JP6538517B2 - Vehicle drive device and combine - Google Patents

Description

  The present invention relates to a drive device for a vehicle and a combine provided with the same.

  BACKGROUND Conventionally, a vehicle drive device mounted on a work vehicle such as a combine has a transmission case for shifting the power of an engine (see Patent Document 1 etc.).

  In the transmission case of Patent Document 1, a cylindrical PTO boss portion is formed on the upper side of the side opposite to the hydraulic CVT (see FIG. 14 of Patent Document 1). The PTO shaft rotatably supports the PTO shaft via a pair of bearing bodies. The PTO shaft has a stepped shape with a plurality of steps, and the shape between the pair of bearing bodies has the largest diameter and the diameter is reduced toward both axial end sides. The bearing bodies are respectively fitted to the middle diameter portions on both sides of the large diameter portion of the PTO shaft. A pair of step portions projecting radially inward are formed on the inner peripheral side of the PTO boss portion.

  Each bearing body is detachably locked in the PTO boss by a snap ring. The large diameter portion of the PTO shaft, each step portion and the retaining ring sandwich the corresponding bearing body in an axially non-disengageable manner. A PTO gear is spline-fitted to the end of the medium diameter portion located inward of the transmission case in the PTO shaft. The PTO gear can not be pulled inward by the retaining ring. A PTO pulley is attached to a small diameter portion of the PTO shaft which is located outside the transmission case.

JP, 2011-179642, A

  However, in the above-mentioned conventional structure, since two retaining rings for bearing bodies and one retaining ring for PTO gears are used for position control of bearing bodies and PTO gears, assembling work of PTO shaft to transmission case However, there is a problem that the manufacturing cost is increased due to the increase in the number of assembling steps. Another problem is that the processing cost is increased because the PTO shaft itself has a multi-step stepped shape.

  This invention makes it a technical subject to provide the drive device for vehicles which examined and improved the present condition as mentioned above, and a combine provided with this.

According to a first aspect of the present invention, in a vehicle drive apparatus including a transmission case for changing the power of an engine, a shaft member is rotatably supported via a bearing body on a cylindrical portion formed in the transmission case. A step portion projecting radially inward is formed on the inner peripheral side of the cylindrical portion, and a large diameter portion having a diameter larger than the inner diameter of the bearing body is formed at the end portion of the shaft member. A rotating member having a diameter larger than the inner diameter of the bearing is detachably mounted, and the bearing is held between the large diameter portion or the rotating member and the stepped portion in the cylindrical portion. A pair of the bearing bodies arranged in the axial direction of the shaft member, and the step portion corresponds to a first bearing body out of the transmission case among the pair of bearing bodies. One step portion and the transmission gear of the pair of bearing bodies A second step portion corresponding to a second bearing body located inward of the shaft, and the large diameter portion is formed at an end portion of the shaft member outboard of the shaft member; The rotary member is detachably mounted at the end portion inward of the transmission case, and the first bearing body is held between the large diameter portion and the first step portion, The second bearing body is held between the two step portions .

According to a second aspect of the present invention, in the vehicle drive device of the first aspect, shaft diameters of both sides of the shaft member across the large diameter portion are set to the same diameter.

A third aspect of the present invention relates to a combine, which comprises the vehicle drive device according to the first or second aspect .

  According to the present invention, in the vehicle drive device including the transmission case for changing the power of the engine, the shaft member is rotatably supported via the bearing body on the cylindrical portion formed in the transmission case, On the inner peripheral side of the cylindrical portion, a step portion projecting radially inward is formed, and at an end portion of the shaft member, a large diameter portion larger in diameter than the inner diameter of the bearing body is formed Alternatively, since the rotating member having a diameter larger than the inner diameter of the bearing is detachably mounted, and the bearing is held by the large diameter portion or the rotating member and the step portion in the cylindrical portion, There is no need to use a dedicated part such as a snap ring for position control of the bearing body. Therefore, the number of parts can be reduced to simplify the pivotal support structure of the shaft member, and the assembling operation can be rationalized to suppress the manufacturing cost.

In particular, the prior SL bearing body, there pair aligned in the axial direction of the shaft member, the stepped portion has a first step portion corresponding to the first bearing member in the transmission case outboard of the pair of bearing members And the second step portion corresponding to the second bearing body located inward of the transmission case among the pair of bearing bodies, and the large diameter at the end portion of the shaft member outboard of the transmission case. Part of the shaft member, the rotary member is detachably mounted on the end of the shaft member inward of the transmission case, and the first bearing body is constituted by the large diameter portion and the first step portion. together sandwiching, from sandwiching said second bearing member and the rotary member by said second stepped portions, only one said retaining ring of said shaft member, said pair of bearing body and the rotating member Suitable for the cylindrical part of the mission case To be mounted, it allows the assembly of very simple manner the shaft member. The maintainability can be improved with respect to the support structure of the shaft member.

Further, according to the second aspect of the present invention, since the shaft diameters of both sides of the shaft member across the large diameter portion are set to the same diameter, the processing cost of the shaft member can be reduced, and thus the parts cost is reduced. Contribute to

It is a left side view of the combine which carries the drive for vehicles of the present invention. It is a right side view of a combine. It is a top view of a combine. It is the perspective view which looked at a traveling body front part from diagonally left front. It is a drive systematic diagram of a combine. FIG. 2 is a drive system diagram of a vehicle drive device. FIG. 2 is a hydraulic circuit diagram of a hydraulic continuously variable transmission. It is the perspective view which looked at the driver's cab and the drive device for vehicles from diagonally left forward. It is a right side view of a drive for vehicles. It is a left side view of a drive for vehicles. It is left side sectional drawing of the transmission case which shows gear arrangement relationship. It is an expanded sectional view of a rectilinear output in a mission case. It is an expanded sectional view of turning output in a mission case. FIG. 7 is a back sectional view of the auxiliary transmission gear mechanism. It is a back sectional view of a PTO boss part. It is a back sectional view of another example which attached the PTO axis to the PTO boss. It is a back sectional view of a turning brake. It is a left view of the drive device for vehicles which shows another example of lubricating structure. It is sectional drawing of the axle tip side.

  Hereinafter, an embodiment of the present invention will be described based on the drawings of a vehicle drive device mounted on a conventional combine. First, the schematic structure of the combine will be described with reference to FIGS. 1 to 3. In the following description, the left side in the forward direction of the traveling vehicle 1 is simply referred to as the left side, and the right side in the forward direction is simply referred to as the right side.

  As shown in FIGS. 1 to 3, the ordinary combine as a working vehicle includes a traveling machine body 1 supported by a pair of left and right crawler belts 2 made of rubber crawlers as a traveling unit. At the front of the traveling vehicle 1, a reaper 3 to be taken in while harvesting uncut rice straw such as rice, wheat, soybeans or corn is mounted so that it can be moved up and down by a single acting hydraulic cylinder 4 for lifting. .

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

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

  According to the above configuration, the tip end side of the uncut grain weir between the left and right weeds 16 is scratched by the scratching reel 14 and the weir side of the uncut grain weir is cut away by the first cutting blade 15, and the scratching auger By the rotational drive of 13, the reaper is collected near the entrance of the feeder house 11 near the center of the lateral width of the grain header 12. The entire amount of the reaper of the grain header 12 is conveyed by the feed conveyor 17 and is introduced into the sip 9 a of the threshing part 9 by the beater 18. A grain control hydraulic cylinder (not shown) for rotating the grain header 12 about the horizontal control fulcrum axis is provided, and the inclination of the grain header 12 in the left-right direction is adjusted by the above-mentioned hydraulic cylinder for horizontal control. It is also possible to support 12 and the 1st cutting blade 15 and the taking-in reel 14 horizontally with respect to an eyebrow scene.

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

  According to the above-described configuration, the reaping grain hopper inserted from the throttling port 9a by the beater 18 is transported toward the rear of the traveling machine body 1 by the rotation of the threshing drum 21, It is kneaded and threshed. De-graining such as grains smaller than the mesh of the receiving net 24 leaks from the receiving net 24. Scales and the like that do not leak from the receiving net 24 are discharged to the field from the dust outlet 23 at the rear of the threshing part 9 by the transport action of the threshing drum 21. A plurality of dust transfer valves (not shown) pivotally connected to the upper side of the threshing cylinder 21 are provided to adjust the speed at which the grain is removed from the throttling chamber. By adjusting the angle of the dust transfer valve, it is possible to adjust the transport speed (residence time) of the grain removal in the throttling chamber in accordance with the type and characteristics of the reaper.

  On the other hand, as a grain sorting mechanism 10 disposed below the threshing part 9, a swing sorting board 26 for sorting with a specific gravity is provided which has a grain pan, chaff sieve, grain sieve, straw rack and the like. Further, as the grain sorting mechanism 10, a blast fan-like carp 29 or the like for supplying sorting air to the swinging sorting board 26 is provided. The degrained threshed by the threshing drum 21 and leaked from the net 24 is a grain (one of the fine grains, etc.) by the specific gravity sorting action of the swing sorting disc 26 and the wind sorting action of the blast fan-like tangerine 29. It is sorted out into a mixture of grain and straw, a mixture of grain and straw (a second thing such as a grain with a stem), and scraps and taken out.

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

  Furthermore, as shown in FIGS. 1 to 4, in the cab 5, a control column 41 and a driver seat 42 on which an operator is seated are disposed. The control column 41 includes an accelerator lever 40 for adjusting the number of revolutions of the engine 5, a round control handle 43 for changing the course of the traveling vehicle 1 by the rotation operation of the operator, and a main for switching the moving speed of the traveling vehicle 1 A shift lever 44 and an auxiliary shift lever 45, a reaper clutch lever 46 for driving or stopping the reaper 3 and a threshing clutch lever 47 for driving or stopping the threshing portion 9 are disposed. Further, a roof 49 for sun protection is attached to a front upper surface side of the glen tank 6 via a sun visor support 48, and the roof 49 for sun protection covers the upper side of the driver's cab 5.

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

  Next, the drive structure of the combine will be described with reference to FIGS. 4 to 6. As shown in FIGS. 4 to 6, a linear hydraulic continuously variable transmission 64 for traveling shift having a linear pump 64 a and a linear motor 64 b is provided in the transmission case 63. The engine 7 is mounted on the upper right side of the front of the traveling vehicle 1, and a transmission case 63 is disposed on the front of the traveling vehicle 1 and on the left of the engine 7. An engine output belt 67 connects an output shaft 65 projecting leftward from the engine 7 with a transmission input shaft 66 projecting leftward from the transmission case 63 so as to transmit power. In addition, a work unit charge pump 68 and a cooling fan 69 for driving the lifting hydraulic cylinder 4 and the like are disposed in the engine 7, and the work unit charge pump 68 and the cooling fan 69 are driven by the engine 7.

  In addition, a steering hydraulic hydraulic variable transmission 70 for steering having a rotary pump 70 a and a rotary motor 70 b is provided in the transmission case 63, and a linear hydraulic hydraulic variable transmission 64 and a hydraulic swing variable transmission 70 via a transmission input shaft 66. Output is controlled by the steering handle 43 and the main and sub shift levers 44 and 45, and the output control of the linear hydraulic stepless transmission 64 and the turning hydraulic stepless transmission 70 is performed to control the linear hydraulic stepless transmission. The left and right crawler belts 2 are driven via the machine 64 and the turning hydraulic continuously variable transmission 70 so as to travel and move in a field or the like. In the embodiment, the straight and swing hydraulic continuously variable transmissions 64 and 70 are disposed on the upper right side of the transmission case 63. The straight and turning hydraulic continuously variable transmissions 64 and 70 and the transmission case 63 constitute a vehicle drive device of the present invention.

  As shown in FIGS. 4 and 5, on the front side of the threshing portion 9, a threshing drum drive case 71 is disposed, which pivotally supports the front end side of the threshing drum shaft 20. Then, a laterally long threshing cylinder input shaft 72 for driving the threshing cylinder 21 is pivotally supported by the threshing cylinder drive case 71. Moreover, the countershaft 73 made to penetrate to the right and left of the threshing part 9 is provided. A counter shaft 73 extending from one side to the other side of the threshing part 9 is provided so as to penetrate the threshing part 9 in the left-right direction through the lower part of the threshing drum 21. A work unit input pulley 83 is provided at the right end of the counter shaft 73. The right end of the counter shaft 73 is connected to the output shaft 65 of the engine 7 via a tension / pulley type threshing clutch 84 and a working unit drive belt 85 so that power can be transmitted.

  A threshing drum input shaft 72 extending in the lateral direction of the traveling machine body 1 above the counter shaft 73 and in front of the threshing cylinder 21, a beater 18 disposed in the lateral direction of the traveling body 1 and a lateral direction of the traveling body 1 An extended reaper input shaft 89 is provided. In addition, as the threshing drum input mechanism 90 for transmitting the driving force of the counter shaft 73 to the threshing drum input shaft 72, the throttling drum drive pulleys 86 and 87 and the throttling drum drive belt 88 are provided. A threshing drum input mechanism 90 (threshing drum drive pulleys 86 and 87 and a threshing drum drive belt 88) is disposed at one end of the counter shaft 73 on the engine 7 side. Further, as a reaper input mechanism 100 for transmitting the driving force of the counter shaft 73 to a reaper input shaft 89, an end portion on the engine 7 side provided with a reaper drive pulley 106, 107 and a reaper drive belt 114 and a threshing drum input mechanism 90 is disposed. The reaper input mechanism 100 (the reaper drive pulleys 106 and 107 and the reaper drive belt 114) is disposed at the other end portion of the counter shaft 73 which is opposite to the first side.

  Furthermore, as shown in FIG. 4, a cutting support frame 36 is installed in front of the threshing part 9 on the upper surface side of the traveling airframe 1. A cutting input shaft 89 is pivotally supported on the front side of the cutting support frame 36 via the cutting bearing body in the left-right direction of the traveling machine body 1 and a beater shaft 82 is provided inside the cutting support frame 36. Support the 18 rotatably. Further, the forward / reverse switching case 121 is attached to the left outer surface of the cutting support frame 36, and the threshing cylinder drive case 71 is attached to the upper surface side of the cutting support frame 36.

  On the other hand, a horizontally-oriented reaper input shaft 89 for driving the feed conveyor 17 in the feeder house 11 is provided. From the other end of the counter shaft 73 on the opposite side to the engine 7, the cutting drive power transmitted from the engine 7 to one end of the counter shaft 73 on the engine 7 side is a forward / reverse transmission shaft 122 of the reaper forward / reverse switching case 121 To communicate. The beater shaft 82 is driven via the forward rotation bevel gear 124 or the reverse rotation bevel gear 125 of the cutting / reverse rotation switching case 121. Further, the cutting drive force is transmitted to the reaping input shaft 89 from the beater shaft 82 on which the beater 18 is supported.

  That is, as shown in FIG. 5, the beater 18 is pivotally supported by the beater shaft 82 in the left-right direction, and the driving force of the engine 7 is transmitted from one end of the beater shaft 82 on the engine 7 side to the reaper 3 The mowing forward and reverse switching case 121 is disposed at the left and right other ends opposite to the engine 7 at 82, and the mowing forward and reverse switching case 121 is disposed from the other end of the counter shaft 73 opposite to the engine 7. It is comprised so that the 7 driving force may be transmitted.

  Further, as shown in FIG. 5, a threshing drum input shaft 72 directed leftward and rightward is provided on the front side of the threshing part 9, and the driving force transmitted from the engine 7 to one end of the counter shaft 73 on the engine 7 side is The threshing drum is provided with a threshing drum input shaft 72 on the front side of the threshing part 9 and is disposed in the left-right direction of the traveling machine body 1 and disposed in the front-rear direction of the traveling body 1 A threshing cylinder 21 is pivotally supported on a shaft 20, and the front end side of the threshing cylinder 20 is connected to the left and right other end opposite to the engine 7 in the throttling cylinder input shaft 72 via a bevel gear mechanism 75 The driving force of the engine 7 is transmitted to the grain sorting mechanism 10 for sorting the grain after threshing and the reaper 3 from the left and right other ends opposite to the engine 7 in.

  The right end of the threshing drum input shaft 72 is connected to the right end of the counter shaft 73 closer to the engine 7 via the threshing drum drive pulleys 86 and 87 and the threshing drum drive belt 88. The front end side of the threshing drum shaft 20 is connected via the bevel gear mechanism 75 to the left end of the threshing drum input shaft 72 extended in the left-right direction. The power of the engine 7 is transmitted from the right end of the counter shaft 73 to the front end side of the threshing drum shaft 20 via the threshing drum input shaft 72, and the throttling barrel 21 is rotationally driven in one direction. On the other hand, the left end of the counter shaft 73 on the side away from the engine 7 via the tang drive pulleys 101 and 102 and the tang drive belt 103 at the left end of the tang shaft 76 supporting the blast fan shaped tang 29 The department is connected. The power of the engine 7 is transmitted from the left end of the counter shaft 73 to the left end of the tang shaft 76 so that the tang 29 is rotationally driven in one direction.

  Furthermore, the left end of the lapping shaft 76 via the conveyor drive belt 111 between the left end of the first conveyor shaft 77 of the conveyor mechanism 30 and the left end of the second conveyor shaft 78 of the second conveyor mechanism 31. The department is connected. The left end of the second conveyor shaft 78 is connected to the left end of a crank-like swinging drive shaft 79 pivotally supported at the rear of the swing sorting disc 26 via a swing sorting belt 112. Accordingly, the threshing clutch 84 is controlled to be turned on and off by the operation of the threshing clutch lever 47 of the operator, and the components of the grain sorting mechanism 10 and the threshing drum 21 are driven by the turning on operation of the threshing clutch 84.

  In addition, the grain conveyor 32 is driven via the conveyor shaft 77 first, and the grain sorted first of the conveyor mechanism 30 is collected in the grain tank 6. Further, the No. 2 reduction conveyor 33 is driven via the No. 2 conveyor shaft 78, and the No. 2 sorted grain (the second thing) in which the scale waste of the No. 2 conveyor mechanism 31 is mixed is the upper surface side of the rocking sorting board 26 Will be returned to Further, in the structure in which a duster 23 is provided with a spreader (not shown) for scattering of scraps, the left end of the rattan shaft 76 is connected to the spreader via the spreader drive pulley 104 and the spreader drive belt 105.

  On the other hand, a beater shaft 82 for supporting the beater 18 is provided. A forward / reverse switching case 121 is disposed at the left end of the beater shaft 82 on the side away from the engine 7. The left end of the beater shaft 82 is inserted into the forward / reverse switching case 121, and the forward / reverse transmission shaft 122 and the forward / reverse switching shaft 123 are provided in the forward / reverse switching case 121. The beater shaft 82 and the forward and reverse transmission shaft 122 are disposed on substantially the same axial center line. The left end of the forward and reverse transmission shaft 122 is connected to the left end of the counter shaft 73 through the reaper drive pulleys 106 and 107, the reaper drive belt 114 and the reaper clutch 115 (tension pulley).

  As shown in FIG. 5, a cutting input shaft 89 is provided as a conveyor input shaft for pivotally supporting the feed end side of the supply conveyor 17. A header drive shaft 91 is rotatably supported on the back side of the right side of the grain header 12. Power can be transmitted between the right end of beater shaft 82 and the right end of reaper input shaft 89 to the left end of header drive shaft 91 extending in the left-right direction through reaper drive chain 116 and sprockets 117 to 119 Connect to The pick-up shaft 93 is provided to support the pick-up auger 13. An intermediate portion of the header drive shaft 91 is connected to the right end of the scratching shaft 93 via a scratching drive chain 92.

  In addition, a reel shaft 94 for supporting the take-in reel 14 is provided. An intermediate portion of the header drive shaft 91 is connected to the right end of the reel shaft 94 via the intermediate shaft 95 and the reel drive chains 96 and 97. The first cutting blade 15 is connected to the right end of the header drive shaft 91 via a first cutting blade driving crank mechanism 98. The feed conveyor 17, the take-in auger 13, the take-in reel 14 and the first cutting blade 15 are driven and controlled by the turning on and off operation of the reaper clutch 115 so that the tip side of the uncut grain weirs in the field is continuously cut off. Configured.

  As shown in FIG. 5, the forward rotation bevel gear 124 integrally formed on the forward and reverse transmission shaft 122, the reverse rotation bevel gear 125 rotatably supported on the reaper input shaft 89, and the reverse rotation bevel gear 125 connected to the forward rotation bevel gear 124. The intermediate bevel gear 126 is installed in the forward / reverse switching case 121. The intermediate bevel gear 126 is always meshed with the forward bevel gear 124 and the reverse bevel gear 125. On the other hand, the slider 127 is slidably spline-engaged on the beater shaft 82 in a slidable manner. The slider 127 is configured to be engageable with the bevel gear 124 for forward rotation via the claw clutch shaped forward rotation clutch 128, and the slider 127 is engaged with the reverse rotation bevel gear 125 via the claw reverse clutch 129. It is configured to be releasably engageable.

  In addition, a forward / reverse switching shaft 123 for sliding operation of the slider 127 is provided, a forward / reverse switching arm 130 is provided on the forward / reverse switching shaft 123, and the forward / reverse switching arm 130 is operated by forward / reverse switching lever (forward / reverse operation tool) operation. It is swung to rotate the forward / reverse switching shaft 123, and the slider 127 is brought into contact with or separated from the forward rotation bevel gear 124 or the reverse rotation bevel gear 125, and the forward rotation bevel gear 124 or the reverse rotation is via the forward clutch 128 or the reverse clutch 129. The slider 127 is selectively engaged with the bevel gear 125, and the reaper input shaft 89 is connected to the forward and reverse transmission shaft 122 in a forward or reverse direction.

  As shown in FIG. 5, the right end of the auger drive shaft 58 is connected to the output shaft 65 of the engine 7 via the tension pulley type auger clutch 56 and the auger drive belt 57. The front end side of the horizontal feed auger 60 at the bottom of the glen tank 6 is connected to the left end of the auger drive shaft 58 via a bevel gear mechanism 59. The vertical feed auger 62 of the grain discharging conveyor 8 is connected to the rear end side of the cross feed auger 60 via a bevel gear mechanism 61. In addition, a grain discharging lever 55 for turning on and off the auger clutch 56 is provided. The grain discharging lever 55 is attached to the front of the grain tank 6 behind the driver's seat 42, and the operator can operate the grain discharging lever 55 from the driver's seat 42 side.

  As shown in FIG. 1, FIG. 2 and FIG. 4, a haircut-like second cutting blade 133 having substantially the same length as the haircut-like first cutting blade 15 is provided. As a second cutting blade frame for mounting the second cutting blade 133 on the traveling machine body 1, a left frame 134, a right frame 135, and a center frame 136 are provided. A second cutting blade base 137 is fixed to the front end side of the left side frame 134, the right side frame 135 and the center frame 136 to constitute a second cutting blade mechanism 132.

  The left and right grounding rods 138 are provided at both ends of the second cutting blade stand 137. The second cutting blade 133 is reciprocably attached between the left and right grounding rods 138 of the second cutting blade stand 137. On the other hand, the base end side of the right side frame 135 is rotatably supported by the cab frame of the traveling body 1. Further, the base end side of the central frame 136 is rotatably supported on the front frame of the traveling body 1.

  As shown in FIG. 5, a second cutting blade drive mechanism 171 for transmitting a driving force from the forward / reverse switching case 121 to the second cutting blade 133 is provided. The second cutting blade drive mechanism 171 includes a second cutting blade drive shaft 172 transmitting a driving force to the second cutting blade 133, and an eccentric rotation shaft 174 coupled to the second cutting blade drive shaft 172 via a bevel gear mechanism 173. , And a second cutting blade drive crank mechanism 175 connected to the eccentric rotation shaft 174. One end side of the second cutting blade drive shaft 172 is pushed into the forward and reverse switching case 121, and the intermediate bevel gear 126 is engaged with the second cutting blade drive shaft 172, and forward and reverse transmission is transmitted via the intermediate bevel gear 126. The second cutting blade drive shaft 172 is connected to the shaft 122.

  The second cutting blade drive crank mechanism 175 includes an eccentric rotary body 177 provided on the eccentric rotary shaft 174, a swing rotary shaft 178 connected to the eccentric rotary body 177, and a swing drive arm 179 connected to the swing rotary shaft 178. And a push / pull rod 180 connecting the second cutting blade 133 to the swinging drive arm 179. It should be noted that instead of the second cutting blade drive shaft 172 and the bevel gear mechanism 173, a pair of sprockets and a transmission chain for connecting the eccentric rotation shaft 174 to the forward and reverse transmission shaft 122 are provided. The driving force of the second cutting blade 133 may be transmitted from the transmission shaft 122 to the second cutting blade drive crank mechanism 175.

  According to the above configuration, one-way rotation of the eccentric rotation shaft 174 is converted into swinging rotation of the swinging rotation shaft 178 (reciprocal rotation for forward and reverse rotation within a predetermined range) to swing the swing drive arm 179, The second cutting blade 133 is made to slide back and forth via the push-pull rod 180, and the remnants of the field immediately after being cut off by the first cutting blade 15 (the stock origin side of the grain scale) are taken by the second cutting blade 133 It is configured to cut and lower the height of stock remaining in the field.

  Further, as shown in FIG. 4, a cylindrical transmission frame 181 having the second cutting blade drive shaft 172 installed therein and a square box-shaped bevel gear case 182 having the bevel gear mechanism 173 installed therein are provided. One end side of the transmission frame 181 is detachably fastened to the forward / reverse switching case 121, and the bevel gear case 182 is detachably fastened to the other end side of the transmission frame 181. That is, the left side frame 134 is supported by the forward and reverse switching case 121 via the eccentric rotation shaft 174, the bevel gear case 182, and the transmission frame 181. The second cutting blade drive crank mechanism 175 is disposed in a second cutting blade drive cover 185 detachably supported on the left side frame 134 (see FIGS. 1 and 3).

  According to the above configuration, by driving the reaper 3 by the operation of the reaper clutch 115, the second cutting blade 133 is operated together with the first cutting blade 15, and the first cutting blade 15 causes the tip of the uncut grain weir of the field The side is cut, and the tip end side of the grain pod is carried from the feeder house 11 to the threshing part 9, and the grain is taken out from the grain sorting mechanism 10 to the grain tank 6. On the other hand, the stumps (remnants) left on the trace where the grain caskets of the field have been cut away by the first cutting blade 15 are appropriately cut at a height by the second cutting blade 133 and left in the field after the harvesting operation The height of) is made low to a substantially constant height. By lowering the height of the stump remaining in the field after the harvesting work, it is possible to improve the post-processing workability (culturing workability, etc.) of the field.

  Next, the power transmission structure of the transmission case 63 and the like will be described with reference to FIGS. 5 and 6. As shown in FIG. 6, a traveling hydraulic linear variable transmission 64 for traveling transmission having a linear pump 64a and a linear motor 64b in a transmission case 63, and a steering hydraulic stepless gear for steering having a turning pump 70a and a turning motor 70b. Machine 70 is provided. The transmission input shaft 66 of the transmission case 63 is configured to be gear-connected and driven by the pump shaft 258 of the linear movement pump 64a and the pump shaft 259 of the swing pump 70a. The engine output belt 67 is wound around a transmission input pulley 169 provided on the projecting end side of the transmission input shaft 66 outside the transmission case 63. The output of the engine 7 is transmitted to the transmission input pulley 169 via the engine output belt 67 to drive the linear pump 64a and the swing pump 70a.

  As shown in FIG. 6, the driving force output from the output shaft 65 of the engine 7 is respectively transmitted to the pump shaft 258 of the linear pump 64a and the pump shaft 259 of the swing pump 70a via the engine output belt 67 and the transmission input shaft 66. It is transmitted. In the linear hydraulic continuously variable transmission 64, hydraulic oil is appropriately fed from the linear pump 64a toward the linear motor 64b by the power transmitted to the pump shaft 258. Similarly, in the swing hydraulic continuously variable transmission 70, hydraulic fluid is appropriately fed from the swing pump 70a to the swing motor 70b by the power transmitted to the pump shaft 259. The pump shaft 259 of the swing pump 70a is attached with a transmission charge pump 151 for supplying hydraulic fluid to the straight drive pump 64a, the straight drive motor 64b, the swing pump 70a and the swing motor 70b.

  The straight forward hydraulic continuously variable transmission 64 shifts straight by changing and adjusting the inclination angle of the rotary swash plate in the straight forward pump 64a in accordance with the amount of turning operation of the main shift lever 44 and the steering handle 43 disposed on the steering column 41. The discharge direction and discharge amount of the hydraulic oil to the motor 64b are changed. As a result, the rotation direction and the number of rotations of the straight moving motor shaft 260 protruding from the straight moving motor 64 b are arbitrarily adjusted.

  As shown in FIG. 6, the rotational power of the rectilinear motor shaft 260 is transmitted from the rectilinear transmission gear mechanism 250 to the auxiliary transmission gear mechanism 251. The auxiliary transmission gear mechanism 251 includes an auxiliary transmission low speed gear 254, an auxiliary transmission middle speed gear 255, and an auxiliary transmission high speed gear 256 which are switched by the auxiliary transmission shifters 252 and 253 linked to each other. The low speed auxiliary transmission shifter 252 is pivotally supported by a parking brake shaft 265 (an auxiliary transmission output shaft) positioned on the output side of the auxiliary transmission gear mechanism 251. The high-speed auxiliary shift shifter 253 is pivotally supported by an auxiliary shift counter shaft 270 constituting the straight transmission gear mechanism 250. By the operation of the auxiliary transmission lever 45 disposed on the control column 41, the output rotational speed of the rectilinear motor shaft 260 is alternatively switched to three speed stages, low speed, medium speed or high speed. In the embodiment, a neutral position (a position at which the output of the auxiliary shift is zero) is provided between the low speed and the intermediate speed of the auxiliary shift.

  As shown in FIG. 6, a drum type parking brake 266 is provided on the parking brake shaft 265 (sub transmission output shaft). The rotational power from the auxiliary transmission gear mechanism 251 is transmitted from the auxiliary transmission output gear 267 fixed to the parking brake shaft 265 to the left and right differential mechanisms 257. The left and right differential mechanisms 257 each include a planetary gear mechanism 268. A straight driving pulser 292 is provided on the parking brake shaft 265. A straight traveling vehicle speed sensor 293 (see FIG. 9) is disposed opposite to the outer periphery of the straight driving pulser 292. The straight traveling vehicle speed sensor 293 detects the number of revolutions of the straight traveling output (also referred to as the straight traveling vehicle speed and the shift output of the auxiliary shift output gear 267).

  As shown in FIG. 6, each of the left and right planetary gear mechanisms 268 includes one sun gear 271 meshing with the auxiliary transmission output gear 267, a plurality of planet gears 272 meshing with the sun gear 271, a ring gear 273 meshing with the planet gears 272, and a plurality of planets The gears 272 are respectively provided with carriers 274 rotatably arranged on the same circumference. The left and right carriers 274 are opposed to each other on the same axis (the axes of the sun gear shaft 275 and the left and right forced differential output shafts 277 described later) with an appropriate interval. The left and right sun gears 271 are fixed to both ends of the sun gear shaft 275 in the axial direction. A center gear 276 is fixed to a midway portion in the axial direction of the sun gear shaft 275.

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

  The turning hydraulic continuously variable transmission 70 turns by changing and adjusting the inclination angle of the rotary swash plate in the turning pump 70a in accordance with the amount of turning operation of the main transmission lever 44 and the steering handle 43 disposed on the steering column 41. The discharge direction and discharge amount of the hydraulic oil to the motor 70b are changed. As a result, the rotational direction and the number of rotations of the swinging motor shaft 261 protruding from the swinging motor 70b are arbitrarily adjusted. A turning pulser 294 is provided on a steering counter shaft 280 (details will be described later). A turning vehicle speed sensor 295 (see FIG. 9) is disposed opposite to the outer circumference of the turning pulser 294. The turning vehicle speed pulser 295 detects the number of revolutions of the turning output (also referred to as turning vehicle speed).

  As shown in FIG. 6, in the transmission case 63, a wet multi-plate type swing brake 279 (steering brake) provided on the swing motor shaft 261 (steering input shaft) and an upstream reduction gear to the swing motor shaft 261 A steering counter shaft 280 connected via 281, a steering output shaft 285 connected to the steering counter shaft 280 via a downstream reduction gear 286, and a steering output shaft 285 via a reverse gear 284 to the left ring gear 273. , And a right input gear mechanism 283 in which the steering output shaft 285 is connected to the right ring gear 273.

  The rotational power of the turning motor shaft 261 is transmitted to the steering counter shaft 280 via the upstream reduction gear 281. 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 of the left input gear mechanism 282 and the reverse gear 284, while the rotational power of the right input gear mechanism 283 is The power is transmitted to the right ring gear 273 as forward rotational power via the right intermediate gear 288.

  When the auxiliary transmission gear mechanism 251 is made neutral, power transmission from the linear motor 64b to the left and right planetary gear mechanisms 268 is blocked. When the auxiliary transmission gear mechanism 251 is set to a gear position other than neutral, power is transferred from the linear motor 64b to the left and right planetary gear mechanisms 268 via the auxiliary transmission low speed gear 254, the auxiliary transmission middle speed gear 255 or the auxiliary transmission high speed gear 256. It is transmitted.

  On the other hand, when the output of the swing pump 70a is in the neutral (neutral) state and the swing brake 279 is in the on state, power transmission from the swing motor 70b to the left and right planetary gear mechanisms 268 is blocked. When the output of the swing pump 70a is 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. And the right ring gear 273 via the right input gear mechanism 283.

  At the time of forward rotation (reverse rotation) of the turning motor 70b, the left ring gear 273 reverses (forwards) at the same rotational speed in the opposite direction, and the right ring gear 273 rotates forward (reverse). That is, the shift output of each motor shaft 260, 261 is transmitted to the drive sprocket 51 of the crawler belt 2 on the left and right through the auxiliary transmission gear mechanism 251 or the differential mechanism 257 on the left and right, respectively. The speed) and the direction of travel are determined.

  That is, when the linear motor 64b is driven while the swing motor 70b is stopped and the left and right ring gears 273 are fixed stationary, the rotational output of the linear motor shaft 260 is transmitted to the left and right sun gears 271 at the same number of rotations. The right and left crawler belts 2 are driven at the same rotational speed in the same direction via the carrier 274, and the traveling body 1 travels straight.

  Conversely, when the linear motor 64b is stopped and the swing motor 70b is driven with the left and right sun gears 271 fixed stationary, the left ring gear 273 rotates forward (reverse) by the rotational power of the swing motor shaft 261 and the right ring gear 273 rotates in the reverse direction (forward rotation). As a result, one of the drive sprockets 51 of the left and right crawler belts 2 rotates forward and the other reversely rotates, and the traveling airframe 1 is turned on the spot (also referred to as pivot turning or spin turn).

  When the left and right ring gears 273 are driven by the swing motor 70b while driving the left and right sun gears 271 by the straight drive motor 64b, a difference occurs in the speeds of the crawler belts 2 and the traveling machine body 1 turns while moving forward or backward. Turn to the left or right (U-turn) with a turning radius greater than the radius. The turning radius at this time is determined according to the speed difference between the left and right crawler belts 2. The traveling driving force of the engine 7 is constantly transmitted to the left and right crawler belts 2 and the vehicle is turned to the left or right.

  Next, the hydraulic circuit structure of the vehicle drive device will be described with reference to FIG. The hydraulic circuit 200 of the vehicle drive device includes a straight drive pump 64a, a straight drive motor 64b, a swing pump 70a, a swing motor 70b, and a transmission charge pump 151. The straight drive pump 64a and the straight drive motor 64b are connected in a closed loop by the straight first oil passage 201a and the straight second oil passage 201b. The straight first oil passage 201 a and the straight second oil passage 201 b constitute a straight closing oil passage 201. The swing pump 70a and the swing motor 70b are connected in a closed loop by the swing first oil passage 202a and the swing second oil passage 202b. The swirling first oil passage 202 a and the swirling second oil passage 202 b constitute a swirling closed oil passage 202. The rotational power of the engine 7 drives the straight drive pump 64a and the swing pump 70a, and controls the swash plate angle of the straight drive pump 64a and the swing pump 70a to discharge hydraulic oil to the straight drive motor 64b and the swing motor 70b. The amount is changed, and the linear movement motor 64b and the turning motor 70b operate in the forward and reverse directions.

  As shown in FIG. 7, the hydraulic circuit 200 of the vehicle drive device is connected to the transmission charge pump 151 via the straight movement valve 203 which is switched in response to the manual operation of the main shift lever 44 and the straight movement valve 203. And a straight-moving cylinder 204. When the straight movement valve 203 is switched and operated, the straight movement cylinder 204 is operated to change the swash plate angle of the straight movement pump 64a and change the rotation number of the straight movement motor shaft 260 of the straight movement motor 64b steplessly or reversely The action is performed. Further, the hydraulic circuit 200 of the vehicle drive device also includes a hydraulic servo mechanism 205 for linear shift. The hydraulic servo mechanism 205 executes a feedback operation in which the straight drive valve 203 returns to neutral by the swash plate angle control of the straight drive pump 64a, and changes the swash plate angle of the straight drive pump 64a in proportion to the manual operation amount of the main shift lever 44, The linear motor shaft 260 rotation speed of the linear motor 60b is changed.

  On the other hand, the hydraulic circuit 200 of the vehicle drive device includes a swing valve 206 which is switched in response to the manual operation of the steering handle 43, and a swing cylinder 207 connected to the transmission charge pump 151 via the swing valve 206. ing. When the turning valve 206 is operated to switch, the turning cylinder 207 operates to change the swash plate angle of the turning pump 70a, and the turning motor shaft 261 rotation speed of the turning motor 70b changes steplessly or reversely. The operation is executed, and the traveling body 1 changes the traveling direction to the left and right to change the direction or correct the course in the field headland. The hydraulic circuit 200 of the vehicle drive device also includes a hydraulic servo mechanism 208 for turning shift. The hydraulic servo mechanism 208 performs feedback operation in which the swing valve 206 returns to neutral by the swash plate angle control of the swing pump 70a, and changes the swash plate angle of the swing pump 70a in proportion to the manual operation amount of the steering handle 43, The rotation motor shaft 261 rotation speed of the rotation motor 70b is changed.

  As shown in FIG. 7, a charge branch oil passage 219 (details will be described later) is connected to all the oil passages 201a, 201b, 202a, 202b of the both closed oil passages 201, 202. A check valve 211 for the straight first oil passage 201a is provided between the charge branch oil passage 219 and the straight first oil passage 201a. A check valve 211 for the straight second oil passage 201b is provided between the charge branch oil passage 219 and the straight second oil passage 201b. Therefore, the straight closing oil passage 201 is provided with two check valves 211. Further, a check valve 212 for the swirling first oil passage 202a is provided between the charge branch oil passage 219 and the swirling first oil passage 202a. Between the charge branch oil passage 219 and the turning second oil passage 202b, a check valve 212 for the turning second oil passage 202b is provided. Therefore, the swing closed oil passage 202 is also provided with two check valves 212.

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

  The suction side of the transmission charge pump 151 is connected to a strainer 217 in the transmission case 63. A charge introduction oil passage 218 is connected to the discharge side of the transmission charge pump 151. A charge branch oil passage 219 is connected to the downstream side of the charge introduction oil passage 218. As described above, the charge branch oil passage 219 is connected to all the oil passages 201a, 201b, 202a, 202b of the both closed oil passages 201, 202. Therefore, while the engine 7 is in operation, hydraulic oil from the transmission charge pump 151 is constantly replenished in both the closed oil passages 201 and 202. The charge branch oil passage 219 is connected to the straight movement cylinder 204 via the straight movement valve 203 and is connected to the turning cylinder 207 via the turning valve 206. The charge branch oil passage 219 is connected via a relief valve 220 to a continuously variable transmission case 323, which will be described later, and to a transmission case 63. Therefore, the surplus of hydraulic oil from the transmission charge pump 151 is returned to the inside of the transmission case 63 via the continuously variable transmission case 323 via the relief valve 220.

  Next, with reference to FIGS. 1 to 3 and 8, a driving operation structure such as the steering handle 43 will be described. As shown in FIG. 8, a step frame 311 is provided which constitutes a footrest flat portion for boarding an operator in the cab 5. A plurality of leg frames 312 are erected on the upper surface side of the traveling machine body 1, and a step frame 311 is erected on the upper end side of the leg frames 312. A landing step (not shown) is fixed to the side surface of the leg frame 312 on the right side outer side of the step frame 311, and the hydraulic oil tank 315 is disposed on the inner side of the landing step (not shown). A hydraulic valve unit body 314 is attached below the front end of the step frame 311 in the upper surface.

  In addition, a steering case 318 having a steering operation shaft 316 and a continuously variable transmission operation shaft 317 is provided. Both ends of the case support horizontal frame 319 are connected between the left and right leg frames 312 on the front lower surface side of the step frame 311, and the steering case 318 is detachably fastened and fixed to the substantially horizontal case support horizontal frame 319. A steering case 318 is supported in multiple stages directly above the hydraulic valve unit body 314 via a case support horizontal frame 319. A steering operation shaft 316 is projected upward from the upper surface of the steering case 318, and the steering handle 43 is connected to the steering handle 43 via the steering shaft 321, and from the left side of the steering case 318 to the left The continuously variable transmission operation shaft 317 is protruded toward the main transmission lever 44, and the continuously variable transmission operation shaft 317 is connected to the main transmission lever 44 via the continuously variable transmission operation rod 322.

  In addition, there is provided a continuously variable transmission case 323 in which the linear hydraulic continuously variable transmission 64 and the turning hydraulic continuously variable transmission 70 are assembled. The continuously variable transmission case 323 is fixed to the upper right side of the transmission case 63, and on the front and rear surfaces of the continuously variable transmission case 323, the continuously variable operation arm body 324 for going straight and turning is disposed. The straight movement control link 345 and the turn control link 346 provided on the rear side of the steering case 318 are connected to the stepless speed change operation arm 324 for going straight and turning respectively, and steering operation of the steering handle 43 and the main speed change lever 44 The linear hydraulic continuously variable transmission 64 and the turning hydraulic continuously variable transmission 70 are operationally controlled by the gear shift operation, and the path and the moving speed of the left and right crawler belts 2 can be changed.

  The hydraulic oil tank 315 is disposed below the right side of the rectangular step frame 311 in plan view, and the continuously variable transmission case 323 is disposed below the left side of the step frame 311, and the hydraulic valve unit is disposed below the front of the step frame 311. Since the body 314 and the steering case 318 are arranged in the upper and lower stages, the engine 7 (hydraulic oil pump) at the rear of the steering case 318 is provided via the space formed between the hydraulic oil tank 315 and the continuously variable transmission case 323. The hydraulic piping can be easily extended between the front hydraulic valve unit body 314, the hydraulic oil tank 315, and the hydraulic actuators (lifting hydraulic cylinders 4) of the respective parts, and maintenance operability of the hydraulic equipment can be improved.

  Next, the schematic structure of the transmission case 63 will be described with reference to FIGS. As shown in FIG. 8, the engine 7 is mounted on the upper right side of the traveling body 1, and the transmission case 63 is disposed in front of the center of the lateral width of the traveling body 1. An engine output pulley 168 is supported at the left end of an output shaft 65 of the engine 7, and an engine output belt 67 is wound around a transmission input pulley 169 and an engine output pulley 168 located on the upper left side of the transmission case 63. The output of the engine 7 is transmitted to the hydraulic continuously variable transmissions 64 and 70 of the transmission case 63 through the engine output belt 67, respectively.

  The transmission case 63 has a split structure that can be vertically divided vertically and horizontally, and has a substantially hollow box shape by fastening with a plurality of bolts. The lower part of the transmission case 63 is a bifurcated shape projecting outward in the left and right direction and projecting downward, and roughly speaking it has a substantially gate-like shape in a front view. An axle case 336 projecting outward in the left and right direction is bolted to a gear case portion 335 which protrudes downward from the lower portion of both left and right side surfaces of the transmission case 63. Axles 278 are rotatably supported in left and right axle cases 336, respectively. Drive sprockets 51 (see FIGS. 1, 2 and 6) are attached to the projecting ends of the left and right axles 278. As shown in FIG. 8, the bottoms of the left and right gear case parts 335 are located below the bottom of the transmission case 63, and the bottom of the transmission case 63 is higher than the left and right axle cases 336.

  On the upper right side of the transmission case 63, there is attached a continuously variable transmission case 323 in which the linear and turning hydraulic continuously variable transmissions 64 and 70 are assembled. In this case, the linear hydraulic stepless transmission 64 (the linear pump 64a and the linear motor 64b) is positioned on the front side in the variable speed case 323, and the swing hydraulic stepless transmission 70 (the turn pump 70a and the turn motor) on the rear side. 70b) is located. In the transmission case 63, gear trains such as the auxiliary transmission gear mechanism 251 and the differential mechanism 257 described with reference to FIG. 6 are accommodated.

  On the front side of the continuously variable transmission case 323, a straight operating shaft 325 for changing the discharge direction and the discharge amount of hydraulic oil to the straight moving motor 64b is made to project forward by operating the swash plate of the straight moving pump 64a. When the linear movement operation shaft 325 is rotated about the axis, the swash plate angle of the linear movement pump 64a is changed, and the discharge direction and the discharge amount of hydraulic fluid to the linear movement motor 64b are changed. On the rear surface side of the continuously variable transmission case 323, a swing operation shaft 326 for changing the discharge direction and discharge amount of the hydraulic oil to the swing motor 70b by operating the swash plate of the swing pump 70a is projected backward. When the turning operation shaft 326 is turned about the axis, the swash plate angle of the turning pump 70a is changed, and the discharge direction and the discharge amount of the hydraulic oil to the turning motor 70b are changed.

  As shown in FIG. 9, the transmission charge pump 151 is attached to the right side of the continuously variable transmission case 323 at a position corresponding to the turning pump 70a. The transmission charge pump 151 is connected to a strainer 221 (see FIG. 7) on the inner bottom side of the transmission case 63 via a suction hose 337 extending vertically. As described above, the transmission charge pump 151 is rotationally driven by the pump shaft 259 of the swing pump 70a. The hydraulic oil on the inner bottom side of the transmission case 63 is drawn into the charge pump 151 via the transmission by the strainer 221 and the suction hose 337 by the drive of the transmission charge pump 151, and the oil passages 201, 202, 211 of the hydraulic circuit 200. , 212, 217 to 210, 222 to 224, and so on.

  As shown in FIG. 9, a parking brake arm 338 for braking the parking brake 266 is provided below the swing motor 70b on the right side surface of the transmission case 63. When the parking brake 266 is braked by the braking operation of the parking brake arm 338, the parking brake shaft 265 and the auxiliary transmission output gear 267 are non-rotatably locked, and the linear output toward the left and right drive sprockets 51 is stopped. When the steering handle 43 and the auxiliary transmission gear mechanism 251 are neutral, the swing brake 279 maintains the swing motor shaft 261 in a stopped (non-rotatable) state. As a result, the output of the swing motor 70b, that is, the swing output toward the left and right drive sprockets 51 is stopped.

  As shown in FIGS. 8 to 10, on the front side of the transmission case 63, an auxiliary transmission arm 339 for operating the auxiliary transmission shifters 252 and 253 of the auxiliary transmission gear mechanism 251 is provided. The auxiliary transmission arm 339 is interlocked with the auxiliary transmission lever 45 on the control column 41. By the operation of the auxiliary transmission arm 339 via the auxiliary transmission lever 45, the auxiliary transmission shifters 252 and 253 are switched and operated in conjunction with each other, and the output rotational speed of the linear motor shaft 260 is low, medium or high. It can be switched to the shift gear alternatively.

  As shown in FIGS. 8 and 10, on the upper left side of the transmission case 63, a transmission input shaft 66 connected to the straight drive pump 64a and the swing pump 70a in a power transmittable manner is protruded outward. The transmission input pulley 169 is fixed to the projecting end side of the transmission input shaft 66, and the engine output belt 67 is wound around the transmission input pulley 169. An oil reservoir 340 (see FIG. 11) is formed on the upper front side in the transmission case 63. Although not shown in detail, one end of the upper external pipe is connected to the upper surface of the oil reservoir 340 of the transmission case 63, and the other end of the upper external pipe is connected to the upper surface of the continuously variable transmission case 323. There is. The hydraulic oil sucked up by the transmission charge pump 151 from the inner bottom side of the transmission case 63 is used by the hydraulic continuously variable transmissions 64 and 70 in the continuously variable transmission case 323, and from the continuously variable transmission case 323 via the upper external piping. Flows into the oil reservoir 340 and is stored.

  A horizontal external pipe 341 is disposed below the transmission input pulley 169 in the left side surface of the transmission case 63. The lateral external piping 341 is externally attached to the transmission case 63. One end side of the horizontal external pipe 341 is connected to the oil reservoir 340 on the left side surface of the transmission case 63. The other end side of the horizontal external piping 341 is connected to the position of the swing motor shaft 261 (swing brake 279) on the left side surface of the transmission case 63. The hydraulic oil in the oil reservoir 340 is sent directly to the pivoting brake 279 of the pivoting motor shaft 261. The hydraulic fluid from the oil reservoir 340 lubricates the turning brake 279.

  Under the lateral external piping 341 on the left side of the transmission case 63, a straight vehicle speed sensor 293 for the straight pulser 292 on the parking brake shaft 265 and a turning vehicle speed sensor 295 for the turning pulser 294 of the steering counter shaft 280 It is provided. The two vehicle speed sensors 293 and 295 are arranged forward and backward on the left side surface of the transmission case 63, and the straight vehicle speed sensor 293 is on the front side and the turning vehicle speed sensor 295 is on the rear side. In the embodiment, two vehicle speed sensors 293 and 295 are provided for the corresponding pulsers 292 and 294 from the viewpoint of fail safe.

  In addition, the diameter of the straight-travel pulser 292 is larger than that of the conventional structure (see, for example, JP 2012-82918 A, etc.), and a thickness having a predetermined width is provided (see FIGS. 12 and 14). Then, the outer peripheral side of the straight pulser 292 is detected by the straight vehicle speed sensor 293. These are designed for the purpose of avoiding interference with the reaper 3 and the like by preventing the straight pulser 292 and the straight vehicle speed sensor 293 from projecting largely to the left outside of the transmission case 63.

  Incidentally, FIG. 19 shows a mounting structure of the axle 278 and the drive sprocket 51 with respect to the axle case 336. As shown in FIG. 19, in the axle case 336, an axle 278 is rotatably supported via two shield type bearings 388. The tip end side of the axle 278 projects left and right outward from the axle case 336. On the tip end side of the axle 278, a spline 278c in which the boss 51a of the drive sprocket 51 is fitted and a screw 278d into which a nut 390 is screwed via a washer 389 are formed. The boss portion 51a of the drive sprocket 51 is spline fitted to the spline portion 278c of the axle 278, and the nut 390 is screwed into the screw portion 278d of the axle 278 via the washer 389. It is worn to rotate.

  On the open side of the axle case 336, a bearing oil seal 391 for sealing the left and right outer sides of the both shield type bearings 388 is fitted. A bearing oil seal 391 is fitted on the outer peripheral side of the bearing seal collar 51 b extending inward in the left and right direction from the boss 51 a of the drive sprocket 51. The opening side of the axle case 336 is closed by the bearing oil seal 391. On the left and right inner side surfaces of the drive sprocket 51, an annular anti-rolling ring body 392 is formed so as to protrude leftward and rightward so as to be concentric with the bearing seal collar 51b. In a state where the drive sprocket 51 is attached to the tip end side of the axle 278, the anti-winding ring body 392 is fitted on the step portion 336a on the outer periphery of the opening of the axle case 336. The engagement between the step portion 336a of the axle case 336 and the anti-rolling wheel body 392 prevents the entry of field grass, mud, etc. between the axle case 336 and the drive sprocket 51.

  On the inner peripheral side of the axle case 336, a stop ring 393 for restricting the positional deviation of the both shield type bearings 388 to the left and right outside is detachably mounted. A positioning collar 394 for restricting the positional deviation of the both shield type bearings 388 to the left and right inside is fitted on a portion of the axle 278 on the left and right sides of the both shield type bearings 388. In a state where the drive sprocket 51 is attached to the tip end side of the axle 278, the both shield type bearings 388 are held by the stop ring 393 and the positioning collar 394 so as not to be displaced. The bearing seal collar 51 b of the drive sprocket 51 abuts the stop ring 393.

  An annular packing body 395 made of rubber is disposed between the end of the spline portion 278 c of the axle 278 and the washer 389. The packing body 395 is in close contact with the front end side of the spline portion 278 c and the washer 389. In the embodiment, lubricating oil (grease or gear oil) is enclosed between the boss 51 a of the drive sprocket 51 and the spline 278 c of the axle 278. The tight structure of the packing body 395 suppresses lubricating oil leakage from between the boss 51a and the spline 278c, and intrusion of muddy water or the like between the boss 51a and the spline 278c and hence into the axle case 336. To suppress. By using the packing body 395, the sealability between the boss portion 51a and the spline portion 278c is improved as compared with the conventional structure (see, for example, JP 2012-231707 A, etc.).

  Next, the internal structure of the transmission case 63 will be described mainly with reference to FIGS. 11 to 13. As shown in FIGS. 11 to 13, on the inner bottom side of the transmission case 63, a pair of left and right differential mechanisms 257 (planetary gear mechanisms 268) are disposed. Each planetary gear mechanism 268 is divided into right and left with a center gear 276 fixed to a sun gear shaft 275 extending to the left and right. On the upper side of the planetary gear mechanism 268, the parking brake shaft 265 located on the output side of the auxiliary transmission gear mechanism 251, the steering output shaft 285, and the rotation shaft of the reverse rotation gear 284 are arranged side by side. A middle intermediate gear 289 which is constantly meshed with the downstream reduction gear 286 is fixed to a midway portion of the steering output shaft 285 (between the left intermediate gear 287 and the right intermediate gear 288). In the embodiment, the center gear 276 and the center intermediate gear 286 are in such a positional relationship as to interfere with the center intermediate gear 286 when the center gear 276 has a normal spur gear shape. For this reason, the center gear 276 of the embodiment has a substantially wedge shape with the outer peripheral portion curved to the left (the outer peripheral portion is offset to the left from the rotation center), and the center intermediate gear on the steering output shaft 285 Avoid interference with 286.

  An auxiliary shift counter shaft 270 is disposed between the planetary gear mechanism 268 and the steering output shaft 285 in the front-rear direction and on the upper side. A steering counter shaft 280 is disposed on the rear side of the auxiliary shift counter shaft 270. A straight advance motor shaft 260 is disposed on the upper side of the auxiliary shift counter shaft 270. A turning motor shaft 261 is disposed on the upper side of the steering counter shaft 280. A swing brake 279 is provided on the swing motor shaft 261. The pump shaft 258 of the linear movement pump 64 a is disposed on the upper side of the linear movement motor shaft 260. The pump shaft 259 of the swing pump 70 a is disposed on the upper side of the swing motor shaft 261. A transmission input shaft 66 is disposed on the upper side between the front and rear directions of both pump shafts 258 and 259.

  As shown in FIG. 11, in the transmission case 63, the height position of the hydraulic fluid surface during driving of the engine 7 is set to such an extent that the parking brake shaft 265 and the steering output shaft 285 are immersed in the hydraulic fluid. For this reason, in the transmission case 63, the auxiliary shift counter shaft 270 and the steering counter shaft 280, and the shafts 66, 258 to 261 above them are located above the hydraulic fluid level. These seven shafts 66, 258-261, 270, 280 do not rotate in a state of being immersed in the hydraulic oil, thereby suppressing an increase in agitation resistance (an increase in power loss).

  As shown in FIGS. 11, 12 and 14, the auxiliary transmission gear mechanism 251, which is an example of the transmission gear mechanism, is divided into an input gear portion 351 and an output gear portion 352. In the embodiment, the low-speed relay gear 354, the medium-speed relay gear 355, and the high-speed relay gear 356 are axially supported by the auxiliary transmission counter shaft 270 which is the input-side transmission shaft as the input side gear portion 351. The low speed relay gear 354 and the middle speed relay gear 355 are fixed to the auxiliary shift counter shaft 270. The high-speed relay gear 356 is rotatably loosely fitted on the auxiliary shift counter shaft 270. Further, as the output side gear portion 352, the auxiliary transmission low speed gear 254, the auxiliary transmission middle speed gear 255, and the auxiliary transmission high speed gear 256 are pivotally supported by the parking brake shaft 265 which is the output transmission shaft. The auxiliary shift low speed gear 254 and the auxiliary shift middle speed gear 255 are rotatably fitted on the parking brake shaft 265. The auxiliary shift high speed gear 256 is fixed to the parking brake shaft 265. By the slide movement of the low speed auxiliary transmission shifter 252, the auxiliary transmission low speed gear 254 and the auxiliary transmission middle speed gear 255 are alternatively connected to the parking brake shaft 265. By the slide movement of the high speed auxiliary shift shifter 253, the auxiliary shift high speed gear 256 is connected to the auxiliary shift counter shaft 270.

  As can be seen from FIG. 11, in the transmission case 63, the auxiliary shift counter shaft 270 on the input side of the auxiliary shift is located above the parking brake shaft 265 on the output side of the auxiliary shift. Therefore, in the transmission case 63, the input gear portion 351 (354 to 356) attached to the auxiliary shift counter shaft 270 and the output gear portion 352 (254 to 256) attached to the parking brake shaft 265 are divided up and down Are placed close to each other. Further, as described above, in the transmission case 63, the height position of the hydraulic fluid surface during driving of the engine 7 is set to such an extent that the parking brake shaft 265 is immersed in the hydraulic fluid. Therefore, a part of the output side gear portion 352 is immersed in the hydraulic oil in the transmission case 63. The input side gear portion 351 is located above the hydraulic fluid surface in the transmission case 63, and does not rotate in a state of being immersed in the hydraulic fluid.

  As shown in FIG. 14, the hydraulic oil splashed up by the output gear section 352 (254 to 256) is guided to the input gear section 351 (354 to 356) on the auxiliary shift counter shaft 270 on the input side of the auxiliary shift. A T-shaped lubrication passage 357 is formed. In the embodiment, the fitting recesses 358 and 359 are formed on both left and right inner walls of the transmission case 63. One end side of the auxiliary shift counter shaft 270 is rotatably fitted in the right fitting recess 358 via the open type bearing 360. The other end side of the auxiliary shift counter shaft 270 is rotatably fitted in the left fitting recess 359 via the open bearing 361. An inlet 357 a of the lubricating passage 357 is opened at one end surface of the auxiliary shift counter shaft 270. The inlet 357 a of the lubricating passage 357 is exposed to the right fitting recess 358. At the outer peripheral surface of the auxiliary shift counter shaft 270, two outlets 357b of the lubricating passage 357 are opened. Each outlet 357 b of the lubricating passage 357 faces the inner peripheral side of the high-speed relay gear 356 close to the high-speed auxiliary transmission shifter 253.

  In this case, the hydraulic oil splashed up at the output side gear portion 352 (254 to 256) is splashed from the outer peripheral side to the input side gear portion 351 (354 to 356) including the high speed auxiliary shift shifter 253. In addition, a part of the hydraulic oil that has been splashed enters the right fitting recess 358 through the right open bearing 360, and the high-speed relay gear 356 through the lubrication passage 357 communicated with the right fitting recess 358. It is supplied to the high speed auxiliary shift shifter 253 located in the vicinity thereof. As a result, the high-speed relay gear 356 and the high-speed auxiliary shift shifter 253 are lubricated.

  As is apparent from the above description and FIGS. 11, 12, and 14, a plurality of continuously variable transmissions 64 and 70 for continuously changing the power of the engine 7 and a plurality of transmission outputs of the continuously variable transmissions 64 and 70 In the vehicle drive device provided with a transmission case 63 incorporating a transmission gear mechanism 251 switched in stages, the transmission gear mechanism 251 is divided into an input gear portion 351 and an output gear portion 352, and the output gear portion The input side in the transmission case 63 is disposed so that a part of the part 352 is immersed in the hydraulic oil in the transmission case 63 and the input side gear portion 351 is positioned above the hydraulic oil surface in the transmission case 63. Since the gear portion 351 and the output side gear portion 352 are divided up and down and arranged close to each other, rotation of the output side gear portion 352 The hydraulic fluid can be splashed on the input side gear portion 351 at a high position, and therefore, the hydraulic fluid level in the transmission case 63 is set high to increase the hydraulic fluid usage without increasing the hydraulic fluid usage amount. The part 351 can be reliably lubricated. Since the input side gear portion 351 is not immersed in the hydraulic fluid, problems such as an increase in power loss and a significant increase in hydraulic fluid temperature can be suppressed.

  In particular, according to the embodiment, since the hydraulic oil splashed up in the output side gear portion 352 can be supplied to the inner peripheral side of the input side gear portion 351 via the lubricating passage 357 of the input side transmission shaft 270, the input side The lubricity of the gear portion 351 (specifically, the high-speed auxiliary shift shifter 253 and the high-speed relay gear 356) can be further improved.

  As shown in FIG. 10, FIG. 12 and FIG. 15, a PTO boss portion 365 as a cylindrical portion is integrally formed below the lateral external piping 341 on the left side surface of the transmission case 63. A PTO shaft 366 (see FIG. 16) as a shaft member for transmitting power to the reaper 3 and the threshing unit 9 can be attached to the PTO boss 365. In the ordinary type combine according to the embodiment, the PTO shaft 366 is unnecessary because the drive power of the engine 7 is directly transmitted to the reaper 3 and the threshing part 9 and the like. Therefore, the opening of the PTO boss 365 is closed by the sealing lid 364 without attaching the PTO shaft 366 to the PTO boss 365 (see FIGS. 12 and 15).

  FIG. 16 shows an example in which the PTO shaft 366 is mounted on the PTO boss 365 by applying the vehicle drive device of the present invention to a self-removing type combine. In the example of FIG. 16, the PTO shaft 366 is rotatably supported by the PTO boss 365 via bearings 367 and 368. The bearing bodies 367 and 368 are paired in the axial direction of the PTO shaft 366. A PTO pulley 369 is mounted on the outer end side of the PTO shaft (the end outside the transmission case 63). On the inner end side of the PTO shaft 366 (the end portion in the transmission case 63), a PTO output gear 370 as a rotating member to which power is transmitted from the auxiliary shift counter shaft 270 is attached. In this case, the PTO input gear 371 is mounted between the low speed relay gear 354 and the middle speed relay gear 355 of the auxiliary shift counter shaft 270. The PTO input gear 371 is constantly meshed with the PTO output gear 370. Therefore, the PTO shaft 366 is always rotationally driven while the engine 7 is driven by the driving force (the driving force of the linear movement motor 64b) via the linear movement motor shaft 260 and the auxiliary shift counter shaft 270.

  On the inner peripheral side of the PTO boss portion 365, step portions 373 and 374 projecting radially outward are formed. A first step portion 373 corresponding to the first bearing 367 is formed at a position outside the transmission case 63 on the inner peripheral side of the PTO boss portion 365. A second step portion 374 corresponding to the second bearing body 368 is formed on the inner peripheral side of the PTO boss portion 365 and inward of the transmission case 63. A large diameter portion 375 larger in diameter than the inner diameter of the bearing body 367, 368 is formed at the end of the PTO shaft 366, or a PTO output gear 370 larger in diameter than the inner diameter of the bearing body 367, 368 is detachable It is wearing. In the example of FIG. 16, a large diameter portion 375 having a diameter larger than the inner diameter of the first bearing 367 is formed on the outer end side of the PTO shaft 366. At the inner end side of the PTO shaft 366, a PTO output gear 370 larger in diameter than the second bearing body 368 is axially slidably and non-rotatably coupled (spline fitting).

  The large diameter portion 375 and the first step portion 373 sandwich the first bearing 367 from both sides in the axial direction. Further, the second bearing body 368 is sandwiched from both sides in the axial direction by the PTO output gear 370 and the second step portion 374. That is, the bearing bodies 367 and 368 are held by the large diameter portion 375 or the PTO output gear 370 and the step portions 373 and 374 in the PTO boss portion 365. A retaining ring 376 is detachably attached to a portion of the PTO shaft 366 further inward of the transmission case 63 than the PTO output gear 370.

  With the above configuration, the PTO shaft 366 can be easily pulled out of the PTO boss 365 by removing the retaining ring 376 with the transmission case 63 separated left and right. Conversely, when attaching the PTO shaft 366 to the PTO boss 365, after attaching the pair of bearing bodies 367 and 368 to the PTO boss 365 with the transmission case 63 separated to the left and right, both sides from the mission case 63 outside The PTO shaft 366 may be inserted into the inner peripheral side of the bearing bodies 367 and 368, and the PTO output gear 370 may be spline-fitted to the inner end side of the PTO shaft 366 to mount the retaining ring 376. Due to the presence of the two step portions 373 and 374, the position of both bearing bodies 367 and 368 can be regulated only by mounting the PTO shaft 366 and the PTO output gear 370.

  Therefore, the attachment of the PTO shaft 366 and the PTO output gear 370 etc. and the attachment and detachment of the sealing lid 374 simplify the configuration of the vehicle drive device (mission case 63) to the specifications with the PTO shaft 366 and the specifications without the PTO shaft 366. Can be changed to One type of vehicle drive device (mission case 63) can be shared by two specifications, one for the self-eliminating type combine and the one for the ordinary type combine, so that the manufacturing cost can be reduced. In the example of FIG. 16, the shaft diameters of both sides of the PTO shaft 366 across the large diameter portion 375 are set to the same diameter.

  As apparent from the above description and FIGS. 12, 15, and 16, in the vehicle drive device provided with the transmission case 63 for changing the power of the engine 7, the cylindrical portion 365 formed in the transmission case 63 is bearing The shaft member 366 is rotatably supported via the bodies 367 and 368, and on the inner peripheral side of the cylindrical portion 365, step portions 373 and 374 projecting radially inward are formed, A large diameter portion 375 larger in diameter than the inner diameter of the bearing 367, 368 may be formed at the end of the shaft member 366, or a rotating member 370 larger in diameter than the inner diameter of the bearing 367, 368 may be detached. , And the bearing body 367, 368 is held by the large diameter portion 375 or the rotating member 370 and the step portion 373, 374 in the cylindrical portion 365, so that the bearing body 3 There is no need to use a dedicated parts of the snap ring or the like for the position regulation of 7,368. Therefore, the number of parts can be reduced to simplify the pivotal support structure of the shaft member 366, and the assembling operation can be rationalized to suppress the manufacturing cost.

  In particular, according to the example of FIG. 16, the bearing bodies 367 and 368 are paired in the axial direction of the shaft member 366, and the step portions 373 and 374 are the transmission of the pair of bearing bodies 367 and 368. The first step portion 373 corresponding to the first bearing 367 located outside the case 63 and the second step corresponding to the second bearing 368 located inside the transmission case 63 of the pair of bearings 367, 368 The large diameter portion 375 is formed at an end portion of the shaft member 366 which is located on the outer side of the transmission case 63, and an end portion of the shaft member 366 which is located on the inner side of the transmission case 63. And the first bearing body 367 is held between the large diameter portion 375 and the first step portion 373, and the rotating portion Since the second bearing body 368 is held between 370 and the second step portion 374, and the retaining ring 376 is attached to a portion of the shaft member 366 further inward of the transmission case 63 than the rotating member 370. The shaft member 366, the pair of bearing bodies 367 and 368, and the rotating member 370 can be suitably attached to the cylindrical portion 365 of the transmission case 63 by only one of the retaining rings 376, and the shaft can be extremely simply The member 366 can be assembled. With respect to the pivotal support structure of the shaft member 366, maintenance can be improved.

  Further, since the diameter of the shaft on both sides of the large diameter portion 375 in the shaft member 366 is set to the same diameter, the processing cost of the shaft member 366 can be reduced, which contributes to the reduction of the cost of parts.

  Now, as described above, in the vehicle drive device of the embodiment, a wet multi-plate-type swing brake 279 is provided on the swing motor shaft 261 (see FIGS. 13 and 17). In the embodiment, the mounting hole 379 is opened at the middle of the upper and lower sides of the left side surface of the transmission case 63. In a state where the cylindrical brake housing 380 is fitted into the mounting hole 379, bolts are fastened. The swing motor shaft 261 is provided with a cylindrical brake cylinder shaft 381. The pivoting motor shaft 261 including the brake cylinder shaft 381 is extended into the transmission case 63 by spline fitting the brake cylinder shaft 381 to the end of the pivoting motor shaft 261 protruding from the continuously variable transmission case 323. .

  The right end side of the brake cylinder shaft 381 is rotatably supported at the right inner wall of the transmission case 63 via an open bearing 382. The brake cylinder shaft 381 enters the inside of the brake housing 380. A mounting recess 383 is formed in the left bottom of the brake housing 380. The left end side of the brake cylinder shaft 381 is rotatably fitted into the mounting recess 383 of the brake housing 380 via the open bearing 384. That is, in the transmission case 63, the swing motor shaft 261 including the brake cylinder shaft portion 381 is rotatably supported via the pair of open type bearings 382, 384. The other end side of the lateral external pipe 341 is communicated with the brake cylinder shaft portion 381 by connecting the other end side of the lateral external pipe 341 from the outside to the left bottom portion of the brake housing 380.

  On the right end side of the brake cylinder shaft portion 381, a turning input gear 385 which always meshes with the upstream reduction gear 281 on the steering counter shaft 280 is attached. An inner hub 386 is spline fitted to the left and right middle portions of the brake cylinder shaft 381. Friction plates 380 a and 386 a are alternately provided on the inner peripheral surface of the brake housing 380 and the outer peripheral surface of the inner hub 386. A compression spring 399 is fitted between the left open bearing 384 and the inner hub 386 in the brake cylinder shaft 381. When the output of the swing motor 70b is less than a predetermined torque, the friction plates 380a and 386a are in pressure contact with each other by the elastic restoring force of the compression spring 399 to brake the brake cylinder shaft 381 and stop the swing motor shaft 261 (non-rotatable) To maintain.

  A plurality of lubricating holes 387 are formed in the side peripheral portion of the brake cylinder shaft 381 to allow the inside and the outside of the brake cylinder shaft 381 to communicate with each other. In the embodiment, the lubrication holes 387 are opened toward the inner peripheral side (spline portion) of the inner hub 386 and the inner peripheral side of the turning input gear 385. The hydraulic oil in the oil reservoir 340 is intensively supplied to the friction plates 380 a and 386 a group from the lateral external piping 341 via the mounting recess 383, the inner peripheral side of the brake cylinder shaft 381 and the lubrication holes 387. . That is, the turning brake 279 is lubricated by the hydraulic oil from the oil reservoir 340.

  Since the brake housing 380 is cylindrical, the hydraulic oil concentratedly supplied to the friction plates 380a and 386a easily accumulates on the inside of the brake housing 381. Here, the left bearing 384 pivotally supporting the brake cylinder shaft 381 is an open type, but the left open bearing is reduced by reducing the relief of the mounting recess 383 with respect to the left open bearing 384. Leakage of hydraulic fluid from 384 to the outside of the brake cylinder shaft 381 is suppressed.

  As described above, in the embodiment, the auxiliary shift counter shaft 270 and the steering counter shaft 280 and the shafts 66, 258 to 261 above these do not rotate in a state of being immersed in the hydraulic oil. For this reason, although it contributes to the reduction of the power loss, there are concerns about wear, a decrease in life, and the like. Therefore, the structure shown in FIG. 18 may be employed. That is, one end of the second horizontal outer pipe 396 is connected to the oil reservoir 340 on the left side surface of the transmission case 63 separately from the horizontal outer pipe 341, and the other end of the second horizontal outer pipe 396 is the transmission case 63. It is connected to the position of the auxiliary shift counter shaft 270 on the left side. Further, the transmission case 63 is provided with a first internal oil passage 397 connecting the portion of the oil reservoir 340 and the portion of the linear motor shaft 260, and the other end side of the horizontal external pipe 341 or the swing motor shaft 261 A second internal oil passage 398 is formed which connects the portion 279) and the portion of the steering counter shaft 280. With this configuration, the linear motor shaft 260, the sub shift counter shaft 270 and the steering counter shaft 280 can also be lubricated by the hydraulic oil from the oil reservoir 340.

DESCRIPTION OF SYMBOLS 1 traveling body 7 engine 63 transmission case 364 sealing lid 365 PTO boss portion 366 PTO shaft 367 first bearing body 368 second bearing body 369 PTO pulley 370 PTO output gear 371 PTO input gear 373 first step portion 374 second step portion 375 Large diameter portion 376 Retaining ring

Claims (3)

In a vehicle drive device provided with a transmission case for changing the power of an engine,
A shaft member is rotatably supported by a cylindrical portion formed in the transmission case via a bearing body, and a step portion projecting radially inward is formed on the inner peripheral side of the cylindrical portion. A large diameter portion larger in diameter than the inner diameter of the bearing is formed at the end of the shaft member, or a rotating member larger in diameter than the inner diameter of the bearing is detachably mounted. A structure in which the bearing body is held between the large diameter portion or the rotating member and a step portion in the cylindrical portion ;
The bearing body is paired in the axial direction of the shaft member, and the step portion is a first step portion corresponding to a first bearing body located outside the transmission case among the pair of bearing bodies, and The bearing member is divided into a second step portion corresponding to a second bearing body located inward of the transmission case among the pair of bearing bodies, and the large diameter portion is formed at an end of the shaft member outboard of the transmission case. The rotary member is detachably mounted on the end of the shaft member inward of the transmission case, and the first bearing body is held between the large diameter portion and the first step portion. And the second bearing body is held between the rotating member and the second step portion,
Vehicle drive system. In the shaft member, shaft diameters on both sides of the large diameter portion are set to the same diameter.
The vehicle drive device according to claim 1. A vehicle drive device according to claim 1 or 2 is provided.
Combine.

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