combine

Abstract

The goal is to make effective use of the dead space around the control unit 5, which is a unique dead space in combine harvesters. [Solution] The combine harvester of the present invention has a cutting unit 3 mounted on the front of a traveling body 1 equipped with an engine 7, a threshing unit 9 mounted behind the cutting unit 3 on the traveling body 1, a control unit 5 positioned to the front side of the threshing unit 9, and an engine 7 mounted below and behind the control unit 5. A battery 230 is mounted in front of the engine 7, which is located on one side of the traveling body 1. A hydraulic valve for operating the implement is positioned behind the engine 7.

Description

Technical Field

[0001] The present invention relates to a combine equipped with a cutting unit for cutting unharvested cereal straws in a field and a threshing unit for threshing grains from the cut cereal straws.

Background Art

[0002] Conventionally, in a combine, generally, an ECU that controls the operation of the combine is often arranged around the 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

Patent Document 2

Summary of the Invention

Problems to be Solved by the Invention

[0004] However, in the case of a combine with an engine mounted behind the control unit, the exhaust heat from the engine may affect the ECU. In recent years, it is desirable that the ECU, which is particularly often in charge of complex control, is less affected by heat from the surroundings as much as possible.

Means for Solving the Problems

[0005] The present invention has a technical problem of providing a combine that has been improved in consideration of the above-described current situation.

[0006] In one embodiment, a combine harvester has a cutting unit mounted on the front of a traveling body equipped with an engine, a threshing unit mounted behind the cutting unit on the traveling body, a control unit positioned to the front side of the threshing unit, and an engine mounted below and behind the control unit. A battery is mounted in front of the engine, which is located on one side of the traveling body. A hydraulic valve for operating the implements is positioned behind the engine. [Effects of the Invention]

[0007] We can provide a combine harvester that incorporates improvements based on the current situation described above. [Brief explanation of the drawing]

[0008] [Figure 1] This is a left side view of the combine harvester according to the present invention. [Figure 2] This is a right side view of the combine harvester. [Figure 3] This is a plan view of the combine harvester. [Figure 4] This is a diagram of the drive system of a combine harvester. [Figure 5] This is a perspective view of a combine harvester seen from a diagonal front angle. [Figure 6] This is a partial plan cross-sectional view of the threshing section. [Figure 7] This is a diagram of the drive system for the transmission case. [Figure 8] This is a cross-sectional view showing the configuration around the engine compartment. [Figure 9] This is a hydraulic circuit diagram showing the configuration of the hydraulic circuit for the work system. [Figure 10] This is a front view showing the arrangement of hydraulic circuit components. [Figure 11] This is an overall perspective view of a combine harvester showing the piping configuration of the hydraulic circuit for the work system. [Figure 12] This is an enlarged perspective view showing the piping configuration of the hydraulic circuit for the traction system. [Figure 13] This is a hydraulic circuit diagram showing the configuration of the hydraulic circuit for the drive system. [Figure 14] This is a perspective view showing the piping workability of the hydraulic piping on the transmission case. [Figure 15] It is a perspective view showing the relationship between the hydraulic piping on the mission case and the connecting link body. [Figure 16] It is a perspective view of the front part of the traveling body seen from the left front obliquely. [Figure 17] It is a perspective view of the periphery of the driver's cab (control section) seen from the left rear obliquely. [Figure 18] It is a front view of the periphery of the driver's cab (control section). [Figure 19] It is a plan view of the periphery of the driver's cab (control section). [Figure 20] It is a perspective view of the periphery of the driver's cab (control section) seen from the right rear obliquely. [Figure 21] It is a perspective view of the periphery of the driver's cab (control section) seen from the front. [Figure 22] It is a perspective view of the mounting position of the ECU seen from the left front obliquely of the traveling body. [Figure 23] It is a front view of the periphery of the driver's cab (control section) showing the mounting position of the ECU. [Figure 24] It is a plan view of the periphery of the driver's cab (control section) showing the mounting position of the ECU. [Figure 25] It is a perspective view of the positional relationship between the ECU and the steering case seen from the right front obliquely. [Figure 26] It is a perspective view of the mounting position of the ECU seen from the right front obliquely.

Mode for Carrying Out the Invention

[0009] Hereinafter, embodiments embodying the present invention will be described based on the drawings (FIGS. 1 to 26) applied to a conventional combine. First, the schematic structure of the combine will be described while referring to FIGS. 1 to 3. In the following description, the left side toward the forward direction of the traveling body 1 is simply referred to as the left side, and the right side toward the same forward direction is simply referred to as the right side.

[0010] As shown in Figures 1 to 3, the conventional combine harvester in this embodiment is equipped with a running body 1 supported by a pair of left and right tracks 2 made of rubber crawler as the running section. At the front of the running body 1, a harvesting section 3 for harvesting and collecting unharvested grain stalks such as rice (or wheat, soybeans, or corn) is mounted so as to be adjustable in height by a single-acting hydraulic cylinder 4 for lifting and lowering.

[0011] On the left side of the traveling machine 1 is a threshing unit 9 for threshing the harvested grain stalks supplied from the harvesting unit 3. Below the threshing unit 9 is a grain sorting mechanism 10 for oscillating sorting and wind sorting. On the front right side of the traveling machine 1 is a control panel 5 where the operator sits. The engine 7, which serves as the power source, is located in the control panel 5 (below the driver's seat 42). Behind the control panel 5 (on the right side of the traveling machine 1) are a grain tank 6 for extracting grain from the threshing unit 9 and a grain discharge conveyor 8 for discharging the grain from the grain tank 6 toward a truck bed (or container, etc.). The grain discharge conveyor 8 is tilted outwards from the machine to transport the grain from the grain tank 6.

[0012] The harvesting unit 3 comprises a feeder house 11 connected to the threshing opening 9a at the front of the threshing unit 9, and a horizontally elongated 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 raking reel 14 with a tine bar is positioned above the front of the raking auger 13. A clipper-shaped cutting blade 15 is positioned at the front of the grain header 12. Left and right dividers 16 are provided protruding 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 grain stalks is provided at the end of the supply conveyor 17 (threshing opening 9a). Furthermore, the lower surface of the feeder house 11 and the front end of the traveling machine body 1 are connected via a lifting hydraulic cylinder 4, and the harvesting unit 3 moves up and down by the harvesting lifting hydraulic cylinder 4, with the harvesting input shaft 89 (feeder house conveyor shaft), which will be described later, as the lifting pivot point.

[0013] With the above configuration, the tip end of the unharvested grain stalks between the left and right dividers 16 is raked in by the raking reel 14, the base end of the unharvested grain stalks is cut by the cutting blade 15, and the rotational drive of the raking auger 13 collects the harvested grain stalks near the entrance of the feeder house 11, closer to the center of the left-right width of the grain header 12. The entire amount of harvested grain stalks in the grain header 12 is transported by the supply conveyor 17 and fed into the threshing opening 9a of the threshing unit 9 by the beater 18. Furthermore, the grain header 12 is equipped with a horizontal control hydraulic cylinder (not shown) that rotates it around a horizontal control pivot axis, and the left-right inclination of the grain header 12 can be adjusted with the horizontal control hydraulic cylinder to support the grain header 12, the cutting blade 15, and the raking reel 14 horizontally with respect to the field surface.

[0014] Furthermore, as shown in Figures 1 and 3, a threshing drum 21 is rotatably mounted inside the threshing chamber of the threshing section 9. The threshing drum 21 is pivotally supported on a threshing drum shaft 20 (see Figure 4) that extends in the front-rear direction of the traveling machine body 1. A receiving net 24 for allowing grain to leak out is stretched across the lower side of the threshing drum 21. On the outer circumferential surface of the front of the threshing drum 21, spiral-shaped screw-blade-like intake blades 25 are provided, protruding radially outward.

[0015] With the above configuration, the harvested grain stalks fed in from the threshing opening 9a by the beater 18 are conveyed toward the rear of the traveling machine body 1 by the rotation of the threshing drum 21, and are mixed and threshed between the threshing drum 21 and the receiving screen 24. Threshed grains smaller than the mesh size of the receiving screen 24 leak through the receiving screen 24. Straw and other materials that do not leak through the receiving screen 24 are discharged into the field from the dust discharge port 23 at the rear of the threshing section 9 by the conveying action of the threshing drum 21.

[0016] Furthermore, a plurality of dust supply valves (not shown) are rotatably pivoted on the upper side of the threshing drum 21 to adjust the conveying speed of the threshed grain in the threshing chamber. By adjusting the angle of the dust supply valves, the conveying speed (residence time) of the threshed grain in the threshing chamber can be adjusted according to the variety and characteristics of the harvested grain stalks. On the other hand, a grain sorting mechanism 10 is located below the threshing section 9 and includes a oscillating sorting plate 26 for specific gravity sorting, which has a grain pan, chaff sieve, grain sieve, and straw rack.

[0017] Furthermore, the grain sorting mechanism 10 includes a fan-shaped winnowing machine 29 that supplies sorting air to the oscillating sorting plate 26. The threshed grain that has been threshed in the threshing drum 21 and leaked out from the receiving net 24 is sorted and removed into grain (first-grade grain such as polished grain), a mixture of grain and straw (second-grade grain such as grain with stems attached), and straw scraps by the specific gravity sorting action of the oscillating sorting plate 26 and the air sorting action of the fan-shaped winnowing machine 29.

[0018] Below the oscillating sorting plate 26, a grain sorting mechanism 10 is provided, consisting of a first conveyor mechanism 30 and a second conveyor mechanism 31. The grain (first grade) that falls from the oscillating sorting plate 26 due to sorting by the oscillating sorting plate 26 and the fan-shaped winnowing machine 29 is collected in the grain tank 6 by the first conveyor mechanism 30 and the grain lifting conveyor 32. The mixture of grain and straw (second grade) is returned to the sorting start end side 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 and other debris are configured to be discharged into the field from the dust discharge port 23 at the rear of the traveling machine body 1.

[0019] Furthermore, as shown in Figures 1 to 3, the driver's cab 5 is equipped with a control column 41 and a driver's seat 42 on which the operator sits. The control column 41 is equipped with an accelerator lever 40 for adjusting the rotational speed of the engine 7, a round steering wheel 43 for changing the direction of the machine 1 by the operator's rotational operation, a main gear lever 44 and a sub-gear lever 45 for switching the speed of the machine 1, a harvesting clutch lever 46 for driving or stopping the harvesting unit 3, and a threshing clutch lever 47 for driving or stopping the threshing unit 9. In addition, a sunshade roof 49 is attached to the front upper surface of the grain tank 6 via a sun visor support 48, and the sunshade roof 49 is configured to cover the upper side of the driver's cab 5.

[0020] As shown in Figures 1 and 2, left and right track frames 50 are arranged on the underside of the running body 1. The track frame 50 is equipped with a drive sprocket 51 that transmits power from the engine 7 to the track 2, a tension roller 52 that maintains tension on the track 2, a plurality of track rollers 53 that keep the ground-contacting side of the track 2 in contact with the ground, and an intermediate roller 54 that holds the non-ground-contacting side of the track 2. The drive sprocket 51 supports the front side of the track 2, the tension roller 52 supports the rear side of the track 2, the track rollers 53 support the ground-contacting side of the track 2, and the intermediate roller 54 supports the non-ground-contacting side of the track 2.

[0021] Next, the drive structure of the combine harvester will be described with reference to Figures 4 to 8. As shown in Figures 4 and 7, a linear hydraulic continuously variable transmission 64 for travel speed change, having a hydraulic linear pump 64a and a hydraulic linear motor 64b, is provided in the transmission case 63. The engine 7 is mounted on the upper right side of the front of the travel body 1, and the transmission case 63 is positioned to the left of the engine 7 at the front of the travel body 1. An output shaft 65 protruding to the left from the engine 7 and a transmission input shaft 66 protruding to the left 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 work section charge pump 59 and a cooling fan 149 that drive the lifting hydraulic cylinder 4, etc., are located on the engine 7, and the work section charge pump 59 and cooling fan 149 are driven by the engine 7.

[0022] Furthermore, a steering slewing hydraulic continuously variable transmission 70 having a hydraulic slewing pump 70a and a hydraulic slewing motor 70b is provided in the transmission case 63, and the output of the engine 7 is transmitted to the straight-line hydraulic continuously variable transmission 64 and the slewing hydraulic continuously variable transmission 70 via the transmission input shaft 66, while the output of the straight-line hydraulic continuously variable transmission 64 and the slewing hydraulic continuously variable transmission 70 is controlled by the steering handle 43, the main shift lever 44 and the sub-shift lever 45, and the left and right tracks 2 are driven via the straight-line hydraulic continuously variable transmission 64 and the slewing hydraulic continuously variable transmission 70, and the vehicle is configured to move around in a field or the like.In this embodiment, the straight-line and slewing hydraulic continuously variable transmissions 64 and 70 are arranged on the upper right side of the transmission case 63.The straight-line and slewing hydraulic continuously variable transmissions 64 and 70 and the transmission case 63 constitute the drive device of the present invention.

[0023] Furthermore, as shown in Figures 1 to 6, a threshing cylinder drive case 71 is provided that pivotally supports the front end of the threshing cylinder shaft 20. The threshing cylinder drive case 71 is positioned on the front side of the threshing unit 9. The threshing cylinder input shaft 72 for driving the harvesting unit 3 and the threshing cylinder 21 is pivotally supported by the threshing cylinder drive case 71. In addition, a main counter shaft 76 is provided as a constant rotation shaft that passes through the left and right sides of the threshing unit 9. A work unit input pulley 83 is provided at the right end of the main counter shaft 76. The right end of the main counter shaft 76 is connected to 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 work unit drive belt 85.

[0024] In front of the threshing drum 21, there is a threshing drum input shaft 72 extending in the left-right direction of the traveling machine 1, beaters 18 positioned in the left-right direction of the traveling machine 1, and a harvesting input shaft 89 extending in the left-right direction of the traveling machine 1. The threshing drum input mechanism 90, which transmits the driving force of the main counter shaft 76 to the threshing drum input shaft 72, is equipped with threshing drum drive pulleys 86, 87 and a threshing drum drive belt 88. The threshing drum input mechanism 90 (threshing drum drive pulleys 86, 87 and threshing drum drive belt 88) is positioned 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, and the threshing drum 21 is driven at a constant rotational speed with the constant rotational output of the engine 7.

[0025] A beater drive mechanism and a harvesting drive mechanism, which transmit the driving force of the main counter shaft 76 to the beater shaft 82 and the harvesting input shaft 89, are provided on the other end of the main counter shaft 76. A sub-counter shaft 104 is positioned between the beater shaft 82 and the main counter shaft 76, and a power relay belt 113 is wound around power relay pulleys 105 and 106 provided on the main counter shaft 76 and the sub-counter shaft 104, forming a power relay mechanism that transmits power to the harvesting drive mechanism.

[0026] A harvesting drive belt 114 is wound around harvesting drive pulleys 107 and 108, respectively, provided on the sub-counter shaft 104 and the beater shaft 82, forming the beater drive mechanism. The harvesting drive belt 114 is tensioned by a harvesting clutch 109, which also serves as a tension roller, so that the rotational power from the engine 7 transmitted to the main counter shaft 76 is input to the beater shaft 82 via a power relay mechanism and the beater drive mechanism. Furthermore, the harvesting drive mechanism is configured to transmit the harvesting drive force from the engine 7 to the harvesting input shaft 89 via a harvesting drive chain 115 and sprockets 116 and 117 from the beater shaft 82, on which the beater 18 is pivotally supported. As a result, the harvesting unit 3 is driven at a constant rotational speed by the constant rotational output of the engine 7 together with the beater 18.

[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 portion of the winnowing shaft 100. In other words, the main counter shaft 76 and the winnowing shaft 100 have a double shaft structure, and the main counter shaft 76 and the winnowing shaft 100 are pivotally supported so that they can rotate relative to each other. In addition, a winnowing drive belt 103 is wound around winnowing drive pulleys 101 and 102 provided on the sub-counter shaft 104 and the winnowing shaft 100, respectively, to constitute the winnowing drive mechanism. Accordingly, 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 at a constant rotational speed with the constant rotational output of the engine 7.

[0028] Furthermore, the threshing unit 9's casing has a harvesting support frame 36 installed on the upper side of the front of the threshing machine casing support column 34 on the upper side of the traveling machine body 1. A harvesting bearing 37 is attached to the front right side of the harvesting support frame 36, and a forward / reverse rotation switching case 121, which will be described later, is attached to the front left side of the harvesting support frame 36. The harvesting input shaft 89 is pivotally supported on the front side of the harvesting support frame 36 via the harvesting bearing 37 and the forward / reverse rotation switching case 121 so as to be able to rotate left and right on the traveling machine body 1, and a left and right oriented beater shaft 82 (beater 18) is pivotally supported inside the harvesting support frame 36 via a beater bearing 38. In addition, a threshing drum drive case 71 is attached to the upper side of the harvesting support frame 36, and a threshing drum input shaft 72 is pivotally supported on the threshing drum drive case 71.

[0029] On the other hand, the feeder house 11 is equipped with left-right oriented harvesting input shafts 89 that drive the supply conveyor 17. The harvesting driving force transmitted from the engine 7 to one end of the main counter shaft 76 on the engine 7 side is transmitted from the other end of the main counter shaft 76, which is on the opposite side of the engine 7, to the forward / reverse transmission shaft 122 of the harvesting forward / reverse switching case 121. The harvesting input shafts 89 are driven via the forward rotation bevel gear 124 or the reverse rotation bevel gear 125 of the harvesting forward / reverse switching case 121.

[0030] Furthermore, left-right threshing drum input shafts 72 are provided on the front side of the threshing unit 9, and the driving force transmitted from the engine 7 to one end of the main counter shaft 76 on the engine 7 side is transmitted to one end of the threshing drum input shaft 72 on the engine 7 side. The threshing drum input shafts 72 provided on the front side of the threshing unit 9 are arranged in the left-right direction of the traveling machine 1, while the threshing drum 21 is pivotally supported on a threshing drum shaft 20 arranged in the front-rear direction of the traveling machine 1. The front end of the threshing drum shaft 20 is connected to the left and right ends of the threshing drum input shaft 72 opposite to the engine 7 via a bevel gear mechanism 75. The driving force of the engine 7 is transmitted from the left and right ends of the main counter shaft 76 opposite to the engine 7 to the grain sorting mechanism 10 or the harvesting unit 3 for sorting the grain after threshing.

[0031] Specifically, the right end of the threshing drum input shaft 72 is connected to the right end of the main counter shaft 76, which is closer 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. Power from 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, causing the threshing drum 21 to rotate in one direction. On the other hand, the driving force of the engine 7 is transmitted from the left end of the main counter shaft 76 to the grain sorting mechanism 10 located below the threshing section 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 to 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 the crank-shaped oscillating drive shaft 79 that pivotally supports the rear of the oscillating sorting platen 26 via an oscillating sorting belt 112. In other words, the threshing clutch 84 is controlled to turn on and off by the operator's operation of the threshing clutch lever 47. The operation of turning on the threshing clutch 84 drives each part of the grain sorting mechanism 10 and the threshing drum 21.

[0033] Furthermore, the grain lifting conveyor 32 is driven via the first conveyor shaft 77, and the first sorted grain from the first conveyor mechanism 30 is collected in the grain tank 6. In addition, the second return conveyor 33 is driven via the second conveyor shaft 78, and the second sorted grain (second grade) mixed with straw debris from the second conveyor mechanism 31 is returned to the upper side of the oscillating sorting plate 26. In addition, in a structure in which a spreader (not shown) for scattering straw debris is provided at the dust discharge port 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 supply conveyor 17 is equipped with a harvesting input shaft 89 as a conveyor input shaft that pivots at the end of the supply process. The header drive shaft 91 is rotatably pivoted on the rear right side of the grain header 12. The left end of the forward / reverse transmission shaft 122 is connected to the left end of the beater shaft 82 via a harvesting drive chain 115 and sprockets 116, 117, and the harvesting input shaft 89 is connected to the forward / reverse transmission shaft 122 via a forward / reverse switching case 121. In addition, the right end of the harvesting 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. The raking shaft 93 pivots the raking auger 13. The middle part of the header drive shaft 91 is connected to the right side of the raking shaft 93 via a raking drive chain 92.

[0035] The system also includes a reel shaft 94 that supports the raking reel 14. The right end of the raking shaft 93 is connected to the right end of the reel shaft 94 via an intermediate shaft 95 and reel drive chains 96 and 97. The cutting blade 15 is connected to the right end of the header drive shaft 91 via a cutting blade drive crank mechanism 98. The supply conveyor 17, raking auger 13, raking reel 14, and cutting blade 15 are driven and controlled by the on / off operation of the harvesting clutch 109, so as to continuously harvest the ear-side of the unharvested grain stalks in the field.

[0036] Furthermore, a forward rotation bevel gear 124 integrally formed on the forward / reverse transmission shaft 122, a reverse rotation bevel gear 125 rotatably supported on the harvesting input shaft 89, and an intermediate bevel gear 126 connecting the forward rotation bevel gear 124 to the reverse rotation bevel gear 125 are housed within 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 spline-engaged and supported on the harvesting input shaft 89. The slider 127 is configured to be detachably engaged with the forward rotation bevel gear 124 via a claw-clutch shaped forward rotation clutch 128, and the slider 127 is configured to be detachably engaged with the reverse rotation bevel gear 125 via a claw-clutch shaped reverse rotation clutch 129.

[0037] Furthermore, the system is equipped with a forward / reverse switching shaft 123 for sliding the slider 127, and a forward / reverse switching arm 130 is provided on the forward / reverse switching shaft 123. By operating the forward / reverse switching lever (forward / reverse operating tool), the forward / reverse switching arm 130 is swung, rotating the forward / reverse switching shaft 123, causing the slider 127 to move toward or away from the forward / reverse bevel gear 124 or the reverse / reverse bevel gear 125. The slider 127 is selectively locked to the forward / reverse bevel gear 124 or the reverse / reverse bevel gear 125 via a forward / reverse clutch 128 or the reverse clutch 129, and the harvesting input shaft 89 is connected to the forward / reverse transmission shaft 122 in either a forward / reverse or reverse direction.

[0038] The structure includes a forward / reverse switching case 121 as a forward / reverse switching mechanism for driving the supply conveyor 17 in the forward or reverse direction, and the supply conveyor 17 is connected to the beater shaft 82 via the forward / reverse switching case 121. Therefore, the supply conveyor 17 of the feeder house 11 can be reversed by operating the forward / reverse switching case 121, and jammed straw inside 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-shaped auger clutch 156 and an auger drive belt 157. The front end of the lateral auger 160 at the bottom of the grain tank 6 is connected to the left end of the auger drive shaft 158 ​​via a bevel gear mechanism 159. The longitudinal auger 162 of the grain discharge conveyor 8 is connected to the rear end of the lateral auger 160 via a bevel gear mechanism 161, and the grain discharge auger 164 of the grain discharge conveyor 8 is connected to the upper end of the longitudinal auger 162 via a bevel gear mechanism 163. The system also includes a grain discharge lever 155 for operating the auger clutch 156. The grain discharge lever 155 is mounted behind the driver's seat 42 and on the front of the grain tank 6, allowing the operator to operate the grain discharge lever 155 from the driver's seat 42 side.

[0040] Next, the power transmission structure of the transmission case 63 will be described with reference to Figures 4 and 7. As shown in Figures 4 and 7, the transmission case 63 is provided with a hydraulic continuously variable transmission 64 for straight-line driving (main driving speed transmission) having a pair of straight-line pumps 64a and straight-line motors 64b, and a hydraulic continuously variable transmission 70 for slewing having a pair of slewing pumps 70a and slewing motors 70b. The pump shafts 258 and 259 of the straight-line pumps 64a and slewing pumps 70a are gear-connected to the transmission input shaft 66 of the transmission case 63 and driven accordingly. An engine output belt 67 is wrapped around a transmission input pulley 69 on the transmission input shaft 66. The output of the engine 7 is transmitted to the transmission input pulley 69 via the engine output belt 67, driving the straight-line pumps 64a and slewing pumps 70a.

[0041] The driving force output from the output shaft 65 of engine 7 is transmitted via the engine output belt 67 and the transmission input shaft 66 to the pump shaft 258 of the straight pump 64a and the pump shaft 259 of the slewing pump 70a, respectively. In the straight hydraulic continuously variable transmission 64, the power transmitted to the pump shaft 258 is used to appropriately supply hydraulic fluid from the straight pump 64a to the straight motor 64b. Similarly, in the slewing hydraulic continuously variable transmission 70, the power transmitted to the pump shaft 259 is used to appropriately supply hydraulic fluid from the slewing pump 70a to the slewing motor 70b.

[0042] The transmission input shaft 66 protrudes from the upper left side of the transmission case 63 toward the feeder house 11, and the transmission input pulley 69 is pivotally attached to the protruding end (left end) of the transmission input shaft 66 in a manner that prevents relative rotation. The transmission input shaft 66 is rotatably supported by a bearing fixed to the transmission case 63, and a power distribution gear 262 is fitted to the middle of the transmission input shaft 66 in a manner that prevents relative rotation. The pump shaft 258 of the linear pump 64a and the pump shaft 259 of the swivel pump 70a are positioned in front of and behind the transmission input shaft 66 in a plan view, and are positioned below the transmission input shaft 66 in a side view.

[0043] A linear input gear 263, which meshes with a power distribution gear 262 fixed to the transmission input shaft 66, is fitted to the protruding end (left end) of the pump shaft 258, which protrudes from the continuously variable transmission case 323 toward the transmission case 63, so as to prevent relative rotation. Similarly, a slewing input gear 264, which meshes with a power distribution gear 262 fixed to the transmission input shaft 66, is fitted to the protruding end (left end) of the pump shaft 259, which protrudes from the continuously variable transmission case 323 toward the transmission case 63, so as to prevent relative rotation.

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

[0045] Furthermore, a transmission charge pump 151 for supplying hydraulic fluid 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 the inclination angle of the rotating swash plate in the linear pump 64a according to the amount of operation of the main shift lever 44 located on the steering column 41 or the steering handle 43, thereby changing the discharge direction and discharge amount of hydraulic fluid to the linear motor 64b.

[0046] The rotational power of the straight-line motor shaft 260 is transmitted from the straight-line 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, which are switched by auxiliary transmission shifters 252 and 253. The auxiliary transmission lever 45 located on the control column 41 is configured to selectively switch the output rotational speed of the straight-line motor shaft 260 to one of three speed settings: low, medium, or high. There is a neutral position (a position where the output of the auxiliary transmission is zero) between the low, medium, and high speeds of the auxiliary transmission.

[0047] A drum-type parking brake 266 is provided on the parking brake shaft 265 (sub-transmission output shaft) located on the output side of the sub-transmission gear mechanism 251. Rotational power from the sub-transmission gear mechanism 251 is transmitted from the sub-transmission output gear 267, which is fixed to the parking brake shaft 265, to the left and right differential mechanisms 257. Each of the left and right differential mechanisms 257 is equipped with a planetary gear mechanism 268. In addition, a straight-line pulse generating rotating wheel 292 is provided on the parking brake shaft 265, and a straight-line vehicle speed sensor (not shown) is configured to detect the rotational 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 comprises one sun gear 271, multiple planetary gears 272 that mesh with the sun gear 271, a ring gear 273 that meshes with the planetary gears 272, and a carrier 274 that rotatably arranges the multiple planetary gears 272 on the same circumference. The carriers 274 of the left and right planetary gear mechanisms 268 are arranged opposite each other on the same axis with an appropriate spacing between them. A center gear 276 is fixed to the sun gear shaft 275 on which the left and right sun gears 271 are mounted.

[0049] Each of the left and right ring gears 273 is arranged concentrically on the sun gear shaft 275, with its inner teeth on the inner circumference meshing with multiple planetary gears 272. The outer teeth on the outer circumference of each of the left and right ring gears 273 are connected to the steering output shaft 285 via intermediate gears 287 and 288 for left and right turning output, which will be described later. Each ring gear 273 is rotatably supported on the left and right forced differential output shafts 277, which protrude outward from the outer surface of the carrier 274. The left and right axles 278 are connected to the left and right forced differential output shafts 277 via final gears 278a and 278b. The left and right drive sprockets 51 are attached to the left and right axles 278. Therefore, the rotational power transmitted from the auxiliary transmission gear mechanism 251 to the left and right planetary gear mechanisms 268 is transmitted from the left and right axles 278 to each drive sprocket 51 in the same direction and at the same rotational speed, driving the left and right tracks 2 in the same direction and at the same rotational speed, causing the vehicle body 1 to move in a straight line (forward, backward).

[0050] The slewing hydraulic continuously variable transmission 70 is configured to arbitrarily adjust the rotation direction and rotation speed of the slewing motor shaft 261 protruding from the slewing motor 70b by changing the tilt angle of the rotating swash plate in the slewing pump 70a in accordance with the amount of rotational operation of the main shift lever 44 or the steering handle 43 located on the steering column 41, thereby changing the discharge direction and discharge amount of hydraulic fluid to the slewing motor 70b. Furthermore, a slewing pulse generating rotating wheel 294 is provided on the steering counter shaft 280, which will be described later, and a slewing rotation sensor (slewing vehicle speed sensor) (not shown) is configured to detect the rotation speed (slewing vehicle speed) of the steering output of the slewing motor 70b.

[0051] Furthermore, the transmission case 63 includes a wet multi-plate type slewing brake 279 (steering brake) mounted on the slewing motor shaft 261 (steering input shaft), a steering counter shaft 280 connected to the slewing 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 reversing 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 slewing motor shaft 261 is transmitted to the steering counter shaft 280. The rotational power transmitted to the steering counter shaft 280 is transmitted to the left ring gear 273 as reverse rotational power via the left intermediate gear 287 and the reverse gear 284 on the steering output shaft 285 in the left input gear mechanism 282, while the rotational power is transmitted to the right ring gear 273 as forward rotational power via the right intermediate gear 288 on the steering output shaft 285 in the right input gear mechanism 283.

[0052] When the auxiliary transmission gear mechanism 251 is in the neutral position, power transmission from the straight motor 64b to the left and right planetary gear mechanisms 268 is blocked. When the auxiliary transmission gear mechanism 251 outputs an auxiliary transmission value other than neutral, power is transmitted from the straight motor 64b to the left and right planetary gear mechanisms 268 via the auxiliary low-speed gear 254, the auxiliary medium-speed gear 255, or the auxiliary high-speed gear 256. On the other hand, when the output of the slewing pump 70a is in the neutral position and the slewing brake 279 is engaged, power transmission from the slewing motor 70b to the left and right planetary gear mechanisms 268 is blocked. When the output of the slewing pump 70a is set to a state other than neutral and the slewing brake 279 is disengaged, 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 reversing gear 284, while it is transmitted to the right ring gear 273 via the right input gear mechanism 283.

[0053] As a result, when the slewing motor 70b rotates forward (or backward), the left ring gear 273 rotates in the opposite direction but at the same speed, while the right ring gear 273 rotates in the forward (or backward) direction. That is, the speed change output from each motor shaft 260, 261 is transmitted to the drive sprockets 51 of the left and right tracks 2 via the sub-transmission gear mechanism 251 or the differential mechanism 257, respectively, and the vehicle speed (traveling speed) and direction of travel of the mobile body 1 are determined.

[0054] In other words, when the straight motor 64b is driven with the slewing motor 70b stopped and the left and right ring gears 273 fixed in place, the rotational output from the straight motor shaft 260 is transmitted to the left and right sun gears 271 at the same rotational speed on both sides. Through the planetary gears 272 and carriers 274, the left and right tracks 2 are driven in the same direction at the same rotational speed, causing the vehicle body 1 to travel in a straight line.

[0055] Conversely, when the straight-line motor 64b is stopped and the left and right sun gears 271 are fixed in place, and the slewing motor 70b is driven, the rotational power from the slewing motor shaft 261 causes the left ring gear 273 to rotate forward (reverse) and the right ring gear 273 to rotate backward (forward). 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 vehicle body 1 to change direction in place (pivot spin turn).

[0056] Furthermore, by driving the left and right sun gears 271 with the straight motor 64b and driving the left and right ring gears 273 with the slewing motor 70b, a speed difference is created between the left and right tracks 2, causing the vehicle body 1 to turn left or right (U-turn) with a turning radius larger than the pivot turning radius while moving forward or backward. The turning radius at this time is determined according to the speed difference between the left and right tracks 2. The vehicle moves to the left or right while the driving force of the engine 7 is constantly transmitted to the left and right tracks 2.

[0057] Next, with reference to Figures 8 to 15, the working hydraulic circuit 180 and the traveling hydraulic circuit 200 in the conventional combine harvester of this embodiment will be described. As shown in Figures 8 to 12, the working hydraulic circuit 180 includes, as hydraulic actuators, a harvesting lifting hydraulic cylinder 4, left and right reel lifting hydraulic cylinders 27L and 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 and 56R that raise and lower the traveling machine body 1, a hydraulic oil tank 57 for storing hydraulic oil, a working section charge pump 59 connected to the hydraulic oil tank 57 via a strainer 58, hydraulic valves 60A to 60E for switching the flow of hydraulic oil, and 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 the hydraulic valve unit 60 mounted on the traveling machine body 1.

[0058] The work unit charge pump 59 is hydraulically connected to the harvesting lifting hydraulic cylinder 4 via the harvesting lifting hydraulic valve 60A. By tilting the harvesting posture lever (not shown) in the operating unit (operator's cab) 5 in the forward and backward directions, the harvesting lifting hydraulic cylinder 4 is activated, allowing the operator to raise and lower the harvesting unit 3 to any height (e.g., harvesting working height or non-working height). On the other hand, the work unit charge pump 59 is hydraulically connected to the reel lifting hydraulic cylinders 27L and 27R via the reel lifting hydraulic valve 60B. By tilting the harvesting posture lever (not shown) in the left and right directions, the reel lifting hydraulic cylinders 27L and 27R are activated, allowing the operator to raise and lower the raking reel 14 to any height and harvest the unharvested grain stalks in the field.

[0059] The work unit charge pump 59 is hydraulically connected to the auger lifting hydraulic cylinder 55 via the auger lifting hydraulic valve 60C. By tilting the grain discharge lever 155 in the operating unit (operator's cab) 5 in the forward and backward directions, the auger lifting hydraulic cylinder 55 is activated, allowing the operator to raise and lower the grain discharge opening of the grain discharge auger 164 on the grain discharge conveyor 8 to any desired height. The electric motor 165 rotates the grain discharge auger 164 horizontally together with the vertical feed auger 162 and the bevel gear mechanism 163, moving the grain discharge opening laterally. In other words, the grain discharge opening is positioned above the truck bed or container, and the grain from the grain tank 6 is discharged into the truck bed or container.

[0060] The hydraulic oil tank 57 and the work unit charge pump 59 are hydraulically connected to the left machine lifting hydraulic cylinder 56L via the left machine lifting hydraulic valve 60D. On the other hand, the hydraulic oil tank 57 and the work unit charge pump 59 are hydraulically connected to the right machine lifting hydraulic cylinder 56R via the right machine lifting hydraulic valve 60E. By operating the left and right machine lifting hydraulic cylinders 56L and 56R independently of each other, the left and right sides of the mobile machine 1 are raised and lowered independently.

[0061] Therefore, when the hydraulic cylinders 56L and 56R for raising and lowering the left and right track frames 50, 50 are simultaneously operated, the vehicle body 1 moves upward (rises) relative to the contact points of the tracks 2, 2 on both sides, and the relative height (vehicle height) of the vehicle body 1 relative to the contact points of the tracks 2, 2 increases. Conversely, when the left and right track frames 50, 50 are simultaneously raised relative to the vehicle body 1, the vehicle body 1 moves closer to the contact points of the tracks 2, 2 on both sides (descends), and the relative height (vehicle height) of the vehicle body 1 relative to the contact points of the tracks 2, 2 decreases.

[0062] Then, by activating the left hydraulic cylinder 56L for lifting the left body to lower the left track frame 50 relative to the vehicle body 1, or by activating the right hydraulic cylinder 56R for lifting the right track frame 50 relative to the vehicle body 1 (or by performing both actions simultaneously), the vehicle body 1 will tilt downwards to the right. Conversely, by activating the right hydraulic cylinder 56R for lifting the right body to lower the right track frame 50 relative to the vehicle body 1, or by activating the left hydraulic cylinder 56L for lifting the right track frame 50 relative to the vehicle body 1 (or by performing both actions simultaneously), the vehicle body 1 will tilt downwards to the left.

[0063] The hydraulic oil tank 57, the work unit charge pump 59, and the hydraulic valve unit 60 are each mounted on the traveling body 1 and are connected to each other via hydraulic piping 181 to 183. On the traveling body 1, the hydraulic oil tank 57 is installed on the front left side, while the work unit charge pump 59 is fixed to the front of the engine 7 mounted on the front right side, and the strainer 58 housed inside the hydraulic oil tank 57 and the work unit charge pump 59 are connected by hydraulic piping 181. Furthermore, the hydraulic valve unit 60 is positioned on the traveling body 1 behind the engine 7, and the discharge side of the work unit charge pump 59 is connected to the hydraulic valve unit 60 via hydraulic piping 182. In addition, the hydraulic valve unit 60 is connected to the hydraulic oil tank 57 via hydraulic piping 183, which serves as a hydraulic oil return pipe, and an oil cooler 62.

[0064] The hydraulic oil tank 57 is installed on the traveling machine body 1 in a space enclosed by the feeder house 11 and the beater 18, with the engine 7 and the hydraulic oil tank 57 positioned side by side at the front of the traveling machine body 1. In other words, the hydraulic oil tank 57 is located in the space enclosed by the feeder house 11 and the machine housing of the threshing unit 9, which prevents dust from the harvesting unit 3 from accumulating in the hydraulic oil tank 57 and prevents contamination of the hydraulic oil by dust entering from the oil inlet 184, etc. Furthermore, because cooling air from the engine 7 flows into the space where the hydraulic oil tank 57 is installed, the rise in hydraulic oil temperature can be suppressed without installing an oil cooler on the working hydraulic circuit 180, and each hydraulic component can be driven properly.

[0065] The hydraulic oil tank 57 has an oil filler port 184 protruding to the left side (outside the machine) on its left side (outside the machine), and also houses a strainer 58 that can be inserted and removed from the left side. Therefore, by removing the threshing cover 185 located on the left side (outside the machine) of the threshing unit 9, the oil filler port 184 and the strainer 58 can be easily accessed. As a result, refueling the hydraulic oil tank 57 and replacing the oil filter in the strainer 58 are made easier, and the maintainability of the hydraulic circuit 180 is improved.

[0066] Furthermore, hydraulic pipes 181 and 183, which connect to the hydraulic oil tank 57, are routed to the left and right in front of the hydraulic oil tank 57 and the engine 7, with hydraulic pipe 182 connecting the work unit charge pump 59 and strainer 58 located in front of the engine 7. In other words, hydraulic pipes 181 and 183 bypass the front of the engine 7 and extend towards the hydraulic oil tank 57 along the output shaft 65 of the engine 7. Also, hydraulic pipes 182 and 183 extend to the rear, passing below the cooling fan 149 located on the right side of the engine 7, and are connected to the hydraulic valve unit 60. Therefore, hydraulic pipes 181 to 183 are arranged in a position where they are less affected by radiant heat from the engine 7 and have a shorter pipe length, thereby suppressing the temperature of the hydraulic oil flowing through the hydraulic pipes from rising.

[0067] As shown in Figures 7, 10, and 12-15, the travel hydraulic circuit 200 includes a straight pump 64a, a straight motor 64b, a slewing pump 70a, a slewing motor 70b, a transmission charge pump 151, an oil filter 152, and an oil cooler 153. In the straight hydraulic continuously variable transmission 64, the straight pump 64a and the straight motor 64b are connected in a closed loop by a straight closed oil passage 201. On the other hand, in the slewing hydraulic continuously variable transmission 70, the slewing pump 70a and the slewing motor 70b are connected in a closed loop by a slewing closed oil passage 202. The rotational power of engine 7 drives the linear pump 64a and the swivel pump 70a, 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 fluid to the linear motor 64b and the swivel motor 70b are changed, causing the linear motor 64b and the swivel motor 70b to operate in forward and reverse directions.

[0068] The drive system hydraulic circuit 200 includes a straight valve 203 that switches in response to manual operation of the main shift lever 44, and a straight cylinder 204 connected to the transmission charge pump 151 via the straight valve 203. When the straight valve 203 is switched, the straight cylinder 204 operates to change the swash plate angle of the straight pump 64a, and a straight-line shift operation is performed, which continuously changes or reverses the rotational speed of the straight motor shaft 260 of the straight motor 64b. The drive system hydraulic circuit 200 also includes a hydraulic servo mechanism 205 for straight-line shifting. The hydraulic servo mechanism 205 performs a feedback operation in which the straight valve 203 returns to neutral based on the swash plate angle control of the straight pump 64a, changing the swash plate angle of the straight pump 64a in proportion to the amount of manual operation of the main shift lever 44, and changing the rotational speed of the straight motor shaft 260 of the straight motor 60b.

[0069] The travel hydraulic circuit 200 includes a slewing valve 206 that operates in response to manual operation of the steering handle 43, and a slewing cylinder 207 connected to the transmission charge pump 151 via the slewing valve 206. When the slewing valve 206 is switched on, the slewing cylinder 207 operates, changing the swash plate angle of the slewing pump 70a, and performing a left-right slewing operation by continuously changing or reversing the rotation speed of the slewing motor shaft 261 of the slewing motor 70b, causing the travel machine 1 to change direction left or right, allowing it to change direction or correct its course at the headland of the field. The travel hydraulic circuit 200 also includes a hydraulic servo mechanism 208 for slewing speed control. A hydraulic servo mechanism 208 performs a feedback operation in which the swivel valve 206 returns to the neutral position by controlling the swash plate angle of the swivel pump 70a. The swash plate angle of the swivel pump 70a is changed in proportion to the amount of manual operation of the control handle 43, thereby changing the rotational speed of the swivel motor shaft 261 of the swivel motor 70b.

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

[0071] A straight bypass oil passage 213 is connected to the straight first oil passage 201a and the straight second oil passage 201b. A straight-side bidirectional relief valve 215 is provided in the straight bypass oil passage 213. A swivel bypass oil passage 214 is connected to the swivel first oil passage 202a and the swivel second oil passage 202b. A swivel bypass oil passage 214 is provided in the swivel side bidirectional relief valve 216. Therefore, each closed oil passage 201, 202 is equipped with one bidirectional relief valve 215, 216.

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

[0073] Furthermore, the charge branch oil passage 219 is connected to the straight cylinder 204 via the straight valve 203 and to the swivel cylinder 207 via the swivel valve 206. In addition, the charge branch oil passage 219 is connected to the transmission case 63 via the excess relief valve 220 and the hydraulic piping 223, and an oil cooler 153 is installed along the hydraulic piping 223. Therefore, when the excess hydraulic fluid from the transmission charge pump 151 is returned to the transmission case 63 via the excess relief valve 220, it is cooled by the oil cooler 153.

[0074] Furthermore, the hydraulic piping 223 is connected by a bypass pipe 224 that bypasses the supply 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 piping 223 and the bypass pipe 224 above the continuously variable transmission case 323, when the hydraulic fluid temperature is low, such as when the engine 7 is started, the hydraulic fluid can be circulated without being sent to the oil cooler 153. Therefore, even when the hydraulic fluid viscosity is high at a low hydraulic fluid temperature, the hydraulic fluid can be smoothly circulated within the drive system hydraulic circuit 200, lubricating the transmission mechanisms inside the transmission case 63 and the continuously variable transmission case 323.

[0075] As described above, an oil cooler 153 is connected to hydraulic piping 221-223 that circulates the hydraulic fluid in the transmission case 63 and the continuously variable transmission case 323 (drive unit), and a bypass pipe (bypass path) 224 that bypasses the oil cooler 153 is provided in the hydraulic piping 223, and this bypass pipe 224 is provided integrally with the transmission case 63 and the continuously variable transmission case 323. Therefore, although connecting the transmission case 63 and the continuously variable transmission case 323 to the oil cooler 153 lengthens the piping route that circulates the fluid in the transmission case 63 and the continuously variable transmission case 323, it can be shortened by the bypass pipe 224.

[0076] By providing a bypass pipe 224 in the hydraulic piping 223 to bypass the oil cooler 153, high-viscosity hydraulic fluid can be circulated, such as when starting the engine in cold climates, and good lubrication can be maintained within the transmission case 63 and the continuously variable transmission case 323. Furthermore, by integrating the transmission case 63 and the continuously variable transmission case 323 into a single unit, the bypass pipe 224 can be incorporated into the transmission case 63, improving ease of assembly and simplifying maintenance of the hydraulic system in the transmission case 63.

[0077] A connecting member (connecting joint) 225, equipped with two communication ports 225a and 225b, is provided on the continuously variable transmission case 323. One end of a bypass pipe 224 is connected to the communication port 225a of the connecting member 225, while a supply pipe 223a communicating with the oil cooler is connected to the communication port 225b of the connecting member 225. A bypass relief valve 226 (see Figure 13) is provided at the connection point between the connecting member 225 and the bypass pipe 224. The connecting member 225 is provided on the upper surface of the continuously variable transmission case 323, on the side of the straight-line hydraulic continuously variable transmission 64 (front side), with the communication port 225a positioned below the communication port 225b. The communication ports 225a and 225b of the connecting member 225 each protrude toward the rear (towards the turning hydraulic continuously variable transmission 70).

[0078] Of the hydraulic piping 223, the return piping 223b to 223d of the oil cooler 153 is configured with a metal intermediate pipe 223c between the upstream return piping 223b, which is connected at one end to the oil cooler 153, and the downstream return piping 223d, which is connected at one end to the upper surface of the transmission case 63. The metal intermediate pipe 223c is fixed to the side of the continuously variable transmission case 323 that is on the side of the slewing hydraulic continuously variable transmission 70 (rear side).

[0079] A connecting plate (fixing member) 227, fixed to the side of the metal connecting pipe 223c, is fastened and fixed to the upper surface of the housing portion for the swivel valve 206 in the continuously variable transmission case 323 (the rear end side of the continuously variable transmission case 323). As a result, the metal connecting pipe 223c is fixedly positioned above the continuously variable transmission case 323, along a direction parallel to the pump shaft 259. The metal connecting pipe 223c also has a T-shape with a communication port (branch pipe) 223e protruding forward from its middle section (towards the straight hydraulic continuously variable transmission 64 side). That is, the communication port 223e in the middle section of the metal connecting 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 extends in the front-to-rear direction above the continuously variable transmission case 323 to connect the communication port 225a of the connecting members 225, which are positioned front to rear, with the communication port 223e of the metal relay pipe 223c. The bypass pipe 224 is constructed 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 also 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 route for bypassing the oil cooler 153 consists of a metal relay pipe 223c, a bypass pipe 224, and a connecting member 225, which are assembled integrally with the continuously variable transmission case 323. Therefore, hydraulic components other than the supply pipe 223a and the upstream return pipe 223b that connect to the oil cooler 153 can be assembled integrally with the continuously variable transmission case 323, improving the ease of assembly and maintainability of the transmission case 63 into which the continuously variable transmission case 323 is assembled.

[0082] The hydraulic pipes 222 and 223, which connect to the transmission case 63 and the continuously variable transmission case 323, are routed to pass beneath the straight-line connecting link 345 and the swivel connecting link 346, which connect to the steering case 318. Therefore, contact between the straight-line connecting link 345 and the swivel connecting link 346 and the hydraulic pipes 222 and 223 is prevented, and maintenance of the straight-line connecting link 345 and the swivel connecting link 346 is made easier. In addition, even if the hydraulic pipes 222 and 223 vibrate due to the drive of the transmission case 63, damage due to contact with the straight-line connecting link 345 and the swivel connecting link 346 can be prevented.

[0083] More specifically, the hydraulic piping 222 connecting the charge pump 151 and the oil filter 152 is routed in the longitudinal direction so as to pass below the linear relay shaft 352 of the linear connecting link body 345, and the hydraulic piping 222 connecting the oil filter 152 and the transmission case 63 is routed in the longitudinal direction so as to pass below the first relay rod of the slewing direct connection link body 346. In addition, the downstream return piping 223b connecting to the transmission case 63 is bent so as to pass below the shaft support 366 of the slewing direct connection 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 Figure 8 and other figures. As shown in Figure 8 and other figures, a pair of left and right engine room support columns 147 are erected on the upper surface of the traveling machine 1, behind the driver's cab 5, and a back panel 148 is stretched between the left and right engine room support columns 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 on the right engine room support column 147, which is located at the right end of the driver's cab 5 on the traveling machine 1, via an opening / closing pivot shaft 171. A dust removal net is stretched over the machine-side opening on the right side of the wind tunnel case 170, and the presence of the dust removal net prevents straw and other debris from entering the inside of the wind tunnel case 170 and, consequently, the inside of the engine room 146. Furthermore, the oil cooler 153 of the travel system hydraulic circuit 200 and the oil cooler 62 of the work system hydraulic circuit 180 are arranged vertically inside the wind tunnel case 170.

[0085] A water-cooling radiator 154 is erected inside the wind tunnel case 170 on the upper side of the traveling body 1, and the radiator 154 is positioned opposite the cooling fan 149 of the engine 7. A shroud 150 is installed to cover the entire ventilation range of the radiator 154, and the cooling fan 149 is positioned in an opening formed in this shroud 150. An oil cooler 153 is also installed inside the wind tunnel case 170. The rotation of the cooling fan 149 draws in outside air (cooling air) into the wind tunnel case 170 from the outer opening on the right side of the wind tunnel case 170, and sends the dust-removed cooling air into the engine room 146 from the inner opening on the left side of the wind tunnel case 170. As a result, the oil cooler 153, radiator 154, and engine 7 are cooled by the cooling air flowing into the engine room 146.

[0086] Next, the operating structure, including the steering handle 43, will be described with reference to Figures 8, 10, and 16-21. As shown in Figures 8, 10, and 16-21, the driver's cab 5 is equipped with a step frame 311 that constitutes a flat footrest for the operator. Multiple support leg frames 312 are erected on the upper side of the traveling body 1, and the step frame 311 is mounted on the upper end of the support leg frames 312. The step frame 311 and the support leg frames 312 constitute a support frame. An entry / exit step 313 is fixed to the side of the support leg 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] The steering case 318 also includes a pivot input shaft 316 and a main transmission input shaft 317. The ends of a case support lateral frame 319 are connected between the left and right support leg frames 312 on the front lower side of the step frame 311, and the steering case 318 is detachably fastened and fixed to the substantially horizontal case support lateral frame 319. The pivot input shaft 316 is projected upward from the top surface of the steering case 318, and the pivot input shaft 316 is connected to the steering handle 43 via a steering shaft 321. The main transmission input shaft 317 is projected to the left from the left side of the steering case 318, and the main transmission input shaft 317 is connected to the main transmission lever 44 via a main transmission operating rod 322.

[0088] As can be seen from the above explanation, the driver's cab 5 (control section) is located on a step frame 311 provided on the upper end of the support leg frame group 312, and the main transmission lever 44, which is a straight-line control device for straight-line operation, and the steering handle 43, which is a turning control device for turning operation, are positioned there. A case support transverse frame 319 is attached by spanning it between the left and right support leg frames 312 located on the lower front side of the step frame 311. The steering case 318, which interlocks the main transmission lever 44 and the steering handle 43 with the drive unit (continuously variable transmission case 323 and transmission case 63), is attached to the case support transverse frame 319. There are two case support transverse frames 319, one in front and one behind the steering case 318. The steering case 318 is then supported by these two case support transverse frames 319.

[0089] Furthermore, an oil filter 152 is positioned on the left side of the steering case 318 at the front of the running body 1, fixed to the step frame 311 at its front end. The oil filter 152 is fixed to a portion protruding to the left from the left support frame 312 at the front of the step frame 311 so that it is positioned in front of the continuously variable transmission case 323. In other words, the oil filter 152 is fixed to the left side of the front end of the step frame 311 via a filter fixing bracket 349, and is positioned in front of the continuously variable transmission case 323 which is fixed to the right side of the transmission case 63. Therefore, when connecting the transmission charge pump 151 and the charge introduction oil passage 218, the hydraulic piping 222, which has the oil filter 152 in its path, can be made shorter.

[0090] A case support lateral frame 319 is installed by spanning it between the left and right support leg frames 312 located on the lower front side of the step frame 311. The steering case 318, which links the main transmission lever 44 and steering handle 43 to the drive unit (continuously variable transmission case 323 and transmission case 63), is attached to the case support lateral frame 319. Therefore, the presence of the case support lateral frame 319 improves the rigidity of the front of the running machine 1 (especially near the driver's cab 5). The steering case 318 can be supported with high rigidity by utilizing the case support lateral frame 319, which plays a role in reinforcing the front of the running machine 1. Consequently, there is no significant discrepancy between the amount of operation of the main transmission lever 44 and steering handle 43 and the output of the drive unit (continuously variable transmission case 323 and transmission case 63), eliminating the risk of the machine running in a state not anticipated by the operator. The reinforcing case support lateral frame 319 can also be used as the mounting point for the steering case 318, eliminating the need for a dedicated mounting base for the steering case 318 and thus contributing to cost reduction.

[0091] The transmission case 323 comprises a continuously variable transmission case 323 into which a straight-line hydraulic continuously variable transmission 64 and a slewing 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-line and slewing operating arms 355 and 369 are positioned on the front and rear surfaces of the continuously variable transmission case 323. In other words, the straight-line hydraulic continuously variable transmission 64 and the slewing hydraulic continuously variable transmission 70 are arranged front to back on the right side of the transmission case 63, opposite to the feeder house 11.

[0092] Therefore, since space is created on the side (left side) of the feeder house 11 in the mission case 63, the design flexibility of the harvesting unit 3 is increased, and the feeder house 11 can be configured to an optimal size for the harvesting amount of the harvesting unit 3 and the harvesting width of the grain header 12. In addition, since the installation width of the feeder house 11 in the left-right direction is increased, the feeder house 11 can be installed on the side closer to the center of gravity when the grain header 12 is raised and lowered, thereby increasing the support strength of the harvesting unit 3 by the feeder house 11.

[0093] A straight-line operation shaft 325, which serves as a straight-line output control unit, protrudes forward from the front outer surface of the continuously variable transmission case 323, and a slewing operation shaft 326, which serves as a slewing output control unit, protrudes backward from the rear outer surface of the continuously variable transmission case 323. Although detailed illustrations are omitted, a straight-line operation arm body 355 is connected to the straight-line operation shaft 325, and a slewing operation arm body 369 is connected to the slewing operation shaft 326. The straight-line and slewing operation arms 355 and 369 are respectively connected to a straight-line connecting link body 345 and a slewing connecting link body 346, which are provided on the rear side of the steering case 318. The straight-line hydraulic continuously variable transmission 64 and the slewing hydraulic continuously variable transmission 70 are operated and controlled by steering operations of the steering handle 43 and shifting operations of the main shift lever 44, making it possible to change the path and speed of the left and right tracks 2.

[0094] A driver's cab (control section) 5 located at the front of the vehicle body 1 is equipped with a main shift lever (straight-line control device) 44 for straight-line operation and a steering handle (turning control device) 43 for turning operation, and a steering column 41 is located on the side of the driver's cab closer to the drive unit (transmission case 63 and continuously variable transmission case 323). Below the driver's cab 5 at the front of the vehicle body 1, a steering case 318 is located to the side of the continuously variable transmission case 323, which is equipped with a straight-line hydraulic continuously variable transmission 64 and a turning hydraulic continuously variable transmission 70, and which changes the output from the transmission case 63 according to the amount of operation of the steering handle 43 and the main shift lever 44.

[0095] In this case, the steering wheel 43 is positioned in the front central part of the driver's cab 5, directly in front of the driver's seat 42, while the main transmission lever 44 is positioned on the left side of the control column 41, which is closer to the drive unit (continuously variable transmission case 323 and transmission case 63). Specifically, the steering case 313 is positioned below the steering wheel 43, and the continuously variable transmission case 323 is positioned below the control column 41 on which the main transmission lever 44 is installed. This allows the various parts of the operating mechanism connecting the steering wheel 43 and the main transmission lever 44 to the continuously variable transmission case 323 via the steering case 313 to be positioned in close proximity to each other, and the link mechanisms 321, 322, 345, and 346 connecting the various parts of the operating mechanism to be made shorter, thereby suppressing fluctuations and deformations. Consequently, the discrepancy between the amount of operation of the main transmission lever 44 and the steering wheel 43 and the output of the drive unit (continuously variable transmission case 323 and transmission case 63) is suppressed, and a stable driving state corresponding to the operator's operation can be maintained.

[0096] The battery 230, which supplies power to the engine 7, is located at the front of the machine body 1, below the driver's cab 5, behind the steering case 318 and to the side of the continuously variable transmission case 32. In other words, the battery 230 that supplies power to the engine 7 and other components is located in the area below the driver's cab 5, surrounded by the steering case 318, the drive unit (continuously variable transmission case 323 and transmission case 63), and the engine 7. This allows the dead space below the driver's cab 5 to be effectively utilized not only as space for the steering case 318 and continuously variable transmission case 323, but also as space for the battery 230. As a result, the battery 230 can be placed close to the engine 7 and driver's cab 5, making the electrical system more compact. Furthermore, it avoids the need to enlarge the combine harvester to accommodate space for the battery 230.

[0097] The driver's cab (control section) 5 is constructed on multiple support frames 312 erected on the upper side of the running body 1. The steering case 318 is fixed to a case support lateral frame (case support frame) 319 that is mounted midway across the multiple support frames 312, and is positioned above the continuously variable transmission case 323 and the battery 230. In this way, the battery 230 and the steering case 318 are arranged in multiple levels vertically below the front of the step frame 311, so that the space formed in the area adjacent to the continuously variable transmission case 323 at the rear of the steering case 318 can be used to easily extend the electrical wiring that supplies power to the engine 7, the driver's cab 5, and other electrical components. This also contributes to improved assembly and maintenance workability of the steering case 318 and the battery 230.

[0098] Furthermore, since the oil filter 152 for filtering the hydraulic fluid in the drive unit (continuously variable transmission case 323 and transmission case 63) is located in the area below the driver's cab 5, the length of the hydraulic piping 222 connecting the drive unit (continuously variable transmission case 323 and transmission case 63) and the oil filter 152 can be shortened, making the routing of the hydraulic piping 222 easier.

[0099] In the upper part of the steering case 318, a lateral main transmission input shaft 317 is positioned on one of the front and rear sides of the steering input shaft 316, and a lateral straight-line output shaft 350 is positioned on the other side. The main transmission input shaft 317 and the straight-line output shaft 350 extend parallel to each other from left to right in a plan view and are pivotally supported in the steering case 318. The main transmission input shaft 317 and the straight-line output shaft 350 are pivotally supported so as to protrude outward (to the left) from the left side of the steering case 318. A steering output shaft 164, which extends perpendicular to the straight-line output shaft 350, is pivotally supported on the rear of the steering case 318, below the straight-line output shaft 350, so as to protrude outward (rearward) from the steering case 318.

[0100] The straight-line connecting link 345 is connected to the straight-line output shaft 350 by inserting the protruding end (left end) of the straight-line output shaft 350 into one end (right end) of the cylindrical shaft connecting 351. The other end (left end) of the shaft connecting 351 has a straight-line intermediate shaft 352 that is pivotally supported by a speed-shift output support bracket 328 fixed to the support leg frame 312 at the left front position of the driver's cab 5. By adjusting the left-right position of the straight-line intermediate shaft 352 relative to the shaft connecting 351, the left-right installation position of the straight-line connecting link 435 is adjusted.

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

[0102] The linear connecting link body 345 connects the linear relay shaft 352, which extends in the left-right direction at a position on the extension of the linear output shaft 350, to the linear relay shaft 352 via the shaft connecting body 351 and is pivotally supported by the speed-shift output support bracket 328 fixed to the support leg frame 312. As a result, the linear relay shaft 352 rotates together with the linear output shaft 350, causing the front end of the linear relay arm body 353, which is fixed to the left end of the linear relay shaft 352, to swing. Then, the linear connecting rod 354, whose ends are pivotally attached to the front end of the linear relay 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 relay arm body 353, thereby rotating the linear operating shaft 325, whose protruding end (front end) is fixed to the other end of the operating arm body 355.

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

[0104] Meanwhile, one end (right end) of a second relay rod 368, which extends to the left and right, is connected to the other end (tip) of a pivoting operating arm body 369, one end (base end) of which is fixed to the protruding end (rear end) of the pivoting operating shaft 326. The second relay rod 368 extends to the left and right along the rear surfaces 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 pivoting relay arm body 367, which is fixed to one end (rear end) of the pivoting relay shaft 365.

[0105] The shaft support 366, which supports the pivot relay shaft 365, is fixed on the transmission case 63, to the left of the continuously variable transmission case 323, by bolting the other end of a support plate 370, one end of which is fixed to the outer circumferential surface of the shaft support 366, to the upper surface of the transmission case 63. In addition, the outer circumferential surface of the shaft support 366 is provided with a pipe fixing portion 372 through which hydraulic piping 223 connected to the transmission case 63 is passed to fix its position.

[0106] The pivoting link body 346 pivotally attaches the right end of a first relay rod 363, which extends in the left-right direction, to an output arm body 362 whose tip swings from side to side in accordance with the rotation of the pivoting output shaft 361 which protrudes from the rear of the steering case 318. As a result, the first relay rod 363 moves in the left-right direction in accordance with the swinging of the output arm body 362, causing the tip of the first pivoting relay arm body 364, whose base end is fixed to the front end of the pivoting relay shaft 365, to swing from side to side. This swinging of the tip of the first pivoting relay arm body 364 causes the pivoting relay shaft 365, which is pivotally supported by the shaft support 366, to rotate, and at the same time, the tip of the second pivoting relay arm body 364, whose base end is fixed to the rear end of the pivoting relay shaft 365, to swing from side to side. Then, the second relay rod 368, whose ends are pivotally attached to the front end of the second pivot relay arm 367 and one end of the pivot operating arm 369, moves left and right in response to the swinging of the second pivot relay arm 367, thereby rotating the pivot operating shaft 326, whose protruding end (rear end) is fixed to the other end of the operating arm 369.

[0107] The main transmission input shaft 317 protrudes from the steering case 318 toward the left-right center of the vehicle body 1. The protruding end (left end) of the main transmission input shaft 317 is pivotally supported by a main transmission input support bracket 381 fixed to the step frame 31·BR>P on the left edge, which is on the side of the transmission case 63. One end (front end) of the 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 which is connected to the main transmission lever 44.

[0108] A straight-line hydraulic continuously variable transmission 64 and a slewing hydraulic continuously variable transmission 70, which change the power of the engine 7, are mounted side by side on the driver's cab (control section) 5 side of the left and right sides of the transmission case 63. The straight-line operating shaft 325 of the straight-line hydraulic continuously variable transmission 64 and the slewing operating shaft 326 of the slewing hydraulic continuously variable transmission 70 are mounted protruding from the front and rear. Because the straight-line hydraulic continuously variable transmission 64 and the slewing hydraulic continuously variable transmission 70 are arranged side by side on the driver's cab 5 side, the connection structure with the steering case 318 can be made shorter.

[0109] Furthermore, by arranging the straight-line operating shaft 325 and the slewing operating shaft 326 front to back, the same positional relationship as the straight-line output shaft 350 and the slewing output shaft 361, which are arranged front to back in the steering case 318, can be achieved. This simplifies the structure of the link mechanism from the steering case 318 to the straight-line hydraulic continuously variable transmission 64 and the slewing hydraulic continuously variable transmission 70, and allows the continuously variable transmission case 323 and the steering case 318 to be installed compactly in close proximity below the driver's cab 5.

[0110] The steering case 318 is positioned below the driver's cab (control section) 5 and above the drive unit (continuously variable transmission case 323 and transmission case 63), with a straight-line output shaft 350 and a slewing output shaft 361 protruding from the steering case 318. A straight-line connecting link 345, which connects the straight-line output shaft 350 to the straight-line operating shaft 325, and a slewing connecting link 346, which connects the slewing output shaft 361 to the slewing operating shaft 326, are installed between the steering case 318 and the continuously variable transmission case 323 in a plan view. In other words, since the straight-line connecting link 345 and the slewing connecting link 346 are positioned on the driver's cab 5 side together with the transmission case 63, assembly and maintenance are improved.

[0111] A straight-line connecting link 345, which interlocks the steering case 318 with the straight-line operation shaft 325, which is the straight-line output control unit, is supported by the support leg frame 312 that supports the driver's cab 5. The steering case 318 is fixed to a case support lateral frame (case support frame) 319 that is installed midway between the left and right support leg frames 312 that support the front position of the driver's cab (control section) 5. The straight-line connecting link 345 is then supported by the left support leg frame 312 on the side of the transmission case 63 (continuously variable transmission case 323).

[0112] A linear connecting link 345, which interlocks the steering case 318 with a linear operation shaft 325 (linear output control unit) provided on the drive unit (continuously variable transmission case 323 and transmission case 63), is supported by a support leg frame 312 that supports the driver's cab 5. Therefore, even if the linear connecting link 345 is subjected to bending or tension due to vibrations of the drive unit (continuously variable transmission case 323 and transmission case 63), the linear connecting link 345 can be supported with high rigidity by the support leg frame 312 that supports the driver's cab 5, and fluctuations and deformations of the linear connecting link 345 can be suppressed. Consequently, there is no significant discrepancy between the amount of operation of the main shift lever 44 or steering wheel 43 and the output of the drive unit (continuously variable transmission case 323 and transmission case 63), eliminating the risk of the vehicle entering a driving state that the operator did not anticipate.

[0113] A continuously variable transmission case 323, which houses a straight-line hydraulic continuously variable transmission 64 and a slewing hydraulic continuously variable transmission 70, is fixed to the upper right side of the transmission case 63. The slewing connecting link 346 is supported on the upper surface of the transmission case 63, on the side of the continuously variable transmission case 323. By utilizing the space between the feeder house 11 and the driver's cab 5, the slewing connecting link 346 can be supported compactly and rigidly on the transmission case 63, which shares the same vibration system as the continuously variable transmission case 323. Consequently, deflection and tension of the slewing connecting link 346 due to mechanical vibration are suppressed, preventing a significant discrepancy between the amount of operation of the main shift lever 44 and the steering handle 43 and the output of the drive system (continuous variable transmission case 323 and transmission case 63), thus eliminating the risk of the vehicle operating in a way that the operator did not anticipate.

[0114] Referring to Figures 22 to 26, the mounting structure of the ECU 401, which controls the operation of the combine harvester, will be explained. As can be seen from the above explanation, in this embodiment, the step section 400, which is the space enclosed by the front of the traveling body 2, the support leg frame group 312, and the step frame group 311, is a dead space, so the steering case 318, the continuously variable transmission case 323, and the battery 230 are arranged in this space.

[0115] An ECU 401, which controls the operation of the combine harvester, is located on the front side of the step section 400. In this embodiment, a shielding plate 402 is positioned to span across the front side of the step section 400, that is, between the front center side of the step frame 311 and the front center side of the case support lateral frame 319. The upper end of the shielding plate 402 is welded to the front center side of the step frame 311. The lower end of the shielding plate 402 is welded to the front center side of the case support lateral frame 319. In other words, the shielding plate 402 is supported by the step section 400 (step frame 311 and case support lateral frame 319). The ECU 401 is fastened to the front side of the shielding plate 402.

[0116] Therefore, the ECU 401 is located on the front side of the step section 400, and the engine 7 is located on the rear side. Furthermore, the steering case 318 and the shielding plate 402 are located between the ECU 401 and the engine 7, and both the steering case 318 and the shielding plate 402 act as shields against the heat discharged from the engine 7. With this configuration, the ECU 401 is positioned as far away from the engine 7 as possible around the driver's cab 5 (control section), thereby reducing the thermal influence from the engine 7 to the ECU 401. This improves the control stability and extends the lifespan of the ECU 401. In particular, the shielding plate 402 blocks the heat discharged from the engine, which is highly effective in reducing the thermal influence from the engine 7 to the ECU 401.

[0117] The outer shape of the shielding plate 402 is larger than the outer shape of the ECU 401. Therefore, the peripheral edge of the shielding plate 402 protrudes from the outer circumference of the ECU 401. Due to the presence of the peripheral edge of the shielding plate 402, it is difficult for the heat exhausted from the engine 7 to flow around to the front side of the ECU 401. In this embodiment, the shielding plate 402 has a cutout at the lower center, giving it a downward-facing, roughly U-shape. The cutout portion 403 is provided for the purpose of reducing the weight of the shielding plate 402 and for the purpose of allowing outside air to reach the back side of the ECU 401 and for releasing heat from the ECU 401.

[0118] The front of the ECU 401 is covered by the front cover 404 of the driver's cab 5. The power supply battery 230, located in the step section 400, is positioned below the steering case 318 and the case support lateral frame 319. Therefore, the ECU 401 is positioned higher than the battery 230. The battery 230 is located in a position on the vehicle body 1 where it is not affected by, for example, muddy water or rainwater in the field (it is not exposed to muddy water, etc.). Since the ECU 401 is also positioned higher than the battery 230, there is an advantage in that the effects of muddy water, etc. on the ECU 401 can be more reliably eliminated. In addition, because the ECU 401 and the battery 230 are located in close proximity, the electrical system can be made more 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 harvesting unit is mounted on the front of a traveling body equipped with an engine, a threshing unit is mounted on the traveling body behind the harvesting unit, a control unit is positioned on the front side of the threshing unit, and an engine is mounted below and behind the control unit, wherein a transmission case is positioned between the harvesting unit and the threshing unit on the traveling body, and a battery for power supply is mounted on the side of the transmission case and below the control unit.

[0121] In the combine harvester of the present invention, the control unit is composed of a plurality of support leg frames erected on the front upper surface side of the traveling body, and the ECU that controls the operation of the combine harvester may be supported by the plurality of support leg 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 leg frames.

[0123] According to the present invention, in a combine harvester in which a harvesting unit is mounted on the front of a traveling body equipped with an engine, a threshing unit is mounted on the traveling body behind the harvesting unit, a control unit is positioned on the front side of the threshing unit, and an engine is mounted below and behind the control unit, a transmission case is positioned between the harvesting unit and the threshing unit on the traveling body, and a battery for power supply is mounted on the side of the transmission case and below the control unit. Therefore, 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 the transmission case but also as a space for the battery.

[0124] In one embodiment, a combine harvester has a cutting unit mounted on the front of a traveling body equipped with an engine, a threshing unit mounted on the traveling body behind the cutting unit, a control unit positioned to the front side of the threshing unit, and an engine mounted below and behind the control unit. A transmission case is positioned between the cutting unit and the threshing unit on the traveling body, and a battery for power supply is mounted to the side of the transmission case and in front of the engine. [Explanation of symbols]

[0125] 1. Mobile Unit 3 Reaping part 5. Driver's cab 7 Engine 9. Threshing section 11 Feeder House 311 Step frame (support frame) 312 Support Leg Frame (Support Frame) 318 Steering Case 319 Case support horizontal frame 400 step section 401 ECU 402 Shielding plate 403 Notch 404 Front cover

Claims

1. In a combine harvester having a cutting unit mounted on the front of a traveling body equipped with an engine, a threshing unit mounted behind the cutting unit on the traveling body, a control unit positioned to the front side of the threshing unit, and an engine mounted below and behind the control unit, A battery is mounted in front of the engine located on one side of the aforementioned mobile body. A hydraulic valve for operating the work equipment is located behind the engine. combine.

2. The hydraulic valve is located below the grain tank that removes grain from the threshing section. The combine harvester according to claim 1.

3. The hydraulic valve includes a hydraulic valve for raising and lowering the harvesting unit, The combine harvester according to claim 1 or 2.

4. The hydraulic valve includes a hydraulic valve for raising and lowering the traveling machine body, A combine harvester according to any one of claims 1 to 3.

5. The hydraulic valve includes an auger lifting hydraulic valve for raising and lowering a grain discharge auger connected to a grain discharge conveyor located at the rear of the grain tank. The combine harvester according to claim 2.

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