Combine

Abstract

To efficiently use a dead space around a steering part 5 which is a dead space peculiar to a combine.SOLUTION: A combine of the present invention includes a reaping part 3 mounted on a front part of a traveling machine body 1 including an engine 7 mounted thereon; a threshing part 9 on a rear side of the reaping part 3 of the traveling machine body 1; a steering part 5 arranged on a front side part of the threshing part 9; and the engine 7 on a lower rear side of the steering part 5. A transmission case 63 is arranged between the reaping part 3 in the traveling machine body 1 and the threshing part 9. A battery 230 for power supply is mounted in a side of the transmission case 63 and in front of the engine 7.SELECTED DRAWING: Figure 24

Description

[Technical field]

[0001] The present invention relates to a combine harvester equipped with a cutting unit that cuts uncut stalks in a field and a threshing unit that threshes grains from the cut stalks. [Background technology]

[0002] Conventionally, in combine harvesters, an ECU that controls the operation of the combine harvester is generally disposed around a control unit mounted on the traveling body (see, for example, Patent Documents 1 and 2, etc.). [Prior art documents] [Patent documents]

[0003] [Patent Document 1] Japanese Patent Application Publication No. 10-295152 [Patent Document 2] JP 2014-14333 A Summary of the Invention [Problem to be solved by the invention]

[0004] However, in the case of combine harvesters that have an engine mounted behind the control unit, the ECU may be affected by the exhaust heat from the engine. In recent years, it is desirable for ECUs, which often handle complex controls, to be as free from thermal influence from the surroundings as possible. [Means for solving the problem]

[0005] The technical object of the present invention is to provide a combine harvester which has been improved based on the above-mentioned current situation.

[0006] A combine harvester according to one embodiment has a reaping unit attached to the front of a traveling body equipped with an engine, a threshing unit mounted on the traveling body behind the reaping unit, a steering unit disposed on the front side of the threshing unit, and an engine mounted below and behind the steering unit. A transmission case is disposed between the reaping unit and the threshing unit on the traveling body, and a battery for supplying power is mounted to the side of the transmission case and in front of the engine. Effect of the Invention

[0007] It is possible to provide a combine harvester that has been improved by considering the current situation as described above. [Brief description of the drawings]

[0008] [Figure 1] FIG. 2 is a left side view of the combine harvester according to the present invention. [Diagram 2] FIG. [Diagram 3] FIG. [Figure 4] FIG. 1 is a diagram showing the drive system of a combine harvester. [Diagram 5] This is a perspective view of the combine harvester as seen diagonally from the front. [Figure 6] A partial cross-sectional plan view of the threshing section. [Figure 7] FIG. 4 is a drive system diagram of the transmission case. [Figure 8] FIG. 2 is a plan cross-sectional view showing the configuration of the engine room and its surroundings. [Figure 9] FIG. 2 is a hydraulic circuit diagram showing a configuration of a working hydraulic circuit. [Figure 10] FIG. 2 is a front view showing the arrangement of hydraulic circuit components. [Figure 11] FIG. 2 is an overall perspective view of a combine harvester showing a piping configuration of a work hydraulic circuit. [Figure 12] FIG. 4 is an enlarged perspective view showing a piping configuration of a traveling hydraulic circuit. [Figure 13] FIG. 2 is a hydraulic circuit diagram showing a configuration of a traveling hydraulic circuit. [Figure 14]FIG. 4 is a perspective view showing the piping construction of hydraulic piping on a transmission case. [Figure 15] FIG. 4 is a perspective view showing the relationship between hydraulic piping on a transmission case and a connecting link body. [Figure 16] This is an oblique view of the front part of the traveling body as seen diagonally from the front left. [Figure 17] This is an oblique view of the driver's seat (control section) and its surroundings seen from diagonally rear left. [Figure 18] This is a front view of the area around the driver's seat (control section). [Figure 19] This is a plan view of the area around the driver's seat (control section). [Figure 20] This is an oblique view of the driver's seat (control section) and its surroundings seen from diagonally rear right. [Figure 21] This is an oblique view of the driver's seat (control section) and its surroundings seen from the front. [Figure 22] This is an oblique view of the mounting position of the ECU as seen from diagonally forward left of the traveling body. [Diagram 23] FIG. 2 is a front view of the driver's seat (control section) and its surroundings, showing the mounting position of the ECU. [Figure 24] FIG. 2 is a plan view of the driver's seat (control section) and its surroundings, showing the mounting position of the ECU. [Diagram 25] 2 is a perspective view showing the positional relationship between the ECU and the steering case as viewed from diagonally forward right. FIG. [Figure 26] FIG. 2 is a perspective view of the mounting position of the ECU as seen from diagonally forward right. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0009] Hereinafter, an embodiment of the present invention will be described with reference to the drawings (FIGS. 1 to 26) in which the present invention is applied to a normal type combine harvester. First, the schematic structure of the combine harvester 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.

[0010] As shown in Figures 1 to 3, the normal type combine harvester in the embodiment includes a traveling body 1 supported by a pair of left and right rubber crawler tracks 2 as a traveling part. A reaping part 3 that harvests and collects unharvested stalks of rice (or wheat, soybeans, or corn) or the like is attached to the front of the traveling body 1 so that it can be adjusted up and down by a single-acting lifting hydraulic cylinder 4.

[0011] A threshing section 9 for threshing the harvested stalks supplied from the reaping section 3 is mounted on the left side of the traveling body 1. A grain sorting mechanism 10 for performing rocking sorting and wind sorting is disposed below the threshing section 9. A cab 5 is mounted on the right front side of the traveling body 1 as a control section in which an operator sits. An engine 7 as a power source is disposed in the cab 5 (below the driver's seat 42). A grain tank 6 for removing grains from the threshing section 9 and a grain discharge conveyor 8 for discharging grains in the grain tank 6 toward the truck bed (or a container, etc.) are disposed behind the cab 5 (to the right of the traveling body 1). The grain discharge conveyor 8 is configured to be tilted toward the outside of the machine so that the grains in the grain tank 6 are transported by the grain discharge conveyor 8.

[0012] 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 arranged above the front of the raking auger 13. A clipper-shaped cutting blade 15 is arranged 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 installed 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.

[0013] With the above configuration, the tips of the uncut culms between the left and right grass segments 16 are raked in by the raking reel 14, the bases of the uncut culms are cut by the cutting blade 15, and the raking auger 13 rotates to collect the cut culms 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 culms in the grain header 12 is transported by the supply conveyor 17 and fed into the handling port 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 support the grain header 12, the cutting blade 15, and the raking reel 14 horizontally relative to the field surface by adjusting the left and right inclination of the grain header 12 with the horizontal control hydraulic cylinder.

[0014] 1 and 3, a threshing drum 21 is rotatably mounted within the threshing chamber of the threshing section 9. The threshing drum 21 is axially supported by a threshing drum shaft 20 (see FIG. 4) extending in the front-to-rear direction of the traveling body 1. A receiving net 24 is stretched below the threshing drum 21 to allow grains to drip through. A helical screw blade-like intake blade 25 is provided on the outer peripheral surface of the front part of the threshing drum 21 so as to protrude radially outward.

[0015] With the above-mentioned configuration, the harvested stalks fed into the threshing opening 9a by the beater 18 are transported toward the rear of the traveling body 1 by the rotation of the threshing drum 21, while being mixed and threshed between the threshing drum 21 and the receiving net 24. Threshed grains, such as grains smaller than the mesh size of the receiving net 24, leak through the receiving net 24. Straw chips, etc. that do not leak through the receiving net 24 are discharged into the field from the dust outlet 23 at the rear of the threshing section 9 by the transporting action of the threshing drum 21.

[0016] In addition, a number of dust-transport valves (not shown) for adjusting the transport speed of the degrain in the threshing chamber are rotatably mounted on the upper side of the threshing drum 21. By adjusting the angle of the dust-transport valves, the transport speed (retention time) of the degrain 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 located below the threshing section 9.

[0017] 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 removed.

[0018] 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 as a result of 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. The 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.

[0019] 1 to 3, the driver's 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 handle 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 driver's cab 5.

[0020] 1 and 2, left and right track frames 50 are disposed on the underside of the traveling vehicle body 1. The track frame 50 is provided with a drive sprocket 51 that transmits power from the engine 7 to the crawler belt 2, a tension roller 52 that maintains the tension of the crawler belt 2, a plurality of track rollers 53 that keep the grounded side of the crawler belt 2 in a grounded state, and an intermediate roller 54 that holds the non-grounded side of the crawler belt 2. The drive sprocket 51 supports the front side of the crawler belt 2, the tension roller 52 supports the rear side of the crawler belt 2, the track roller 53 supports the grounded side of the crawler belt 2, and the intermediate roller 54 supports the non-grounded side of the crawler belt 2.

[0021] Next, the drive structure of the combine will be described with reference to Figs. 4 to 8. As shown in Figs. 4 and 7, a hydraulic linear pump 64a and a hydraulic linear motor 64b are provided in a transmission case 63. An engine 7 is mounted on the upper right side of the front part of the traveling body 1, and the 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 provided in the engine 7, and the working section charge pump 59 and the cooling fan 149 are driven by the engine 7.

[0022] In addition, a hydraulic swing hydraulic continuously variable transmission 70 for steering having a hydraulic swing pump 70a and a hydraulic swing motor 70b is provided in the transmission case 63, and 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, while the output of the linear hydraulic continuously variable transmission 64 and the swing hydraulic continuously variable transmission 70 are controlled by the steering handle 43, the main shift lever 44, and the sub shift lever 45, and the left and right crawlers 2 are driven via the linear hydraulic continuously variable transmission 64 and the swing hydraulic continuously variable transmission 70, so that the vehicle travels in a field or the like. 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.

[0023] Furthermore, as shown in Figs. 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.

[0024] Provided in front of the threshing drum 21 are a threshing drum input shaft 72 extending left and right of the traveling body 1, a beater 18 arranged left and right of the traveling body 1, and a reaping input shaft 89 extending left and right of 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.

[0025] A beater drive mechanism and a reaping drive mechanism that transmit the drive 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, and a power relay belt 113 is wound around power relay pulleys 105, 106 provided on the main counter shaft 76 and the sub counter shaft 104, forming a power relay mechanism that transmits power to the reaping drive mechanism.

[0026] A mowing drive belt 114 is wound around mowing drive pulleys 107, 108 provided on the sub counter shaft 104 and the beater shaft 82, respectively, to form a beater drive mechanism. The mowing drive belt 114 is tensioned by a mowing clutch 109 that 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 to transmit the mowing drive force from the engine 7 to the mowing input shaft 89 from the beater shaft 82, on which the beater 18 is journalled, 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.

[0027] The winnowing shaft 100, which is the rotating shaft of the fan-shaped winnowing machine 29, has a hollow tubular shape, and the main counter shaft 76 is inserted into the hollow part 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. In addition, 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 winnowing machine 29 is driven to rotate at a constant speed by the constant rotational output of the engine 7.

[0028] Furthermore, the machine housing of the threshing section 9 has a reaping support frame 36 installed on the upper surface side of the front part of the threshing machine housing support 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 described later is attached to the front left side of the reaping support frame 36. The reaping input shaft 89 is axially supported on the front side of the reaping support frame 36 so as to be rotatable in the left-right direction of the traveling machine body 1 via the reaping bearing body 37 and the forward / reverse rotation changeover case 121, and the beater shaft 82 (beater 18) oriented left-right is axially supported inside the reaping support frame 36 so as to be rotatable via a beater bearing body 38. A threshing drum drive case 71 is attached to the upper surface side of the reaping support frame 36, and a threshing drum input shaft 72 is axially supported on the threshing drum drive case 71.

[0029] On the other hand, there is provided a reaping input shaft 89 facing left and right which drives the supply conveyor 17 in the feeder house 11. The reaping driving force transmitted from the engine 7 to one end of the main counter shaft 76 on the engine 7 side is transmitted from the other end of the main counter shaft 76 on the opposite side to the engine 7 to a forward / reverse transmission shaft 122 of a reaping forward / reverse rotation switching case 121. The reaping input shaft 89 is driven via a forward rotation bevel gear 124 or a reverse rotation bevel gear 125 of the reaping forward / reverse rotation switching case 121.

[0030] In addition, 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. In addition, the threshing drum input shaft 72 provided on the front side of the threshing section 9 is arranged to face left and right of the traveling body 1, while the threshing drum 21 is journaled on the threshing drum shaft 20 arranged in the front-rear direction of the traveling body 1. The front end side of the threshing drum shaft 20 is connected to the other left and right ends of the threshing drum input shaft 72 on the opposite side to the engine 7 via a bevel gear mechanism 75. The driving force of the engine 7 is transmitted from the other left and right ends of the main counter shaft 76 on the opposite side to the engine 7 to the grain sorting mechanism 10 that sorts the grains after threshing or to the reaping section 3.

[0031] That is, the right end of the threshing drum input shaft 72 is connected to the right end of the main counter shaft 76 closest to the engine 7 via threshing drum drive pulleys 86, 87 and a threshing drum drive belt 88. The front end of the threshing drum shaft 20 is connected to the left end of the threshing drum input shaft 72, which extends in the left-right direction, via a bevel gear mechanism 75. 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 the grain sorting mechanism 10 disposed below the threshing unit 9.

[0032] 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 plate 26 via an oscillating sorting belt 112. That is, the threshing clutch 84 is controlled to be turned on and off by the operator's operation of the threshing clutch lever 47. The threshing clutch 84 is configured to be turned on to drive each part of the grain sorting mechanism 10 and the threshing drum 21.

[0033] 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).

[0034] The feed conveyor 17 is supported at its feed end by a reaping input shaft 89, which serves as a conveyor input shaft. 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 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 transmission shaft 122 via a forward / reverse switching case 121. The right end of the reaping input shaft 89 is connected to the left end of the header drive shaft 91, which extends in the left-right direction, via a header drive chain 118 and sprockets 119, 120. A raking shaft 93 is provided to support the raking auger 13. The middle part of the header drive shaft 91 is connected to the right part of the raking shaft 93 via a raking drive chain 92.

[0035] The header drive shaft 91 also includes a reel shaft 94 that supports the raking reel 14. The right end of the reel shaft 94 is connected to the right end of the raking 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 cutting blade 15 via a cutting blade drive crank mechanism 98. By turning the cutting 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 so that the tips of uncut stalks in the field are continuously cut.

[0036] A forward rotation bevel gear 124 formed integrally with the forward / reverse transmission shaft 122, a reverse rotation bevel gear 125 rotatably supported on the reaping input shaft 89, and an intermediate bevel gear 126 connecting the forward rotation bevel gear 124 to the reverse rotation bevel gear 125 are provided inside the forward / reverse rotation switching case 121. The intermediate bevel gear 126 is always meshed with the forward rotation bevel gear 124 and the reverse rotation bevel gear 125. Meanwhile, a slider 127 is slidably supported on the reaping input shaft 89 by spline engagement. The slider 127 is configured to be releasably engaged with the forward rotation bevel gear 124 via a forward clutch 128 in the form of a claw clutch, and the slider 127 is configured to be releasably engaged with the reverse bevel gear 125 via a reverse clutch 129 in the form of a claw clutch.

[0037] The forward / reverse switching shaft 123 is provided with a forward / reverse switching arm 130, and a forward / reverse switching lever (forward / reverse operating device) is operated to swing the forward / reverse switching arm 130, thereby rotating the forward / reverse switching shaft 123 and moving the slider 127 toward 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 the forward clutch 128 or the reverse clutch 129, and the cutting input shaft 89 is connected in forward or reverse direction to the forward / reverse transmission shaft 122.

[0038] The structure is provided with a forward / reverse switching case 121 as a forward / reverse switching mechanism for driving the supply conveyor 17 in 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 can be reversed by operating the forward / reverse switching case 121 to perform a reverse switching operation, and any straw stuck in the feeder house 11 can be quickly removed.

[0039] The right end of the auger drive shaft 158 ​​is connected to the output shaft 65 of the engine 7 via a tension pulley-like auger clutch 156 and an auger drive belt 157. The left end of the auger drive shaft 158 ​​is connected to the front end of a horizontal feed auger 160 at the bottom of the grain tank 6 via a bevel gear mechanism 159. The rear end of the horizontal feed auger 160 is connected to the vertical feed auger 162 of the grain discharge conveyor 8 via a bevel gear mechanism 161, and the upper end of the vertical feed auger 162 is connected to the grain discharge auger 164 of the grain discharge conveyor 8 via a bevel gear mechanism 163. In addition, 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.

[0040] 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.

[0041] 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, the power transmitted to the pump shaft 258 sends hydraulic oil from the linear pump 64a to the linear motor 64b as needed. Similarly, in the swing hydraulic continuously variable transmission 70, the power transmitted to the pump shaft 259 sends hydraulic oil from the swing pump 70a to the swing motor 70b as needed.

[0042] 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 journaled 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 journaled rotatably 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.

[0043] A linear input gear 263 that meshes with a power distribution gear 262 fixed to the mission input shaft 66 is fitted to the protruding end (left end) of the pump shaft 258 that protrudes from the continuously variable transmission case 323 toward the inside of the transmission case 63 so as to be non-rotatable relative to the pump shaft 258. Similarly, a rotary input gear 264 that meshes with the power distribution gear 262 fixed to the mission input shaft 66 is fitted to the protruding end (left end) of the pump shaft 259 that protrudes from the continuously variable transmission case 323 toward the inside of the transmission case 63 so as to be non-rotatable relative to the pump shaft 258.

[0044] When the driving force output from the output shaft 65 of the engine 7 is transmitted to the mission input pulley 69, the mission input shaft 66 and the power distribution gear 262 rotate together with the mission 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 swing pump 70a via the swing input gear 264. That is, by meshing the linear input gears 263 and the swing input gears 264 of the pump shafts 258, 259 with the power distribution gear 262 of the mission input shaft 66 disposed between the pump shafts 258, 259, the driving force from the engine 7 can be efficiently transmitted to the linear hydraulic continuously variable transmission 64 and the swing hydraulic continuously variable transmission 70, respectively.

[0045] A transmission charge pump 151 for supplying hydraulic oil to each of the hydraulic pumps 64a, 70a and each of the hydraulic motors 64b, 70b is attached to the pump shaft 259. The linear hydraulic continuously variable transmission 64 is configured to arbitrarily adjust the rotation direction and rotation speed of the linear motor shaft 260 protruding from the linear motor 64b by changing and adjusting the inclination angle of the rotating swash plate in the linear pump 64a in accordance with the amount of operation 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 linear motor 64b.

[0046] The rotational power of the straight-travel motor shaft 260 is transmitted from the straight-travel transmission gear mechanism 250 to the auxiliary transmission gear mechanism 251. 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 that are switched by auxiliary transmission shifters 252, 253. By operating the auxiliary transmission lever 45 arranged on the steering column 41, the output rotation speed of the straight-travel motor shaft 260 is selectively switched to one of three speed stages: low speed, medium speed, or high speed. Note that there is a neutral position (a position where the output of the auxiliary transmission becomes zero) between the low speed, medium speed, and high speed of the auxiliary transmission.

[0047] 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. Rotational power from the sub-transmission gear mechanism 251 is transmitted to left and right differential mechanisms 257 from a sub-transmission output gear 267 fixed to the parking brake shaft 265. The left and right differential mechanisms 257 each include a planetary gear mechanism 268. In addition, a straight-line pulse generating rotating wheel 292 is provided on the parking brake shaft 265, and a straight-line vehicle speed sensor (not shown) is configured to detect the rotation speed of the straight-line output (straight-line vehicle speed = shift output of the sub-transmission output gear 267).

[0048] Each of the left and right planetary gear mechanisms 268 includes one 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 carrier 274 that rotatably arranges the plurality of planetary gears 272 on the same circumference. The carriers 274 of the left and right planetary gear mechanisms 268 are arranged facing each other on the same axis with an appropriate gap between them. A center gear 276 is fixed to a sun gear shaft 275 on which the left and right sun gears 271 are provided.

[0049] Each of the left and right ring gears 273 is disposed concentrically on a sun gear shaft 275 with the inner teeth on its inner peripheral surface meshing with the planetary gears 272. The outer teeth on the outer peripheral surface of each of the left and right ring gears 273 are connected to a steering output shaft 285 via intermediate gears 287, 288 for left and right turning output, which will be described later. Each of the ring gears 273 is rotatably supported by left and right forced differential output shafts 277 that protrude outward 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 sub-transmission gear mechanism 251 to the left and right planetary gear mechanisms 268 is transmitted from the left and right axles 278 to each drive sprocket 51 at the same rotational speed and in the same direction, driving the left and right tracks 2 at the same rotational speed and in the same direction, thereby moving the running body 1 in a straight line (forward and backward).

[0050] 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.

[0051] Also provided within the transmission case 63 are 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, a steering output shaft 285 connected to the steering counter shaft 280 via a reduction gear 286, a left input gear mechanism 282 connecting the steering output shaft 285 to the left ring gear 273 via a reverse gear 284, and a right input gear mechanism 283 connecting the steering output shaft 285 to the right ring gear 273. The rotational power of the swing motor shaft 261 is transmitted to the steering counter shaft 280. The rotational power transmitted to the steering countershaft 280 is transmitted as reverse rotational power to the left ring gear 273 via the left intermediate gear 287 and the reverse gear 284 on the steering output shaft 285 in the left input gear mechanism 282, while it is transmitted as forward rotational power to the right ring gear 273 via the right intermediate gear 288 on the steering output shaft 285 in the right input gear mechanism 283.

[0052] 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, when the output of the swing pump 70a is in neutral and the swing brake 279 is on, power transmission from the swing motor 70b to the left and right planetary gear mechanisms 268 is blocked. When the output of the slewing pump 70a is in a state other than neutral and the slewing brake 279 is turned off, the rotational power of the slewing motor 70b is transmitted to the left ring gear 273 via the left input gear mechanism 282 and the reverse gear 284, and is transmitted to the right ring gear 273 via the right input gear mechanism 283.

[0053] As a result, when the swing motor 70b rotates forward (reversely), the left ring gear 273 rotates backward (forward) and the right ring gear 273 rotates forward (reverse) at the same rotation speed in the opposite directions. That is, the speed change outputs from the motor shafts 260, 261 are transmitted to the drive sprockets 51 of the left and right crawler belts 2 via the sub-speed change gear mechanism 251 or the differential mechanism 257, respectively, and the vehicle speed (traveling speed) and traveling direction of the traveling machine body 1 are determined.

[0054] In other words, when the slewing motor 70b is stopped and the left and right ring gears 273 are fixed stationary, when the linear motor 64b is driven, the rotational output from the linear 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.

[0055] 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 traveling body 1 to change direction on the spot (pivot spin turn).

[0056] In addition, by driving the left and right sun gears 271 by the linear motor 64b while driving the left and right ring gears 273 by the turning motor 70b, a difference in speed occurs between the left and right tracks 2, and the traveling machine body 1 turns (makes a U-turn) to the left or right 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 tracks 2. The traveling drive force of the engine 7 is constantly transmitted to the left and right tracks 2 and the traveling machine body 1 turns to the left or right.

[0057] Next, the working hydraulic circuit 180 and the traveling hydraulic circuit 200 in the normal type combine harvester of this embodiment will be described with reference to Fig. 8 to Fig. 15. As shown in Fig. 8 to Fig. 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, left and right machine body lifting hydraulic cylinders 56L, 56R that raise and lower the traveling machine body 1, a hydraulic oil tank 57 that stores hydraulic oil, a working unit charge pump 59 connected to the hydraulic oil tank 57 via a strainer 58, hydraulic valves 60A to 60E that switch the flow of hydraulic oil, and an oil cooler 62 provided in the return piping from the hydraulic valves 50A to 60E to the hydraulic oil tank 57. The hydraulic valves 60A to 60E are incorporated into a hydraulic valve unit 60 mounted on the traveling machine body 1.

[0058] A working unit charge pump 59 is hydraulically connected to the hydraulic cylinder 4 for reaping lifting via a hydraulic valve 60A for reaping lifting. The hydraulic cylinder 4 for reaping lifting is operated by tilting a reaping position lever (not shown) in the driving operation unit (driver's seat) 5 in the forward and backward directions, and the operator can raise and lower the reaping unit 3 to a desired height (for example, reaping work height or non-work height). Meanwhile, a working unit charge pump 59 is hydraulically connected to the hydraulic cylinders 27L, 27R for reel lifting via a hydraulic valve 60B for reel lifting. The hydraulic cylinders 27L, 27R for reel lifting are operated by tilting the reaping position lever (not shown) in the left and right directions, and the operator can raise and lower the raking reel 14 to a desired height to reap uncut stalks in the field.

[0059] A working unit charge pump 59 is hydraulically connected to the auger lifting hydraulic cylinder 55 via the auger lifting hydraulic valve 60C. The auger lifting hydraulic cylinder 55 is operated by tilting the grain discharge lever 155 on the driving operation unit (driver's cab) 5 in the forward and backward directions, and the operator raises and lowers the rice throwing opening of the grain discharge auger 164 on the grain discharge conveyor 8 to a desired height. The electric motor 165 rotates the grain discharge auger 164 together with the vertical feed auger 162 and the bevel gear mechanism 163 in the horizontal direction 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.

[0060] A hydraulic oil tank 57 and a working unit charge pump 59 are hydraulically connected to the left machine body lifting hydraulic cylinder 56L via a left machine body lifting hydraulic valve 60D. Meanwhile, a hydraulic oil tank 57 and a working unit charge pump 59 are hydraulically connected to the right machine body lifting hydraulic cylinder 56R via a 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 traveling machine bodies 1 independently.

[0061] Therefore, when the left and right machine body lifting hydraulic cylinders 56L, 56R are operated simultaneously to simultaneously lower the left and right track frames 50, 50 relative to the traveling body 1, the traveling 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 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 raised simultaneously relative to the traveling body 1, the traveling 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 body 1 to the ground contact portions of the tracks 2, 2 becomes lower.

[0062] Then, when the left machine body lifting hydraulic cylinder 56L is operated to lower the left track frame 50 relative to the traveling machine body 1, or when the right machine body lifting hydraulic cylinder 56R is operated to raise the right track frame 50 relative to the traveling machine body 1 (or when both of these operations are performed simultaneously), the traveling machine body 1 tilts downward to the right. Conversely, when the right machine body lifting hydraulic cylinder 56R is operated to lower the right track frame 50 relative to the traveling machine body 1, or when the left machine body lifting hydraulic cylinder 56L is operated to raise the right track frame 50 relative to the traveling machine body 1 (or when both of these operations are performed simultaneously), the traveling machine body 1 tilts downward to the left.

[0063] The hydraulic oil tank 57, the working unit charge pump 59, and the hydraulic valve unit 60 are mounted on the traveling machine body 1, and are connected to each other via hydraulic pipes 181-183. On the traveling machine body 1, the hydraulic oil tank 57 is installed on the front left side, while the working unit 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 unit charge pump 59 are connected by hydraulic pipes 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 unit charge pump 59 is connected to the hydraulic valve unit 60 via hydraulic pipes 182. Furthermore, the hydraulic valve unit 60 is connected to the hydraulic oil tank 57 via hydraulic pipes 183, which serve as a hydraulic oil return pipe, and an oil cooler 62.

[0064] 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 a space surrounded by the feeder house 11 and the machine housing of the threshing unit 9, so that dust from the reaping unit 3 can be prevented from accumulating in the hydraulic oil tank 57, and contamination of the hydraulic oil due to dust entering from the oil supply port 184, etc. can also be prevented. In addition, since the cooling air from the engine 7 flows into the installation space of the hydraulic oil tank 57, it is possible to suppress an increase in the hydraulic oil temperature without providing an oil cooler on the working hydraulic circuit 180, and each hydraulic member can be driven appropriately.

[0065] The hydraulic oil tank 57 has an oil supply port 184 on its left side (the side facing the outside of the machine) that protrudes toward the left side (the side facing the outside of the machine), and is equipped with a strainer 58 that can be inserted and removed from the left side. Therefore, the oil supply port 184 and the strainer 58 can be easily accessed by removing the threshing cover 185 provided on the left side (the side facing the outside of the machine) of the threshing section 9. This makes it easy to fill the hydraulic oil tank 57 and to replace the oil filter in the strainer 58, and improves the maintainability of the work system hydraulic circuit 180.

[0066] Hydraulic pipes 181, 183 connected to the hydraulic oil tank 57 are arranged to extend left and right in front of the hydraulic oil tank 57 and the engine 7, and hydraulic pipe 182 connects the working unit charge pump 59 arranged in front of the engine 7 to the strainer 58. That is, the hydraulic pipes 181, 183 are arranged to extend along the output shaft 65 of the engine 7, bypassing the front of the engine 7 toward the hydraulic oil tank 57. The hydraulic pipes 182, 183 are arranged to extend rearward, passing below the cooling fan 149 provided on the right side of the engine 7, and are connected to the hydraulic valve unit 60. Therefore, the hydraulic pipes 181 to 183 are arranged to be short in length and in positions that are less susceptible to the effects of radiant heat from the engine 7, and the temperature of the hydraulic oil flowing through the hydraulic pipes can be prevented from increasing.

[0067] 7, 10 and 12 to 15, the traveling system hydraulic circuit 200 includes a linear pump 64a, a linear motor 64b, a swing pump 70a, a swing motor 70b, a transmission charge pump 151, an oil filter 152, and an oil cooler 153. The linear pump 64a and the linear motor 64b in the linear hydraulic continuously variable transmission 64 are connected in a closed loop by a linear closed oil passage 201. On the other hand, the swing pump 70a and the swing motor 70b in the swing hydraulic continuously variable transmission 70 are connected in a closed loop by a swing closed oil passage 202. The linear pump 64a and the swivel pump 70a are driven by the rotational power of the engine 7, and by controlling the swash plate angle of the linear pump 64a and the swivel pump 70a, the discharge direction and discharge amount of hydraulic oil to the linear motor 64b and the swivel motor 70b are changed, and the linear motor 64b and the swivel motor 70b operate in forward and reverse directions.

[0068] The traveling hydraulic circuit 200 includes a linear valve 203 that is switched in response to the 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, and a linear speed change operation is performed in which the rotation speed of the linear motor shaft 260 of the linear motor 64b is changed steplessly or reversed. The traveling hydraulic circuit 200 also includes a hydraulic servo mechanism 205 for linear speed change. The 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 the swash plate angle of the linear pump 64a is changed in proportion to the amount of manual operation of the main shift lever 44, and the rotation speed of the linear motor shaft 260 of the linear motor 60b is changed.

[0069] The traveling hydraulic circuit 200 is equipped with a swing valve 206 which is switched in response to manual operation of the steering 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 on 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.

[0070] As shown in FIG. 13, a charge branch oil passage 219 (details will be described later) is connected to all the oil passages 201a, 201b, 202a, and 202b of both closed oil passages 201 and 202. Between the charge branch oil passage 219 and 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. Therefore, the straight closed oil passage 201 has two check valves 211. In addition, between the charge branch oil passage 219 and the swing first oil passage 202a, a check valve 212 for the swing first oil passage 202a is provided. Between the charge branch oil passage 219 and the swing second oil passage 202b, a check valve 212 for the swing second oil passage 202b is provided. Therefore, the swing closed oil passage 202 also has two check valves 212 .

[0071] 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. Therefore, each of the closed oil passages 201, 202 is provided with one bidirectional relief valve 215, 216.

[0072] The suction side of transmission charge pump 151 is connected to a strainer 217 inside transmission case 63 via hydraulic piping 221. A charge introduction oil passage 218 is connected to the discharge side of transmission charge pump 151 via hydraulic piping 222, and an oil filter 152 is installed midway through hydraulic piping 222. A charge branch oil passage 219 connected to both closed oil passages 201, 202 is connected to the downstream side of charge introduction oil passage 218. Therefore, while engine 7 is running, hydraulic oil from transmission charge pump 151 is constantly replenished to both closed oil passages 201, 202.

[0073] Furthermore, charge branch oil passage 219 is connected to linear cylinder 204 via linear valve 203, and is also connected to swing cylinder 207 via swing valve 206. Furthermore, charge branch oil passage 219 is connected to transmission case 63 via surplus relief valve 220 and hydraulic pipe 223, and oil cooler 153 is installed midway through hydraulic pipe 223. Therefore, when surplus hydraulic oil from transmission charge pump 151 is returned to the inside of transmission case 63 via surplus relief valve 220, it is cooled by oil cooler 153.

[0074] In addition, the hydraulic pipes 223 are connected by a bypass pipe 224 that bypasses the feed pipe 223a and the return pipes 223b to 223d, and the bypass pipe 224 is fixed above the continuously variable transmission case 323 on the side of the transmission case 63. By arranging the hydraulic pipes 223 and the bypass pipe 224 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 in the traveling system hydraulic circuit 200, and the transmission mechanisms in the transmission case 63 and the continuously variable transmission case 323 are lubricated.

[0075] As described above, the oil cooler 153 is connected to the hydraulic pipes 221-223 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, and the bypass pipe 224 is provided integrally with the transmission case 63 and the continuously variable transmission case 323. Therefore, although the piping path that circulates the oil in 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 be used to shorten the length.

[0076] By providing the bypass pipe 224 in the hydraulic piping 223 to bypass the oil cooler 153, it is possible to circulate highly viscous hydraulic oil when starting the engine in cold climates, and to maintain good lubrication within the transmission case 63 and the continuously variable transmission case 323. Furthermore, by providing the transmission case 63 and the continuously variable transmission case 323 integrally with each other, 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.

[0077] 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 straight-travel hydraulic continuously variable transmission 64 side (front side) of the upper surface of the continuously variable transmission case 323, and the communication port 225a is disposed below the communication port 225b. The communication ports 225a and 225b of the connecting member 225 are each provided to protrude rearward (toward the turning hydraulic continuously variable transmission 70 side).

[0078] Of the hydraulic piping 223, the return piping 223b-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).

[0079] 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. The metal relay pipe 223c has a T-shape with a communication port (branch pipe) 223e protruding forward (toward the linear hydraulic continuously variable transmission 64) from a midway portion. That is, the communication port 223e of the midway portion 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.

[0080] 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 relay pipe 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.

[0081] The bypass path that bypasses the oil cooler 153 is made up of a metal relay pipe 223c, a bypass pipe 224, and a connecting member 225 that are assembled integrally with the continuously variable transmission case 323. Therefore, hydraulic parts other than the feed pipe 223a and the upstream return pipe 223b that are connected to the oil cooler 153 can be assembled integrally with the continuously variable transmission case 323, improving ease of assembly and maintainability of the transmission case 63 to which the continuously variable transmission case 323 is assembled.

[0082] The hydraulic pipes 222, 223 connecting the transmission case 63 and the continuously variable transmission case 323 are arranged so as to pass under the linear connection link body 345 and the revolving connection link body 346 which are connected to the steering case 318. 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.

[0083] More specifically, the hydraulic pipe 222 connecting the charge pump 151 and the oil filter 152 is arranged in the front-rear direction so as to pass below the straight-travel relay shaft 352 of the straight-travel connecting link body 345, and 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 of the turning direct-connected link body 346. In addition, 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-connected link body 346, and is connected to a metal relay pipe 223c fixed to the continuously variable transmission case 323.

[0084] Next, the engine room 146 in which the engine 7 is installed will be described with reference to FIG. 8 and the like. As shown in FIG. 8 and the like, a pair of left and right engine room supports 147 are erected on the rear side of the cab 5 on the upper surface of the traveling body 1, and a back plate body 148 is stretched between the left and right engine room supports 147 to cover the rear of the engine room 146 below the driver's seat 42. In addition, a box-shaped wind tunnel case 170 is erected via an opening / closing fulcrum shaft 171 on the right engine room support 147 provided at the right end of the cab 5 in the traveling body 1. A dust removal net is stretched over the outer opening on the right side of the wind tunnel case 170, and the dust removal net prevents straw and the like from entering the inside of the wind tunnel case 170 and, by extension, the inside of the engine room 146. In addition, an oil cooler 153 in the traveling system hydraulic circuit 200 and an oil cooler 62 in the working system hydraulic circuit 180 are arranged vertically in the wind tunnel case 170.

[0085] A water-cooling radiator 154 is erected on the inside of the wind 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 the shroud 150. An oil cooler 153 is also installed in the wind tunnel case 170. By rotating the cooling fan 149, outside air (cooling air) is taken into the wind tunnel case 170 from the outside opening on the right side of the wind tunnel case 170, and the dust-free cooling air is sent into the engine room 146 from the inside opening on the left side of the wind tunnel case 170. As a result, the oil cooler 153, the radiator 154, the engine 7, etc. are cooled by the cooling air flowing into the engine room 146.

[0086] Next, the driving operation structure of the steering wheel 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 provided with a step frame 311 which constitutes a flat footrest section for the operator on the driver's seat 5. A plurality of support frames 312 are erected on the upper surface side of the traveling body 1, and the step frame 311 is erected on the upper end side of the support frame 312. The step frame 311 and the support frame 312 constitute a support frame. A boarding and 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 upper surface of the traveling body 1.

[0087] In addition, there is a steering case 318 having a turning input shaft 316 and a main transmission 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 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 transmission input shaft 317 protrudes leftward from the left side surface of the steering case 318 and is connected to the main transmission lever 44 via a main transmission operating rod 322.

[0088] As can be seen from the above description, the main speed change lever 44, which is a straight-line operation tool for straight-line operation, and the operation handle 43, which is a turning operation tool for turning operation, are arranged on the driver's seat 5 (operating section) on the step frame 311 provided on the upper end side of the support frame 312 group. A case support horizontal frame 319 is attached to span between the left and right support frame 312 on the front lower side of the step frame 311. A steering case 318 is attached to the case support horizontal frame 319, which interlocks the main speed change lever 44 and the operation handle 43 with the drive unit (continuously variable transmission case 323 and transmission case 63). 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.

[0089] In addition, 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 a portion protruding leftward from the left support leg frame 312 in the front part of the step frame 311 so as to be disposed in front of the continuously variable transmission case 323. That is, the oil filter 152 is disposed in front of the continuously variable transmission case 323 fixed to the right side of the transmission case 63 by being fixed to the left side of the front end part of the step frame 311 via a filter fixing bracket 349. Therefore, when connecting the hydraulic pipe 222 in which the oil filter 152 is provided midway between the transmission charge pump 151 and the charge introduction oil passage 218, the hydraulic pipe 222 can be configured to be short.

[0090] The case support horizontal frame 319 is installed between the left and right support frame 312 on the lower front side of the step frame 311, and the steering case 318 that links the main speed change lever 44 and the control handle 43 with the drive unit (stepless speed change case 323 and transmission case 63) is installed on the case support horizontal frame 319, so that the rigidity of the front part of the traveling body 1 (particularly near the driver's seat 5) can be improved by the presence of the case support horizontal frame 319. The steering case 318 can be supported with high rigidity by using the case support horizontal frame 319 that plays a role in reinforcing the front part of the traveling body 1. Therefore, there is no significant difference between the operation amount of the main speed change lever 44 and the control handle 43 and the output of the drive unit (stepless speed change case 323 and transmission case 63), and the risk of the operator being in a driving state that he or she does not expect can be eliminated. 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.

[0091] The vehicle is provided with a continuously variable transmission case 323 to which the straight hydraulic continuously variable transmission 64 and the swing hydraulic continuously variable transmission 70 are assembled. The continuously variable transmission case 323 is fixed to the upper right side of the transmission case 63, and the straight and swing operation arm bodies 355, 369 are disposed on the front and rear surfaces of the continuously variable transmission case 323. That is, the straight hydraulic continuously variable transmission 64 and the swing hydraulic continuously variable transmission 70 are arranged 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.

[0092] Therefore, because space is created on the side (left side) of the transmission case 63 on the feeder house 11 side, design freedom for the reaping unit 3 is increased, and the feeder house 11 can be configured with a size that is optimal for the reaping volume of the reaping unit 3 and the reaping width of the grain header 12. Also, because the installation width of the feeder house 11 is increased in the left-right direction, the feeder house 11 can be installed on the side closer to the center of gravity of the grain header 12 when it is raised and lowered, and the support strength of the feeder house 11 for the reaping unit 3 can be increased.

[0093] 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.

[0094] A driver's 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 driver's cab near the drive unit (transmission case 63 and continuously variable transmission case 323). Below the driver's 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.

[0095] In this case, the steering handle 43 is disposed in the front center part of the driver's seat 42 of the driver's cab 5, and the main speed change lever 44 is disposed on the steering column 41 on the left side, which is the side part near the drive device (stepless variable transmission case 323 and transmission case 63). That is, the steering case 313 is disposed below the steering handle 43, and the stepless variable transmission case 323 is disposed below the steering column 41 on which the main speed change lever 44 is installed. This allows each part of the operation system mechanism that connects the steering handle 43 and the main speed change lever 44 to the stepless variable transmission case 323 via the steering case 313 to be disposed close to each other, and each link mechanism 321, 322, 345, 346 that connects each part of the operation system mechanism can be configured short, thereby suppressing their fluctuation and deformation. Therefore, it is possible to suppress the deviation between the operation amount of the main speed change lever 44 or the steering handle 43 and the output of the drive device (stepless variable transmission case 323 and transmission case 63), and to maintain a stable running state according to the operation of the operator.

[0096] The battery 230 that supplies power to the engine 7 is disposed below the cab 5 in the front part of the traveling body 1, behind the steering case 318 and to the side of the continuously variable transmission case 32. That is, the battery 230 that supplies power to the engine 7 and the like is disposed in an area surrounded by the steering case 318, the drive device (the continuously variable transmission case 323 and the transmission case 63) and the engine 7 under the cab 5. 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. Therefore, the battery 230 can be disposed close to the engine 7 and the cab 5, and the electrical system can be made compact. In addition, it is possible to avoid making the combine larger in size in order to secure an arrangement space for the battery 230.

[0097] 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 vertically arranged in multiple stages below the front part of the step frame 311, so that electrical wiring for supplying power to the 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.

[0098] In addition, since an oil filter 152 for filtering the hydraulic oil in the drive unit (the continuously variable transmission case 323 and the transmission case 63) is disposed in the above-mentioned area below the cab 5, the length of the hydraulic piping 222 connecting the drive unit (the continuously variable transmission case 323 and the transmission case 63) and the oil filter 152 can be shortened, and the handling of the hydraulic piping 222 becomes simpler.

[0099] A horizontal main transmission input shaft 317 is disposed at one of the front and rear sides of the turning input shaft 316 in the upper part of the steering case 318, and a horizontal linear output shaft 350 is disposed at the other side. The main transmission input shaft 317 and the linear output shaft 350 extend parallel to each other in the left and right directions 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 in a direction perpendicular to the linear output shaft 350 is supported on the back surface of the steering case 318, below the linear output shaft 350, so as to protrude outward (rearward) from the steering case 318.

[0100] The linear connection link body 345 is connected to the linear output shaft 350 by inserting a protruding end (left end) of the linear output shaft 350 into one end (right end) of a cylindrical shaft connection body 351. A linear intermediate shaft 352 supported by a speed change output support bracket 328 fixed to a support leg frame 312 at the left front position of the cab 5 is inserted into the other end (left end) of the shaft connection body 351. The installation position of the linear connection link body 435 in the left-right direction is adjusted by adjusting the left-right position of the linear intermediate shaft 352 relative to the shaft connection body 351.

[0101] One end (rear end) of a rectilinear relay arm body 353 extending in the front-rear direction is fixed to the other end of the rectilinear relay shaft 352, and the other end (front end) of the rectilinear relay arm body 353 swings up and down in response to rotation of the rectilinear relay shaft 352. The other end (front end) of the rectilinear relay arm body 353 is connected to one end (upper end) of a rectilinear connecting rod 354 extending up and down, and the other end (lower end) of the connecting rod 354 is connected to a rectilinear operating arm body 355.

[0102] The linear connecting link body 345 connects the linear intermediate shaft 352, which is provided extending in the left-right direction at a position on an extension line of the linear output shaft 350, by a shaft connecting body 351, and is supported by a speed change output support bracket 328 fixed to the support leg frame 312. As a result, the linear intermediate shaft 352 rotates together with the linear output shaft 350, and swings the front end of the linear intermediate arm body 353 fixed to the left end of the linear intermediate shaft 352. Then, the linear connecting rod 354, both ends of which are pivotally connected to the front end of the linear intermediate arm body 353 and one end of the linear operating arm body 355, moves up and down in response to the swing of the linear intermediate arm body 353, thereby rotating the linear operating shaft 325, the protruding end (front end) of which is fixed to the other end of the operating arm body 355.

[0103] On the other hand, the swivel connection link body 346 connects one end (right end) of a first relay rod 363 extending laterally to the other end (tip end) of an output arm body 362, one end (base end) of which is fixed to the protruding end (rear end) of the swivel output shaft 361. The first relay rod 363 extends laterally so as to straddle the upper front part of the continuously variable transmission case 323 at a position rearward of the steering case 318, and the other end (left end) of the first relay rod 363 is connected to a first swivel relay arm body 364 fixed to one end (front end) of a swivel relay shaft 365. The swivel relay shaft 365 is supported by being passed through a tubular shaft support body 366.

[0104] Meanwhile, one end (right end) of a second relay rod 368 extending left and right is connected to the other end (tip) of a rotating operation arm body 369, one end (base end) of which is fixed to the protruding end (rear end) of the rotating operation shaft 326. The second relay rod 368 extends left and right along the back surface of the transmission case 63 and the continuously variable transmission case 323, and the other end (left end) of the second relay rod 368 is connected to a second rotating relay arm body 367 fixed to one end (rear end) of the rotating relay shaft 365.

[0105] The shaft support 366 that supports the turning intermediate shaft 365 is fixed to the transmission case 63 at a position on the left side 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.

[0106] The right end of the first relay rod 363 extending in the left-right direction is pivotally attached to the output arm body 362, the tip of which swings left and right in accordance with the rotation of the rotation output shaft 361 protruding from the rear of the steering case 318. 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 the first swing relay arm body 364, the base end of which is fixed to the front end of the swing relay shaft 365, left and right. This swing of the tip of the first swing relay arm body 364 causes the swing relay shaft 365 journaled by the shaft support 366 to rotate, and at the same time, the tip of the second swing relay arm body 364, the base end of which is fixed to the rear end of the swing relay shaft 365, swings left and right. A second relay rod 368, the both ends of which are pivotally attached to the front end of the second rotating relay arm body 367 and one end of the rotating operating arm body 369, moves left and right in response to the swinging of the second rotating relay arm body 367, thereby rotating the rotating operating shaft 326, the protruding end (rear end) of which is fixed to the other end of the operating arm body 369.

[0107] A main transmission input shaft 317 protrudes from a steering case 318 toward the left-right center of the traveling machine body 1. The protruding end (left end) of the main transmission input shaft 317 is journaled by a main transmission input support bracket 381 fixed to the step frame 31·BR>P on the left edge on the transmission case 63 side. In addition, one end (front end) of a main transmission arm body 382 is connected to the protruding end (left end) of the main transmission input shaft 317, and the other end (rear end) of the main transmission arm body 382 is connected to a main transmission operating rod 322 connected to the main transmission lever 44.

[0108] The linear hydraulic continuously variable transmission 64 and the swing hydraulic continuously variable transmission 70, which 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 linear operation shaft 325 of the linear hydraulic continuously variable transmission 64 and a swing operation shaft 326 of the swing hydraulic continuously variable transmission 70 are provided protrudingly, allocated to the front and rear. Since the linear hydraulic continuously variable transmission 64 and the swing 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.

[0109] 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 arrange the continuously variable transmission case 323 and the steering case 318 in close proximity to each other below the cab 5 for compact installation.

[0110] A steering case 318 is disposed below the cab (operating section) 5 and above the drive unit (the continuously variable transmission case 323 and the transmission case 63), and a linear output shaft 350 and a swing output shaft 361 are protruded from the steering case 318. A linear connection link body 345 that connects the linear output shaft 350 and the linear operation shaft 325, and a swing connection link body 346 that connects the swing output shaft 361 and the swing operation shaft 326 are each installed between the steering case 318 and the continuously variable transmission case 323 in a plan view. That is, since the linear connection link body 345 and the swing connection link body 346 are disposed on the cab 5 side together with the transmission case 63, ease of assembly and maintenance are improved.

[0111] 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.

[0112] A linear connection link body 345 that interlocks and connects the steering case 318 and the linear operation shaft 325 (linear output control section) provided on the drive device (continuously variable transmission case 323 and transmission case 63) is supported by the support leg frame 312 that supports the cab 5. Therefore, even if the linear connection link body 345 is subjected to bending or tension due to vibration of the drive device (continuously variable transmission case 323 and transmission case 63), the support leg frame 312 that supports the cab 5 can support the linear connection link body 345 with high rigidity, and fluctuation or deformation of the linear connection link body 345 can be suppressed. Therefore, no significant discrepancy occurs between the operation amount of the main speed change lever 44 or the steering handle 43 and the output of the drive device (continuously variable transmission case 323 and transmission case 63), and the risk of the vehicle entering a driving state that the operator does not expect can be eliminated.

[0113] 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 driver's 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 discrepancy between the operation amount of the main speed change lever 44 or the operating 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.

[0114] 22 to 26, the mounting structure of the ECU 401 that controls the operation of the combine harvester will be described. As can be seen from the above description, in the embodiment, the step section 400, which is the space surrounded by the front part of the traveling body 2, the group of support frames 312, and the group of step frames 311, is dead space, so that the steering case 318, the continuously variable transmission case 323, and the battery 230 are arranged by utilizing this space.

[0115] An ECU 401 that controls the operation of the combine 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 fastened to the front side of the shielding plate 402.

[0116] Therefore, the ECU 401 is located in front of the space of the step portion 400, and the engine 7 is located in the rear. In addition, 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 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), reducing the thermal effect from the engine 7 on the ECU 401. This allows the ECU 401 to have stable control and a long life. In particular, the shielding plate 402 can block exhaust heat from the engine, which is highly effective in reducing the thermal effect from the engine 7 on the ECU 401.

[0117] The outer shape of the shielding plate 402 is larger than that of the ECU 401. Therefore, 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. Note that 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 weight from the shielding plate 402 and for the purpose of allowing outside air to hit the back side of the ECU 401 and releasing heat from the ECU 401.

[0118] The front side of the ECU 401 is covered by a front cover 404 of the cab 5. The battery 230 for supplying power arranged in the step section 400 is placed below the steering case 318 and the case support horizontal frame 319. Therefore, the ECU 401 is placed at a higher position than the battery 230. The battery 230 is placed at a position in the traveling body 1 that is not affected by, for example, muddy water in a farm field or rainwater (is not splashed with muddy water, etc.). Since the ECU 401 is placed at a high position for such a 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 arranged close to each other, the electrical system can be made compact.

[0119] 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.

[0120] <Notes on the invention> The present invention relates to a combine harvester in which a cutting unit is attached to the front of a running body on which an engine is mounted, a threshing unit is mounted on the running body rear of the cutting unit, a control unit is located to the front side of the threshing unit, and an engine is mounted below and rear of the control unit, in which a transmission case is located between the cutting unit and early threshing unit on the running body, and a battery for supplying power is mounted to the side of the transmission case and below the control unit.

[0121] In the combine of the present invention, the steering section may be composed of a plurality of support frames erected on the front upper surface side of the running body, and an ECU that controls the operation of the combine may be supported by the plurality of support frames.

[0122] In the combine harvester of the present invention, the ECU may be attached to a step frame provided on the plurality of support frames.

[0123] According to the present invention, in a combine harvester in which a cutting unit is attached to the front of a running body equipped with an engine, a threshing unit is mounted on the running body rear of the cutting unit, a control unit is located to the front side of the threshing unit, and an engine is mounted below and rear of the control unit, a transmission case is disposed between the cutting unit and early threshing unit on the running body, and a battery for supplying power is mounted to the side of the transmission case and below the control unit, so that the dead space around the control unit, which is a dead space unique to combine harvesters, can be effectively utilized not only as a space for arranging the transmission case, but also as a space for arranging the battery. [Explanation of symbols]

[0124] 1 Running vehicle 3 Reaping part 5. Cab 7 Engine 9. Threshing Department 11. Feeder House 311 Step frame (support frame) 312 Support frame (support frame) 318 Steering case 319 Case support horizontal frame 400 Step section 401 ECU 402 Shielding plate 403 Cutout part 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 transmission case is disposed between the reaping section and the threshing section in the traveling machine body, and a battery for supplying power is mounted on the side of the transmission case and in front of the engine. combine.

2. The battery is disposed below the control unit. The combine according to claim 1.

3. The control unit is configured on a plurality of support frames erected on the upper surface side of the traveling body, The battery is disposed in a space surrounded by the plurality of support frames. A combine harvester according to claim 1 or 2.

4. An ECU that controls the operation of the combine is supported by the multiple support frames. The combine according to claim 3.

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