hydraulic oil in the drive unit (continuously variable transmission case 323 and transmission case 63) is disposed in the above-mentioned area below the cab 5, the length of the hydraulic piping 222 connecting the drive unit (continuously variable transmission case 323 and transmission case 63) and the oil filter 152 can be shortened, and the handling of the hydraulic piping 222 is simplified.

A horizontal main transmission input shaft 317 is disposed on one of the front and rear sides of the turning input shaft 316 at the top of the steering case 318, and a horizontal linear output shaft 35 is disposed on the other side.
0 is arranged. The main transmission input shaft 317 and the linear output shaft 350 extend parallel to each other in the left-right direction in a plan view, and are rotatably supported by the steering case 318. The main transmission input shaft 317 and the linear output shaft 350 are supported so as to protrude outward (leftward) from the left side surface of the steering case 318. The turning output shaft 164 extending perpendicular to the linear output shaft 350 is supported on the back surface of the steering case 318 and below the linear output shaft 350, so as to protrude outward (rearward) from the steering case 318.

The linear connection link body 345 is connected to one end (right end) of a cylindrical shaft connection body 351.
The shaft connector 3 is connected to the linear output shaft 350 by inserting the protruding end (left end) of the shaft connector 3 into the linear output shaft 350.
A straight-travel intermediate shaft 352 is inserted into the other end (left end) of 51 and supported by a transmission output support bracket 328 fixed to the support leg frame 312 at the left front position of the cab 5. By adjusting the lateral position of the straight-travel intermediate shaft 352 with respect to the shaft connector 351, the installation position of the straight-travel connection link body 435 in the lateral direction is adjusted.

One end (rear end) of a straight-movement relay arm body 353 extending in the front-to-rear direction is fixed to the other end of the straight-movement relay shaft 352, and the other end (front end) of the straight-movement relay arm body 353 swings up and down in response to rotation of the straight-movement relay shaft 352. The other end (front end) of the straight-movement relay arm body 353 is connected to one end (upper end) of a straight-movement connecting rod 354 extending up and down, and the other end (lower end) of the connecting rod 354 is connected to a straight-movement operating arm body 355.

The linear connection link body 345 connects a linear relay shaft 352, which is provided on an extension line of the linear output shaft 350 and extends in the left-right direction, to the support frame 3 by a shaft connector 351.
12. As a result, the linear motion relay shaft 352 rotates together with the linear motion output shaft 350, swinging the front end of the linear motion relay arm body 353 fixed to the left end of the linear motion relay shaft 352. The linear motion connecting rod 354 has both ends pivotally connected to the front end of the linear motion relay arm body 353 and one end of the linear motion operating arm body 355, respectively.
However, by moving up and down in response to the swinging of the straight-movement relay arm body 353, the operation arm body 35
5. Rotate the linear operation shaft 325, the protruding end (front end) of which is fixed to the other end.

On the other hand, the swivel connection link body 346 is connected at one end (base end) to the protruding end (rear end) of the swivel output shaft 361.
The first relay rod 3 is fixed to the other end (tip) of the output arm body 362.
The first relay rod 363 is extended left and right at a rear position of the steering case 318 so as to straddle the upper front part of the continuously variable transmission case 323, and the other end (left end) of the first relay rod 363 is connected to one end (front end) of the first relay shaft 365.
The intermediate shaft 365 is connected to a tubular shaft support 366.
The support is provided by penetrating the

On the other hand, one end (base end) of a rotating operation arm body 369 is fixed to the protruding end (rear end) of the rotating operation shaft 326. One end (right end) of a second relay rod 368 is attached to the other end (tip) of the rotating operation arm body 369.
The second relay rod 368 is connected to the transmission case 63 and the continuously variable transmission case 32.
The other end (left end) of the second relay rod 368 is connected to a second rotating relay arm body 367 fixed to one end (rear end) of the rotating relay shaft 365.

The shaft support 366 which supports the turning intermediate shaft 365 is fixed to the transmission case 63 at a position to the left of the continuously variable transmission case 323 by a support plate 370 having one end fixed to the outer circumferential surface of the shaft support 366 and the other end bolted to the upper surface of the transmission case 63. In addition, a pipe fixing part 372 is provided on the outer circumferential surface of the shaft support 366, and the hydraulic pipe 223 connected to the transmission case 63 is passed through the pipe fixing part 372 to fix the position.

The turning connection link body 346 is connected to the turning output shaft 33 which is protruded from the rear of the steering case 318.
The right end of a first relay rod 363 extending in the left-right direction is pivotally attached to an output arm body 362 whose tip swings left and right in accordance with the rotation of the output arm body 361. Therefore, the first relay rod 363 moves left and right in accordance with the swing of the output arm body 362, swinging the tip of a first revolving relay arm body 364 whose base end is fixed to the front end of a revolving relay shaft 365 left and right. This swinging of the tip of the first revolving relay arm body 364 causes the revolving relay shaft 365 journaled by a shaft support 366 to rotate, and at the same time, the tip of a second revolving relay arm body 364 whose base end is fixed to the rear end of the revolving relay shaft 365 swings left and right. Then, a second relay rod 368 whose both ends are pivotally attached to the front end of the second revolving relay arm body 367 and one end of a revolving operation arm body 369,
The second rotating relay arm body 367 moves left and right in response to the swinging of the second rotating relay arm body 367, whereby the operating arm body 36
9, the rotating operation shaft 326, the protruding end (rear end) of which is fixed to the other end, is rotated.

The main transmission input shaft 317 protrudes from the steering case 318 toward the left-right center of the traveling vehicle body 1. The protruding end (left end) of the main transmission input shaft 317 is connected to the transmission case 63.
The main speed change input shaft 317 is journalled by a main speed change input support bracket 381 fixed to the left edge of the step frame 311 which is the side closest to the main speed change input shaft 317. Furthermore, one end (front end) of a main speed change arm body 382 is connected to the protruding end (left end) of the main speed change input shaft 317, and the other end (rear end) of the main speed change arm body 382 is connected to a main speed change operating rod 322 which is connected to the main speed change lever 44.

A linear hydraulic continuously variable transmission 64 and a turning hydraulic continuously variable transmission 70 that change the speed of the power of the engine 7
are arranged side by side in the front and rear on the left and right sides of the transmission case 63 on the side of the cab (operating section) 5. A straight operation shaft 325 of the straight hydraulic continuously variable transmission 64 and a turning operation shaft 326 of the turning hydraulic continuously variable transmission 70 are allocated to the front and rear and protrude. Since the straight hydraulic continuously variable transmission 64 and the turning hydraulic continuously variable transmission 70 are arranged side by side on the side of the cab 5, the connection structure with the steering case 318 can be made short.

Furthermore, by arranging the linear operation shaft 325 and the turning operation shaft 326 in the front and rear, they can be placed in the same positional relationship as the linear output shaft 350 and the turning output shaft 361 that are arranged in the front and rear of the steering case 318. This makes it possible to simplify 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, and also makes it possible to install the continuously variable transmission case 323 and the steering case 318 in close proximity to each other below the cab 5 in a compact manner.

The steering case 318 is disposed below the driver's seat (operating section) 5 and above the drive unit (the continuously variable transmission case 323 and the transmission case 63).
A linear output shaft 350 and a slewing output shaft 361 protrude from steering case 318. A linear connection link body 345 connecting the linear output shaft 350 and linear operation shaft 325, and a slewing connection link body 346 connecting the slewing output shaft 361 and slewing operation shaft 326 are each installed between steering case 318 and continuously variable transmission case 323 in a plan view. In other words, since the linear connection link body 345 and the slewing connection link body 346 are arranged on the driver's cab 5 side together with the transmission case 63, ease of assembly and maintenance is improved.

A linear connection link body 345 that interlocks and connects the steering case 318 and the linear operation shaft 325, which is the linear output control section, is supported by the support frame 312 that supports the cab 5. The steering case 318 is fixed to a case support horizontal frame (case support frame) 319 installed in the middle of the left and right support frames 312 that support the front position of the cab (operating section) 5. The linear connection link body 345 is supported by the left support frame 312 on the transmission case 63 (continuously variable transmission case 323) side.

A steering case 318 and a drive mechanism (a continuously variable transmission case 323 and a transmission case 6
3) and a linear operation shaft 325 (linear output control section) provided on the linear connection link body 3
45 is supported by the support frame 312 that supports the driver's cab 5.
The linear connecting link body 34
Even if bending or tension acts on the driver's cab 5, the support frame 312 supporting the driver's cab 5 can support the linear connecting link body 345 with high rigidity, thereby suppressing fluctuation or deformation of the linear connecting link body 345. Therefore, there is no significant discrepancy between the amount of operation of the main speed change lever 44 or the control handle 43 and the output of the drive device (the continuously variable transmission case 323 and the transmission case 63), eliminating the risk of the vehicle entering a traveling state that the operator does not anticipate.

The continuously variable transmission case 323, which houses the linear hydraulic continuously variable transmission 64 and the swing hydraulic continuously variable transmission 70, is fixed to the upper position of the right side of the transmission case 63. The swing connection link body 346 is supported on the top surface of the transmission case 63 on the continuously variable transmission case 323 side. By utilizing the space between the feeder house 11 and the cab 5, the swing connection link body 346 can be supported compactly and with high rigidity on the transmission case 63, which has the same vibration system as the continuously variable transmission case 323. Therefore, the bending and tension of the swing connection link body 346 due to mechanical vibration is suppressed, and there is no significant deviation between the operation amount of the main speed change lever 44 or the operation handle 43 and the output of the drive device (the continuously variable transmission case 323 and the transmission case 63), and the risk of the vehicle being in a traveling state that the operator does not expect can be eliminated.

22 to 26, a mounting structure of an ECU 401 that controls the operation of the combine harvester will be described. As will be understood from the above description, in the embodiment, the front part of the traveling body 2,
The step portion 4 is a space surrounded by the leg frames 312 and the step frames 311.
Since 00 is a dead space, this space is utilized to arrange the steering case 318, the continuously variable transmission case 323, and the battery 230.

An ECU 401 that controls the operation of the combine harvester is disposed on the front side of the step portion 400. In this embodiment, a shielding plate 402 is disposed so as to span the front side of the step portion 400, i.e., between 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. In other words, 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 disposed on the front side of the shielding plate 402.
has been concluded.

Therefore, the ECU 401 is located at the front of the space of the step portion 400, and the engine 7 is located at the rear. 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 act as shields against the exhaust heat from the engine 7. With this configuration, the ECU 401 is located as far away as possible from the engine 7 around the cab 5 (operating section), and the thermal effect from the engine 7 on the ECU 401 can be reduced. ECU
This can stabilize the control and extend the life of the ECU 401. In particular, since the shielding plate 402 can block the exhaust heat from the engine, it is highly effective in reducing the thermal influence from the engine 7 to the ECU 401.

The outer shape of the shielding plate 402 is larger than the outer shape of the ECU 401.
The peripheral portion of the shielding plate 402 protrudes from the outer periphery of the ECU 401. The presence of the peripheral portion of the shielding plate 402 makes it difficult for the exhaust heat from the engine 7 to reach the front side of the ECU 401. The shielding plate 402 of the embodiment is cut out at the center of the lower portion, and has a generally downward U-shaped form. The cutout portion 403 is provided for the purpose of removing the weight from the shielding plate 402 and for the purpose of reducing the amount of heat emitted from the engine 7.
This is for the purpose of allowing outside air to blow on the rear side of the CU 401 and dissipating heat from 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 supplying power, which is disposed in the step portion 400, is placed below the steering case 318 and the case support horizontal frame 319. Therefore, the ECU 401 is
0. The battery 230 is placed in a position in the traveling machine body 1 that is not affected by, for example, muddy water in a farm field or rainwater (is not exposed to muddy water, etc.). Since the ECU 401 is placed in a high position for such battery 230, there is also the advantage that the influence of muddy water, etc. on the ECU 401 can be more reliably eliminated. In addition, since the ECU 401 and the battery 230 are placed close to each other, the electrical system can be made more compact.

The configuration of each part in the present invention is not limited to the illustrated embodiment, and various modifications are possible without departing from the spirit of the present invention.

1 Traveling machine body 3 Harvesting section 5 Cab 7 Engine 9 Threshing section 11 Feeder house 311 Step frame (support frame)
312 Support frame (support frame)
318 steering case 319 case support horizontal frame 400 step portion 401 ECU
402 Shielding plate 403 Cutout portion 404 Front cover

Claims (1)

A combine harvester in which a reaping unit is attached to the front of a traveling body equipped with an engine, a threshing unit is mounted on the traveling body behind the reaping unit, a steering unit is disposed on the front side of the threshing unit, and an engine is mounted below and behind the steering unit,
A battery for supplying power is mounted below the steering unit, and an ECU for controlling the operation of the combine is attached to a support frame on the lower front side of the steering unit, and the battery is disposed between the engine and the ECU,
A cooling fan that blows cooling air into the engine compartment is arranged on the side opposite the threshing section as viewed from the engine,
A hydraulic oil tank for storing hydraulic oil is arranged on the side of the engine and between the reaping unit and the threshing unit.
combine.

Images