JP2023030202A - combine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To enable effective use of a dead space around an operation part 5 that is a dead space unique to a combine.

SOLUTION: In a combine of the present invention, a mowing part 3 is mounted in a front portion of a travel machine body 1 mounted with an engine 7, a threshing part 9 is mounted behind the mowing part 3 in the travel machine body 1, an operation part 5 is arranged in a front side part of the threshing part 9, and the engine 7 is mounted in a lower rear side of the operation part 5. A transmission case 63 is arranged between the mowing part 3 and the threshing part 9 in the travel machine body 1. A battery 230 for power supply is mounted in a side portion of the transmission case 63 and a lower portion of the operation part 5.

SELECTED DRAWING: Figure 24

COPYRIGHT: (C)2023,JPO&INPIT

Description

TECHNICAL FIELD The present invention relates to a combine harvester equipped with a harvesting section for harvesting uncut grain culms in a field and a threshing section for shedding grains of the harvested grain culms.

2. Description of the Related Art Conventionally, in a combine harvester, an ECU for controlling the operation of the combine harvester is generally arranged around a control section mounted on a traveling machine body (see, for example, Patent Documents 1 and 2).

JP-A-10-295152 JP 2014-14333 A

However, in the case of a combine having an engine mounted behind the control section, exhaust heat from the engine may affect the ECU. In recent years, it is desirable for ECUs, which often manage particularly complicated controls, to have as little thermal influence from the surroundings as possible.

A technical problem of the present invention is to provide a combine harvester that has been improved in consideration of the above-described current situation.

In the present invention, a reaper is attached to the front of a traveling machine body equipped with an engine, a threshing section is mounted behind the reaper in the traveling machine, and a control section is arranged on the front side of the threshing section. In a combine harvester in which an engine is mounted below and behind the operation unit, a mission case is arranged between the reaper and the threshing unit of the traveling machine body, and the transmission case is located on the side of the transmission case and the operation is performed. A battery for power supply is mounted under the unit.

In the combine harvester according to the present invention, the operating section is composed of a plurality of supporting leg frames erected on the upper surface side of the front portion of the traveling machine body, and an ECU that controls the operation of the combine is supported by the plurality of supporting leg frames. You can make it as it is.

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

According to the invention of the present application, a reaper is attached to the front part of a traveling machine body on which an engine is mounted, a threshing part is mounted behind the reaper part of the traveling machine body, and a control part is provided on the front side of the threshing part. In a combine harvester in which an engine is mounted on the lower rear side of the control section, a mission case is arranged between the reaping section and the preceding threshing section in the traveling machine body, and is located on the side of the transmission case and the Since the battery for power supply is mounted below the control section, the dead space around the control section, which is a dead space peculiar to combine harvesters, can be used not only as a space for arranging the mission case but also as a space for arranging the battery. can also be used effectively.

It is a left view of the combine which concerns on this invention. It is a right view of the same combine. It is a top view of the same combine. It is a drive system diagram of a combine. It is a perspective view of the combine seen diagonally from the front. It is a partial plane sectional view of a threshing part. It is a drive system diagram of a mission case. FIG. 2 is a cross-sectional plan view showing the configuration around the engine room; FIG. 2 is a hydraulic circuit diagram showing the configuration of a work system hydraulic circuit; It is a front view which shows the arrangement configuration of hydraulic circuit components. 1 is an overall perspective view of a combine harvester showing a piping configuration of a work system hydraulic circuit; FIG. Fig. 2 is an enlarged perspective view showing a piping configuration of a traveling system hydraulic circuit; FIG. 2 is a hydraulic circuit diagram showing the configuration of a traveling system hydraulic circuit; FIG. 4 is a perspective view showing plumbing workability of hydraulic piping on the transmission case; FIG. 4 is a perspective view showing the relationship between hydraulic piping on the transmission case and a connecting link body; It is the perspective view which looked at the traveling body front part from the diagonally forward left. It is the perspective view which looked at the periphery of the cab (operating part) from the diagonally rear left. It is a front view around a cab (controller). It is a top view around a cab (operation part). It is the perspective view which looked at the cab (operating part) periphery from the diagonally right rear. It is the perspective view which looked at the cab (operating part) periphery from the front. It is the perspective view which looked at the attachment position of ECU from the diagonally left front of the traveling body. It is a front view around the driver's cab (operation part) which shows the attachment position of ECU. FIG. 2 is a plan view around a driver's cab (operating section) showing the mounting position of an ECU; FIG. 4 is a perspective view of the positional relationship between an ECU and a steering case as seen obliquely from the front right. It is the perspective view which looked at the attachment position of ECU from the diagonally right front.

EMBODIMENT OF THE INVENTION Below, embodiment which actualized this invention is described based on drawing (FIGS. 1-26) applied to the common combine. First, the general structure of the combine will be described with reference to FIGS. 1 to 3. FIG. In the following description, the left side in the forward direction of the traveling body 1 is simply referred to as the left side, and the right side in the forward direction is simply referred to as the right side.

As shown in FIGS. 1 to 3, the ordinary combine harvester in the embodiment includes a running body 1 supported by a pair of left and right crawler belts 2 made of rubber crawlers as a running section. A reaping unit 3 for reaping and taking in uncut stalks such as rice (or wheat, soybeans, or corn) is attached to the front part of the traveling body 1 so as to be vertically adjustable by a single-acting hydraulic cylinder 4 for lifting. ing.

A threshing unit 9 for threshing the reaping grain culms supplied from the reaping unit 3 is mounted on the left side of the traveling body 1 . Below the threshing section 9, a grain sorting mechanism 10 for swing sorting and wind sorting is arranged. A driver's cab 5 is mounted on the front right side of the traveling body 1 as a control section on which an operator rides. An engine 7 as a power source is arranged in the cab 5 (below the driver's seat 42). Behind the cab 5 (on the right side of the traveling body 1) are a grain tank 6 for taking out grains from the threshing unit 9, and a grain tank for discharging the grains in the grain tank 6 toward the truck bed (or container, etc.). A discharge conveyor 8 is arranged. The grain discharge conveyor 8 is tilted to the outside of the machine so that the grains in the grain tank 6 are carried out by the grain discharge conveyor 8.例文帳に追加

The harvesting section 3 includes a feeder house 11 communicating with a threshing opening 9 a in front of the threshing section 9 , and a horizontally long bucket-shaped grain header 12 connected to the front end of the feeder house 11 . A raking auger 13 (platform auger) is rotatably journalled within the grain header 12 . A scraping reel 14 with a tine bar is arranged above the front portion of the scraping auger 13 . A clipper-shaped cutting blade 15 is arranged in the front part of the grain header 12.例文帳に追加Right and left division bodies 16 are protruded on both left and right sides of the front part of the grain header 12.例文帳に追加Also, a supply conveyor 17 is installed inside the feeder house 11 . A beater 18 (front rotor) for throwing harvested grain stalks is provided on the feeding end side (handling port 9a) of the supply conveyor 17 . The lower surface portion of the feeder house 11 and the front end portion of the traveling body 1 are connected via a hydraulic cylinder 4 for lifting, and the reaping unit 3 reaps using a reaping input shaft 89 (feeder house conveyor shaft), which will be described later, as an elevating fulcrum. It is moved up and down by a hydraulic cylinder 4 for elevating.

With the above configuration, the tip side of the uncut grain culm between the left and right cutting bodies 16 is raked by the raking reel 14, the culm base side of the uncut grain culm is reaped by the cutting blade 15, and the raking auger 13 is used. Due to the rotational drive, harvested grain culms are collected near the entrance of the feeder house 11 near the central portion of the left-right width of the grain header 12 . The whole amount of harvested grain culms of the grain header 12 is conveyed by the supply conveyor 17 and thrown into the threshing section 9 a by the beater 18 . A horizontal control hydraulic cylinder (not shown) for rotating the grain header 12 around the horizontal control fulcrum axis is provided, and the lateral inclination of the grain header 12 is adjusted by the horizontal control hydraulic cylinder, so that the grain header can be adjusted. 12, cutting blade 15 and rake reel 14 can also be supported horizontally with respect to the field.

Further, as shown in FIGS. 1 and 3, a threshing cylinder 21 is rotatably provided in the threshing chamber of the threshing section 9 . A squeezing cylinder 21 is pivotally supported on a scouring cylinder shaft 20 (see FIG. 4) extending in the longitudinal direction of the traveling body 1 . A receiving net 24 is stretched on the lower side of the handling cylinder 21 to allow grains to leak down. On the outer peripheral surface of the front portion of the handling drum 21, a spiral screw blade-like take-in blade 25 protrudes radially outward.

With the above configuration, the harvested culms thrown from the hauling opening 9a by the beater 18 are transported toward the rear of the traveling machine body 1 by the rotation of the hauling drum 21, and are conveyed between the hauling drum 21 and the receiving net 24. kneaded and threshed. Threshed grains such as grains smaller than the mesh of the receiving net 24 leak from the receiving net 24. - 特許庁Straw scraps and the like that do not leak from the receiving net 24 are discharged to the field from the dust outlet 23 at the rear of the threshing section 9 by the conveying action of the threshing drum 21 .

A plurality of dust feed valves (not shown) for adjusting the conveying speed for threshing grains in the threshing chamber are rotatably pivoted on the upper side of the threshing drum 21 . By adjusting the angle of the dust feed valve, it is possible to adjust the conveying speed (residence time) for threshing in the hulling chamber according to the variety and properties of harvested grain culms. On the other hand, as the grain sorting mechanism 10 arranged below the threshing section 9, a rocking sorting disc 26 for gravity sorting having grain pans, chaff sieves, grain sieves, straw racks, etc. is provided.

Moreover, as the grain sorting mechanism 10, a blower fan-shaped winnow 29 or the like for supplying sorting air to the swing sorting disc 26 is provided. The threshed grains threshed by the threshing drum 21 and leaked from the receiving net 24 are separated by the specific gravity sorting action of the rocking sorting disc 26 and the wind sorting action of the fan-shaped winnow 29 to separate the grains (such as refined grains). 1st crop), a mixture of grains and straw (2nd crop such as grains with branch stems), straw waste, etc. are sorted and taken out.

A first conveyor mechanism 30 and a second conveyor mechanism 31 are provided below the swing sorting board 26 as the grain sorting mechanism 10 . Grains (first grains) dropped from the swinging sorting board 26 by sorting with the swing sorting board 26 and the fan-shaped winnowing machine 29 are collected in the grain tank 6 by the first conveyor mechanism 30 and the grain-lifting conveyor 32. be. A mixture of grains and straw (second product) is returned to the sorting start end side of the swing sorting disc 26 via the second conveyor mechanism 31 and the second return conveyor 33, etc., and is sorted again by the swing sorting disc 26. be. Straw and the like are configured to be discharged from a dust outlet 23 at the rear of the traveling machine body 1 to the field.

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

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

Next, the driving structure of the combine will be described with reference to FIGS. 4 to 8. FIG. As shown in FIGS. 4 and 7, a transmission case 63 is provided with a linear hydraulic continuously variable transmission 64 having a hydraulic linear pump 64a and a hydraulic linear motor 64b. An engine 7 is mounted on the upper right side of the front part of the traveling body 1, and a mission case 63 is arranged on the front part of the traveling body 1 on the left side of the engine 7. - 特許庁An output shaft 65 projecting leftward from the engine 7 and a transmission input shaft 66 projecting leftward from the mission case 63 are connected via an engine output belt 67, an engine output pulley 68 and a transmission input pulley 69. there is In addition, the work section charge pump 59 and the cooling fan 149 for driving the lifting hydraulic cylinder 4 and the like are arranged in the engine 7 , and the work section charge pump 59 and the cooling fan 149 are driven by the engine 7 .

In addition, a turning hydraulic continuously variable transmission 70 for steering having a hydraulic turning pump 70a and a hydraulic turning motor 70b is provided in the transmission case 63, and a straight hydraulic continuously variable transmission 64 and a turning hydraulic continuously variable transmission 64 are connected via a transmission input shaft 66. While the output of the engine 7 is transmitted to the continuously variable transmission 70, the straight hydraulic continuously variable transmission 64 and turning hydraulic continuously variable transmission 70 are output by the steering handle 43, the main transmission lever 44, and the auxiliary transmission lever 45. The left and right crawler belts 2 are driven through a straight hydraulic continuously variable transmission 64 and a turning hydraulic continuously variable transmission 70 to travel in a field or the like. In the embodiment, straight and turning hydraulic continuously variable transmissions 64 and 70 are arranged on the upper right side surface of the transmission case 63 . The linear and turning hydraulic continuously variable transmissions 64 and 70 and the transmission case 63 constitute the driving device of the present invention.

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

A threshing cylinder input shaft 72 extending in the left-right direction of the traveling body 1, a beater 18 disposed in the left-right direction of the traveling body 1, and a reaping input shaft extending in the left-right direction of the traveling body 1 are provided in front of the threshing cylinder 21. 89 is provided. A threshing cylinder drive pulley 86, 87 and a threshing cylinder drive belt 88 are provided as a threshing cylinder input mechanism 90 for transmitting the driving force of the main counter shaft 76 to the threshing cylinder input shaft 72. A pallet cylinder input mechanism 90 (a pallet drive pulley 86, 87 and a pallet drive belt 88) is arranged at one end of the counter shaft 76 on the side of the engine 7, and the pallet cylinder 21 is driven to rotate at a constant speed by the constant rotational output of the engine 7. It is configured as follows.

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

A reaping drive belt 114 is wound around reaping drive pulleys 107 and 108 provided on the sub-counter shaft 104 and the beater shaft 82, respectively, to form a beater drive mechanism. When the reaping drive belt 114 is stretched by the reaping clutch 109 which also serves as a tension roller, the rotational power from the engine 7 transmitted to the main counter shaft 76 is transferred to the beater through the power relay mechanism and the beater drive mechanism. Input to axis 82 . A reaping drive mechanism is constructed such that a reaping driving force from the engine 7 is transmitted from a beater shaft 82 on which the beater 18 is supported to a reaping input shaft 89 via a reaping drive chain 115 and sprockets 116 and 117. ing. As a result, the reaper 3 and the beater 18 are driven for constant rotation by the constant rotation output of the engine 7 .

A winnowing shaft 100, which is a rotating shaft of the blower fan-shaped winnowing shaft 29, has a hollow tubular shape, and a main counter shaft 76 is inserted in the hollow portion of the winnowing shaft 100. As shown in FIG. That is, 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 supported so as to be relatively rotatable with each other. A winnow drive belt 103 is wound around winnow drive pulleys 101 and 102 provided on the sub-counter shaft 104 and winnow shaft 100, respectively, to constitute a winnow drive mechanism. Therefore, the rotational power from the engine 7 transmitted to the main counter shaft 76 is input to the beater shaft 82 via the power relay mechanism and the winnow drive mechanism, and the winnow 29 is driven to rotate at a constant speed by the constant rotation output of the engine 7 .

Further, the machine housing of the threshing unit 9 has a reaper support frame 36 installed on the upper surface side of the front part of the threshing machine housing strut 34 on the upper surface side of the traveling machine body 1 . A reaping bearing 37 is attached to the front right side of the reaping support frame 36, and a forward/reverse switching case 121, which will be described later, is attached to the front left side of the reaping support frame 36. As shown in FIG. A reaping input shaft 89 is rotatably supported in the front side of the reaping support frame 36 via the reaping bearing 37 and the forward/reverse switching case 121, and the reaping support frame 36 A left and right beater shaft 82 (beater 18) is rotatably supported in the interior of the body through the beater bearing member 38. As shown in FIG. A threshing cylinder drive case 71 is attached to the upper surface of the reaping support frame 36 , and a threshing cylinder input shaft 72 is supported on the threshing cylinder drive case 71 .

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

A threshing cylinder input shaft 72 is 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 applied to one end of the threshing cylinder input shaft 72 on the engine 7 side. is communicated to the department. A threshing cylinder input shaft 72 provided on the front side of the threshing part 9 is arranged in the lateral direction of the traveling machine body 1, while a grading cylinder 21 is pivotally supported on a grading cylinder shaft 20 arranged in the longitudinal direction of the traveling machine body 1. - 特許庁The front end side of the handling cylinder shaft 20 is connected via a bevel gear mechanism 75 to the left and right other ends of the handling cylinder input shaft 72 opposite to the engine 7 . The driving force of the engine 7 is transmitted to the grain sorting mechanism 10 for sorting the grains after threshing or the harvesting unit 3 from the other left and right ends of the main counter shaft 76 opposite to the engine 7 . .

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

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

The grain-elevating conveyor 32 is driven via the first conveyor shaft 77 , and the most sorted grains of the first conveyor mechanism 30 are collected in the grain tank 6 . In addition, the second reduction conveyor 33 is driven via the second conveyor shaft 78, and the second sorted grain (second grain) mixed with straw scraps of the second conveyor mechanism 31 is moved to the upper surface side of the swing sorting board 26. returned to Further, in the structure in which a spreader (not shown) for scattering straw waste is provided at the dust outlet 23, the left side of the main counter shaft 76 is attached to the spreader via a spreader drive pulley (not shown) and a spreader drive belt (not shown). Join the ends.

A reaping input shaft 89 is provided as a conveyor input shaft that pivotally supports the feed end side of the supply conveyor 17 . A header driving shaft 91 is rotatably supported on the rear side of the right side of the grain header 12 . The left end of a forward/reverse transmission shaft 122 is connected to the left end of the beater shaft 82 via a reaping drive chain 115 and sprockets 116 and 117, and the reaping input shaft 89 transmits forward/reverse rotation through a forward/reverse switching case 121. It is connected with the shaft 122 . Also, the right end of the reaping input shaft 89 is connected to the left end of the header drive shaft 91 extending in the left-right direction via the header drive chain 118 and the sprockets 119 and 120 . A scraping shaft 93 that supports the scraping auger 13 is provided. An intermediate portion of the header driving shaft 91 is connected to the right portion of the scraping shaft 93 via a scraping drive chain 92 .

It also has a reel shaft 94 that supports the scraping 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 . A cutting blade 15 is connected to the right end of the header drive shaft 91 via a cutting blade drive crank mechanism 98 . By turning the reaping clutch 109 on and off, the supply conveyor 17, the rake auger 13, the rake reel 14, and the reaping blade 15 are driven and controlled to continuously reap the tips of uncut grain culms in the field. It consists of

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 reaping input shaft 89, and an intermediate bevel gear 126 connecting the forward rotation bevel gear 124 to the reverse rotation bevel gear 125 are provided. , are provided inside the forward/reverse switching case 121 . An intermediate bevel gear 126 is always meshed with the bevel gear 124 for forward rotation and the bevel gear 125 for reverse rotation. On the other hand, the reaping input shaft 89 slidably supports a slider 127 through spline engagement. A slider 127 can be removably engaged with a forward rotation bevel gear 124 via a claw clutch-shaped forward rotation clutch 128, and the slider 127 is engaged with a reverse rotation bevel gear 125 via a claw clutch-shaped reverse rotation clutch 129. It is configured to be detachably engageable.

A forward/reverse switching shaft 123 for slidingly operating a slider 127 is provided, and a forward/reverse switching arm 130 is provided on the forward/reverse switching shaft 123. The forward/reverse switching arm 130 is operated by operating a forward/reverse switching lever (forward/reverse operation tool). oscillating to rotate the forward/reverse switching shaft 123 to bring the slider 127 into contact with or away from the forward rotation bevel gear 124 or the reverse rotation bevel gear 125, and the forward rotation bevel gear 124 or the reverse rotation bevel gear 124 or the reverse rotation bevel gear 127 through the forward rotation clutch 128 or the reverse rotation clutch 129. A slider 127 is alternatively engaged with the bevel gear 125, and the reaping input shaft 89 is connected to the forward/reverse transmission shaft 122 for forward rotation or reverse rotation.

The forward/reverse switching case 121 is provided as a forward/reverse switching mechanism for driving the supply conveyor 17 forward or backward. Therefore, the feeding conveyor 17 of the feeder house 11 can be reversed by the reverse switching operation of the normal/reverse switching case 121, and clogged straw in the feeder house 11 can be quickly removed.

The right end of the auger drive shaft 158 is connected to the output shaft 65 of the engine 7 via a tension pulley-shaped auger clutch 156 and an auger drive belt 157 . The front end side of the horizontal feed 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 . A vertical auger 162 of the grain discharging conveyor 8 is connected to the rear end side of the horizontal feeding auger 160 via a bevel gear mechanism 161, and a grain of the grain discharging conveyor 8 is connected to the upper end side of the vertical feeding auger 162 via a bevel gear mechanism 163. Grain discharge auger 164 is connected. It also has a grain discharge lever 155 for turning on and off the auger clutch 156 . A grain discharge lever 155 is attached to the rear of the driver's seat 42 and in front of the grain tank 6 so that the operator can operate the grain discharge lever 155 from the driver's seat 42 side.

Next, the power transmission structure of the transmission case 63 and the like will be described with reference to FIGS. 4 and 7. FIG. As shown in FIGS. 4 and 7, a hydraulic continuously variable transmission 64 for straight traveling (traveling main transmission) having a pair of straight traveling pumps 64a and a straight traveling motor 64b and a pair of slewing pumps 70a are mounted in a transmission case 63. and a turning hydraulic continuously variable transmission 70 having a turning motor 70b. The transmission input shaft 66 of the transmission case 63 is gear-connected to the pump shafts 258 and 259 of the linear pump 64a and the orbiting pump 70a to drive them. An engine output belt 67 is wound around a transmission input pulley 69 on a transmission input shaft 66 . The output of the engine 7 is transmitted to the transmission input pulley 69 via the engine output belt 67 to drive the linear pump 64a and the rotary pump 70a.

A driving force output from the output shaft 65 of the engine 7 is transmitted to the pump shaft 258 of the linear pump 64a and the pump shaft 259 of the rotary pump 70a via the engine output belt 67 and the transmission input shaft 66, respectively. In the linear hydraulic continuously variable transmission 64, the power transmitted to the pump shaft 258 feeds hydraulic oil from the linear pump 64a to the linear motor 64b as appropriate. Similarly, in the swing hydraulic continuously variable transmission 70, the power transmitted to the pump shaft 259 causes the hydraulic oil to be appropriately fed from the swing pump 70a to the swing motor 70b.

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

A linear input gear 263 meshing with a power distribution gear 262 fixed to the transmission input shaft 66 rotates relative to the protruding end (left end) of the pump shaft 258 protruding from the continuously variable transmission case 323 into the mission case 63. Impossibly attached. Similarly, a turning input gear 264 meshing with a power distribution gear 262 fixed to the transmission input shaft 66 is provided at the projecting end (left end) of the pump shaft 259 projecting from the continuously variable transmission case 323 into the mission case 63 . are fitted so as not to rotate relative to each other.

When the driving force output from the output shaft 65 of the engine 7 is transmitted to the mission input pulley 69, the mission input shaft 66 and the power distribution gear 262 rotate together with the mission input pulley 69, and through the straight input gear 263, While the pump shaft 258 of the linear pump 64a is rotated, the pump shaft 259 of the rotary pump 70a is rotated via the rotary input gear 264. That is, by meshing the power distribution gear 262 of the transmission input shaft 66 arranged between the pump shafts 258 and 259 with the straight input gear 263 and the turning input gear 264 of the pump shafts 258 and 259, the power from the engine 7 is reduced. Driving force can be efficiently transmitted to each of the straight hydraulic continuously variable transmission 64 and turning hydraulic continuously variable transmission 70 .

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

Rotational power of the motor shaft 260 for straight travel is transmitted from the straight travel transmission gear mechanism 250 to the auxiliary transmission gear mechanism 251 . The sub-transmission gear mechanism 251 has a sub-transmission low speed gear 254 , a sub-transmission medium speed gear 255 and a sub-transmission high speed gear 256 that are switched by sub-transmission shifters 252 and 253 . By operating the sub-transmission lever 45 arranged on the control column 41, the output rotation speed of the motor shaft 260 for straight movement is configured to be selectively switched to three gear stages of low speed, medium speed, or high speed. . In addition, there is a neutral position (a position where the output of the sub-transmission is zero) between the low, medium, and high speeds of the sub-transmission.

A parking brake shaft 265 (sub-transmission output shaft) provided on the output side of the sub-transmission gear mechanism 251 is provided with a drum-type parking brake 266 . Rotational power from the sub-transmission gear mechanism 251 is transmitted to the left and right differential mechanisms 257 from the sub-transmission output gear 267 fixed to the parking brake shaft 265 . The left and right differential mechanisms 257 each have a planetary gear mechanism 268 . Further, a straight-travel pulse generating rotating wheel 292 is provided on the parking brake shaft 265, and a straight-travel vehicle speed sensor (not shown) detects the number of rotations of the straight-travel output (straight-travel vehicle speed = shift output of the sub-transmission output gear 267). are doing.

Each of the left and right planetary gear mechanisms 268 has one sun gear 271, a plurality of planetary gears 272 meshing with the sun gear 271, a ring gear 273 meshing with the planetary gears 272, and a plurality of planetary gears 272 rotatable on the same circumference. each with a carrier 274 for placement. The carriers 274 of the left and right planetary gear mechanisms 268 are arranged on the same axis so as to face each other with an appropriate gap. A center gear 276 is fixed to a sun gear shaft 275 on which left and right sun gears 271 are provided.

Each of the left and right ring gears 273 is arranged concentrically with the sun gear shaft 275 with the inner teeth of the inner peripheral surfaces of the ring gears 273 meshing with the plurality of planetary gears 272 . Further, the external teeth of the outer peripheral surfaces of the left and right ring gears 273 are connected to a steering output shaft 285 via intermediate gears 287 and 288 for outputting left and right turning, which will be described later. Each ring gear 273 is rotatably supported by left and right forced differential output shafts 277 projecting left and right outward from the outer surface of the carrier 274 . Left and right axles 278 are connected to left and right forced differential output shafts 277 via final gears 278a and 278b. Left and right drive sprockets 51 are attached to the left and right axles 278 . Therefore, the rotational power transmitted from the sub-transmission gear mechanism 251 to the left and right planetary gear mechanisms 268 is transmitted from the left and right axles 278 to the drive sprockets 51 at the same rotational speed, and the left and right crawler belts 2 are rotated in the same direction. at the same number of revolutions to move the traveling machine body 1 straight (forward, backward).

The slewing hydraulic continuously variable transmission 70 changes and adjusts the inclination angle of the swash plate of the slewing pump 70a according to the amount of rotation of the main gear shift lever 44 and the steering handle 43 arranged on the steering column 41. By changing the discharge direction and discharge amount of hydraulic oil to the turning motor 70b, the rotation direction and rotation speed of the turning motor shaft 261 projecting from the turning motor 70b are arbitrarily adjusted. A turning pulse generating rotating wheel 294 is provided on a steering counter shaft 280, which will be described later, and a turning rotation sensor (turning vehicle speed sensor) (not shown) detects the number of rotations (turning vehicle speed) of the steering output of the turning motor 70b. configured to detect

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

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

As a result, when the turning motor 70b rotates forward (reverse rotation), the left ring gear 273 rotates in the reverse direction (normal rotation) and the right ring gear 273 rotates forward (reverse rotation) at the same number of rotations in opposite directions. That is, the speed change output from each motor shaft 260, 261 is transmitted to the drive sprockets 51 of the left and right crawler belts 2 via the auxiliary speed change gear mechanism 251 or the differential mechanism 257, respectively. is determined.

That is, when the straight motor 64b is driven while the turning motor 70b is stopped and the left and right ring gears 273 are stationary and fixed, the rotational output from the straight motor shaft 260 is transmitted to the left and right sun gears 271 at the same number of revolutions. Through the gear 272 and the carrier 274, the left and right crawler belts 2 are driven at the same number of rotations in the same direction, and the traveling machine body 1 travels straight.

Conversely, when the turning motor 70b is driven while the straight motor 64b is stopped and the left and right sun gears 271 are stationary and fixed, the rotational power from the turning motor shaft 261 causes the left ring gear 273 to rotate forward (reverse). rotation), and the right ring gear 273 rotates in the reverse direction (forward direction). As a result, one of the drive sprockets 51 of the left and right crawler belts 2 rotates forward and the other rotates backward, and the traveling machine body 1 changes direction (spin turn) on the spot.

Further, 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 turning motor 70b, a difference in speed is generated between the left and right crawler belts 2, and the traveling body 1 moves forward or backward while turning. Turn left or right (U-turn) with a turning radius greater than the radius. The turning radius at this time is determined according to the speed difference between the left and right crawler belts 2 . The traveling driving force of the engine 7 is always transmitted to the left and right crawler belts 2, and the vehicle turns to the left or right.

Next, the work system hydraulic circuit 180 and the travel system hydraulic circuit 200 in the ordinary combine harvester of the present embodiment will be described with reference to FIGS. 8 to 15. FIG. As shown in FIGS. 8 to 12, the working system hydraulic circuit 180 includes, as hydraulic actuators, a reaping lifting hydraulic cylinder 4, left and right reel lifting hydraulic cylinders 27L and 27R supporting the rake reel 14 so as to be able to move up and down, Hydraulic cylinders 55 for lifting and lowering the auger supporting the grain discharge auger 164 so as to be able to move up and down, left and right hydraulic cylinders 56L and 56R for lifting and lowering the traveling body 1, a hydraulic oil tank 57 for storing hydraulic oil, and hydraulic oil. A working section charge pump 59 connected to the tank 57 via a strainer 58, hydraulic valves 60A to 60E for switching the flow of hydraulic oil, and an oil cooler provided in the return piping from the hydraulic valves 50A to 60E to the hydraulic oil tank 57. 62. The hydraulic valves 60A to 60E are incorporated in a hydraulic valve unit 60 mounted on the traveling body 1. As shown in FIG.

The working portion charge pump 59 is hydraulically connected to the reaping lifting hydraulic cylinder 4 via the reaping lifting hydraulic valve 60A. By tilting a reaping posture lever (not shown) in the operation control unit (cab) 5 in the front-rear direction, the reaping lifting hydraulic cylinder 4 is operated, and the operator can move the reaping unit 3 to an arbitrary height (for example, a reaping work height). or non-working height, etc.). On the other hand, the working portion 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 reaping attitude lever (not shown) in the horizontal direction, the hydraulic cylinders 27L and 27R for elevating the reels are actuated, and the operator raises and lowers the raking reel 14 to an arbitrary height, and the uncut grains in the field are moved. It is configured to cut the culm.

The work portion 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 operation control unit (cab) 5 in the front-back direction, the auger lifting hydraulic cylinder 55 is operated, and the operator moves the grain discharge auger 164 on the grain discharge conveyor 8. is moved up and down to an arbitrary height. The grain discharge auger 164 is horizontally rotated together with the vertical feed auger 162 and the bevel gear mechanism 163 by the electric motor 165 to move the chaff throwing port in the horizontal direction. That is, the grains in the grain tank 6 are discharged into the truck bed or container by locating the paddy throwing port above the truck bed or container.

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

Therefore, when the left and right body lifting hydraulic cylinders 56L, 56R are simultaneously operated to simultaneously lower the left and right track frames 50, 50 with respect to the traveling body 1, the traveling body 1 moves to the left and right crawler belts 2, 2 contacting portions. , and the relative height (vehicle height) of the traveling machine body 1 with respect to the crawler belts 2, 2 ground contact portion increases. Conversely, when the left and right track frames 50 , 50 are simultaneously raised with respect to the traveling body 1 , the traveling body 1 approaches (lowers) the left and right crawler belts 2 , 2 contacting portions, and the crawler belts 2 of the traveling body 1 , 2 relative height (vehicle height) to the ground contact portion becomes lower.

Then, the left truck frame 50 is lowered with respect to the traveling machine body 1 by operating the left machine body lifting hydraulic cylinder 56L, or the right track frame 50 is raised with respect to the traveling machine body 1 by operating the right machine body lifting hydraulic cylinder 56R. (or even if both actions are executed at the same time), the traveling machine body 1 tilts downward to the right. Conversely, the right truck frame 50 is lowered relative to the traveling machine body 1 by activating the right machine body lifting hydraulic cylinder 56R, or the right track frame 50 is moved relative to the traveling machine body 1 by operating the left machine body lifting hydraulic cylinder 56L. When raised (or when both actions are performed at the same time), the traveling machine body 1 leans downward to the left.

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

The hydraulic oil tank 57 is installed on the traveling machine body 1 at a spatial position surrounded by the feeder house 11 and the beater 18, and the engine 7 and the hydraulic oil tank 57 are arranged side by side in front of the traveling machine body 1. there is That is, the hydraulic oil tank 57 is arranged in a space surrounded by the feeder house 11 and the machine housing of the threshing unit 9, and dust from the reaping unit 3 can be suppressed from accumulating in the hydraulic oil tank 57. It is also possible to prevent contamination of the working oil due to dust entering from the oil supply port 184 or the like. In addition, since the cooling air from the engine 7 flows into the installation space of the hydraulic oil tank 57, it is possible to suppress the temperature rise of the hydraulic oil without providing an oil cooler on the work system hydraulic circuit 180, and the hydraulic members can be controlled. It can be driven properly.

The hydraulic oil tank 57 has an oil filler port 184 projecting leftward (outside the machine) on the left side (outside the machine), and has a strainer 58 that can be inserted and removed from the left side. Therefore, by removing the threshing cover 185 provided on the left side of the threshing section 9 (outside the machine), the oil filler port 184 and the strainer 58 can be easily accessed. Therefore, the operation of supplying oil to the hydraulic oil tank 57 and the operation of replacing the oil filter in the strainer 58 are facilitated, and maintenance of the work system hydraulic circuit 180 can be improved.

Hydraulic pipes 181 and 183 connected to the hydraulic oil tank 57 extend left and right in front of the hydraulic oil tank 57 and the engine 7 . and the strainer 58 . That is, the hydraulic pipes 181 and 183 bypass the front of the engine 7 and extend along the output shaft 65 of the engine 7 toward the hydraulic oil tank 57 . Hydraulic pipes 182 and 183 extend rearward through a cooling fan 149 provided on the right side of the engine 7 and are connected to the hydraulic valve unit 60 . Therefore, the hydraulic pipes 181 to 183 are arranged so that the length of the pipes is short at positions that are less likely to be affected by radiant heat from the engine 7, thereby suppressing an increase in the temperature of the hydraulic oil flowing through the hydraulic pipes. can.

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

The travel system hydraulic circuit 200 includes a rectilinear valve 203 that switches in response to manual operation of the main shift lever 44 and a rectilinear cylinder 204 that is connected to the transmission charge pump 151 via the rectilinear 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, thereby steplessly changing or reversing the rotation speed of the straight motor shaft 260 of the straight motor 64b. Action is performed. The travel system hydraulic circuit 200 also includes a hydraulic servomechanism 205 for straight-ahead shifting. The hydraulic servomechanism 205 executes a feedback operation in which the rectilinear valve 203 returns to neutral by controlling the swash plate angle of the rectilinear pump 64a, and changes the swash plate angle of the rectilinear pump 64a in proportion to the amount of manual operation of the main shift lever 44, The rotation speed of the straight motor shaft 260 of the straight motor 60b is changed.

The traveling system hydraulic circuit 200 includes a turning valve 206 that switches and operates in response to manual operation of the steering handle 43 and a turning cylinder 207 that is connected to the transmission charge pump 151 via the turning valve 206 . When the swivel valve 206 is switched, the swivel cylinder 207 operates to change the swash plate angle of the swivel pump 70a, and steplessly change or reverse the rotational speed of the swivel motor shaft 261 of the swivel motor 70b. A left-right turning operation is executed, and the traveling machine body 1 changes the traveling direction to the left or right to change direction or correct the course at the headland of the field. The travel system hydraulic circuit 200 also includes a hydraulic servomechanism 208 for turning speed change. The hydraulic servomechanism 208 performs a feedback operation for returning the swing valve 206 to neutral by controlling the swash plate angle of the swing pump 70a to change the swash plate angle of the swing pump 70a in proportion to the amount of manual operation of the steering handle 43, The rotational speed of the turning motor shaft 261 of the turning motor 70b is changed.

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

A straight bypass oil passage 213 is connected to the first straight oil passage 201a and the second straight oil passage 201b. The straight bypass oil passage 213 is provided with a straight side two-way relief valve 215 . A turning bypass oil passage 214 is connected to the first turning oil passage 202a and the second turning oil passage 202b. A swing-side two-way relief valve 216 is provided in the swing bypass oil passage 214 . Therefore, each closed oil passage 201,202 is provided with one bidirectional relief valve 215,216.

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

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

Further, the hydraulic pipe 223 is connected by a bypass pipe 224 that bypasses the feed pipe 223a and the return pipes 223b to 223d, and the bypass pipe 224 is fixed above the continuously variable transmission case 323 on the side of the transmission case 63. there is By arranging the hydraulic pipe 223 and the bypass pipe 224 above the continuously variable transmission case 323, it is possible to circulate the hydraulic oil without sending it to the oil cooler 153 when the hydraulic oil temperature is low, such as when the engine 7 is started. can. Therefore, even when the hydraulic oil temperature is low and the viscosity of the hydraulic oil is high, the hydraulic oil can be smoothly circulated in the traveling system hydraulic circuit 200, and the transmission case 63 and the continuously variable transmission case 323 can be smoothly circulated. lubricate each transmission mechanism.

As described above, the oil cooler 153 is connected to the hydraulic pipes 221 to 223 that circulate the working oil in the mission case 63 and the continuously variable transmission case 323 (driving device), and the oil cooler 153 is bypassed by a bypass pipe (bypass pipe). 224 is provided in the hydraulic pipe 223 , and the bypass pipe 224 is provided integrally with the transmission case 63 and the continuously variable transmission case 323 . Therefore, by connecting the transmission case 63 and the continuously variable transmission case 323 to the oil cooler 153, the piping path for circulating the transmission case 63 and the continuously variable transmission case 323 becomes long, but the bypass pipe 224 can shorten the length.

By providing a bypass pipe 224 in the hydraulic pipe 223 to bypass the oil cooler 153, high-viscosity hydraulic oil can be circulated in the transmission case 63 and the continuously variable transmission case 323 when the engine is started in cold regions. can maintain good lubricity. In addition, by integrally providing the transmission case 63 and the continuously variable transmission case 323 with the transmission case 63 and the continuously variable transmission case 323, the bypass pipe 224 can be incorporated into the transmission case 63, thereby improving the assembly efficiency and the hydraulic system in the transmission case 63. maintenance becomes easier.

A connection member (connection joint) 225 having two communication ports 225 a and 225 b is provided in the continuously variable transmission case 323 . One end of the bypass pipe 224 is connected to the communication port 225a of the connecting member 225, while the feed 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 FIG. 13) is provided at the connecting portion between the connecting member 225 and the bypass pipe 224 . The connecting member 225 is provided on the upper surface of the continuously variable transmission case 323 on the straight hydraulic continuously variable transmission 64 side (front side), and the communication port 225a is arranged below the communication port 225b. Communication ports 225a and 225b of the connecting member 225 are respectively projected rearward (turning hydraulic continuously variable transmission 70 side).

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

A connecting plate (fixing member) 227 fixed to the side surface of the metal relay pipe 223c is fastened and fixed to the upper surface of the portion of the continuously variable transmission case 323 accommodating the revolving valve 206 (on the rear end side of the continuously variable transmission case 323). As a result, the metal relay pipe 223 c is fixedly arranged above the continuously variable transmission case 323 so as to extend parallel to the pump shaft 259 . Further, the metal relay pipe 223c has a T-shape with a communication port (branch pipe) 223e projecting forward (toward the linear hydraulic continuously variable transmission 64) from the middle portion. That is, the communication port 223e of the intermediate portion of the metal relay pipe 223c is provided at the same height as the communication port 225a of the connecting member 225 and protrudes toward the communication port 225a of the connecting member 225. As shown in FIG.

The bypass pipe 224 extends in the front-rear direction above the continuously variable transmission case 323 so as to connect the communication port 225a of the connecting member 225 and the communication port 223e of the metal relay 223c. The bypass pipe 224 connects 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. configured as follows. A bypass relief valve 226 that opens and closes the connecting portion of the connecting member 225 with the communication port 225b is provided on the metal pipe 223a.

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

Hydraulic pipes 222 , 223 connected to the transmission case 63 and the continuously variable transmission case 323 are laid under the straight connecting link 345 and turning connecting link 346 connected to the steering case 318 . Therefore, it is possible to prevent contact between the straight connecting link body 345 and the turning connecting link body 346 and the hydraulic pipes 222 and 223, and maintenance of each of the straight moving connecting link body 345 and the turning connecting link body 346 becomes easy. Further, even if the hydraulic pipes 222 and 223 vibrate due to the driving of the transmission case 63 or the like, damage due to contact with the linear connecting link body 345 and the turning connecting link body 346 can be prevented.

More specifically, the hydraulic pipe 222 that connects the charge pump 151 and the oil filter 152 is arranged in the longitudinal direction so as to pass under the straight relay shaft 352 of the straight connecting link 345 . , and the transmission case 63 is arranged in the longitudinal direction so as to pass under the first relay rod of the direct swing link 346 . Further, the downstream return pipe 223b connected to the transmission case 63 is bent so as to pass below the shaft support 366 in the direct turning link 346, and is connected to the metal relay pipe 223c fixed to the continuously variable transmission case 323. It is

Next, an engine room 146 in which the engine 7 is installed will be described with reference to FIG. 8 and the like. As shown in FIG. 8 and the like, a pair of left and right engine room struts 147 are erected on the rear side of the cab 5 on the upper surface of the traveling body 1, and a rear plate body 148 is stretched between the left and right engine room struts 147 to operate. It covers the rear of the engine room 146 below the seat 42 . A box-shaped wind tunnel case 170 is erected on the right engine room support 147 provided at the right end of the driver's cab 5 of the traveling body 1 via an opening/closing fulcrum shaft 171 . A dust-removing net is stretched over the air-outside opening on the right side of the wind tunnel case 170 , and the existence of the dust-removing net prevents dust and the like from entering the inside of the wind tunnel case 170 and the inside of the engine room 146 . In the wind tunnel case 170, the oil cooler 153 in the travel system hydraulic circuit 200 and the oil cooler 62 in the work system hydraulic circuit 180 are arranged vertically.

A water-cooling radiator 154 is erected inside the wind tunnel case 170 on the upper surface side of the traveling body 1 , and the radiator 154 faces the cooling fan 149 of the engine 7 . A shroud 150 is installed to cover the entire ventilation range of the radiator 154 , and a cooling fan 149 is arranged in an opening formed in the shroud 150 . An oil cooler 153 is installed inside the wind tunnel case 170 . By the rotation of the cooling fan 149, outside air (cooling air) is taken into the wind tunnel case 170 from the machine-external opening on the right side of the wind tunnel case 170, and dust-free cooling air is introduced into the engine room 146 from the machine-inside opening on the left side of the wind tunnel case 170. send to As a result, the oil cooler 153, the radiator 154, the engine 7, and the like are cooled by the cooling air that flows into the engine room 146. As shown in FIG.

Next, with reference to FIGS. 8, 10, and 16 to 21, a driving operation structure such as the steering handle 43 will be described. As shown in FIGS. 8, 10, and 16 to 21, a step frame 311 is provided on the cab 5 to form a flat footrest for an operator to ride on. A plurality of support leg frames 312 are erected on the upper surface side of the traveling body 1, and a step frame 311 is constructed on the upper end side of the support leg frames 312. - 特許庁The step frame 311 and the support frame 312 constitute a support frame. A boarding step 313 is fixed to the side surface of the support leg frame 312 on the right 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 .

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

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

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

Between the left and right support leg frames 312 on the lower front part of the step frame 311, a case support horizontal frame 319 is mounted across and attached. Since the steering case 318 interlockingly connects the case 323 and the transmission case 63), the presence of the case support horizontal frame 319 improves the rigidity of the front part of the traveling body 1 (especially near the cab 5). The steering case 318 can be supported with high rigidity by using the case support horizontal frame 319 that serves to reinforce the front part of the traveling body 1 . Therefore, there is no significant difference between the amount of operation of the main gearshift lever 44 and the steering handle 43 and the output of the driving device (continuously variable transmission case 323 and transmission case 63), and the operator is not expected to be in a running state. eliminate the risk of becoming The case support horizontal frame 319 for reinforcement can also be used as the mounting portion of the steering case 318, and a dedicated mounting base for the steering case 318 is not required, contributing to cost reduction.

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

Therefore, since a space is created on the side (left side) of the feeder house 11 side in the transmission case 63, the degree of freedom in designing the reaping unit 3 is increased, and the feeder house 11 can be adjusted to the reaping amount of the reaping unit 3 and the reaping width of the grain header 12. can be configured in the optimum size for In addition, since the installation width of the feeder house 11 in the horizontal direction is widened, the feeder house 11 can be installed on the side close to the center of gravity when the grain header 12 is lifted and lowered, and the support strength of the feeder house 11 for the reaping part 3 is increased. can increase

A straight driving operation shaft 325 as a straight driving output control unit is protruded forward from the front outer surface of the continuously variable transmission case 323, and a turning operation shaft 326 as a turning output control unit is projected rearward from the rear outer surface of the continuously variable transmission case 323. is made to protrude. Although detailed illustration is omitted, the linear operation shaft 325 is connected to the operation arm body 355 for straight movement, and the turning operation shaft 326 is connected to the operation arm body 369 for turning. The operation arms 355 and 369 for straight movement and turning are connected to a straight movement connection link body 345 and a turn connection link body 346 provided on the back side of the steering case 318, respectively, so that the steering operation of the steering handle 43 and the main shift lever are performed. 44, the linear hydraulic continuously variable transmission 64 and turning hydraulic continuously variable transmission 70 are controlled to change the course and moving speed of the left and right crawler belts 2.

A driver's cab (operating section) 5 provided in the front part of the traveling body 1 includes a main transmission lever (straight operating tool) 44 for straight operation and a steering handle (swivel operating tool) 43 for turning operation. The control column 41 is arranged on the side portion of the driving device (the transmission case 63 and the continuously variable transmission case 323). A steering case 318 for changing the output from the mission case 63 in accordance with the amount of operation of the steering handle 43 and the main transmission lever 44 is located below the driver's cab 5 in the front part of the traveling machine body 1, and is a linear hydraulic continuously variable transmission. 64 and a continuously variable transmission case 323 equipped with a turning hydraulic continuously variable transmission 70 .

In this case, the control handle 43 is arranged in the front central portion of the driver's cab 5 that is in front of the driver's seat 42, and the control handle 43 is located on the left side of the drive device (continuously variable transmission case 323 and transmission case 63). A main shift lever 44 is arranged on the column 41 . That is, a steering case 313 is arranged below the steering handle 43, and a continuously variable transmission case 323 is arranged below the steering column 41 on which the main transmission lever 44 is installed. As a result, the parts of the operating system mechanism that connect the steering handle 43 and the main transmission lever 44 to the continuously variable transmission case 323 via the steering case 313 can be arranged close to each other, and the parts of the operating system mechanism can be connected. Each link mechanism 321, 322, 345, 346 can be configured to be short to suppress fluctuation and deformation thereof. Therefore, it suppresses the deviation between the amount of operation of the main transmission lever 44 and the steering handle 43 and the output of the driving device (continuously variable transmission case 323 and transmission case 63), and maintains a stable running state according to the operator's operation. can.

A battery 230 that supplies power to the engine 7 is arranged behind the steering case 318 and on the side of the continuously variable transmission case 32 in the front portion of the traveling body 1 below the cab 5 . That is, a battery 230 for supplying electric power to the engine 7 and the like is arranged in a region surrounded by the steering case 318, the driving device (the continuously variable transmission case 323 and the transmission case 63) and the engine 7 on the lower side of the cab 5. . As a result, the dead space under the cab 5 can be effectively used not only as a space for arranging the steering case 318 and the continuously variable transmission case 323 but also as a space for arranging the battery 230 . Therefore, the battery 230 can be arranged close to the engine 7 and the cab 5, and the electric system can be made compact. Also, it is possible to avoid increasing the size of the combine in order to secure the installation space for the battery 230 .

A driver's cab (operating section) 5 is configured on a plurality of support leg frames 312 erected on the upper surface side of the traveling body 1 . A steering case 318 is fixed to a case support horizontal frame (case support frame) 319 installed in the middle of the plurality of supporting leg frames 312 and arranged above the continuously variable transmission case 323 and the battery 230 . Since the battery 230 and the steering case 318 are arranged in multiple stages below the front portion of the step frame 311, the space formed in the rear portion of the steering case 318 adjacent to the continuously variable transmission case 323 can be utilized. Therefore, the electric wiring for supplying electric power to the electric members of each part including the engine 7 and the cab 5 can be easily extended. It also contributes to improvement in workability in assembling the steering case 318 and the battery 230 and in maintenance workability.

In addition, since the oil filter 152 for filtering the working oil in the driving device (continuously variable transmission case 323 and transmission case 63) is arranged in the region below the cab 5, the driving device (continuously variable transmission case 323 The length of the hydraulic piping 222 connecting the transmission case 63) and the oil filter 152 can be shortened, and the routing of the hydraulic piping 222 is simplified.

In the upper part of the steering case 318, a sideways main transmission input shaft 317 is arranged on one of the front and rear sides of the turning input shaft 316, and a sideways straight output shaft 350 is arranged on the other side. . The main transmission input shaft 317 and the straight output shaft 350 extend laterally in parallel with each other in a plan view, and are rotatably supported by the steering case 318 . The main transmission input shaft 317 and the straight output shaft 350 are pivotally supported so as to protrude outward (left side) from the left side surface of the steering case 318 . A turning output shaft 164 extending in a direction perpendicular to the straight output shaft 350 is pivotally supported on the rear surface of the steering case 318 and below the straight output shaft 350 so as to protrude outward (rearward) from the steering case 318 . .

The rectilinear connecting link 345 is connected to the rectilinear output shaft 350 by inserting the projecting end (left end) of the rectilinear output shaft 350 into one end (right end) of the cylindrical shaft connecting body 351 . At the other end (left end) of the shaft connecting body 351, a straight relay shaft 352 is inserted which is pivotally supported by a shift output support bracket 328 fixed to a support leg frame 312 at the left front position of the cab 5. By adjusting the lateral position of the rectilinear relay shaft 352 with respect to the shaft connecting body 351, the lateral installation position of the rectilinear connecting link body 435 is adjusted.

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

The rectilinear connecting link 345 connects the rectilinear relay shaft 352 extending in the left-right direction at a position on the extension line of the rectilinear output shaft 350 with the shaft connecting member 351 . It is pivotally supported by a support bracket 328 . As a result, the relay shaft for straight movement 352 rotates together with the output shaft for straight movement 350 , and swings the front end of the relay arm for straight movement 353 fixed to the left end of the relay shaft for straight movement 352 . A connecting rod 354 for straight movement, whose both ends are pivotally attached to the front end of the relay arm body 353 for straight movement and one end of the operation arm body 355 for straight movement, moves up and down according to the swing of the relay arm body 353 for straight movement. As a result, the rectilinear operation shaft 325 whose protruding end (front end) is fixed to the other end of the operation arm body 355 is rotated.

On the other hand, the turning connecting link body 346 extends laterally from the other end (front end) of the output arm body 362 , one end (base end) of which is fixed to the projecting end (rear end) of the turning output shaft 361 . One end (right end) of the relay rod 363 is connected. The first relay rod 363 extends to the left and right so as to straddle the upper front side of the continuously variable transmission case 323 at the rear position of the steering case 318, and the other end (left end) of the first relay rod 363 serves as a turning relay. It is connected to the first turning relay arm body 364 fixed to one end (front end) of the shaft 365 . The turning relay shaft 365 is supported by penetrating a tubular shaft support 366 .

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

A shaft support 366 that pivotally supports the turning relay shaft 365 is mounted on the transmission case 63 by bolting the other end of a support plate 370 to the outer peripheral surface of the shaft support 366 and bolting the other end to the upper surface of the transmission case 63 . and fixed to the left side of the continuously variable transmission case 323 . A pipe fixing portion 372 is provided on the outer peripheral surface of the shaft support 366 to fix the position thereof by passing the hydraulic pipe 223 connected to the transmission case 63 .

The turn connection link body 346 is a first relay rod extending in the left-right direction on an output arm body 362 whose tip end swings left and right in accordance with the rotation of a turn output shaft 361 projecting rearward of the steering case 318 . The right end of 363 is pivoted. Therefore, the first relay rod 363 moves in the left-right direction along with the swing of the output arm body 362, and the tip of the first turning relay arm body 364 whose base end is fixed to the front end of the turning relay shaft 365 moves left and right. oscillate. By swinging the tip of the first turning relay arm 364, the turning relay shaft 365 supported by the shaft support 366 rotates, and at the same time, the base end is fixed to the rear end of the turning relay shaft 365. The tip of the second turning relay arm body 364 swings left and right. A second relay rod 368 having both ends pivotally attached to the front end of the second turning relay arm body 367 and one end of the turning operation arm body 369 moves left and right in accordance with the swing of the second turning relay arm body 367 . , the turning operation shaft 326 having the protruding end (rear end) fixed to the other end of the operation arm body 369 is rotated.

A main transmission input shaft 317 protrudes from the steering case 318 toward the left-right central side of the traveling machine body 1 . A projecting end (left end) of the main transmission input shaft 317 is supported by a main transmission input support bracket 381 fixed to the step frame 31·BR>P on the left edge of the transmission case 63 side. One end (front end) of a main transmission arm body 382 is connected to the projecting end (left end) of the main transmission input shaft 317 , and the other end (rear end) of the main transmission arm body 382 is connected to the main transmission lever 44 . It is connected to a main transmission operating rod 322 connected to the .

A linear hydraulic continuously variable transmission 64 and a turning hydraulic continuously variable transmission 70 for shifting the power of the engine 7 are arranged side by side on the cab (control section) 5 side of the left and right sides of the transmission case 63 . . A straight operation shaft 325 of the straight hydraulic continuously variable transmission 64 and a turning operation shaft 326 of the turning hydraulic continuously variable transmission 70 are protruding forward and backward. Since the linear hydraulic continuously variable transmission 64 and the turning hydraulic continuously variable transmission 70 are arranged side by side on the cab 5 side, the connection structure with the steering case 318 can be shortened.

Further, by arranging the straight operation shaft 325 and the turning operation shaft 326 in the front and rear direction, it is possible to have the same positional relationship as the straight output shaft 350 and the turning output shaft 361 arranged in the front and rear direction in the steering case 318 . As a result, the structure of the link mechanism from the steering case 318 to the straight hydraulic continuously variable transmission 64 and the turning hydraulic continuously variable transmission 70 can be simplified. can be installed in close proximity to each other in a compact manner.

A steering case 318 is arranged below the cab (operating section) 5 and above the driving device (continuously variable transmission case 323 and transmission case 63), and a straight output shaft 350 and a turning output shaft 361 protrude from the steering case 318. is set. A straight connecting link 345 that connects the straight output shaft 350 and the straight operation shaft 325, and a turning connection link 346 that connects the turning output shaft 361 and the turning operation shaft 326 are independent of the steering case 318 in plan view. It is installed between the gear shift cases 323 . That is, since the straight connecting link body 345 and the swivel connecting link body 346 are arranged together with the transmission case 63 on the side of the driver's cab 5, the ease of assembly and the ease of maintenance are improved.

A straight connecting link 345 that interlocks the steering case 318 and the straight driving operation shaft 325 as a straight driving output control unit is supported by the supporting leg frame 312 that supports the cab 5 . A steering case 318 is fixed to a case support lateral frame (case support frame) 319 installed in the middle of the left and right support leg frames 312 that support the front position of the driver's cab (operator) 5 . The straight connecting link body 345 is supported by the left leg frame 312 on the mission case 63 (continuously variable transmission case 323) side.

A support leg frame 312 that supports the driver's cab 5 includes a straight connecting link 345 that interlocks and connects the steering case 318 and the straight operation shaft 325 (straight output control section) provided in the drive device (continuously variable transmission case 323 and transmission case 63). supported by Therefore, even if the linear connecting link 345 is bent or pulled by vibrations of the driving device (continuously variable transmission case 323 and transmission case 63), the support leg frame 312 supporting the cab 5 supports the linear connecting link 345 with high rigidity. can be supported, and the fluctuation and deformation of the rectilinear connecting link body 345 can be suppressed. Therefore, there is no significant difference between the amount of operation of the main gearshift lever 44 or the steering handle 43 and the output of the driving device (continuously variable transmission case 323 and transmission case 63), and the operator can be in an unexpected running state. eliminate the risk of becoming

A continuously variable transmission case 323 that accommodates the linear hydraulic continuously variable transmission 64 and the turning hydraulic continuously variable transmission 70 is fixed at an upper position on the right side surface of the transmission case 63 . The turning connection link body 346 is supported on the upper surface of the transmission case 63 on the continuously variable transmission case 323 side. By utilizing the space between the feeder house 11 and the cab 5, the turning connection link body 346 can be compactly and highly rigidly supported on the transmission case 63 having the same vibration system as the continuously variable transmission case 323. Therefore, bending and tension of the turning connection link body 346 due to mechanical vibration are suppressed, and the amount of operation of the main transmission lever 44 and the steering handle 43 and the output of the driving device (continuously variable transmission case 323 and transmission case 63) are controlled. A large deviation does not occur between them, and the possibility of a running state that the operator does not expect can be eliminated.

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

An ECU 401 that controls the operation of the combine is arranged on the front side of the step portion 400 . In the embodiment, the shielding plate 402 is arranged to bridge between the front side of the step portion 400 , that is, between the front center side of the step frame 311 and the front center side of the case support horizontal frame 319 . The upper end side of the shielding plate 402 is welded and fixed to the front central side of the step frame 311 . The lower end side of the shielding plate 402 is welded and fixed to the front central side of the case support horizontal frame 319 . In other words, the shield plate 402 is supported by the step portion 400 (step frame 311 and case support horizontal frame 319). The ECU 401 is fastened to the front side of the shielding plate 402 .

Accordingly, the ECU 401 is positioned on the front side of the space of the step portion 400, and the engine 7 is positioned on the rear side. Moreover, the steering case 318 and the shielding plate 402 are located between the ECU 401 and the engine 7 , and both the steering case 318 and the shielding plate 402 serve as shields against exhaust heat from the engine 7 . With this configuration, the ECU 401 is arranged as far away from the engine 7 as possible in the vicinity of the cab 5 (operating section), so that the thermal influence of the engine 7 on the ECU 401 can be reduced. Control stabilization and life extension of ECU401 can be attained. In particular, since exhaust heat from the engine can be blocked by the shielding plate 402, the effect of reducing thermal influence from the engine 7 to the ECU 401 is high.

The outer shape of shielding plate 402 is larger than the outer shape of ECU 401 . Therefore, the peripheral portion of shielding plate 402 protrudes from the outer periphery of ECU 401 . Existence of the peripheral portion of the shielding plate 402 makes it difficult for exhaust heat from the engine 7 to flow to the front side of the ECU 401 . Note that the shielding plate 402 of the embodiment is notched at the lower center side, and has a substantially downward U-shape. The notch portion 403 is provided for the purpose of removing light from the shielding plate 402 and for the purpose of exposing the back side of the ECU 401 to external air and releasing the heat of the ECU 401 .

The front side of the ECU 401 is covered with a front cover 404 of the cab 5 . A power supply battery 230 arranged in the step portion 400 is placed below the steering case 318 and the case support horizontal frame 319 . Therefore, the ECU 401 is positioned higher than the battery 230 . The battery 230 is placed in a position where it is not affected by, for example, muddy water or rain water in the field (not exposed to muddy water). Since the ECU 401 is arranged at a high position in such a battery 230 as well, there is an advantage that the influence of muddy water or the like on the ECU 401 can be eliminated more reliably. Also, since the ECU 401 and the battery 230 are arranged close to each other, the electric system can be made compact.

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

1 traveling body 3 reaping part 5 cab 7 engine 9 threshing part 11 feeder house 311 step frame (support frame)
312 support leg frame (support frame)
318 steering case 319 case support horizontal frame 400 step portion 401 ECU
402 Shielding plate 403 Notch portion 404 Front cover

Claims (3)

A reaper is attached to the front part of a traveling machine body equipped with an engine, a threshing part is mounted behind the reaper part of the traveling machine body, and a control part is arranged on the front side of the threshing part to operate the threshing machine. In a combine with an engine mounted on the lower rear side of the part,
A transmission case is arranged between the reaping unit and the threshing unit of the traveling machine body, and a battery for power supply is mounted on the side of the transmission case and below the control unit.
combine. The operation unit is composed of a plurality of support leg frames erected on the front upper surface side of the traveling machine body, and an ECU that controls the operation of the combine is supported by the plurality of support leg frames.
A combine according to claim 1. The ECU is attached to a step frame provided on the plurality of support leg frames,
The combine according to claim 2.

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