WO2014208117A1 - Dispositif de transmission pour engin de travaux, et moissonneuse - Google Patents

Dispositif de transmission pour engin de travaux, et moissonneuse Download PDF

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Publication number
WO2014208117A1
WO2014208117A1 PCT/JP2014/052998 JP2014052998W WO2014208117A1 WO 2014208117 A1 WO2014208117 A1 WO 2014208117A1 JP 2014052998 W JP2014052998 W JP 2014052998W WO 2014208117 A1 WO2014208117 A1 WO 2014208117A1
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WO
WIPO (PCT)
Prior art keywords
transmission
shaft
gear
speed
state
Prior art date
Application number
PCT/JP2014/052998
Other languages
English (en)
Japanese (ja)
Inventor
奥山天
加藤裕治
森学
竹内由明
加藤勝秀
大谷大樹
一二三慶城
林茂幸
籔中歩荷
高崎和也
有本敬
木曾田雄星
Original Assignee
株式会社クボタ
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from JP2013136520A external-priority patent/JP6095506B2/ja
Priority claimed from JP2013136519A external-priority patent/JP6095505B2/ja
Priority claimed from JP2013189765A external-priority patent/JP6104110B2/ja
Priority claimed from JP2013189767A external-priority patent/JP6029556B2/ja
Application filed by 株式会社クボタ filed Critical 株式会社クボタ
Priority to CN202010067316.8A priority Critical patent/CN111066488B/zh
Priority to CN201480032975.0A priority patent/CN105283339B/zh
Priority to KR1020157032539A priority patent/KR101799175B1/ko
Priority to KR1020177032617A priority patent/KR102048136B1/ko
Publication of WO2014208117A1 publication Critical patent/WO2014208117A1/fr
Priority to PH12015502618A priority patent/PH12015502618A1/en

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
    • B60K17/06—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of change-speed gearing
    • B60K17/08—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of change-speed gearing of mechanical type
    • A—HUMAN NECESSITIES
    • A01—AGRICULTURE; FORESTRY; ANIMAL HUSBANDRY; HUNTING; TRAPPING; FISHING
    • A01D—HARVESTING; MOWING
    • A01D41/00—Combines, i.e. harvesters or mowers combined with threshing devices
    • A01D41/12—Details of combines
    • A01D41/127—Control or measuring arrangements specially adapted for combines
    • A01D41/1274—Control or measuring arrangements specially adapted for combines for drives
    • A—HUMAN NECESSITIES
    • A01—AGRICULTURE; FORESTRY; ANIMAL HUSBANDRY; HUNTING; TRAPPING; FISHING
    • A01D—HARVESTING; MOWING
    • A01D41/00—Combines, i.e. harvesters or mowers combined with threshing devices
    • A01D41/12—Details of combines
    • A01D41/127—Control or measuring arrangements specially adapted for combines
    • A01D41/1278—Control or measuring arrangements specially adapted for combines for automatic steering
    • A—HUMAN NECESSITIES
    • A01—AGRICULTURE; FORESTRY; ANIMAL HUSBANDRY; HUNTING; TRAPPING; FISHING
    • A01D—HARVESTING; MOWING
    • A01D69/00—Driving mechanisms or parts thereof for harvesters or mowers
    • A01D69/06—Gearings
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
    • B60K17/06—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of change-speed gearing
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K20/00—Arrangement or mounting of change-speed gearing control devices in vehicles
    • B60K20/02—Arrangement or mounting of change-speed gearing control devices in vehicles of initiating means
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K23/00—Arrangement or mounting of control devices for vehicle transmissions, or parts thereof, not otherwise provided for
    • B60K23/02—Arrangement or mounting of control devices for vehicle transmissions, or parts thereof, not otherwise provided for for main transmission clutches
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H47/00—Combinations of mechanical gearing with fluid clutches or fluid gearing
    • F16H47/02—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
    • B60Y2200/00—Type of vehicle
    • B60Y2200/20—Off-Road Vehicles
    • B60Y2200/22—Agricultural vehicles
    • B60Y2200/222—Harvesters

Definitions

  • the present invention relates to a transmission device for a working machine such as a transmission device for a harvesting machine.
  • Working machines include ordinary harvesters (whole-throw-in type) combiners, self-removing combine harvesters, carrot harvesters and corn harvesters, as well as transport vehicles and tractors, but are not limited to these. Absent.
  • the present invention also relates to a working machine such as a harvesting machine.
  • a transmission device for a harvester that is an example of a work machine
  • a left-right driven shaft that is adjacent to the input shaft of the transmission case in a parallel posture and a transmission that is linked to an output rotating body provided on the driven shaft.
  • Left-right side clutch shaft provided with a rotator, a selection gear type transmission for shifting power from the input shaft, and a left-right travel device located on the side clutch shaft from the transmission rotator
  • a pair of side clutches for intermittently interrupting transmission to are built in the transmission case.
  • the transmission is decelerated through a pair of gears from the auxiliary transmission input shaft (input shaft) to the auxiliary transmission intermediate transmission shaft (driven shaft) in the transmission case (transmission case).
  • the sub-transmission intermediate transmission in a state where the sub-transmission device (transmission) is transmitted from the transmission body provided so as to be shiftable to the sub-transmission intermediate transmission shaft to the sub-transmission output shaft provided so as to be relatively rotatable to the sub-transmission input shaft.
  • the transmission device for a work machine for example, a pair of interlocking rotators that are individually interlocked and connected to the left and right traveling devices, and a pair of side clutches that individually interrupt the transmission to the pair of interlocking rotators. Equipped on the side clutch shaft built into the transmission case in the left-right direction.
  • a pair of side clutches are respectively a cylindrical moving side rotating body having a meshing portion at one side end, and a fixed side having a meshed portion at one side end.
  • Each side clutch in a transmission case that includes a rotating body and a compression spring that biases the moving-side rotating body toward an entering position where the meshing portion and the meshed portion mesh with each other, and includes a pair of side clutches, etc.
  • Each side clutch can be attached to and detached from the side clutch shaft from the outside of the transmission case. (For example, refer to Patent Document 2).
  • the harvester is provided, for example, outside the transmission case, and the power from the engine is shifted continuously in the forward and reverse directions so that the side wall on one end side of the transmission case is moved from the outside of the case to the inside of the case.
  • a main transmission that outputs from an output shaft that is inserted toward the side, and a transmission that is internally mounted in the transmission case and that shifts the motive power transmitted from the output shaft into two steps depending on the working state.
  • a gear-type auxiliary transmission for transmission is provided, for example, outside the transmission case, and the power from the engine is shifted continuously in the forward and reverse directions so that the side wall on one end side of the transmission case is moved from the outside of the case to the inside of the case.
  • the output shaft of the main transmission is provided in a cantilever shape by inserting the side wall on one end side of the transmission case from the outer side of the case toward the inner side of the case.
  • the output gear is extrapolated to the output shaft so as to be rotatable integrally, and the transmission input transmission gear provided on the transmission input shaft of the auxiliary transmission and the output gear mesh with each other to transmit power to the auxiliary transmission.
  • the harvesting machine is provided with, for example, a main transmission that shifts the driving force from the engine continuously in a forward and reverse direction, a gear case that is incorporated in the transmission case, and that can be combined in a plurality of combinations.
  • a gear-type sub-transmission device that shifts the driving force output from a plurality of stages according to the working state and transmits it to the traveling device, a working clutch that turns on and off the driving force transmission to the working unit, and the main transmission device.
  • a main transmission operating tool that performs a shifting operation; a sub-transmission operating tool that performs a shifting operation of the auxiliary transmission; and a clutch operating tool that performs an on / off operation of the work clutch.
  • This harvester can reliably avoid unexpected operation of the cutting part when traveling on a high-speed road and sudden high-speed start of the body during low-speed cutting harvesting work.
  • JP ⁇ 2000-184817 JP ⁇ 2000-184817 A
  • JP-B 61-003310 JP ⁇ S61-003310 Y
  • the torque applied to the transmission increases by decelerating from the input shaft (sub-transmission input shaft) to the driven shaft (sub-transmission intermediate transmission shaft). For this reason, the torque applied to the transmission is increased, so that the drive gear (transmission gear) and the driven gear are disengaged during traveling, and the transmission is in a neutral state. is there.
  • the transmission case transmission case
  • a speed reduction structure a pair of gears
  • the object of the present invention is to simplify the transmission structure in the transmission case, and the transmission device while rationally configuring the transmission structure in the transmission case to prevent the transmission from being lost in the transmission built in the transmission case. It is to be able to reduce the size and weight.
  • An object of the present invention is to facilitate the assembly of the side clutch to the side clutch shaft.
  • the driving reaction force on the output gear from the lower side of the transmission causes the output gear and the lower side shift input.
  • the cantilevered output shaft is bent and deformed in a direction in which the meshing gears are separated from each other, and the gears may mesh in an oblique state. If such a driving state continues, the gears are damaged early, or the gears are unevenly worn and good transmission cannot be performed early. There was a risk of being unable to do so.
  • An object of the present invention is to provide a harvester that can maintain a good transmission state in a transmission mechanism over a long period of time.
  • the harvesting machine performs various operations such as normal mowing work, fallen cereal harvesting work, crossing the shore, running on the road, etc., and various appropriate running speeds (having a certain range) according to each of these works. ) Exists. For this reason, the harvesting machine described in Patent Document 1 is provided with a sub-transmission device that can be switched to three speeds separately from the main transmission device, so that an appropriate traveling speed can be easily obtained.
  • the present invention can easily produce various appropriate traveling speeds while minimizing an increase in the number of parts and space, and can display various appropriate traveling speeds.
  • An object of the present invention is to provide a combine that can prevent the shifting of gears.
  • the input shaft is provided on a left-right output shaft provided in an external device connected to the transmission case, in a state of rotating integrally with the output shaft around the axis of the output shaft,
  • the transmission is configured to be transmitted from the input shaft to the driven shaft, and is provided across the input shaft and the driven shaft.
  • the input shaft of the transmission case that rotates integrally with the output shaft around the shaft center of the output shaft provided in the external device connected to the transmission case can be used as the drive shaft of the transmission. Accordingly, for example, a transmission structure such as a gear that transmits from the input shaft to the drive shaft can be made unnecessary as compared with a case where a dedicated drive shaft having a configuration different from that of the input shaft is provided in parallel with the input shaft. As a result, it is possible to facilitate manufacturing by simplifying the transmission structure in the transmission case and to reduce the size and weight of the transmission device. In addition, the transmission structure can prevent a shift from being lost due to an increase in torque applied to the transmission, which may be caused when the transmission is decelerated from the input shaft to the drive shaft.
  • the transmission rotor is arranged in the center of the side clutch shaft, and the pair of side clutches are distributed on the left and right of the transmission rotor.
  • two transmission systems that individually transmit from the side clutch shaft to the left and right traveling devices via these side clutches, and these
  • the case portion of the transmission case that covers the transmission system can be configured symmetrically with a good balance.
  • two transmission systems including a pair of side clutches can be configured with common parts.
  • the transmission structure extending from the side clutch shaft to the left and right traveling devices can be configured in a stable state with a good balance of left and right symmetry while simplifying the configuration using common parts.
  • the output rotating body is arranged at the center of the driven shaft.
  • a pair of shafts in a transmission case that supports both ends of the driven shaft by arranging an output rotating body that rotates in a state where torque is always applied regardless of the speed of the transmission at the center of the driven shaft. It becomes easy to equalize the torque applied to the branch.
  • the driven gear of the transmission is mounted on the driven shaft in a state adjacent to the output rotating body.
  • the transmission can be reduced in size and weight, and the transmission device can be reduced in size and weight.
  • the driven gear is mounted on the driven shaft in a state adjacent to both side portions of the output rotating body.
  • an unnecessary interval between the transmission gear and the driven gear on the driven shaft can be eliminated and the driven shaft can be shortened while increasing the number of transmission stages of the transmission.
  • a gear portion is provided on one end side of the driven gear, and a gear selection linkage portion is provided on the other end side of the driven gear, so that the driven gear serves as a shift mechanism for gear selection operation.
  • the linkage gear is configured to be linked, and the linkage gear is mounted on the driven shaft in a state where the gear portion is adjacent to the output rotating body.
  • the gear portion of the driven gear can be arranged on the center side of the driven shaft as compared with the case where the linkage portion of the linkage gear is adjacent to the output rotating body.
  • the torque concerning a pair of shaft support part in the transmission case which supports the both ends of a driven shaft can be substantially equalized.
  • the transmission is configured in a constant mesh type
  • As the linkage gear a linkage gear different from the linkage gear adjacent to the output rotating body is provided,
  • Each of the linkage gears includes a spline boss portion as the linkage portion, A spline shaft portion that rotates integrally with the driven shaft between the spline boss portion of the linkage gear adjacent to the output rotating body and the spline boss portion of the another linkage gear.
  • the driven shaft is installed in an intervening state.
  • the transmission structure can be simplified by reducing the number of spline shafts and shifters, the transmission can be reduced in size and weight, and the transmission device can be reduced in size and weight.
  • the transmission includes a linkage gear provided on one end side with a linkage portion linked to a shift mechanism for gear selection operation,
  • the linking gear is mounted on the input shaft or the driven shaft in a state where the linking portion is located at an end of the input shaft or the driven shaft opposite to the input side end of the input shaft.
  • the input shaft away from the input side end of the input shaft or the shaft end side of the driven shaft becomes the operation region for gear selection, and accordingly, the input shaft that does not require the operation region for gear selection or
  • the extension length from the input side end portion of the driven shaft can be shortened, and the width dimension in the extending direction of the input shaft or the driven shaft in the transmission can be shortened.
  • the transmission can be reduced in size and weight, and the transmission device can be reduced in size and weight.
  • the transmission includes a linkage gear linked to a shift mechanism for gear selection operation, Either one of the input shaft and the driven shaft is disposed below the other, The linkage gear is mounted on the input shaft or the driven shaft arranged below.
  • the surface height of the lubricating oil stored in the transmission case can be reduced as compared with the case where the linkage gear is provided on the input shaft or the driven shaft arranged above, and the oil in the transmission case can be reduced.
  • the amount of storage can be reduced. As a result, it is possible to shorten the work time required for oil change, reduce the cost, and reduce the weight of the transmission device.
  • the transmission is configured as a constant mesh type having a plurality of linkage gears having a spline boss portion on one end side as a linkage portion linked to a shift mechanism for gear selection operation,
  • the input shaft or the driven shaft equipped with the plurality of linkage gears so as to be relatively rotatable can be linked to the adjacent spline boss portion via the shift mechanism at the adjacent portion to the spline boss portion.
  • the input shaft or the driven shaft is constituted by a spline boss that is detachably fitted on the input shaft or the driven shaft.
  • spline bosses constituting the predetermined spline shaft portion for example, each spline formed on the outer peripheral surface thereof extends over both ends of the spline bosses.
  • the spline boss is formed to have a length, when the spline boss is spline fitted to the driven shaft, the spline fitting can be easily performed without considering the direction of the spline boss.
  • the transmission case includes an opening that exposes an end of the input shaft opposite to the input side.
  • the continuously variable transmission or motor When the operation tool is operated to the neutral position or the stop position, it is possible to directly recognize whether or not the input shaft has stopped rotating.
  • the neutral adjustment of the continuously variable transmission or the stop adjustment of the motor can be easily performed when the continuously variable transmission or the motor is adopted as the external device.
  • an oil passage is provided for supplying oil returned from the hydraulic device to the inside of the transmission case to a linkage gear linked to a gear selection operation shift mechanism in the transmission.
  • left and right traveling drive shafts extending from the transmission case to the corresponding traveling device and left and right traveling drive shafts, and left and right reduction mechanisms that transmit the power via the corresponding side clutches to the traveling drive shafts at a reduced speed.
  • a relay shaft facing left and right is provided between the side clutch shaft and the left and right travel drive shafts,
  • Each of the left and right speed reduction mechanisms includes a first speed reduction portion that extends from the side clutch shaft to the relay shaft, and a second speed reduction portion that extends from the relay shaft to the travel drive shaft.
  • the speed reduction ratio in each speed reduction mechanism can be increased while reducing the diameter of the driven rotating body employed in each speed reduction mechanism and increasing the degree of freedom of arrangement of each speed reduction mechanism in the transmission case. Can do.
  • each of the first reduction part and the second reduction part is configured in a gear transmission type in which a pair of gears are engaged and interlocked with each other,
  • the relay shaft is disposed at a front upper position with respect to the travel drive shaft, and the side clutch shaft is disposed at a rear upper position with respect to the relay shaft.
  • each speed reduction mechanism can be shortened as compared with the case where the side clutch shaft, the relay shaft, and the travel drive shaft are arranged in the vertical direction.
  • the driving force from the side clutch shaft and the driving reaction force from each traveling drive shaft applied to each relay shaft are reduced by the mutual cancellation of the vertical components, while the relay shaft Are distributed to the side clutch shaft and each travel drive shaft via the gears of the side clutch shaft and the gears of the relay shaft and the travel drive shaft.
  • the driving force and the driving reaction force applied to the relay shaft are applied only to the relay shaft, while the vertical components cancel each other.
  • the torque applied to each shaft support portion that supports the relay shaft can be reduced as compared with the case where the driving force and the driving reaction force are applied only to the relay shaft during forward traveling that is frequently used. .
  • the output rotator and the transmission rotator are configured by gears that mesh and interlock with each other,
  • the driven shaft is disposed at a front upper position with respect to the side clutch shaft, and the input shaft is disposed at a rear upper position with respect to the driven shaft.
  • the vertical length of the transmission can be shortened as compared with the case where the input shaft, the driven shaft, and the side clutch shaft are arranged in the vertical direction.
  • the driving force from the input shaft on the driven shaft and the driving reaction force from the side clutch shaft are reduced by the mutual cancellation of the vertical components, while the driven gear of the driven shaft.
  • the input shaft drive gear, and the output gear and the side clutch shaft gear on the driven shaft are dispersed to the input shaft and the side clutch shaft.
  • reverse travel which is less frequently used, the driving force and the driving reaction force applied to the driven shaft are applied only to the driven shaft, while the vertical components cancel each other.
  • the torque applied to each shaft supporting portion that supports the driven shaft can be reduced.
  • the side clutch shaft is arranged at a position behind the input shaft and the travel drive shaft.
  • the relay shaft is arranged at a position ahead of the driven shaft.
  • a side clutch shaft having a pair of interlocking rotators that are individually interlocked and connected to the left and right traveling devices, and a pair of side clutches that individually connect and disconnect transmission to the pair of interlocking rotators in the transmission case. Equipped on the shaft, Each of the pair of side clutches has a cylindrical shaft that is externally fitted to the side clutch shaft so as to be rotatable relative to the side clutch shaft in a state where the side clutch shaft can be attached and detached by sliding in the axial direction of the side clutch shaft.
  • the moving-side rotating body having a meshing portion at a side end, a fixed-side rotating body having a meshed portion at one side end, and an entry position where the meshing portion and the meshed portion mesh with each other.
  • a compression spring that biases the body, a stopper that receives the moving-side rotating body at the entry position, and a spring receiver that receives one end of the compression spring;
  • the moving side rotating body, the compression spring, the stopper, and the spring receiver are arranged on the outer periphery of the cylindrical shaft, and the moving side rotation is performed between the stopper and the spring receiver.
  • An arrangement in which the body and the compression spring are positioned, and the moving-side rotating body rotates integrally with the cylinder shaft in a state in which the moving-side rotating body is slidable in the axial direction of the side clutch shaft with respect to the cylinder shaft. Equipped with the cylinder shaft, the moving-side rotating body, the compression spring, the stopper, and the spring receiver slidably and detachably with respect to the side clutch shaft in the axial direction of the side clutch shaft. It is configured as a sliding unit.
  • each side clutch when assembling each side clutch to the side clutch shaft, by attaching each sliding unit to the side clutch shaft, the moving side rotating body and the compression spring, which are the components of each side clutch, are side-mounted. Can be attached to the clutch shaft.
  • each sliding unit is mounted on the side clutch shaft, a large force against the action of the compression spring is not required, so that the moving side rotating body and the compression spring can be easily attached to the side clutch shaft. can do.
  • attachment / detachment of the moving side rotating body or compression spring to / from the cylinder shaft that requires a large force against the action of the compression spring can be freely performed using the necessary tools without limiting the work area outside the transmission case. Since it can be performed, it is possible to easily attach the moving side rotating body or the compression spring to the cylinder shaft.
  • a transmission rotating body that is transmitted to the pair of interlocking rotating bodies via the pair of side clutches is disposed in a central portion of the side clutch shaft,
  • the pair of interlocking rotators and the pair of side clutches are distributed to the left and right of the transmission rotor, and the pair of side clutches are transmitted from the transmission rotor to the interlocking rotors on the same left and right sides. Is configured to be intermittent.
  • a pair of side clutches and a pair of interlocking rotating bodies arranged on the side clutch shaft are transmitted separately from the side clutch shaft to the left and right traveling devices via these side clutches and the interlocking rotating bodies.
  • the two transmission systems and the case part of the transmission case that covers these transmission systems can be configured symmetrically with a good balance.
  • two transmission systems including a pair of side clutches and a pair of interlocking rotating bodies can be configured with common parts.
  • the transmission structure extending from the side clutch shaft to the left and right traveling devices can be configured in a stable state with a good balance of left and right symmetry while simplifying the configuration using common parts.
  • each of the pair of side clutches is configured such that the moving side rotating body functions as a driven side rotating body, and the fixed side rotating body functions as a driving side rotating body,
  • Each of the sliding units is configured to include the corresponding interlocking rotating body as one of the components.
  • the moving-side rotating body which is one of the components of the sliding unit, is used as the driven-side rotating body of the side clutch, so that it is disposed on the lower side in the transmission direction of the side clutch on the side clutch shaft.
  • the interlocking rotator can also be configured as one of the components of the sliding unit, thereby improving the assembly of the side clutch and the interlocking rotator with respect to the side clutch shaft.
  • the transmission case includes an opening that allows passage of the sliding unit at a position facing each of the pair of side clutches in the axial direction of the side clutch shaft, and the opening.
  • a cover member for closing the cover is detachably mounted, and each of the sliding units is configured to be detachable from the outside of the transmission case with respect to the side clutch shaft.
  • the side clutch shaft can be moved from the outside of the transmission case through the opening to the side clutch shaft assembled in the transmission case without requiring a large force against the action of the compression spring. Can be easily installed.
  • each sliding unit when performing maintenance of each sliding unit, can be attached and detached from the opening of the transmission case without disassembling the transmission case. Then, disassembly and assembly of each sliding unit that requires a large force against the action of the compression spring can be freely performed using a necessary tool without limiting the work area outside the transmission case.
  • each of the cover members includes a shaft support portion that supports an end portion of the side clutch shaft.
  • each cover member by attaching each cover member to the transmission case, the end portion of the side clutch shaft can be supported by each shaft support portion. Moreover, by removing each cover member from the transmission case, each shaft support portion can be removed from the transmission case together with each cover member.
  • each cover member and each shaft support portion with respect to the transmission case can be improved, and the maintainability for each sliding unit and each shaft support portion can be improved.
  • each of the fixed-side rotators is externally fitted to the side clutch shaft in a state where it can be attached to and detached from the side clutch shaft by sliding in the axial direction of the side clutch shaft,
  • Each of the openings is formed in a size that allows passage of the fixed-side rotating body.
  • the fixed-side rotating body together with each sliding unit is opened from the outside of the transmission case to the side clutch shaft assembled in the transmission case without requiring a large force against the action of the compression spring. Can be easily attached to and detached from the side clutch shaft.
  • each of the pair of side clutches includes, as the fixed-side rotator, a spur gear having a tooth width that is at least twice as long as a meshing length with the meshing portion of the moving-side rotator. Yes.
  • each of the fixed-side rotating bodies is externally fitted to a portion of the side clutch shaft that is closer to the shaft end than the sliding unit.
  • a drive gear is provided as the pair of interlocking rotating bodies,
  • the pair of side clutches are configured such that the moving-side rotating body functions as a driven-side rotating body, and the fixed-side rotating body functions as a driving-side rotating body, Is configured to include the corresponding drive gear as one of the components.
  • the moving-side rotating body which is one of the components of the sliding unit, is used as the driven-side rotating body of the side clutch, so that it is disposed on the lower side in the transmission direction of the side clutch on the side clutch shaft.
  • the interlocking rotator can also be configured as one of the components of the sliding unit, thereby improving the assembly of the side clutch and the interlocking rotator with respect to the side clutch shaft.
  • the interlocking rotating body is a driving pulley or a driving sprocket
  • the sliding unit including the interlocking rotating body is attached to or detached from the side clutch shaft from the opening of the transmission case
  • the driving pulley or the drive is driven from the opening. Since it takes time to attach / detach the transmission belt or transmission chain to / from the sprocket, it becomes difficult to attach / detach the sliding unit to / from the side clutch shaft from the opening.
  • the interlocking rotating body is a drive gear
  • the attachment / detachment from the opening of the transmission case to the side clutch shaft of the sliding unit including the drive gear is not required as described above. It can be done easily.
  • each of the sliding units is equipped with the drive gear on the cylindrical shaft.
  • the driving gear when the driving gear is provided on the moving side rotating body, the driving gear slides with respect to the driven gear that meshes with the driving gear and interlocks with the sliding displacement of the moving side rotating body due to the on / off operation of the side clutch. Due to the displacement, wear due to the sliding displacement occurs between the drive gear and the driven gear.
  • the transmission case is equipped with a multi-plate side brake that brakes the corresponding traveling device on the outer peripheral side of each sliding unit on the axis of the side clutch shaft,
  • Each of the sliding units includes a corresponding brake hub of the side brake as one of the component parts so as to rotate integrally with the cylindrical shaft.
  • each of the sliding units includes a spline boss that rotates integrally with the cylindrical shaft,
  • Each of the spline bosses is configured as a combination part in which one end side functions as the drive gear and the other end side functions as the brake hub.
  • each spline boss is a dual-purpose part that serves both as a drive gear and a brake hub, the structure can be simplified and the assembly can be improved by reducing the number of parts.
  • each of the spline bosses has a spline hole portion fitted on a spline shaft portion provided on one end side of the corresponding cylindrical shaft on the inner peripheral surface on the drive gear side, and a brake hub.
  • the inner peripheral surface on the side is provided with an enlarged diameter portion that forms a storage space for a compression spring between the cylinder shaft.
  • the spline boss can be removably fitted to the cylinder shaft by using the drive gear side of each spline boss that becomes longer in the axial direction by serving as the drive gear and the brake hub. it can.
  • the spline boss can be replaced.
  • the wear of the drive gear or the brake hub is reduced. Maintenance costs can be reduced.
  • each spline boss using the brake hub side of each spline boss, it is possible to equip the cylinder shaft, the compression spring, and the spline boss in a state where they are overlapped in the radial direction of the cylinder shaft. As a result, the length in the axial direction of each sliding unit can be shortened as compared with the case where the compression spring and the spline boss are arranged side by side in the axial direction of the cylinder shaft. It is possible to reduce the size of the transmission device by narrowing the left and right widths of the transmission device together with the shortening of the length.
  • each of the cylindrical shafts constitutes the spring receiver with a stepped portion provided on the outer peripheral portion thereof, and the spline shaft portion extends from the stepped portion to the shaft end on the large diameter side.
  • Formed into Each of the spline shaft portions is provided with an engagement portion formed in a substantially annular recess on the outer peripheral side thereof, and a C-shaped retaining ring is fitted on the engagement portion.
  • Each of the spline bosses has the spline hole portion extending from the retaining ring to the stepped portion and the enlarged diameter portion extending from the stepped portion to the boss end on the brake hub side. Yes.
  • the spline boss can be easily and reliably fixed at a predetermined position with respect to the cylinder shaft with a simple configuration using the step portion of the cylinder shaft, the retaining ring, and the compression spring.
  • each of the side brakes slides a plurality of brake disks and a plurality of separator plates alternately arranged in the axial direction of the side clutch shaft in the axial direction of the side clutch shaft. Equipped in a state that can be removed laterally outward of the transmission case by Each of the openings is sized to allow passage of the brake disc and the separator plate.
  • a plurality of brake discs and a plurality of separator plates in each side brake can be easily attached and detached from each opening of the transmission case.
  • each side brake such as assembly of each side brake and replacement of a brake disk and a separator plate.
  • each of the moving side rotating bodies includes a pressing portion acting on the brake disc and the separator plate on an outer peripheral portion thereof,
  • the corresponding moving-side rotating body is moved from the cut position where the meshing portion of the moving-side rotating body and the meshed portion of the fixed-side rotating body release the meshing,
  • the brake disc and the separator are released from the brake release state in which the brake disc and the separator plate release the pressure contact due to the action of the pressing portion as they slide toward the braking position located in the opposite direction.
  • Each of the plates is switched to a braking state in which the plate is pressed by the action of the pressing portion, and the corresponding moving-side rotator slides from the braking position toward the cutting position. It is configured to switch to the brake release state.
  • each side clutch can be used as a side brake operating tool, and accordingly, the side clutch and the side brake can be appropriately interlocked.
  • each of the fixed-side rotating bodies can be attached to and detached from the side clutch shaft by sliding in the axial direction of the side clutch shaft, and from the sliding unit on the side clutch shaft.
  • Each of the cover members includes an auxiliary opening that allows passage of the fixed-side rotator, and is detachably equipped with an auxiliary cover member that closes the auxiliary opening, and is a shaft that supports an end portion of the side clutch shaft.
  • a branch is provided in the auxiliary cover member.
  • each of the auxiliary openings is formed in a circular shape centered on the axis of the side clutch shaft
  • Each of the auxiliary cover members includes a large-diameter portion that fits in the auxiliary opening, and a small-diameter portion that forms an annular space between the auxiliary opening, and the small-diameter portion is located on the inner side of the transmission case.
  • Each of the sliding units is equipped on the side clutch shaft in a state where the moving side rotating body faces the space, A state in which an annular piston that slides the moving-side rotating body is fitted into the space in a state in which it can slide in the axial direction of the side clutch shaft, and the space functions as an oil chamber for operating the piston. It is configured.
  • the hydraulic operation section for the side clutch and the side brake can be configured using the space between the cover member and the auxiliary cover member. Then, by removing the cover member or the auxiliary cover member, the hydraulic operation unit can be removed, and maintenance on the hydraulic operation unit can be easily performed.
  • the operability of the side clutch and the side brake can be improved by the hydraulic operation part while suppressing the complication of the configuration, and the maintainability for the hydraulic operation part can be improved.
  • each of the moving side rotating bodies includes an enlarged diameter portion that allows the stopper to enter at the entering position on the inner peripheral surface on the stopper side.
  • the length of each sliding unit in the axial direction can be further shortened as compared with the case where the enlarged diameter portion is not formed.
  • the stopper is constituted by a C-shaped retaining ring that is detachably fitted in an engagement groove that is annularly recessed and formed on the outer peripheral side of the cylindrical shaft.
  • the enlarged diameter portion for the stopper is formed to a size that prevents the stopper from being detached from the engaging groove.
  • the assembled state of the stopper with respect to the engagement groove of each cylinder shaft can be easily determined by sliding of the moving side rotating body by the action of the compression spring after the assembly. If the engagement of the stopper with the groove is incomplete, the engagement can be improved immediately.
  • the transmission case It is provided outside the transmission case and has an output shaft that passes through the side wall on one end side of the transmission case from the outer side of the case to the inner side of the case.
  • a main transmission that outputs from the output shaft;
  • a gear-type sub-transmission device that is internally mounted in the transmission case and that shifts the power transmitted from the output shaft to a high and low two-stage according to a working state and transmits it to the traveling device;
  • the output shaft passes through the transmission case and is inserted into the side wall on the other end side so that the shaft end is exposed to the outside of the case.
  • the side wall on the one end side and the side wall on the other end side And harvester that is provided in a state of being rotatably supported by each.
  • the output shaft of the main transmission is provided in a state where the side wall on one end side of the transmission case is inserted from the case outer side toward the case inner side.
  • the output shaft passes through the transmission case, passes through the side wall on the other end side, and the shaft end portion is exposed to the outside of the case, and between the side wall on the one end side and the side wall on the other end side.
  • Each is provided in a state of being rotatably supported.
  • the output shaft is rotatably supported on each of the side wall on one end side and the side wall on the other end side in the transmission case, so that the drive reaction force from the lower transmission side to the output gear causes The possibility that the output shaft is bent and deformed is reduced, and a good gear meshing state can be maintained. As a result, it was easy to maintain a good transmission state.
  • the output shaft is inserted through the side wall on the other end side and the shaft end on the other end side is exposed outside the case, whether the output shaft is rotating from the outer side of the mission case or not Can be visually confirmed. Then, for example, when adjusting the operation state when the main transmission is operated to the neutral position with the shift operation tool, whether or not the main transmission is in the neutral state, that is, whether the output shaft is in the rotation stop state or not.
  • the adjustment work can be performed with high accuracy while visually confirming.
  • an input gear for input on the input side of the auxiliary transmission is provided with an input gear that meshes with and interlocks with an output gear provided on the output shaft.
  • the output gear provided on the output shaft and the input gear provided on the input shaft for shifting of the auxiliary transmission are meshed with each other, and the output of the main transmission is transmitted to the auxiliary transmission. Due to the driving reaction force from the lower transmission side, the output shaft is less likely to bend and deform even when force is applied in the direction where the output gear and input gear are engaged. It became easy to maintain a good transmission state without any disadvantages such as meshing with each other.
  • the transmission input shaft is provided with a high-speed transmission drive gear on the side closer to the input gear and a low-speed transmission drive gear on the side far from the input gear.
  • the driving load when the auxiliary transmission is in a high speed state, the driving load is large, such as performing a cutting operation at a high speed, and when the auxiliary transmission is in a low speed state, the driving load is performed, for example, performing a cutting operation at a low speed.
  • the driving load Is considered to be small.
  • a relatively large driving reaction force acts on a portion where a high-speed transmission drive gear is provided, and a relatively small driving reaction force acts on a portion provided with a low-speed transmission drive gear. I think that.
  • the high-speed transmission drive gear is provided on the side close to the input gear, the power can be transmitted with minimal torsional deformation of the transmission input shaft when it is in a high-speed state.
  • the torsional deformation of the transmission input shaft is small.
  • the low-speed transmission drive gear is provided with a space in the axial direction between the shift input shaft and a shaft support member that rotatably supports the shift input shaft on the side wall on the other end side. It is.
  • each of the low-speed transmission drive gear and the shaft support member can be continuously operated smoothly by appropriately supplying the lubricating oil, and it is easy to maintain a good transmission state. .
  • the high-speed transmission drive gear is provided with an interval in the axial direction between the input gear and the input gear.
  • each of the drive gear for high speed transmission and the input gear can be continuously operated smoothly by appropriately supplying the lubricating oil, and it is easy to maintain a good transmission state.
  • a high-speed transmission driven gear in which the high-speed transmission drive gear meshes and interlocks with an output-side shift output shaft in the sub-transmission device, and a low-speed transmission driven gear in which the low-speed transmission drive gear meshes and interlocks, It is preferable that a driving gear that meshes with and is interlocked with a lower transmission gear positioned on the lower transmission side of the auxiliary transmission is provided.
  • the power of the transmission input shaft in the auxiliary transmission is transmitted via the high-speed transmission drive gear and the high-speed transmission driven gear, or via the low-speed transmission drive gear and the low-speed transmission driven gear. It is transmitted to the shift output shaft.
  • the power of the transmission output shaft is transmitted to the lower transmission side of the auxiliary transmission device via a drive gear provided separately from the high-speed transmission driven gear and the low-speed transmission driven gear and the lower transmission gear meshing with the drive gear.
  • the driving gear is provided in a state of being positioned between the high-speed transmission driven gear and the low-speed transmission driven gear.
  • the driving gear is provided between the high-speed transmission driven gear and the low-speed transmission driven gear on the transmission output shaft.
  • the gear-type auxiliary transmission includes a switching operation mechanism for switching between a state where power is transmitted to the driven gear for high speed transmission and a state where power is transmitted to the driven gear for low speed transmission. This switching operation mechanism is provided at a corresponding location between the high-speed transmission driven gear and the low-speed transmission driven gear.
  • the space between the driven gear for high speed transmission and the driven gear for low speed transmission provided in a state of being separated in the axial direction is compactly driven. Gears can be deployed.
  • the driving gear is provided at a position close to the high-speed driven gear.
  • the driving gear since the driving gear is provided at a position close to the high-speed transmission driven gear, the power transmitted to the high-speed transmission driven gear is transmitted to the high-speed transmission driven gear when the driving load is high. Power can be transmitted to the lower transmission side through the drive gear located near the gear as much as possible with little torsional deformation of the output shaft for shifting. In the low speed state, the driving load is often small, and even if the driving gear is provided at a position far from the low speed driven gear, the torsional deformation of the transmission output shaft is small.
  • the auxiliary transmission includes an input-side transmission input shaft, an output-side transmission output shaft, a high-speed transmission drive gear and a low-speed transmission drive gear that are provided so as to be rotatable relative to the transmission input shaft. And a driven gear for high speed transmission and a driven gear for low speed transmission provided in a fixed state on the output shaft for shifting,
  • the high-speed transmission drive gear and the low-speed transmission drive gear are configured so as to be non-slidable in the axial direction in a state where they are always meshed with the high-speed transmission driven gear and the low-speed transmission driven gear, respectively.
  • a spline is externally fitted to the transmission input shaft, and the high-speed transmission drive gear is provided rotatably relative to the transmission input shaft.
  • a shifter that is slidable between a high-speed transmission operation position that meshes with the spline portion and a low-speed transmission operation position that meshes with and interlocks with the spline portion of the low-speed transmission drive gear that is relatively rotatable with respect to the transmission input shaft. It is suitable if it is provided with.
  • the shifter when the shifter is slid to the high-speed transmission operation position, the shifter meshes with and interlocks with the spline portion of the high-speed transmission drive gear, so that the high-speed transmission drive gear rotates integrally. Then, the high-speed power shifted by the high-speed transmission drive gear and the high-speed transmission driven gear meshing and interlocking with each other is transmitted to the traveling device via the transmission output shaft.
  • the shifter when the shifter is slid to the operation position for low-speed transmission, the shifter meshes with the spline portion of the low-speed transmission drive gear, so that the low-speed transmission drive gear rotates integrally. Then, the low-speed power that is shifted by the low-speed transmission drive gear and the low-speed transmission driven gear meshing and interlocking with each other is transmitted to the traveling device via the transmission output shaft.
  • the auxiliary transmission can be switched between the high speed state and the low speed state by sliding the shifter.
  • a drive gear that meshes with and engages with a lower transmission gear located on the lower transmission side of the auxiliary transmission is provided between the high-speed transmission driven gear and the low-speed transmission driven gear on the transmission output shaft.
  • a shift fork for sliding the shifter is provided in a state of passing through a space between the shifter and the driving gear.
  • the shifter is provided between the high-speed transmission drive gear and the low-speed transmission drive gear on the transmission input shaft, and between the high-speed transmission driven gear and the low-speed transmission driven gear on the transmission output shaft. Is provided with a driving gear. A shift fork for sliding the shifter is provided in a state of passing through a space between the shifter and the driving gear.
  • the shift fork can be satisfactorily deployed in a state where there is little risk of interference with other transmission shafts.
  • the shift fork is configured to engage with a region equal to or more than a half circumference in an engagement circumferential groove provided on an outer periphery of the shifter.
  • the shifter is slid by the shift fork in a state where it is engaged with a region equal to or more than a half circumference in the engagement circumferential groove provided on the outer periphery of the shifter.
  • the shift fork operating force acts on the shifter over a wide area that is more than half the circumference of the shifter, and the shift fork operating force acts locally on the shifter.
  • the shifter is less likely to tilt with respect to the input shaft for shifting, and smoothly slides in a state where there is no risk of dripping.
  • the shift fork is configured to be engaged with two positions located on a diameter of an engagement circumferential groove provided on an outer periphery of the shifter.
  • the shifter is slid with the shift fork while engaged with two positions located on the diameter of the engaging circumferential groove provided on the outer periphery of the shifter.
  • the output shaft is provided with a pair of divided transmission shafts which are divided along the axial direction and linked together so as to be integrally rotatable.
  • the output shaft is constituted by a pair of divided transmission shafts divided along the axial direction, for example, one of the output rotating shafts extending in a cantilever manner from the main transmission is provided.
  • the other divided transmission shaft in a state of being linked along the axial direction of one of the divided transmission shafts and being linked and interlocked so as to be integrally rotatable, the output shaft Can be configured. That is, it is not necessary to significantly improve the structure of the main transmission by effectively utilizing the configuration of the existing cantilevered output rotating shaft.
  • An output gear for transmitting power from the output shaft to the auxiliary transmission is externally fitted to each of the pair of split transmission shafts so as to be integrally rotatable, and the pair of split transmission shafts are driven by the output gear. It is preferable to be linked and linked.
  • the output gear for transmitting power to the auxiliary transmission is effectively used, and each of the pair of split transmission shafts is linked and interlocked so as to be integrally rotatable. Therefore, the pair of transmission shafts are linked and linked.
  • the output shaft can be constituted by the pair of split transmission shafts in a state where there is no disadvantage such as making the structure complicated by using a dedicated connecting member.
  • main transmission case that covers the periphery of the main transmission and the transmission case are connected in a flange-coupled state
  • a concentric fitting groove centered on the axis of the output shaft is formed in each of the connection surfaces of the main transmission case and the connection surface of the transmission case where the output shaft is inserted, It is preferable that a collar member for axial alignment is provided in a state of fitting into the fitting groove of the main transmission case and the fitting groove of the transmission case.
  • the main transmission case that covers the periphery of the main transmission and the transmission case are flange-connected, and the side wall of the transmission case on the side to which the main transmission case is connected is outside the case, that is, inside the main transmission case.
  • the output shaft is provided so as to be inserted from the inner side toward the inner side of the case.
  • a concentric fitting groove centering on the axis of the output shaft is formed in each of the connection surface of the main transmission case and the connection surface of the transmission case where the output shaft is inserted.
  • a collar member for axial alignment is provided in a state of fitting into the fitting groove of the transmission case and the fitting groove of the transmission case.
  • the same collar member is mounted in a state of fitting into the fitting groove of the main transmission case and the fitting groove of the transmission case, the center of the fitting groove of the main transmission case and the fitting groove of the transmission case are fitted.
  • the main transmission case and the transmission case are flange-coupled with each other in a state in which the center of the gear is aligned.
  • the output shaft provided in a state of being inserted from the inside of the main transmission case toward the inner side of the transmission case is positioned at the axial center position by the main transmission case and the transmission case in which the fitting grooves are aligned. It can be rotatably supported in a good state with little deviation.
  • a pair of left and right axles for separately transmitting the power shifted by the auxiliary transmission to the left and right traveling devices are provided in a state of being inserted through the left and right axle cases fixedly extending from the transmission case.
  • Each of the pair of left and right axles is configured with a small-diameter power transmission portion at an end on the inner side in the lateral direction of the fuselage, and a laterally extending portion with a large diameter on the outer side in the lateral direction of the fuselage, and
  • the connecting portion between the small-diameter power transmission portion and the large-diameter laterally extending portion is formed in a tapered shape so that the diameter increases from the small-diameter power transmission portion toward the outer side in the lateral direction of the fuselage. It is preferable that
  • the pair of left and right axles transmits the motive power after the shift to the power transmission unit inside the transmission case, and the traveling device via the laterally extending portion that inserts the power into the axle case.
  • the traveling device via the laterally extending portion that inserts the power into the axle case.
  • the connecting portion between the small-diameter power transmission portion and the large-diameter laterally extending portion is formed in a tapered shape such that the diameter increases from the small-diameter power transmission portion toward the outer side in the lateral direction of the fuselage. Therefore, at the end of the axle case on the inner side in the lateral direction of the fuselage, the inner side in the lateral direction of the fuselage is wider between the inner surface of the axle case and the tapered connecting portion, and the outer side in the lateral direction of the fuselage. A narrowing gap is formed.
  • the lubricating oil supplied from the mission case side is introduced from the wide inner side end portion in the gap toward the outer side in the lateral direction of the fuselage, so that the lubricating oil can be supplied satisfactorily. It can be carried out.
  • a main transmission that shifts the driving force from the engine continuously in a forward and reverse direction;
  • the gear case is provided with a gear train that can be combined in a plurality of combinations, and the driving force output from the main transmission is shifted to a plurality of stages according to the working state and transmitted to the traveling device.
  • a transmission A working clutch that turns on and off the transmission of driving force to the working part;
  • a main speed changer for shifting the main speed change device;
  • a sub-transmission operating tool for performing a shift operation on the sub-transmission device;
  • a clutch operating tool for performing on / off operation of the working clutch;
  • a check mechanism that checks that when the work clutch is engaged and operated, the main transmission operating tool is operated to a speed increasing side from a predetermined command position in the forward operation path of the main transmission operating tool. It is in the point.
  • the forward speed range by the main transmission is different between when the work clutch is engaged and when it is disengaged. That is, two types of speed regions appear on condition that the work clutch is turned on and off. Therefore, the combine is capable of revealing an appropriate traveling speed region twice as many as the number of shifting regions of the auxiliary transmission. Moreover, it is only necessary to check the operation of the main transmission operation tool, it is not necessary to increase the number of parts and space in the transmission case, and compared to increasing the number of gear combinations of the auxiliary transmission, can do. In addition, since the space does not increase, it is possible to increase the durability of the auxiliary transmission by using that amount to increase the gear thickness.
  • the check mechanism controls the operation of the main transmission operating tool from the predetermined command position in the forward operation path to the speed increasing side, so that the working unit is driven. In this state, the traveling speed is not changed beyond a certain traveling speed. Accordingly, it is possible to prevent the traveling device from exceeding the appropriate traveling speed due to an erroneous operation.
  • the operation of the main transmission operating tool in the path between the predetermined command position and the neutral position in the forward operation path and the reverse operation path can be freely performed. It is preferable.
  • the gear is not shifted beyond a certain traveling speed that is the state in which the working unit is driven, but the shifting to the low speed side including the backward traveling is possible. Therefore, in the middle of the current work, when it is necessary to perform a work with an appropriate travel speed equal to or lower than the appropriate travel speed for the current work or a reverse travel, the travel speed can be smoothly changed.
  • the predetermined command position is set to a position on the speed increasing side with respect to the intermediate position in the forward operation path.
  • the operable region of the main transmission operating tool at the time of check is set to more than half of the forward operation path. That is, the difference in the upper limit speed between the check state and the non-check state is relatively small, which is effective when the difference in the appropriate traveling speed is small between the working state and the non-working state.
  • the auxiliary transmission can be switched between two states, a high speed shift state and a low speed shift state,
  • the check mechanism is It is preferable to check that the engine is operated to the speed increasing side from the predetermined command position in the forward operation path.
  • the work unit is driven and the transition to the state of traveling at a considerably higher speed than the current speed is performed.
  • the speed can be efficiently increased to the appropriate traveling speed.
  • the user forgets to operate the auxiliary transmission device in the high speed transmission state.
  • the driver even if the driver operates the main transmission operating tool to increase the speed, the driver cannot operate the speed higher than the predetermined command position, and the travel speed is the appropriate travel speed. Will be lower. As a result, the driver becomes aware that the auxiliary transmission is in the low speed shifting state.
  • the auxiliary transmission can be switched between two states, a high speed shift state and a low speed shift state
  • the check mechanism is configured such that when the work clutch is engaged and operated in a state in which the sub-transmission device is operated in the high-speed shift state, the main transmission operating tool is moved from the predetermined command position in the forward operation path. It is preferable to check the operation to the speed increasing side.
  • the main transmission is operated to the high-speed transmission side when the sub-transmission is in a high-speed shift state and the engine load is high, such as when a working unit that requires a large driving force is driven.
  • the engine load is high, such as when a working unit that requires a large driving force is driven.
  • a main transmission lever of a swinging operation type is provided, and as a clutch operation tool, a clutch lever of a swinging operation type is provided.
  • the check mechanism is provided with a check portion that can be moved back and forth with respect to the forward operation path, and a link portion that links the check portion and the clutch lever. When the clutch lever is operated to the clutch engagement position, it is preferable that the check portion protrudes to a position corresponding to the predetermined command position in the forward operation path.
  • the main transmission operating tool is a forward / backward swing type main transmission lever
  • the check portion protrudes to a position corresponding to a predetermined command position
  • the main transmission lever is operated to the speed increasing side and the main transmission lever is operated.
  • the clutch operating tool is a forward / backward swing type clutch lever, and the movement is simple, and the check portion is moved back and forth with respect to the forward operation path, and the movement is simple.
  • the link portion that links the clutch lever and the check portion can have a simple structure.
  • the main transmission lever is provided on a side panel of the driving unit,
  • the clutch lever is provided behind the main transmission lever in the side panel, It is preferable that the check portion is slidable along the front-rear direction, and is retracted to the front side of the forward operation path when the clutch lever is operated to the clutch disengagement position.
  • the main swing lever and the clutch lever of the front / rear swing type are arranged in the front / rear direction on the side panel, and the check portion slides in the front / rear direction from the front of the forward operation path to perform the forward operation. Project into the path. That is, since the movement of all the members is along the front-rear direction, the link portion can have a shape along the front-rear direction and a movement along the front-rear direction. As a result, the check mechanism is simple in structure and compact in the left-right direction.
  • a restricting portion for restricting movement of the clutch lever from the clutch engaged position to the opposite side of the clutch disengaged position.
  • An arm member that swings integrally with the clutch lever around the swing axis of the clutch lever is linked to the link portion, and one end thereof is linked to the arm member so as to be rotatable around the first axis.
  • a rod member whose other end is linked to the check portion so as to be rotatable around the second axis, and
  • the link portion is configured such that the first axis is a rear side of the swing axis when viewed along the direction of the swing axis.
  • a straight line connecting the first axis and the second axis is preferably configured to move across the swing axis.
  • the check portion is provided with a guide member that extends along the forward operation path at a position deviated from the forward operation path and is slidable along the front-rear direction.
  • Support brackets are provided at two different positions along the front-rear direction, The guide member is preferably supported by the support bracket.
  • the support bracket is provided with two through holes located at two different positions along the front-rear direction, It is preferable that the guide member is supported through the through hole.
  • the restraining portion is provided with a protruding member that is provided at the distal end portion of the guide member and that can protrude into the forward operation path.
  • a support bracket different from the support bracket is provided,
  • the other support bracket is formed with a long hole through which the projecting member is penetrated to allow the projecting member to slide in the front-rear direction.
  • the another support bracket is preferably provided on the opposite side of the support bracket across the forward operation path.
  • the projecting member is supported by the support bracket on one side and the other side is supported by another support bracket across the portion that contacts the main transmission lever. That is, the protruding member is stably supported on both end sides with the abutting portion interposed therebetween. Therefore, in this configuration, the guide member is stably supported as a whole, and when the main transmission lever is restrained, the main transmission lever is hardly deformed or twisted even if the main transmission lever comes into contact. It is possible to reliably check the movement to the speed increasing side.
  • the working unit is a reaping portion and the working clutch is a reaping clutch.
  • the upper limit speed is lowered during the cutting operation and the upper limit speed is increased during the non-cutting operation, so that an optimum speed region can be obtained with a simple configuration.
  • the main transmission is preferably a hydrostatic continuously variable transmission.
  • the transmission device 13 for the harvester includes a left and right driven shaft 45 adjacent to the input shaft 44 in a parallel posture, and an output gear 81 (an output rotating body of the output rotating body) provided on the driven shaft 45.
  • a transmission 47 of a selection gear type that shifts the power from the input shaft 44 and a transmission from the transmission rotating body 82 to the left and right crawlers (an example of a traveling device) 7 positioned on the side clutch shaft 46 are individually provided.
  • a pair of side clutches 83 that are intermittently connected to each other are built in the transmission case 43.
  • the input shaft 44 is provided on a left-right output shaft 34 provided in the external device A connected to the transmission case 43 so as to rotate integrally with the output shaft 34 around the axis of the output shaft 34.
  • the transmission 47 is configured to transmit from the input shaft 44 to the driven shaft 45 and is provided across the input shaft 44 and the driven shaft 45.
  • the transmission rotating body 82 is arranged at the center of the side clutch shaft 46.
  • the pair of side clutches 83 are distributed on the left and right of the transmission rotor 82.
  • the output rotator 81 is disposed at the center of the driven shaft 45.
  • the transmission 47 is equipped with the driven gears 63 and 65 on the driven shaft 45 in a state adjacent to both sides of the output rotating body 81.
  • Each driven gear 63, 65 includes gear portions 63A, 65A on one end thereof, and a gear selection linkage portion Ba on the other end thereof, and is linked to a shift mechanism 66 for gear selection operation.
  • the linkage gear B is configured.
  • the transmission 47 is configured as a constant mesh type. Further, as the linkage gear B, a linkage gear B (driven gear 61) different from the linkage gear B (driven gears 63, 65) adjacent to the output rotating body 81 is provided. Each linkage gear B includes spline boss portions 61B, 63B, and 65B as the linkage portion Ba. Another linkage gear B is located between the spline boss portion 65B of the linkage gear B (driven gear 65) adjacent to the output rotating body 81 and the spline boss portion 61B of another linkage gear B (driven gear 61).
  • the driven shaft 45 is equipped with a spline shaft portion 45 ⁇ / b> A that rotates integrally with the driven shaft 45.
  • the linking gear B (driven gear 63) located at the end of the driven shaft 45 opposite to the input side end of the input shaft 44 has the linking portion Ba as the input shaft of the driven shaft 45. 44 is mounted on the driven shaft 45 in a state of being located at the end opposite to the input side end of 44.
  • the transmission 47 is configured such that a driven shaft 45 equipped with a plurality of linkage gears B so as to be relatively rotatable is positioned below the input shaft 44.
  • the driven shaft 45 is integrated with spline shaft portions 45A and 45B that enable linkage with the adjacent spline boss portions 61B, 63B, and 65B via the shift mechanism 66 at adjacent portions to the spline boss portions 61B, 63B, and 65B. It is prepared in a rotating state. Then, among the spline shaft portions 45A and 45B, a plurality of splines 74a for linking are formed only on one end side of the outer peripheral surface of a predetermined spline shaft portion 45B for which a single linkage gear B is to be linked. In this state, the spline boss 74 is detachably fitted to the driven shaft 45.
  • the transmission case 43 includes an opening 43 ⁇ / b> A that exposes an end of the input shaft 44 opposite to the input side.
  • the transmission 13 is an oil passage 137 that supplies oil returned to the inside of the transmission case 43 from a hydraulic device (for example, the valve unit 107; see FIGS. 3 to 5) provided in the transmission case 43 to each linkage gear B of the transmission 47. It has.
  • a hydraulic device for example, the valve unit 107; see FIGS. 3 to 5
  • the transmission 13 decelerates and transmits power to the traveling drive shaft 50 via the left and right traveling drive shafts 50 extending from the transmission case 43 to the corresponding crawler 7 (see FIG. 1) and the corresponding side clutch 83.
  • a left and right speed reduction mechanism 49 (hereinafter also referred to as “transmission mechanism 49”) is provided.
  • the transmission case 43 includes a laterally extending relay shaft 119 between the side clutch shaft 46 and the left and right traveling drive shafts 50.
  • Each speed reduction mechanism 49 travels from a side reduction shaft 122 extending from the side clutch shaft 46 to the relay shaft 119 (an example of a first transmission portion; hereinafter, also referred to as “first transmission portion 122”) and the relay shaft 119.
  • a second speed reduction portion 123 (an example of a second transmission portion; hereinafter, also referred to as “second transmission portion 123”) over the drive shaft 50 is provided.
  • the first speed reduction part 122 and the second speed reduction part 123 are each configured as a gear transmission type in which a pair of gears 92 and 124 to 126 are engaged with each other. Then, the relay shaft 119 including the driven gear (an example of a driven rotor) 124 of the first reduction part 122 and the drive gear (an example of a drive rotor) 125 of the second reduction part 123 is connected to the second reduction part 123.
  • a side clutch shaft 46 provided at a front upper position with respect to the travel drive shaft 50 including a gear (an example of a driven rotor) 126 and including a drive gear 92 of the first reduction gear 122 is disposed at a rear upper position with respect to the relay shaft 119. Deployed in position.
  • the output rotator 81 and the transmission rotator 82 are constituted by gears that mesh and interlock with each other.
  • the driven shaft 45 including the driven gears 61, 63, 65 and the output rotating body 81 is disposed at a front upper position with respect to the side clutch shaft 46 including the transmission rotating body 82, and each driven gear of the driven shaft 45 is provided.
  • An input shaft 44 including drive gears 60, 62, and 64 that mesh with and interlock with 61, 63, and 65 is disposed at a rear upper position with respect to the driven shaft 45.
  • the side clutch shaft 46 is disposed at a position behind the input shaft 44 and the travel drive shaft 50. Further, the relay shaft 119 is arranged at a position ahead of the driven shaft 45.
  • the transmission device 13 for the work machine includes a pair of drive gears (an example of an interlocking rotating body) 92 individually interlocked and connected to the left and right crawlers 7 (see FIG. 1). And a pair of side clutches 83 for individually connecting and disconnecting transmission to the pair of drive gears 92 are provided on the side clutch shaft 46 built in the transmission case 43 in the left-right direction.
  • Each side clutch 83 includes a cylindrical shaft 85 that is fitted on the side clutch shaft 46 so as to be rotatable relative to the side clutch shaft 46 in a state in which the side clutch shaft 46 can be attached and detached by sliding in the axial direction of the side clutch shaft 46.
  • the moving-side rotating body 86 provided with the meshing portion 86A, the fixed-side rotating body 87 provided with the meshed portion 87A at one end, and the moving side toward the entering position where the meshing portion 86A and the meshed portion 87A mesh.
  • a compression spring 88 that biases the rotating body 86, a stopper 89 that receives the moving-side rotating body 86 at the entry position, and a spring receiver 90 that receives one end of the compression spring 88.
  • each side clutch 83 the moving side rotating body 86, the compression spring 88, the stopper 89, and the spring receiver 90 are arranged on the outer peripheral portion of the cylindrical shaft 85 and between the stopper 89 and the spring receiver 90.
  • 86 and the compression spring 88 are positioned so that the moving side rotating body 86 can rotate integrally with the cylinder shaft 85 in a state in which it can slide in the axial direction of the side clutch shaft 46 with respect to the cylinder shaft 85. Equipped with the cylinder shaft 85, the moving side rotating body 86, the compression spring 88, the stopper 89, and the spring receiver 90 so as to be detachably integrated with the side clutch shaft 46 in the axial direction of the side clutch shaft 46.
  • the sliding unit 91 is configured.
  • a transmission rotating body 82 that is transmitted to each drive gear 92 via a pair of side clutch 83 is provided in the center portion of the side clutch shaft 46. Then, a pair of drive gears 92 and a pair of side clutches 83 are dispersedly arranged on the left and right of the transmission rotating body 82 so that the pair of side clutches 83 are transmitted from the transmission rotating body 82 to the drive gear 92 located on the same left and right side. Is configured to be intermittent.
  • Each side clutch 83 is configured so that the moving-side rotating body 86 functions as a driven-side rotating body and the fixed-side rotating body 87 functions as a driving-side rotating body.
  • the driving gear 92 (interlocking rotating body) is configured as one of the components.
  • the transmission case 43 includes an opening 43B that allows the sliding unit 91 to pass therethrough at a position facing each of the pair of side clutches 83 in the axial direction of the side clutch shaft 46, and covers the opening 43B.
  • the sliding units 91 are configured to be detachable from the outside of the transmission case 43 with respect to the side clutch shaft 46.
  • Each cover member 102 includes a shaft support portion 105 that supports the end portion of the side clutch shaft 46.
  • Each fixed-side rotating body 87 is externally fitted to the side clutch shaft 46 so as to be attachable to and detachable from the side clutch shaft 46 by sliding in the axial direction of the side clutch shaft 46.
  • each opening 43B of the transmission case 43 is formed in the magnitude
  • Each side clutch 83 is provided with a spur gear having a tooth width that is at least twice as long as the meshing length with the meshing portion 86A of the movable rotating body 86 as the stationary rotating body 87.
  • Each fixed-side rotating body 87 is externally fitted to a portion of the side clutch shaft 46 that is closer to the shaft end than the sliding unit 91.
  • the transmission device 13 includes a drive gear 92 as a pair of interlocking rotating bodies, and each sliding unit 91 includes the corresponding drive gear 92 as one of the components on the cylindrical shaft 85.
  • the transmission case 43 is equipped with a multi-plate side brake 84 for braking the corresponding crawler 7 on the outer peripheral side of each sliding unit 91 on the side clutch shaft 46.
  • Each sliding unit 91 includes a brake hub 94 of the corresponding side brake 84 as one of the components in a state of rotating integrally with the cylindrical shaft 85.
  • Each sliding unit 91 includes a spline boss 99 that rotates integrally with the cylinder shaft 85.
  • Each spline boss 99 is configured as a dual-purpose part whose one end functions as the drive gear 92 and whose other end functions as the brake hub 94.
  • the inner peripheral surface on the drive gear side is provided with a spline hole portion 99A fitted on the spline shaft portion 85A provided on one end side of the corresponding cylindrical shaft 85, and the inner peripheral surface on the brake hub side is provided with a cylindrical shaft.
  • An enlarged diameter portion 99B that forms a storage space 100 for the compression spring 88 is provided.
  • Each cylindrical shaft 85 forms a spring receiver 90 with a stepped portion 85C provided on the outer peripheral portion thereof, and the spline shaft portion 85A is formed with a length extending from the stepped portion 85C to the shaft end on the large diameter side.
  • Each spline shaft portion 85A includes an engagement portion 85E that is formed in a substantially annular recess on the outer peripheral side thereof, and a C-shaped retaining ring 101 is fitted on the engagement portion 85E.
  • Each spline boss 99 has a spline hole 99A formed in a length extending from the retaining ring 101 to the stepped portion 85C, and an enlarged diameter portion 99B formed in a length extending from the stepped portion 85C to the boss end on the brake hub side. ing.
  • Each side brake 84 includes a plurality of brake disks 96 and a plurality of separator plates 95 arranged alternately in the axial direction of the side clutch shaft 46, and the transmission case 43 by sliding in the axial direction of the side clutch shaft 46. Equipped in a state that can be removed laterally.
  • Each opening 43 ⁇ / b> B of the transmission case 43 is formed in a size that allows passage of the brake disk 96 and the separator plate 95.
  • Each moving-side rotating body 86 includes a rim portion 86C (an example of a pressing portion; hereinafter, also referred to as “pressing portion 86C”) that acts on the brake disk 96 and the separator plate 95 on the outer peripheral portion thereof.
  • Each side brake 84 is moved from the cut position where the corresponding moving-side rotating body 86 releases the meshing portion 86A of the moving-side rotating body 86 and the engaged portion 87A of the fixed-side rotating body 87 to the entering position.
  • the brake disk 96 and the separator plate 95 are slid toward the braking position located in the opposite direction, the brake disk 96 and the separator plate 95 are released from the brake release state in which the pressure contact due to the action of the pressing portion 86C is released.
  • Each of 95 is switched to a braking state in which it is pressed by the action of the pressing portion 86C, and as the corresponding moving-side rotating body 86 slides from the braking position to the cutting position, it changes from the braking state to the braking release state. It is configured to switch.
  • Each fixed-side rotating body 87 is externally fitted to a portion of the side clutch shaft 46 that is closer to the shaft end than the sliding unit 91.
  • Each cover member 102 is provided with an auxiliary opening 102A that allows passage of the fixed-side rotator 87, and an auxiliary cover member 103 that closes the auxiliary opening 102A is detachably provided.
  • the auxiliary cover member 103 is provided with a shaft support portion 105 that supports the shaft.
  • Each auxiliary opening 102 ⁇ / b> A is formed in a circular shape centered on the axis of the side clutch shaft 46.
  • Each auxiliary cover member 103 includes a large-diameter portion 103A that fits in the auxiliary opening 102A and a small-diameter portion 103B that forms an annular space 104 between the auxiliary opening 102A, and the small-diameter portion 103B is located inside the transmission case 43. It is prepared in the state located in.
  • Each sliding unit 91 is equipped on the side clutch shaft 46 in a state in which the moving side rotating body 86 faces the space 104.
  • annular piston 106 for sliding the corresponding moving side rotating body 86 is fitted in each space 104 in a state in which it can slide in the axial direction of the side clutch shaft 46, and each space 104 is operated for piston operation.
  • annular space is also referred to as “oil chamber 104”.
  • the stopper 89 is constituted by a C-shaped retaining ring that is detachably fitted in an engaging groove 85D that is formed in an annular recess on the outer peripheral side of the cylindrical shaft 85.
  • the moving-side rotator 86 is provided with an enlarged diameter portion 86E that allows the stopper 89 to enter at the insertion position on the inner peripheral surface on the stopper side.
  • the enlarged diameter portion 86E is formed in a size that prevents the stopper 89 from being detached from the engagement groove 85D.
  • the ordinary combine illustrated in the present embodiment harvests unharvested cereals to be harvested that are located in front of the vehicle body at the left side of the front end portion of the traveling vehicle body 1 to the rear.
  • a cutting and conveying device 2 as a harvesting device to be conveyed is connected so as to be movable up and down in a state of extending toward the front of the traveling vehicle body 1.
  • a threshing device 3 is mounted on the left half of the traveling vehicle body 1 to perform a handling process on the harvested cereal mash conveyed by the harvesting conveyance apparatus 2 and to perform a sorting process on a processed product obtained by the handling process.
  • the grain lifted from the bottom of the threshing device 3 via the lifting conveyor (not shown) is temporarily stored in the hopper 4A in the rear region of the right half of the traveling vehicle body 1, and the grain of the grain is stored.
  • a bagging device 4 that enables packing into the bag 5 is mounted.
  • a bagging specification a normal type combine is replaced with the bagging apparatus 4, for example, the grain tank which stores the grain lifted by the lifting conveyor, and grain You may comprise in the grain tank specification equipped with grain discharging apparatuses, such as a screw conveyance type or a bucket conveyance type, which enables discharge
  • the traveling vehicle body 1 includes a vehicle body frame 6 configured by connecting a plurality of steel materials such as a square pipe material.
  • the left and right crawlers 7 are arranged as full crawler specifications.
  • a boarding operation unit 8 is formed in the front half region of the right half of the vehicle body frame 6, and a water-cooled diesel engine (hereinafter referred to as an engine) 10 is provided below a driver seat 9 provided on the rear side of the boarding operation unit 8. Etc. are deployed.
  • a belt-type transmission mechanism 11 that enables transmission from the output shaft (not shown) of the engine 10 to the left and right crawlers 7 at the front left and right central positions of the body frame 6, and an external device A
  • a hydrostatic continuously variable transmission (hereinafter referred to as HST) 12 and a transmission 13 are provided.
  • the traveling vehicle body 1 is equipped with left and right front wheels and left and right rear wheels as left and right crawlers 7, or left and right crawlers 7 as left and right crawlers 7, respectively.
  • a semi-crawler specification equipped with front wheels and left and right rear crawlers may be configured.
  • the water-cooled diesel engine 10 for example, an air-cooled diesel engine or a water-cooled or air-cooled gasoline engine may be provided.
  • a hybrid specification including the engine 10 and an electric traveling motor, or an electric specification including an electric traveling motor instead of the engine 10 may be configured.
  • the boarding operation unit 8 may be formed at the front side portion of the left half of the vehicle body frame 6 or the like. Furthermore, you may equip the cabin which covers the boarding operation part 8. FIG.
  • the vehicle body frame 6 includes a pedestal portion 6A in the boarding operation portion formation region.
  • the entire boarding operation portion 8 is made HST12. And it arrange
  • the boarding operation unit 8 includes a front panel 14 erected at the front end portion of the pedestal portion 6A, a side panel 15 erected in a state connected to the left end portion of the front panel 14 at the left end portion of the pedestal portion 6A, and the like.
  • a boarding space that allows passengers to enter and exit from the right side of the vehicle is formed.
  • a control lever 16 that is configured to be a cross swing type and a neutral return type is provided.
  • a main transmission lever 17 and a sub transmission lever 18 that are configured to be position-holding and swinging back and forth are provided on the upper portion of the side panel 15.
  • a brake pedal 19 configured as a self-returning type capable of maintaining the position at the depressed position against the spring bias to the depressed position is provided at the foot portion.
  • the reaping and conveying apparatus 2 reapers the harvested culm and collects it at a predetermined position, and directs the harvested cereal collected at the predetermined position toward the culm input (not shown) of the threshing device 3. It is equipped with a feeder 21 consisting of a slat conveyor for conveying.
  • the harvesting and collecting unit 20 distributes left and right dividers 22 at both the left and right ends of the front end of the front and rear parts to separate the uncut harvested potatoes into harvested and unharvested grains. is doing.
  • a rotating reel 23 is disposed at an upper portion of the front portion, and the tip of the harvest target grain culm divided by the left and right dividers 22 is scraped back.
  • the bottom is equipped with a clipper-shaped cutting mechanism 24 that cuts the stock source side of the harvested cereal, and the harvested cereal after cutting by the cutting mechanism 24 is placed in the left-right direction at the rear portion of the cutting mechanism 24.
  • An auger drum 25 that is gathered at a predetermined position and sent from the predetermined position toward the rear feeder 21 is provided.
  • the feeder 21 is configured to extend from a cereal feed outlet (not shown) formed immediately behind a predetermined position in the harvesting and collecting unit 20 to a cereal inlet (not shown) of the threshing apparatus 3.
  • the rear end portion is equipped with a left-right feeder drive shaft 26 that also serves as an input shaft of the cutting and conveying device 2, and the feeder drive shaft 26 is connected to the front wall of the threshing device 3 so as to be relatively rotatable.
  • the cutting and conveying apparatus 2 is configured to move up and down with the feeder drive shaft 26 as a fulcrum by the operation of a hydraulic control unit 27 for lifting and lowering.
  • the oil stored in the oil tank 28 is supplied to the hydraulic control unit 27 by the operation of the first hydraulic pump 29.
  • the hydraulic control unit 27 includes a hydraulic lift cylinder (not shown) installed over the vehicle body frame 6 and the feeder 21, a lift valve unit (not shown) for changing the operating pressure on the lift cylinder, and the like. It has.
  • the raising / lowering valve unit is linked to the control lever 16 via a raising / lowering mechanical linkage mechanism (not shown). Based on the swinging operation of the control lever 16 in the front-rear direction, the flow of oil between the oil tank 28, the first hydraulic pump 29, and the lifting cylinder is controlled to change the operating pressure on the lifting cylinder. It is configured as follows.
  • the cutting and conveying device 2 is moved up and down to a lower work area for harvesting unharvested cereal to be harvested and an upper non-work position for not harvesting. Can be made.
  • the cutting height can be adjusted by changing the height position of the cutting mechanism 24 with respect to the harvest target cereal, thereby setting the work position of the cutting and conveying device 2 to an arbitrary height position. Can be changed.
  • the cutting and conveying apparatus 2 is configured to be displaced up and down over an arbitrary work position in the lower work area and an upper non-work position by a swinging operation of the control lever 16 in the front-rear direction.
  • the cutting and conveying apparatus 2 when the cutting and conveying apparatus 2 is located at an arbitrary work position, the cutting and conveying apparatus 2 is in a state of covering at least the front of the upper portion of the transmission device 13 (state indicated by a solid line in FIG. 1) When located at the position, the transmission device 13 is configured to open the front in the entire vertical direction (state indicated by a two-dot chain line in FIG. 1).
  • the cutting and conveying apparatus 2 may be configured to move up and down based on operations such as an operation lever dedicated to the lifting operation or a switch dedicated to the lifting operation that is configured to swing back and forth and to be in a neutral return type. Good. Moreover, you may comprise so that a sliding displacement or a rocking
  • the HST 12 is configured by incorporating a hydraulic pump 31 and a hydraulic motor 32 in a speed change case 30. Further, the pump shaft of the hydraulic pump 31 is configured as the input shaft 33 of the HST 12, and the motor shaft of the hydraulic motor 32 is configured as the output shaft 34 of the HST 12.
  • the traveling vehicle body 1 is mounted in a vertically long and horizontal posture in which the hydraulic motor 32 is positioned directly below the hydraulic pump 31 with the input shaft 33 and the output shaft 34 being left and right.
  • the transmission case 30 includes a case body 35 having a recess 35A that houses the hydraulic pump 31 and the hydraulic motor 32, a port block 36 that closes the recess 35A, and the like.
  • the hydraulic motor 32 is an axial plunger type fixed capacity motor.
  • the input shaft 33 and the output shaft 34 of the HST 12 pass through the port block 36 and protrude out of the case.
  • the output pulley 37 of the belt-type transmission mechanism 11 is integrally rotated with the input shaft 33 of the HST 12 around the axis of the input shaft 33 via the relay shaft 38 and the like. Linked to the state.
  • the port block 36 includes an input portion through which the input shaft 33 penetrates at an upper portion thereof, and an output portion through which the output shaft 34 penetrates at a lower portion thereof. And the one end part of the cylindrical input case 39 which encloses the input shaft 33, the relay shaft 38, etc. is bolt-connected to the input part. Further, the output portion is connected to the upper portion of the right side surface of the transmission device 13 in a state where the output portion is connected to the input portion of the transmission device 13.
  • the HST 12 includes a speed change operation shaft 40 for operating a pump swash plate (not shown) of the hydraulic pump 31 so as to protrude forward from the front wall of the speed change case 30.
  • the speed change operation shaft 40 has its front end so that the operation angle of the pump swash plate is changed to an angle corresponding to the operation position of the main speed change lever 17 in conjunction with the swinging operation of the main speed change lever 17 in the front-rear direction.
  • the linkage arm 41 provided in the section is linked to the main transmission lever 17 via a main transmission mechanical linkage mechanism 42.
  • the HST 12 is mounted on the traveling vehicle body 1 in a state where it is configured to function as a main transmission.
  • the HST 12 is configured to replenish oil stored in the oil tank 28 by operation of a charge pump (not shown) provided therein.
  • the HST 12 is, for example, a vertically long posture in which the hydraulic motor 32 is positioned directly below the hydraulic pump 31 with the input shaft 33 and the output shaft 34 facing forward or backward, or its input.
  • the traveling vehicle body 1 may be mounted in a laterally long posture before and after the hydraulic pump 31 and the hydraulic motor 32 are arranged in the front-rear direction with the shaft 33 and the output shaft 34 facing left-right.
  • an axial plunger type variable capacity motor may be provided as the hydraulic motor 32.
  • the transmission 13 includes a castable transmission case 43, a left-right input shaft 44, a driven shaft 45, a side clutch shaft 46, and a constant mesh type selection gear type transmission. 47, a pair of side clutch brake units 48, left and right transmission mechanisms 49, and the like.
  • the left and right traveling drive shafts 50 extending from the lower portion of the transmission case 43 to the corresponding crawlers 7 on the left and right sides, and the left and right drive shafts that rotatably support the left and right traveling drive shafts 50 in an individually enclosed state. Case 51 is provided.
  • the transmission case 43 includes a main case part 52 and left and right auxiliary case parts 53.
  • the main case component 52 has a left and right divided structure that can be divided into a left case member 54 and a right case member 55.
  • the left and right case members 54 and 55 are connected to each other by bolts so that the first space 56 and the auxiliary space 57 are provided as internal spaces.
  • a recessed portion 52A that is recessed toward the inside of the main case component 52 is provided.
  • the left and right auxiliary case parts 53 are bolted to the left and right side walls of the main case part 52 so as to cover the recessed portions 52A, so that the left and right side case and the left and right auxiliary case parts 53 are left and right.
  • a second space 58 is provided.
  • the transmission case 43 includes a first space 56, an auxiliary space 57, and left and right second spaces 58 as internal spaces.
  • the transmission case 43 includes an input unit connected to the output unit provided in the port block 36 of the HST 12 on the upper portion of the right side wall on the boarding operation unit side. ing. And with the output part of the port block 36 connected to the input part, the HST 12 is equipped on the upper part of the right side wall by bolt connection.
  • the input shaft 44 of the transmission device 13 is spline-fitted via the cylindrical shaft 59 to the output shaft 34 of the HST 12 provided with the right end portion serving as the input side end portion thereof as the external device A connected to the transmission case 43.
  • the output shaft 34 is configured to rotate integrally with the output shaft 34 around the axis.
  • the transmission case 43 includes a first opening 43 ⁇ / b> A that exposes a left end portion that is an end portion of the input shaft 44 opposite to the input side end portion on the upper side of the left side wall.
  • the external device A connected to the transmission case 43 includes, for example, a belt-type continuously variable transmission, a hydraulic mechanical continuously variable transmission (HMT), a belt-type transmission mechanism, or an electric motor. It may be.
  • a belt-type continuously variable transmission for example, a hydraulic mechanical continuously variable transmission (HMT), a belt-type transmission mechanism, or an electric motor. It may be.
  • HMT hydraulic mechanical continuously variable transmission
  • the transmission 47 is provided at the upper portion of the first space portion 56 in the transmission case 43 for low-speed transmission that is least frequently used when traveling over a bridge.
  • a high-speed drive gear 64 and a high-speed driven gear 65 for high-speed transmission, which are used most frequently, and a shift mechanism 66 that enables gear selection operation thereof are provided, and the gear selection operation of the shift mechanism 66 is performed. It is configured so that a three-stage shift is possible.
  • the drive gears 60, 62, 64 integrally form the low-speed drive gear 60 on the cylindrical shaft 59 that is spline-fitted to the input shaft 44 of the transmission device 13, and connect the medium-speed drive gear 62 and the high-speed drive gear 64 to the transmission device 13.
  • the input shaft 44 of the transmission device 13 It equips with the input shaft 44 of the transmission 13 rotating integrally with the shaft center as a center.
  • the low speed drive gear 60 is positioned on the right end side of the input shaft 44
  • the medium speed drive gear 62 is positioned on the left end side of the input shaft 44
  • the high speed drive gear 64 is positioned on the center side of the input shaft 44. It is set. That is, the input shaft 44 of the transmission device 13 is configured to also serve as the drive shaft of the transmission 47 that supports the drive gears 60, 62, and 64 so as to rotate together.
  • Each driven gear 61, 63, 65 is externally fitted to a driven shaft 45 disposed adjacently below the input shaft 44 so as to be relatively rotatable. Further, gear portions 61A, 63A, and 65A that are always meshed with the corresponding drive gears 60, 62, and 64 are provided at one end side thereof, and a spline boss is provided at the other end side as a gear selection linkage portion Ba.
  • the parts 61 ⁇ / b> B, 63 ⁇ / b> B, and 65 ⁇ / b> B are provided, and the linkage gear B is linked to the shift mechanism 66.
  • the low-speed driven gear 61 is disposed on the right end side of the driven shaft 45 with the gear portion 61A positioned on the right end side of the driven shaft 45 and the spline boss portion 61B positioned on the center side of the driven shaft 45. is doing. Further, the medium-speed driven gear 63 is moved to the center side of the driven shaft 45 with the gear portion 63A positioned on the center side of the driven shaft 45 and the spline boss portion 63B positioned on the left end side of the driven shaft 45. Have deployed.
  • the high-speed driven gear 65 is arranged on the center side of the driven shaft 45 with the gear portion 65A positioned on the center side of the driven shaft 45 and the spline boss portion 65B positioned on the right end side of the driven shaft 45. is doing.
  • the shift mechanism 66 includes a first spline shaft portion 45A and a second spline shaft portion 45B provided on the driven shaft 45 in a state of rotating integrally with the driven shaft 45, a first shifter 67 that is spline-fitted to the first spline shaft portion 45A, Shift fork 69, shift fork 69 provided with second shifter 68 that is spline fitted to second spline shaft portion 45B, first fork portion 69A for operating the first shifter, and second fork portion 69B for operating the second shifter
  • the left and right shift support shafts 70 that support the slidable movement, the shift fork 69 and the position maintaining detent mechanism 71 interposed between the shift support shafts 70 and the shift forks 69 are slid in the left and right directions.
  • An operation arm 72, a front-rear shift operation shaft 73 that supports the operation arm 72, and the like are provided.
  • the first spline shaft portion 45 ⁇ / b> A is integrally formed on the right side portion of the driven shaft 45 located between the low speed driven gear 61 and the high speed driven gear 65.
  • the spline boss portion 61B of the low-speed driven gear 61 and the spline boss portion 65B of the high-speed driven gear 65 are adjacent to the left and right sides, so that the two driven gears 61 and 65 for low-speed and high-speed use are linked. It is configured in the state.
  • the second spline shaft portion 45B is configured by a spline boss 74 that is detachably splined to the left end portion of the driven shaft 45. And the spline boss
  • the first shifter 67 and the second shifter 68 change the shift state of the transmission 47 as the shift fork 69 slides along the shift support shaft 70 on the shift support shaft 70.
  • the spline boss portion 61B of the low speed driven gear 61 is splined to the first spline shaft portion 45A of the driven shaft 45 and the spline boss portion 63B of the medium speed driven gear 63 is driven to the driven shaft by the second shifter 68.
  • the detent mechanism 71 includes a ball 75 and a compression spring 76 provided in the recess 69 ⁇ / b> C of the shift fork 69, and three engagement grooves formed annularly on the outer peripheral surface of the transmission support shaft 70. 70A, 70B, 70C, etc., to shift the shift fork 69 at a low speed position corresponding to the low speed transmission state of the transmission 47, a medium speed position corresponding to the medium speed transmission state of the transmission 47, and a high speed transmission of the transmission 47. It is configured to engage and hold at a high speed position corresponding to the state.
  • the operation arm 72 of the transmission 47 swings in the left-right direction around the axis of the speed change operation shaft 73, and the free end thereof is shifted to the shift fork 69. Is engaged with the shift fork 69 in a state in which the relative displacement is allowed.
  • the speed change operation shaft 73 passes through the front wall of the transmission case 43, has an operation arm 72 at the inner end located inside the transmission case 43, and has an outer end protruding forward from the front wall of the transmission case 43.
  • the operation arm 72 and the linkage arm 77 are interlocked and connected to each other.
  • the linkage arm 77 has its free end so that the operation position of the shift fork 69 is changed to a position corresponding to the operation position of the sub transmission lever 18 in conjunction with the swinging operation of the sub transmission lever 18 in the front-rear direction. This portion is linked to the auxiliary transmission lever 18 via a mechanical linkage mechanism 78 for auxiliary transmission.
  • the transmission 47 is built in the transmission case 43 in a state configured to function as an auxiliary transmission.
  • the transmission 47 is equipped across the input shaft 44 and the driven shaft 45 of the transmission device 13 in a state where the transmission 47 is transmitted from the input shaft 44 of the transmission device 13 to the driven shaft 45. Then, by selecting the driven gears 61, 63, 65 linked to the driven shaft 45 by the gear selection operation of the shift mechanism 66 that is linked to the operation of the auxiliary transmission lever 18, the transmission state is changed from the output shaft 34 of the HST 12. Is transmitted to the driven shaft 45 via the low-speed drive gear 60 and the low-speed driven gear 61, and is transmitted to the driven shaft 45 via the medium-speed drive gear 62 and the medium-speed driven gear 63. It is configured to selectively switch between a state and a high-speed transmission state that is transmitted to the driven shaft 45 via the high-speed drive gear 64 and the high-speed driven gear 65.
  • the driven shaft 45 that supports the driven gears 61, 63, 65 so as to be relatively rotatable and supports the first shifter 67 and the second shifter 68 so as to be relatively slidable is located at a position below the input shaft 44.
  • the low-speed driven gear 61 and the high-speed driven gear 65 are configured to be linked with the first spline shaft portion 45A provided on the driven shaft 45, for example, the low-speed driven gear 61 is linked.
  • the driven shaft 45 has a spline shaft portion dedicated to low speed and a spline shaft portion dedicated to high speed driven gear 65
  • the spline shaft portion and shifter in the transmission 47 Can be reduced, and the length of the driven shaft 45 can be shortened.
  • the configuration of the transmission 47 can be simplified, the transmission 47 can be reduced in size and weight, and the assembling property to the transmission case 43 can be improved.
  • the medium-speed driven gear 63 disposed at the position farthest from the right end portion that is the input side end portion of the input shaft 44 is used. Since the driven shaft 45 is mounted on the driven shaft 45 with the spline boss portion 63B positioned on the left end side of the driven shaft 45, the medium speed driven gear 63 is driven by the gear portion 63A. Compared with the case where the driven shaft 45 is mounted in the opposite direction in which the spline boss portion 63B is located on the left end side of the shaft 45 and located on the center side of the driven shaft 45, the medium speed driven gear 63 is The medium speed drive gear 62 that meshes with each other can be arranged on the right side.
  • the length of the input shaft 44 extending to the left can be made shorter than the driven shaft 45.
  • the high-speed drive gear 64 having the highest use frequency among the drive gears 60, 62, 64 is arranged on the center side of the input shaft 44, and the use frequency is lower than that of the high-speed drive gear 64. Since the low-speed drive gear 60 and the medium-speed drive gear 62 are arranged on the shaft end side of the input shaft 44, the torque applied to the input shaft 44 in the high-speed transmission state in which the high-speed drive gear 64 with the highest use frequency is used. In order to support both ends of the input shaft 44, it can be received in a balanced manner by shaft support portions such as left and right bearings 79 provided on the left and right side walls of the transmission case 43.
  • the low-speed driven gear 61 having the lowest usage frequency among the driven gears 61, 63, 65 is arranged on the right end side of the driven shaft 45, and the usage frequency is higher than that of the low-speed driven gear 61. Since the medium-speed driven gear 63 and the high-speed driven gear 65 are arranged on the center side of the driven shaft 45, the medium-speed transmission state and the high-speed transmission using the medium-speed driven gear 63 or the high-speed driven gear 65 that are frequently used are used. In this state, the torque applied to the driven shaft 45 can be received in a well-balanced manner by shaft support portions such as left and right bearings 80 provided on the left and right side walls of the transmission case 43 in order to support both ends of the driven shaft 45.
  • shaft support portions such as left and right bearings 80 provided on the left and right side walls of the transmission case 43 in order to support both ends of the driven shaft 45.
  • the spline boss 74 constituting the second spline shaft portion 45B includes, for example, each spline 74a linked to the medium speed driven gear 63 formed on the outer peripheral surface of the spline boss 74 over both ends of the spline boss 74.
  • the spline boss 74 is formed to have a length, when the spline boss 74 is fitted to the driven shaft 45 by spline, the spline can be easily fitted without considering the direction of the spline boss 74.
  • a plurality of splines 74a for linking are formed only on one end side of the outer peripheral surface, and the chamfering process described above is performed only on one end portion of the spline 74a located at the end portion of the spline boss 74. (See FIGS. 7 and 10).
  • the transmission 47 replaces the constant mesh type with each driven gear 61, 63 on a cylindrical shaft that is externally fitted so as to rotate integrally with the driven shaft 45 while being slidable relative to the driven shaft 45, for example.
  • , 65 and a gear selection linking portion linked to the gear selection operation shift mechanism 66, and the driven gears 61, 63, 65 are slid integrally by operation of the shift mechanism 66.
  • the linkage gear B is linked to the shift mechanism 66, and the gear selection operation by the shift mechanism 66 causes the shift state to be a low-speed transmission state in which the low-speed drive gear 60 and the low-speed driven gear 61 are engaged with each other.
  • each driven gear 61, 63, 65 is equipped with each driven gear 61, 63, 65 so as to rotate integrally with the driven shaft 45 while being individually slidable on the driven shaft 45.
  • each driven gear 61, 63, 65 is provided with a gear selection linking portion linked to the gear selection operation shift mechanism 66, and each driven gear 61, 63, 65 is linked to the shift mechanism 66.
  • the linked gear B is configured so that the driven gears 61, 63, 65 are linked to the shift mechanism 66 so that they are integrally slid by the operation of the shift mechanism 66, and the gear selection operation by the shift mechanism 66 is performed.
  • the low-speed drive gear 60 and the low-speed driven gear 61 are meshed and interlocked with each other, the medium-speed drive gear 62 and the medium-speed driven gear 63 are meshed and interlocked, In the high-speed transmission state where the driving gear 64 and the high-speed driven gear 65 is interlocked engagement, it may be configured to sliding mesh type switching to alternative.
  • the transmission 47 is replaced with, for example, the spline boss portions 61B, 63B, 65B of the driven gears 61, 63, 65, and the first spline shaft portion 45A or the second spline adjacent thereto, instead of the constant mesh type.
  • You may comprise in the synchromesh system provided with the synchronous part which synchronizes those peripheral speeds between the axial parts 45B.
  • the transmission 47 may be configured as a two-speed transmission that can be switched between a low-speed transmission state for work travel and a high-speed transmission state for mobile travel instead of the three-speed transmission. Further, it may be configured as a multi-stage transmission type that can be switched at four or more stages with a low-speed transmission state that is slower than the low-speed transmission state.
  • the transmission 47 replaces the configuration in which each driven gear 61, 63, 65 is mounted on the driven shaft 45 as a linkage gear B that can be selected by the shift mechanism 66, and each drive gear 60, 62, 64 is provided. May be provided on the input shaft 44 as a linkage gear B that allows a gear selection operation by the shift mechanism 66.
  • the input shaft 44 may be arranged adjacently below the driven shaft 45.
  • the first spline shaft portion 45A in the transmission 47 may be constituted by a spline boss that is detachably splined to the driven shaft 45. Further, the second spline shaft portion 45 ⁇ / b> B in the transmission 47 may be integrally formed with the driven shaft 45.
  • the arrangement of the drive gears 60, 62, 64 and the driven gears 61, 63, 65 on the input shaft 44 or the driven shaft 45 can be variously changed according to the frequency of use of the gears 60 to 65. .
  • the low-speed drive gear 60 and the low-speed driven gear 61 are used frequently, the low-speed drive gear 60 and the low-speed driven gear 61 may be arranged on the center side of the input shaft 44 or the driven shaft 45.
  • the high-speed drive gear 64 and the high-speed driven gear 65 are used less frequently, the high-speed drive gear 64 and the high-speed driven gear 65 may be arranged on the input shaft 44 or the driven shaft 45 on the shaft end side.
  • the driven shaft 45 has a small-diameter output gear that functions as an output rotating body 81 of the transmission 47 at a central portion between the medium-speed driven gear 63 and the high-speed driven gear 65.
  • 81 is spline-fitted so that the driven shaft 45 and the output gear 81 rotate together.
  • the side clutch shaft 46 is disposed in the upper and lower intermediate portions of the first space portion 56 in the transmission case 43.
  • a large-diameter transmission gear 82 as a transmission rotating body 82 meshing with and interlocking with the output gear 81 is integrally rotated at the left and right intermediate positions in a state where the side clutch shaft 46 and the transmission gear 82 are not relatively slidable.
  • the transmission structure from the driven shaft 45 to the side clutch shaft 46 is configured as a gear transmission type by the output gear 81 and the transmission gear 82, and the power after the shift by the transmission 47 is transferred from the driven shaft 45 to the side clutch shaft 46. It is configured to transmit deceleration.
  • the transmission structure from the driven shaft 45 to the side clutch shaft 46 is replaced with a gear transmission type, for example, a small-diameter sprocket provided on the driven shaft 45 as the output rotating body 81, and the side clutch shaft 46.
  • a large-diameter sprocket provided as a transmission rotating body 82 and a transmission chain wound around these sprockets may be configured as a chain transmission type.
  • a belt transmission type includes a small-diameter pulley provided as an output rotator 81 on the driven shaft 45, a large-diameter pulley provided as a transmission rotator 82 on the side clutch shaft 46, and a transmission belt wound around these pulleys.
  • the output rotating body 81 may be integrally formed with the driven shaft 45, for example, or may be connected to the driven shaft 45 via a key so as to rotate integrally with the driven shaft 45.
  • the transmission rotating body 82 may be formed integrally with the side clutch shaft 46, for example, or may be connected to the side clutch shaft 46 via a key so as to rotate integrally with the side clutch shaft 46.
  • the side clutch shaft 46 may be externally fitted so as to be relatively rotatable.
  • each side clutch brake unit 48 includes a meshing side clutch 83 for intermittently transmitting power from the transmission gear 82 to the corresponding crawler 7, and the corresponding crawler 7. And a multi-plate type side brake 84 for braking the vehicle. Then, on the side clutch shaft 46, the left side clutch brake unit 48 is arranged on the left side in a distributed manner so as to be symmetric with respect to the transmission gear 82.
  • the left crawler 7 acts on the left crawler 7 via the transmission mechanism 49 and the left traveling drive shaft 50
  • the right side clutch brake unit 48 is connected to the right crawler via the right transmission mechanism 49 and the right traveling drive shaft 50. 7 is configured to act.
  • Each side clutch 83 has a cylindrical shaft 85 that is externally fitted to the side clutch shaft 46 so as to be rotatable relative to the side clutch shaft 46 in a state in which the side clutch shaft 46 can be attached and detached by sliding in the axial direction of the side clutch shaft 46.
  • the moving-side rotating body 86 provided with the meshing portion 86A, the fixed-side rotating body 87 provided with the meshed portion 87A, and the moving-side rotating body 86 is biased toward the entering position where the meshing portion 86A and the meshed portion 87A mesh.
  • a compression spring 88 a stopper 89 made of a C-shaped retaining ring that receives the moving side rotating body 86 at the entry position, a spring receiver 90 that receives one end of the compression spring 88, and the like. Then, when the corresponding moving side rotating body 86 slides to the entry position by the action of the compression spring 88, the meshing portion 86A of the moving side rotating body 86 and the engaged portion 87A of the fixed side rotating body 87 are engaged with each other. By switching to the state and sliding to the cutting position against the action of the compression spring 88, the meshing portion 86A of the moving side rotating body 86 and the meshed portion 87A of the fixed side rotating body 87 release the meshing. It is configured to switch to the shut-off state.
  • Each cylindrical shaft 85 includes a first spline shaft portion 85A having a large diameter on the inner end side close to the transmission gear 82. Further, a small-diameter second spline shaft portion 85B is provided on the outer end side away from the transmission gear 82. The step portion 85C located at the inner end of the first spline shaft portion 85A is configured to function as the spring receiver 90. Further, an annular engagement groove 85D into which the stopper 89 is detachably fitted is formed at the outer end portion of the second spline shaft portion 85B.
  • Each moving-side rotating body 86 is configured such that its inner peripheral portion functions as a spline boss portion 86B that is spline-fitted to the second spline shaft portion 85B of the cylindrical shaft 85 so as to be relatively slidable. Also, by forming a plurality of internal teeth at a constant pitch in the circumferential direction on the inner peripheral portion on the outer end side of the rim portion 86C that forms the outer peripheral portion, the inner peripheral portion of the rim portion 86C functions as the meshing portion 86A. It is configured to do.
  • Each fixed-side rotating body 87 is configured by a spur gear provided with a plurality of external teeth so that the outer peripheral portion functions as a meshed portion 87A. Then, the side clutch shaft 46 has a shaft more than the corresponding cylindrical shaft 85 so as to rotate integrally with the side clutch shaft 46 in a state where the side clutch shaft 46 can be attached and detached by sliding in the axial direction of the side clutch shaft 46. Spline fitting is performed at both end portions on the end side so as to be adjacent to the cylindrical shaft 85.
  • each fixed-side rotating body 87 is configured to function as a driving-side rotating body that rotates integrally with the transmission gear 82 via the side clutch shaft 46 in the left and right side clutches 83.
  • each side clutch 83 the moving side rotating body 86, the compression spring 88, the stopper 89, and the spring receiver 90 are disposed on the outer periphery of the cylindrical shaft 85.
  • the moving-side rotating body 86 and the compression spring 88 are arranged side by side between the moving-side rotating body 86 and the moving-side rotating body 86 can slide in the axial direction of the side clutch shaft 46 with respect to the cylinder shaft 85.
  • the cylinder shaft 85, the moving side rotating body 86, the compression spring 88, the stopper 89, and the spring receiver 90 are mounted on the side clutch shaft 46 with respect to the side clutch shaft 46.
  • the sliding unit 91 is configured to slide integrally in a detachable manner in the axial direction.
  • Each sliding unit 91 is provided with a drive gear 92 as an interlocking rotating body interlockingly connected to the corresponding crawler 7 so as to rotate integrally with the cylinder shaft 85 as one of the components.
  • the moving side rotating body 86 provided in each sliding unit 91 is configured to function as a driven side rotating body that rotates integrally with the drive gear 92 via the cylindrical shaft 85 in each side clutch 83. .
  • a thrust collar 93 is interposed between the transmission gear 82 and the left and right sliding units 91 on the side clutch shaft 46 to receive the force acting in the axial direction of the side clutch shaft 46 therebetween.
  • the side brakes 84 are alternately arranged in the axial direction of the brake hub 94 that rotates integrally with the sliding unit 91, the plurality of separator plates 95 that are externally fitted to the brake hub 94, and the plurality of separator plates 95 and the side clutch shaft 46.
  • a plurality of brake disks 96 and a single pressure plate 97, a brake housing 98 that supports the plurality of brake disks 96 and the single pressure plate 97, and the like are configured.
  • Each brake hub 94 is fitted on the corresponding sliding unit 91 as one of its components.
  • the plurality of separator plates 95 are supported so as to rotate integrally with the sliding unit 91 in a state in which the separator plates 95 can slide in the axial direction of the side clutch shaft 46.
  • Each brake housing 98 has a substantially cylindrical shape that surrounds the separator plate 95, the brake disc 96, and the like, and is integrally formed at the upper and lower intermediate portions of the left and right side walls of the transmission case 43.
  • a plurality of brake discs 96 and a single pressure plate 97 are supported in a non-rotatable manner while being slidable in the axial direction of the side clutch shaft 46.
  • a receiving portion 98A for receiving the separator plate 95 and the brake disc 96 that slides inward of the transmission case 43 along the axis of the side clutch shaft 46 is provided at the inner end portions thereof.
  • Each sliding unit 91 includes a spline boss 99 that rotates integrally with the cylinder shaft 85.
  • Each spline boss 99 serves as a dual-purpose part whose inner end located on the left and right center side in the transmission case functions as the drive gear 92 and whose outer end located on the left and right ends in the transmission case functions as the brake hub 94. It is composed.
  • the drive gear side has an inner peripheral surface provided with a spline hole 99A that fits outside the first spline shaft portion 85A provided on the inner end side of the corresponding cylinder shaft 85, and on the inner peripheral surface on the brake hub side.
  • a diameter-expanded portion 99B that forms a storage space 100 for a compression spring is provided between the cylindrical shaft 85 and the cylindrical shaft 85.
  • Each cylindrical shaft 85 has a first spline shaft portion 85A formed from the stepped portion 85C of the cylindrical shaft 85 to a length extending from the shaft end on the large diameter side. Then, an engagement portion 85E is formed on the outer peripheral side of the first spline shaft portion 85A at the shaft end portion on the large diameter side, and the C-shaped retaining ring 101 is attached to and detached from the engagement portion 85E. Equipped with external fitting as possible.
  • Each spline boss 99 has its spline hole 99A formed in a length extending from the retaining ring 101 to the stepped portion 85C, and the enlarged diameter portion 99B from the stepped portion 85C to the boss end on the brake hub side (the side far from the retaining ring 101). The boss end).
  • Each moving-side rotating body 86 is formed with a ring-shaped recess 86D that allows the end of the spline boss 99 on the brake hub side to be engaged between the spline boss portion 86B and the rim portion 86C.
  • the inner end side of the spline boss portion 86B is engaged with the enlarged diameter portion 99B of the corresponding spline boss 99, and the rim
  • the inner end side of the portion 86C is externally fitted to the spline boss 99
  • the inner end of the rim portion 86C is a plurality of separator plates 95 and brake discs 96 that are externally fitted to the brake hub side of the spline boss 99. It is comprised so that it may press toward the receiving part 98A of the brake housing 98.
  • each moving-side rotating body 86 is configured to function as a pressing portion 86 ⁇ / b> C that acts on the separator plate 95 and the brake disc 96 of the corresponding side brake 84.
  • each side brake 84 slides from the cut position described above to the braking position located in the direction opposite to the entry position, against the action of the compression spring 88 by the corresponding moving side rotating body 86.
  • the transmission case 43 has sliding units 91 at positions facing the side clutch brake units 48 in the axial direction of the side clutch shaft 46 on the left and right side walls.
  • the separator plate 95, the brake disc 96, the pressure plate 97, and the like are provided with a second opening 43B that allows passage, and the cover member 102 that closes the second opening 43B is detachably provided by bolt connection. Yes.
  • Each cover member 102 includes an auxiliary opening 102A that allows passage of the fixed-side rotator 87, and an auxiliary cover member 103 that closes the auxiliary opening 102A is detachably attached by bolt connection.
  • Each auxiliary opening 102 ⁇ / b> A is formed in a circular shape centered on the axis of the side clutch shaft 46.
  • Each auxiliary cover member 103 includes a large-diameter portion 103A that fits in the auxiliary opening 102A and a small-diameter portion 103B that forms an annular space 104 between the auxiliary opening 102A, and the small-diameter portion 103B is located inside the transmission case 43. It is prepared in the state located in.
  • the small-diameter portion 103B is provided with a shaft support portion 105 such as a bearing that supports the end portion of the side clutch shaft 46.
  • Each sliding unit 91 is mounted on the side clutch shaft 46 in a state where the rim portion 86C of the moving side rotating body 86 faces the annular space 104 provided in the cover member 102.
  • Each cover member 102 is fitted and fitted with an annular piston 106 that slides the moving side rotating body 86 in the annular space 104 so as to be slidable in the axial direction of the side clutch shaft 46.
  • the annular space 104 is configured to function as an oil chamber 104 for operating the piston.
  • Each piston 106 slides in the axial direction of the side clutch shaft 46 by the operation of the steering valve unit 107, and by this sliding, the corresponding moving side rotating body 86 is slid in the axial direction of the side clutch shaft 46. It is configured to be operated dynamically. Specifically, as the pressure of the oil chamber 104 is increased by the operation of the valve unit 107, it slides along the axis of the side clutch shaft 46 toward the center side of the side clutch shaft 46. The side rotating body 86 is slid from the entry position to the cut position against the action of the compression spring 88, and then slid from the cut position to the braking position.
  • the oil chamber 104 As the oil chamber 104 is depressurized by the operation of the valve unit 107, it slides along the axis of the side clutch shaft 46 toward the shaft end side of the side clutch shaft 46, and this sliding causes the corresponding movement side rotation.
  • the body 86 is slid from the braking position to the cutting position by the action of the compression spring 88, and then slid from the cutting position to the entry position.
  • the steering valve unit 107 is linked to the steering lever 16 via the steering mechanical linkage mechanism 108 so that the operating state is switched based on the swinging operation of the steering lever 16 in the left-right direction. Specifically, in a state where the control lever 16 is positioned at the neutral position, a reduced pressure state in which the operation pressure on each piston 106 is reduced is maintained. When the control lever 16 is swung to the left from the neutral position, the pressure is switched from the reduced pressure state to the left pressure increasing state in which the operating pressure on the left piston 106 is increased. When the control lever 16 is swung rightward from the neutral position, the pressure is switched from the reduced pressure state to the right pressure increasing state in which the operating pressure on the right piston 106 is increased. When the control lever 16 is swung to the neutral position, the left pressure increasing state or the right pressure increasing state is switched to the pressure reducing state.
  • the valve unit 107 for steering can be maintained in a reduced pressure state, whereby each moving-side rotating body 86 can be maintained in the entering position.
  • the traveling state can be maintained in a straight traveling state in which the left and right crawlers 7 are driven at a constant speed.
  • the steering valve unit 107 can be switched from the reduced pressure state to the left increased pressure state.
  • the left-side moving rotating body 86 can be slid from the entering position to the cutting position or the braking position. As a result, the left crawler 7 is driven or braked from the straight traveling state to the vehicle body.
  • the steering valve unit 107 can be switched from the reduced pressure state to the right increased pressure state. While maintaining the entering position, the right moving rotator 86 can be slid from the entering position to the cutting position or the braking position. As a result, the right crawler 7 is driven or braked from the straight running state. It is possible to switch to a right turn state in which the vehicle body turns rightward. Then, by swinging the control lever 16 to the neutral position in the left turn state or the right turn state, the steering valve unit 107 can be switched from the left boosted state or the right boosted state to the reduced pressure state.
  • either the left or right moving side rotating body 86 located at the cutting position or the braking position can be slid to the entering position, and as a result, the traveling state is switched from the left turning state or the right turning state to the straight traveling state. be able to.
  • each side clutch brake unit 48 employs a shared structure in which each moving side rotating body 86 is also used as an operating tool for both the side clutch 83 and the side brake 84, thereby simplifying the configuration by reducing the number of parts.
  • the side clutch 83 and the side brake 84 can be appropriately interlocked with each other so that the traveling state by the left and right crawlers 7 can be changed from a straight traveling state to a left turning state or a right turning state, It is possible to smoothly shift from the turning state or the right turning state to the straight traveling state.
  • each side clutch brake unit 48 the moving side rotating body 86 and the fixed side rotation with respect to the side clutch shaft 46 built in the transmission case 43 and each brake housing 98 provided in the transmission case 43.
  • the body 87, the separator plate 95, the brake disk 96, and the like can be attached and detached from the openings 43A of the transmission case 43.
  • the operation piston 106 for each side clutch brake unit 48, the shaft support portion 105 for the side clutch shaft, and the like can be attached to and detached from the transmission case 43 together with the cover member 102 that closes each opening 43A.
  • the transmission case 43 is connected to each cover member. By removing 102, it can carry out easily, without requiring the effort which disassembles the transmission case 43.
  • FIG. 10 regarding the maintenance work for the fixed side rotating body 87, the piston 106, and the shaft support portion 105, the moving side rotating body 86, the separator plate 95, and the brake disk 96 are removed by removing the auxiliary cover member 103 from the cover member 102. , And the like can be maintained in the transmission case by the cover member 102, and maintenance work can be performed on the fixed-side rotating body 87, the piston 106, and the shaft support portion 105.
  • the cylindrical shaft 85 of the side clutch 83, the moving side rotating body 86, the compression spring 88, the stopper 89, the spring receiver 90, the drive gear 92, the brake hub 94 of the side brake 84, and the like are attached to the side clutch shaft 46. Since the sliding unit 91 is detachably integrated as a unit, the side clutch shaft is compared with the case where the moving side rotating body 86 and the compression spring 88 are individually attached to and detached from the side clutch shaft 46. The detachability with respect to 46 can be improved.
  • the moving side rotating body 86 and the compression spring 88 are attached to and detached from the side clutch shaft 46 in a united state, so that the movement against the action of the compression spring 88 is achieved.
  • the side rotator 86, the stopper 89, and the like may be attached to and detached from the cylindrical shaft 59 outside the transmission case 43 where the work area is not limited. As a result, the moving side rotator 86, the stopper 89, etc. with respect to the side clutch shaft 46 The detachability of the can be greatly improved.
  • each sliding unit 91 since the spline boss 99 that rotates integrally with the cylinder shaft 85 is a dual-purpose part that also serves as the drive gear 92 and the brake hub 94, the structure can be simplified and assembled by reducing the number of parts. Can be improved. Further, the spline boss 99 has an enlarged diameter portion 99B that forms a storage space 100 for the compression spring between the inner surface of the brake hub side of the spline boss 99 and the cylindrical shaft 85 and the compression spring 88. The spline boss 99 can be equipped in a state where the spline boss 99 is overlapped in the radial direction of the cylinder shaft 85. As a result, the sliding units 91 can be prevented from becoming longer in the axial direction. As a result, the side clutch shaft 46 is shortened and the left and right widths at the upper and lower intermediate portions of the transmission device 13 are reduced. Therefore, the transmission device 13 can be downsized.
  • each moving side rotating body 86 is inserted into the stopper 89 on the inner peripheral surface of the spline boss portion 86B when the moving side rotating body 86 slides to the entering position.
  • An allowed enlarged diameter portion 86E is formed.
  • Each enlarged diameter portion 86E is formed in a size that prevents the stopper 89 from being detached from the engaging groove 85D.
  • each sliding unit 91 in the axial center direction can be further shortened as compared with the case where the diameter-expanded portion 86E is not formed, thereby shortening the side clutch shaft 46 and transmitting power. It is possible to further reduce the size of the transmission device 13 by narrowing the left and right widths at the upper and lower intermediate portions of the device 13.
  • each fixed-side rotating body 87 has a meshing length of 2 with the meshing portion 86A of the moving-side rotating body 86.
  • the tooth width is more than doubled.
  • the life of the fixed side rotating body 87 can be doubled, and the running cost required for the side clutch brake unit 48 can be reduced.
  • each side clutch brake unit 48 the lubricating oil stored in the transmission case 43 is used for operation, and the steering valve unit 107 is operated by the operation of the second hydraulic pump 109. Is supplied through.
  • the steering valve unit 107 is based on the switching valve 110 that switches the flow of oil to the oil chamber 104 of each side clutch brake unit 48 based on the operation of the control lever 16 in the left-right direction, and on the operation of the control lever 16.
  • a variable relief valve 111 for changing the relief pressure for the oil chamber 104 of the left and right side clutch brake units 48 is provided.
  • the pair of side clutch brake units 48 may be configured such that the operating state is switched based on an operation of a steering-dedicated operation lever or a steering wheel that is configured to be a left-right swinging and neutral return type. Good.
  • the pair of side clutch brake units 48 may be configured to be, for example, an electric type that switches the operating state of the side clutch 83 and the side brake 84 by operating an electric cylinder.
  • a pair of side clutches 83 are arranged side by side on the side clutch shaft 46 side by side without the transmission rotating body 82 interposed therebetween, and the power from the side clutch shaft 46 is intermittently configured.
  • the body 82 may be arranged on the left and right ends of the side clutch shaft 46.
  • the pair of side clutches 83 may be configured such that the moving side rotating body 86 functions as a driving side rotating body and the fixed side rotating body 87 functions as a driven side rotating body.
  • the side clutch shaft 46 is fixedly installed, and on the shaft of the side clutch shaft 46, the pair of side clutches 83 intermittently transmit power from the transmission rotating body 82 to the corresponding drive gear (interlocking rotating body) 92. It may be configured.
  • the transmission rotator 82 After each sliding unit 91 is arranged on the side clutch shaft 46 so that the moving-side rotator 86 is adjacent to the transmission rotator 82, the transmission rotator 82 includes an engaged portion 87A.
  • the fixed side rotating body 87 is also used and the moving side rotating body 86 provided with the meshing portion 86A is also used as the interlocking rotating body so that the configuration can be simplified by reducing the number of parts. Good.
  • the transmission rotating body 82 instead of the configuration in which the transmission rotating body 82 also serves as the fixed-side rotating body 87, the fixed-side rotating body 87 that is detachably fitted to the side clutch shaft 46 is rotated in a state of rotating integrally with the transmission rotating body 82.
  • the body 82 may be configured to be engaged and connected.
  • Each sliding unit 91 may be configured to include the drive gear 92 and the brake hub 94 individually. Moreover, you may comprise so that either one or both of the drive gear 92 and the brake hub 94 may not be included as the component.
  • Each sliding unit 91 may be configured such that a spline boss 99 serving as the drive gear 92 and the brake hub 94 is integrally formed on the cylindrical shaft 85.
  • either one of the drive gear 92 and the brake hub 94 may be formed integrally with the cylinder shaft 85.
  • Each sliding unit 91 may be configured such that the compression spring 88 and the spline boss 99 are arranged side by side in the axial direction of the cylindrical shaft 85 without providing the storage space 100.
  • a stepped portion that functions as a stopper 89 for receiving the moving side rotating body 86 at the entering position may be formed on each cylindrical shaft 85. Further, each moving-side rotating body 86 may not include the enlarged diameter portion 86E that allows the stopper 89 to enter.
  • the spring receiver 90 that receives one end of the compression spring 88 may be configured by a C-shaped retaining ring that is externally fitted to each cylindrical shaft 85. Further, a step portion located at the boundary between the spline hole 99A and the enlarged diameter portion 99B on the inner peripheral surface of the spline boss 99 may function as the spring receiver 90.
  • each fixed-side rotating body 87 a spur gear having the same tooth width as the meshing length with the meshing portion 86A of the moving-side rotating body 86 may be adopted.
  • the cover member 102 may not be provided with the auxiliary opening 102A and the auxiliary cover member 103.
  • a shaft support portion 105 may be provided between the transmission case 43 and each cover member 102.
  • the transmission case 43 may include an annular piston 106 for slidingly operating each moving-side rotating body 86 and an oil chamber 104 for operating the piston.
  • a drive sprocket or a drive pulley may be provided instead of the drive gear 92.
  • the side brake 84 provided in the right side clutch brake unit 48 located on the boarding operation unit side functions as the parking brake 112.
  • the right side brake 84 is linked to the brake pedal 19 via the parking brake operating mechanism 113 and the parking brake mechanical linkage mechanism 114.
  • the parking brake operating mechanism 113 rotates the ring-shaped operating member 115 and the operating member 115 fitted in the right cover member 102 around the axis of the side clutch shaft 46 so as to act on the pressure plate 97.
  • an operating member 115 are provided.
  • the mechanical linkage mechanism 114 for parking brake links the free end portion of the linkage arm 117 in the operation mechanism 113 for parking brake to the brake pedal 19.
  • the braking operation shaft 116 is rotated forward in conjunction with the operation, and the operation member 115 is moved in conjunction with the forward rotation.
  • the right side brake 84 is configured to switch from the brake released state to the brake state.
  • the right side brake 84 is configured to be switched from the braking state to the braking release state by releasing the pressure applied to the right pressure plate 97 by sliding to the right side.
  • the brake pedal 19 When the brake pedal 19 is depressed to the depressed position, the brake pedal 19 is held at the depressed position against the spring bias to the depressed release position by the action of a holding mechanism (not shown) linked to the operation. be able to. Further, when the brake pedal 19 is depressed in this position holding state, the holding of the brake pedal 19 at the depressed position can be released by the action of a holding mechanism linked to the operation, and spring bias is used. The depression release operation from the depressed position of the brake pedal 19 to the depressed release position can be performed.
  • the brake pedal 19 can be held at the depressed position by depressing the brake pedal 19 to the depressed position, and the brake on the right side brake 84 is released.
  • the braking state can be switched from the state to the braking state, and the braking force by the right side brake 84 can be applied to the left and right crawlers 7 via the left and right side clutch brake units 48.
  • the right side brake 84 can function as the parking brake 112.
  • the left side brake 84 may function as the parking brake 112. Further, both the left and right side brakes 84 may function as the parking brake 112.
  • a dedicated parking brake 112 that brakes the left and right crawlers 7 via the left and right side clutch brake units 48 may be provided.
  • the parking brake operation mechanism 113 is an electric type that switches the right side brake 84 from the brake released state to the braked state by turning off the power supply, or the right side brake 84 is changed from the brake released state to the braked state by depressurization. You may comprise the hydraulic type to switch.
  • a brake lever configured to be able to switch and hold between a parking position and a parking release position, a switch for operating a parking brake, or the like may be provided.
  • the transmission case 43 corresponds to the first space 56 with the left and right relay shafts 119 at positions between the side clutch shaft 46 and the left and right travel drive shafts 50. It is deployed in a left-right orientation across the second space 58.
  • the left and right side walls of the main case component 52 are provided with first shaft support portions 120 such as bearings that support inner end portions of the corresponding relay shaft 119 located on the left and right center sides of the transmission case 43.
  • each auxiliary case component 53 includes a second shaft support portion 121 such as a bearing that supports outer end portions of the corresponding relay shaft 119 positioned on the left and right ends of the transmission case 43.
  • each relay shaft 119 can be supported in a stable manner so as to be rotatable in a both-side supported state in which both end portions thereof are supported.
  • Each transmission mechanism 49 is positioned at the first transmission portion 122 extending across the side clutch shaft 46 and the relay shaft 119 corresponding to the side clutch shaft 46 in the first space portion 56 positioned on the left and right center side of the transmission case 43, and on both left and right ends of the transmission case 43.
  • the left and right second space portions 58 are provided with corresponding relay shafts 119 and second transmission portions 123 extending across the travel drive shaft 50.
  • the first transmission unit 122 is configured to be symmetrical with respect to the transmission gear 82 in a state where the first transmission unit 122 is positioned above the second transmission unit 123.
  • Each first transmission section 122 includes a drive gear 92 provided in the corresponding sliding unit 91 and a driven gear 124 as a driven rotating body that is larger in diameter than the drive gear 92 and rotates integrally with the corresponding relay shaft 119.
  • the gears 92 and 124 are engaged with each other, and are configured so as to function as a first reduction unit that decelerates the power via the corresponding side clutch brake unit 48.
  • Each driven gear 124 is spline-fitted to the inner end portion of the relay shaft 119 located in the first space portion 56.
  • Each of the second transmission parts 123 includes a small-diameter drive gear 125 as a driving rotary body integrally formed with the corresponding relay shaft 119 and a large-diameter driven gear 126 as a driven rotary body that rotates integrally with the corresponding traveling drive shaft 50.
  • the gears 125 and 126 are meshed and interlocked with each other, and function as a second reduction gear that decelerates from the corresponding first transmission portion 122 to the travel drive shaft 50.
  • each transmission mechanism 49 is configured to function as a deceleration mechanism that decelerates the power that has passed through the corresponding side clutch brake unit 48 in two stages and transmits it to the corresponding travel drive shaft 50.
  • the transmission case 43 includes support portions 127 such as bearings that rotatably support the boss portions 126A on the main case component side of the corresponding driven gear 126 on the left and right side walls of the main case component 52.
  • each auxiliary case component 53 includes a support portion 128 such as a bearing that rotatably supports the boss portion 126B on the auxiliary case component side in the corresponding driven gear 126.
  • Each driven gear 126 is provided with a spline hole portion 126C as a spline fitting portion that enables interlocking connection with the corresponding traveling drive shaft 50 at the center thereof.
  • Each traveling drive shaft 50 includes a spline shaft portion 50A as a spline fitting portion that enables interlocking connection with the corresponding driven gear 126 at the end portion on the transmission case side thereof.
  • the traveling drive shafts 50 are fixed to the outer ends of the traveling drive shafts 50 so that the drive sprockets 129 of the corresponding crawlers 7 are spline-fitted.
  • Each drive shaft case 51 supports the corresponding travel drive shaft 50 so that it can rotate and cannot slide in the axial direction of the travel drive shaft 50.
  • Each auxiliary case component 53 is detachably bolted to an opening 53A through which the traveling drive shaft 50 linked to the driven gear 126 passes and a flange portion 51A provided at the end of the corresponding drive shaft case 51 on the transmission case side. Connected portion 53B.
  • each 2nd transmission part 123 can be exposed comparatively easily, without requiring big effort like the case where the main case component 52 is divided
  • each second transmission portion 123 Even in the state where each second transmission portion 123 is exposed, the driving gear 125 and the driven gear 126 of each relay shaft 119 and each second transmission portion 123 are placed at appropriate positions in the respective recessed portions 52A of the main case component 52. Further, it can be stably supported by the first shaft support portions 120 or the support portions 127 on the main case component side. As a result, the spline fitting of the travel drive shaft 50 to the driven gear 126 and the support of the relay shaft 119 and the driven gear 126 by the second shaft support portion 121 or the support portion 128 on the auxiliary case component side are performed. Assembling work for bolting the part 53 to the left and right side walls of the main case part 52 can be easily performed.
  • each drive shaft case 51 when removing each drive shaft case 51 from the transmission case 43, the bolt connection of each drive shaft case 51 to each auxiliary case component 53 is released, and each drive shaft case 51 is covered with the corresponding auxiliary case component 53.
  • the travel drive shaft 50 can be easily removed from the transmission case 43 together with each drive shaft case 51 by separating the auxiliary case part 53 from the connecting portion 53B to the laterally outward direction.
  • the drive shaft case 51 when each drive shaft case 51 is attached to the transmission case 43, the drive shaft case 51 is placed at an appropriate position with respect to each auxiliary case component 53 by spline fitting each travel drive shaft 50 to the corresponding driven gear 126. Can be positioned stably. Thereby, the bolt connection of each drive shaft case 51 to each auxiliary case component 53 can be easily performed, and the corresponding traveling drive shaft 50 and the driven gear 126 can be maintained in the spline fitting state by this connection. it can.
  • each traveling drive shaft 50 and each drive shaft case 51 can be easily attached to and detached from the transmission case 43.
  • each traveling drive shaft 50 and each drive shaft case 51 are removed from the transmission case 43, so that the transmission device 13 is connected to each traveling drive shaft 50 and each drive shaft case 51. It is possible to achieve a compact state with no overhang in the left-right direction, which is advantageous in terms of transportation.
  • the tread width of the left and right crawlers 7 can be easily adjusted according to the model while using the same transmission device 13. Can be changed.
  • the left and right transmission mechanisms 49 are configured symmetrically, the drive gears 92 and 125, the driven gears 124 and 126 used for the left and right transmission mechanisms 49, and the relay shaft 119 are shared. Can be a part. As a result, it is possible to facilitate the parts management and improve the assembling performance due to the same assembling process of each transmission mechanism 49.
  • each side clutch brake unit 48 by providing a transmission mechanism 49 that functions as a speed reduction mechanism on the lower side in the transmission direction with respect to each side clutch brake unit 48, torque applied to each side clutch brake unit 48 can be reduced, and each side clutch brake unit 48. It is possible to facilitate the operation. In addition, a large torque can be generated in the left and right traveling drive shafts 50 even though the speed reduction mechanism is not provided between the input shaft 44 and the transmission 47.
  • each transmission mechanism 49 is configured such that the drive gear 125 of the second transmission portion 123 that rotates integrally with the corresponding relay shaft 119 is detachably fitted to the relay shaft 119. Also good.
  • a single relay shaft 119 is fixed to the transmission case 43 in the lateral direction, and the driven gear 124 of the first transmission portion 122 and the drive gear 125 of the second transmission portion 123 are integrally formed on the relay shaft 119. You may comprise so that a cylindrical shaft may be externally fitted so that relative rotation is possible.
  • the left and right auxiliary case parts 53, the left and right traveling drive shafts 50, and the left and right drive shaft cases 51 have the same left and right shapes that can be used both left and right. Consists of common parts. Thereby, compared with the case where the left and right auxiliary case parts 53, the left and right traveling drive shafts 50, and the left and right drive shaft cases 51 are individually configured in a shape unique to the left and right, parts management is facilitated, etc. It is possible to prevent the left and right from being combined with each other.
  • the transmission case 43 has a left and right central side portion located between the left and right second transmission portions 123 at the bottom thereof, An upward concave portion 43 ⁇ / b> C that is brought close to the first transmission portion 122 is provided, and its bottom portion is formed in an inverted U shape.
  • the concave end side of the concave portion 43 ⁇ / b> C is located between the left and right traveling drive shafts 50 at the bottom of the transmission case 43 and extends across the left and right side walls of the main case component 52.
  • the transmission device 13 has the relay shafts 119 disposed at the front upper position with respect to the travel drive shaft 50. Further, the side clutch shaft 46 is disposed at a rear upper position with respect to each relay shaft 119.
  • the driving force F1 from the side clutch shaft 46 applied to each relay shaft 119 and the driving reaction force F2 from each traveling drive shaft 50 are: While the vertical components F1a and F2a are reduced by canceling each other, the driven gear 124 of each relay shaft 119 and each drive gear 92 of the side clutch shaft 46, and the drive gear 125 and each travel drive shaft of each relay shaft 119 are reduced.
  • the side clutch shaft 46 and the travel drive shafts 50 are distributed via the 50 driven gears 126.
  • the driving force F ⁇ b> 1 and the driving reaction force F ⁇ b> 2 applied to each relay shaft 119 decrease as the vertical components F ⁇ b> 1 a and F ⁇ b> 2 a cancel each other.
  • only the relay shaft 119 is applied.
  • each shaft supporting portion (bearing) supporting each relay shaft 119 is compared.
  • the load on 120, 121 can be reduced, and the durability of each pivotal support 120, 121 can be improved.
  • the transmission device 13 is provided with a driven shaft 45 of the transmission 47 at a front upper position with respect to the side clutch shaft 46.
  • an input shaft 44 that also serves as a drive shaft of the transmission 47 is disposed at a rear upper position with respect to the driven shaft 45.
  • the driven gears 61, 63, 65 of the driven shaft 45 and the drive gears 60, 62, 64 of the input shaft 44, and the output gear 81 of the driven shaft 45 and the side are lowered while the components F 3 a, F 4 a are canceled out.
  • the input shaft 44 and the side clutch shaft 46 are dispersed via the transmission gear 82 of the clutch shaft 46.
  • the driving force F3 and the driving reaction force F4 applied to the driven shaft 45 decrease as the vertical components F3a and F4a cancel each other.
  • only the driven shaft 45 is applied.
  • each shaft support (bearing) 80 that supports the driven shaft 45 is compared with a case where the driving force F3 and the driving reaction force F4 are applied only to the driven shaft 45 during forward traveling with high use frequency. Load can be reduced, and the durability of each shaft support can be improved.
  • the transmission device 13 has the side clutch shaft 46 disposed behind the input shaft 44 and each travel drive shaft 50. Further, each relay shaft 119 is arranged at a position ahead of the driven shaft 45. Thereby, while suppressing that the vertical length of the transmission device 13 becomes long, the separation distance between the side clutch shaft 46 and each relay shaft 119, and between each relay shaft 119 and each travel drive shaft 50. The separation distance can be increased. As a result, the reduction ratio between each drive gear 92 and each driven gear 124 between the side clutch shaft 46 and each relay shaft 119, and each drive between each relay shaft 119 and each travel drive shaft 50. The reduction ratio between the gear 125 and each driven gear 126 can be increased, and a large torque can be generated in the left and right traveling drive shafts 50.
  • the cutting and conveying device 2 has a working position covering the front of the transmission device 13 and the transmission device 13 by swinging the control lever 16 in the front-rear direction as described above. It is configured to move up and down over a non-working position where the front is opened.
  • the relay shafts 119 including the large-diameter driven gears 124 are arranged at positions ahead of the input shaft 44, the driven shaft 45, the side clutch shaft 46, and the travel drive shafts 50,
  • the lower side of the front wall that corresponds to the location of each relay shaft 119 is bulged forward.
  • the upper side of the front wall has a shape that is biased rearward than the lower side.
  • An oil filter 130 that filters the oil stored in the transmission case and the steering valve unit 107 that controls the oil from the oil filter 130 are installed on the front side of the front wall. In such a state that the valve unit 107 is positioned on the right side, the left and right sides are arranged detachably.
  • the steering valve unit 107 is equipped with the valve operating shaft 131 in a state of protruding forward from the front wall of the valve case 132 on the upper side of the valve unit 107. Then, a linkage arm 133 that moves integrally with the valve operating shaft 131 is mounted on the front end portion that is the protruding end portion of the valve operating shaft 131 in a state of extending to the right side that is the boarding operation portion side. The end side is linked to the control lever 16 through a mechanical linkage mechanism 108 for steering.
  • the HST 12 is provided on the upper portion of the right side wall of the transmission case 43 on the boarding operation unit side, and is equipped with the speed change operation shaft 40 so as to protrude forward from the front wall of the speed change case 30. Yes.
  • the linkage arm 41 provided at the front end portion which is the protruding end portion of the speed change operation shaft 40 is linked to the main speed change lever 17 via a main gear shift mechanical linkage mechanism 42.
  • the speed change operation shaft 73 passes through an upper portion of the oil filter 130 on the front wall of the transmission case 43, and the front end portion serving as the protruding end portion of the speed change operation shaft 73 is more than the valve unit 107 for steering. It is configured to be located in the front. Then, a linkage arm 77 that moves integrally with the speed change operation shaft 73 is provided at the front end portion of the speed change operation shaft 73 so as to extend to the right side, which is the boarding operation portion side, and the extension end side is sub-shifted.
  • the lever 18 is linked via a mechanical linkage mechanism 78 for auxiliary transmission.
  • the parking brake 112 is configured by using a side brake 84 provided in the right side clutch brake unit 48 located on the boarding operation unit side. Then, the braking operation shaft 116 provided in the parking brake operating mechanism 113 is protruded from the right side wall of the transmission case 43 located on the boarding driving part side to the right outer side on the boarding driving part side, The linkage arm 117 provided at the right end portion is linked to the brake pedal 19 via a mechanical linkage mechanism 114 for parking brake.
  • the oil filter 130 and the steering valve unit 107 can be replaced, or the mechanical linkage mechanism 108 for steering, the mechanical linkage mechanism 42 for main transmission, and the mechanical linkage mechanism 78 for auxiliary transmission.
  • the cutting and conveying device 2 is raised to the non-working position, whereby the oil filter 130, the steering valve unit 107, the steering mechanical linkage mechanism 108, and the main transmission
  • the front of the mechanical linkage mechanism 42 and the mechanical linkage mechanism 78 for sub-transmission can be opened, and the above-described maintenance work can be easily performed from the front thereof.
  • the mechanical linkage mechanism 42 for main transmission, the mechanical linkage mechanism 78 for auxiliary transmission, the mechanical linkage mechanism 108 for steering, and the mechanical linkage mechanism 114 for parking brake are respectively connected to the boarding operation unit 8.
  • the transmission case 43 can be configured in a state in which their linkage length is shortened as much as possible. Since each of the speed change operation shafts 40 and 73 and the valve operation shaft 131 protrude forward, the main gear shift mechanical linkage mechanism 42 and the sub gear shift mechanical linkage with respect to the operation shafts 40, 73, and 131 are provided.
  • the mechanism 78 or the mechanical linkage mechanism 108 for steering can be easily connected from the front thereof.
  • the auxiliary transmission lever 18 and the transmission operation shaft 73 of the transmission 47 are connected via the mechanical linkage mechanism 78 for the auxiliary transmission.
  • the linkage can be easily performed without being obstructed by the oil filter 130.
  • adhesion of mud or the like to the oil filter 130 and the steering valve unit 107 can be suppressed by the lower side of the transmission case 43 that bulges forward.
  • the working posture when the oil filter 130 and the steering valve unit 107 are replaced is excessive. It can be a less comfortable posture. As a result, the maintainability of the oil filter 130 and the steering valve unit 107 can be improved.
  • the transmission case 43 includes the side clutch brake units 48 at positions behind the steering valve unit 107.
  • the left and right cover members 102 that are the left and right case portions covering the side clutch brake units 48 are provided with pipe connection portions 102 ⁇ / b> B communicating with the oil chambers 104 of the side clutch brake units 48.
  • Each connection part 102B is arranged at a position below the oil filter 130 in the left and right cover members 102.
  • the steering valve unit 107 includes a pipe connection 107A for the left side clutch brake unit 48 on the left side wall, and a pipe connection 107B for the right side clutch brake unit 48 on the upper side wall. I have.
  • the left side hydraulic pipe 134 extending between the transmission case side connecting portion 102 ⁇ / b> B and the valve unit side connecting portion 107 ⁇ / b> A to the left side clutch brake unit 48 does not protrude forward from the front wall of the valve unit 107. Piping to pass below.
  • the right hydraulic pipe 135 extending between the transmission case side connecting portion 102B and the valve unit side connecting portion 107B with respect to the right side clutch brake unit 48 does not protrude forward from the front wall of the valve unit 107. Piping to pass right side of.
  • the transmission case 43 sucks oil stored in the transmission case 43 by the operation of the second hydraulic pump 109 on the inner surface of the lower side of the front wall of the main case part 52.
  • the oil suction port 43D that enables the above is formed.
  • an internal oil passage 43 ⁇ / b> E extending from the oil suction port 43 ⁇ / b> D to the oil inlet 130 ⁇ / b> A of the oil filter 130 is formed on the front wall of the main case part 52.
  • an oil outlet that enables the oil stored in the transmission case 43 to be taken out is formed in the transmission case 43, and a hydraulic pipe extending from the oil outlet to the oil inlet 130 ⁇ / b> A of the oil filter 130 is connected to the transmission case 43.
  • a hydraulic pipe extending from the oil outlet to the oil inlet 130 ⁇ / b> A of the oil filter 130 is connected to the transmission case 43.
  • the oil suction port 43 ⁇ / b> D and the internal oil passage 43 ⁇ / b> E are provided with a groove 55 ⁇ / b> B that is recessed and formed in the mating surface 55 ⁇ / b> A of the right case member 55 of the transmission case 43 with the left case member 54.
  • the mating surfaces 55A and 55B of the left case member 54 and the right case member 55 are formed. Thereby, it is not necessary to consider the shape of the groove 55B formed in the mating surface 55A of the right case member 55 for the gasket 136 interposed between the mating surfaces 55A and 55B of the left case member 54 and the right case member 55.
  • the left case member 54 and the right case member 43D and the inner oil passage 43E are formed by recessing both the mating surface 54A of the left case member 54 and the mating surface 55A of the right case member 55.
  • the mating surfaces 55A and 55B with 55 are formed across the mating surfaces 55A and 55B, it is necessary to provide the gasket 136, and there is no need for an elongated hole for communicating the groove on the left case member side and the groove on the right case member side. can do.
  • the sealing property of the gasket 136 with respect to the mating surfaces 54A and 55A between the left case member 54 and the right case member 55 and the strength of the gasket 136 can be easily ensured.
  • the oil suction port 43 ⁇ / b> D is formed between the left and right driven gears 126 having the lowest rotation speed in the first space 56 between the left and right transmission mechanisms 49. That is, since the left and right driven gears 12 have the lowest rotation speed in the first space portion 56, the number of bubbles generated along with the rotation at the time of driving thereof is reduced. Since the oil suction port 43D is formed between the left and right driven gears 126 that are separated from each other, it is possible to effectively prevent the occurrence of inconvenience that bubbles generated along with the rotation of each driven gear 12 are sucked from the oil suction port 43D together with oil. Can be suppressed.
  • the transmission case 43 utilizes the fact that the lower side is bulged forward, and receives the oil at the lower part of the oil filter 130 on the front wall to transmit the transmission case 43.
  • An oil guide 43F is formed to guide the left side wall of 43.
  • the transmission case 43 supplies oil returned from the steering valve unit 107, which is a hydraulic device, to the inside of the transmission case 43.
  • the oil passage 137 for lubrication is provided to each of the driven gears 61, 63, 65 rotating relative to the motor 45.
  • the lubricating oil passage 137 is formed by a hydraulic pipe 138 extending from the steering valve unit 107 to the transmission case 43, an internal oil passage 45C formed in the driven shaft 45, and the like.
  • hydraulic equipments such as a valve unit for raising / lowering or HST
  • the transmission case 43 can incorporate an auxiliary space portion 57 provided in the upper portion thereof and an auxiliary transmission mechanism (not shown) for the working device. It is formed into a shape. And the 4th opening 43H which enables taking out of auxiliary power from an auxiliary power transmission mechanism is formed in the predetermined position in the left side wall opposite to the right side wall provided with the 3rd opening 43G for input, and this A lid member 139 that closes the fourth opening 43H is detachably mounted.
  • this transmission apparatus 13 employ
  • the auxiliary space 57 has a built-in auxiliary transmission mechanism for power distribution to the cutting and conveying device, so that the specification can be easily changed to a transmission structure suitable for self-removing combine. can do. That is, it is possible to obtain a highly versatile transmission 13 that can be applied to a self-removing combine.
  • the interference between the work transmission system that transmits the power extracted from the fourth opening 43H of the transmission case 43 to the work apparatus and the HST 12 that is the input system to the transmission apparatus 13 or the like It becomes easy to avoid.
  • the extension length of the input shaft 44 to the left in the transmission 47 is shorter than the driven shaft 45, and the left-right width at the top of the transmission 13 is narrowed to the right.
  • the HST 12 is detachably equipped with an oil filter 140 at the upper part of the case main body 35.
  • the front of the oil filter 140 can be opened, and maintenance work for the oil filter 140 such as replacement of the oil filter 140 can be performed from the front. It can be done easily.
  • the transmission device for the working machine according to the first embodiment described above is used in, for example, harvesting machines such as ordinary combine harvesters, self-removing combine harvesters, carrot harvesters, corn harvesters, and transport vehicles, tractors, and the like. Can be applied.
  • the combine is supported by a self-propelled traveling machine body 201 having a pair of left and right crawler-type traveling devices 202 and on the front part of the traveling machine body 201 so as to be swingable up and down.
  • An unloader 206 for discharging to the outside is provided.
  • the cutting part 203 is a reel 207 that scrapes the planted cereal toward the machine, a cutting device 208 that cuts the stock of the planted cereal and reaps the planted cereal, and feeds the harvested cereal to the feed.
  • An auger 209 that collects and feeds backwards, and a feeder 210 that conveys the harvested cereals fed from the auger 209 toward the entrance of the threshing device 204 at the rear upper side of the machine body.
  • the harvested culm is threshed and sorted by the threshing device 204, and the threshed grain is conveyed to the Glen tank 205 and stored.
  • the stored grain can be discharged to the outside by the unloader 206.
  • the driving unit 211 is arranged on one side (right side) of the front part of the traveling machine body 201.
  • the threshing device 204 is disposed on the opposite side of the driving unit 211 in the rear part of the traveling machine body 201, the Glen tank 205 is disposed on the same side as the driving unit 211, and the threshing device 204 and the Glen tank 205 are arranged side by side. It is out.
  • the front end portion of the threshing device 204 overlaps with the rear portion of the operation unit 211.
  • an engine 212 is provided in the lower part of the driving unit 211, and a transmission 213 is provided in front of the engine 212.
  • the transmission 213 is connected to a main transmission 214 composed of a hydrostatic continuously variable transmission (HST) and a transmission case 216 in which an auxiliary transmission 215 and other reduction gears are housed. It is configured.
  • HST hydrostatic continuously variable transmission
  • the power from the engine 212 is shifted continuously in the forward and reverse directions by the main transmission 214 and further shifted by the auxiliary transmission 215 built in the transmission case 216 and then provided on the lower transmission side of the auxiliary transmission 215.
  • the steering transmission mechanism 219, the intermediate gear mechanism 220, and the pair of left and right axles 221 are transmitted to the left and right traveling devices 202.
  • the power of the engine 212 is configured to be transmitted to the threshing device 204 via the threshing clutch 223 that can be intermittently operated by the threshing clutch lever 222 provided in the operation unit 211, and further transmitted to the threshing device 204.
  • the motive power is transmitted to the cutting unit 203 via a cutting clutch 225 that can be intermittently operated by a cutting clutch lever 224 provided in the operation unit 211.
  • the main transmission 214 is entirely covered with a main transmission case 226, and is provided outside the transmission case 216 on the right side (left side in the drawing) on the upper side.
  • the transmission case 216 is flange-connected.
  • the main transmission case 226 and the transmission case 216 are connected by connecting a plurality of locations with the bolts 227 in a state in which the connection surfaces in the vertical orientation are in contact with each other.
  • the main transmission 214 transmits the power of the engine 212 to the input shaft 228.
  • the transmission case 216 has an output shaft 229 through which the right side wall 216A as a side wall on one end side of the transmission case 216 is inserted from the outer side of the case toward the inner side of the case. Then, it is configured to output from the output shaft 229.
  • concentric fitting grooves M1 and M2 are formed at connecting portions of the cases 226 and 216 in the insertion holes 230 and 231 formed in the main transmission case 226 and the transmission case 216, respectively.
  • a collar member 280 for axial alignment is provided in a state in which the fitting groove M1 and the fitting groove M2 of the transmission case 216 are fitted.
  • the collar member 280 aligns the axes of the insertion holes 230 and 231 of both cases, and can support the output shaft 229 with high accuracy.
  • the output shaft 229 is rotatably supported by the right side wall 216A by the bearing 232 provided in the insertion hole 230 formed in the right side wall 216A of the mission case 216. Further, the transmission case 216 It extends to the left side wall 216B as the other end side through the inside.
  • the output shaft 229 is further rotatably supported by a bearing 233 as a shaft support member provided in the insertion hole 231 formed in the left side wall 216B, and the shaft end portion 229a is exposed to the outside of the case. It is prepared in the state to do. Therefore, the output shaft 229 is rotatably supported on the right side wall 216A and the left side wall 216B via the bearings 232 and 233, respectively.
  • the output shaft 229 is configured to include a pair of split transmission shafts 229A and 229B that are divided along the axial direction and linked together so as to be integrally rotatable. Power is transmitted from the output shaft 229 to the auxiliary transmission 215.
  • the output gear 234 is fitted to the pair of split transmission shafts 229A and 229B so as to be integrally rotatable, and the pair of split transmission shafts 229A and 229B are linked and linked by the output gear 234.
  • the output shaft 229 extends from the first split transmission shaft 229A extending from the inside of the main transmission 214 and is positioned on the same axis in a state of being in contact with the shaft end of the first split transmission shaft 229A.
  • the second split transmission shaft 229B is provided.
  • Spline portions 235 and 236 are formed on the outer peripheral portions of the first divided transmission shaft 229A and the second divided transmission shaft 229B, and the spline portions 235 and 236 of the first divided transmission shaft 229A and the second divided transmission shaft 229B, respectively.
  • An output gear 234 that is externally fitted in a meshed state is provided.
  • the second split transmission shaft 229B has one end on the first split transmission shaft 229A meshing with the output gear 234 and the other end inserted through an insertion hole 231 formed in the left side wall 216B of the transmission case 216.
  • the shaft end 229a is rotatably supported on the left side wall 216B via a bearing 233 as a shaft support member in a state where the shaft end 229a is exposed to the outside (outside) of the mission case 216.
  • the output gear 234 is provided in a state of being located at an end portion of the output shaft 229 on the main transmission device 214 side, and an output shaft 229 has an output at a position opposite to the main transmission device 214.
  • a collar 238 for holding the gear 234 in a state where the gear 234 is positioned at the end on the main transmission 214 side is extrapolated.
  • the output shaft 229 of the main transmission 214 passes through the transmission case 216 and is inserted through the left side wall 216B so that the shaft end 229a is exposed to the outside of the case, and the bearings 232 and 233 are disposed. Via the right side wall 216A and the left side wall 216B.
  • the sub-transmission device 215 is a gear-type transmission that shifts the power transmitted from the output shaft 229 to two steps according to the working state and transmits it to the traveling device 202.
  • a shift-side input shaft 239 and an output-side shift output shaft 240 are provided.
  • the transmission input shaft 239 is supported by the transmission case 216 so as to be rotatable in a state along the vehicle body lateral direction (the horizontal direction in the drawing of FIG. 21).
  • the speed change input shaft 239 is provided with an input gear 241 that meshes with and interlocks with the output gear 234 provided on the output shaft 229 in a state where the input shaft 239 rotates integrally and cannot slide.
  • the transmission input shaft 239 has a low-speed transmission drive gear (hereinafter referred to as a low-speed drive gear) 242 and a high-speed transmission drive gear (referred to as a high-speed drive gear) in a state in which the input shaft 239 is relatively rotatable and cannot slide.
  • a low-speed drive gear hereinafter referred to as a low-speed drive gear
  • a high-speed transmission drive gear referred to as a high-speed drive gear
  • the transmission output shaft 240 is supported by the transmission case 216 so as to be rotatable in a state along the lateral width direction of the vehicle body in a posture parallel to the transmission input shaft 239.
  • the transmission output shaft 240 is in a state of being integrally rotated and incapable of sliding movement, and a low-speed transmission driven gear (hereinafter referred to as a low-speed driven gear) 244 and a high-speed transmission driven gear (hereinafter referred to as a high-speed driven gear). ) 245 and drive gear 246 are provided.
  • the low-speed drive gear 242 and the low-speed driven gear 244 are set in the vehicle width direction so that they are always engaged, and the high-speed drive gear 243 and the high-speed driven gear 245 are set in the vehicle width direction so that they are always engaged. Yes.
  • a shifter 247 is spline-fitted between the low-speed drive gear 242 and the high-speed drive gear 243 of the transmission input shaft 239 so as to be integrally rotatable and slidable.
  • the shifter 247 moves in the left-right direction and engages with a spline portion 248 formed on the low-speed drive gear 242, a high-speed position P3 meshed with the spline portion 249 formed on the high-speed drive gear 243, and the low-speed drive gear 242. And a neutral position P2 that does not mesh with any of the high-speed drive gear 243.
  • a shift fork 250 for sliding the shifter 247 is supported so as to be slidable in a state parallel to the speed change input shaft 239 along the left-right direction.
  • the shift fork 250 is supported by the three positions (low speed position P1, It is configured to be switchable between a high speed position P3 and a neutral position P2) and to be able to hold a position at each position.
  • the swing arm 258 when the swing arm 258 is operated through an interlocking operation mechanism 257 including a link mechanism or the like in accordance with the operation of the auxiliary transmission lever 256 provided in the operation unit 211, for example.
  • a locking tool 260 provided on an operation arm 259 that swings integrally with the swing arm 258 is provided in a state of engaging with an engagement groove 261 formed on the shift fork 250, and the swing arm 258 swings. Accordingly, the shift fork 250 is configured to slide along the axial direction of the shaft member 251.
  • the position of the shift fork 250 is maintained when the ball 254 enters and engages with one of the circumferential grooves 253.
  • the ball 254 follows the sliding movement and climbs over a mountain between the circumferential groove 253 and the circumferential groove 253 and is positioned in another circumferential groove 253.
  • the shift fork 250 can be held at that position after being changed to a desired position.
  • the shift fork 250 is configured to engage at two positions located on the diameter of the engaging circumferential groove 262 of the shifter 247. Further, it is provided in a state of passing through a space between a shifter 247 provided on the transmission input shaft 239 and a driving gear 246 provided on the transmission output shaft 240.
  • the shift fork 250 is formed with an engagement action portion 250c having a substantially C-shape in a side view of the machine body in a state of extending integrally from the slide support portion 250a.
  • the engaging action portion 250c enters and engages with the engaging circumferential groove 262 formed on the outer peripheral portion of the shifter 247, and slides the shifter 247 in the axial direction in accordance with the sliding operation.
  • the engaging action portion 250c engages with two locations where the pair of tip portions are located on the diameter of the engaging circumferential groove 262 of the shifter 247, and pushes these two locations in the axial direction, thereby shifting the shifter 247. Is configured to slide. In this way, by pushing the two locations located on the diameter of the engaging circumferential groove 262, the shifter 247 can be smoothly slid in a state where there is little fear of twisting.
  • a high speed drive gear 243 is provided on the side near the input gear 241 and a low speed drive gear 242 is provided on the side far from the input gear 241 in the speed change input shaft 239.
  • the high-speed drive gear 243 is provided in a state of being spaced apart from the input gear 241 in the axial direction. That is, a collar 281 is provided between the high-speed drive gear 243 and the input gear 241 so as to maintain the distance between the high-speed drive gear 243 and the input gear 241.
  • the low-speed drive gear 242 is provided with a space in the axial direction between the transmission input shaft 239 and a bearing 233 for rotatably supporting the left side wall 216B of the transmission case 216. That is, a collar 282 is provided between the low-speed drive gear 242 and the bearing 233 so as to maintain the distance between the low-speed drive gear 242 and the bearing 233 so that the distance between the two is maintained at the set value.
  • the sub-transmission device 215 switches the power, which is shifted by the main transmission device 214 and input to the transmission input shaft 239 by the movement of the shifter 247, to high and low two stages via the shifter 247. Is possible. If the shifter 247 is in the neutral position P2, the power transmission is cut off and the neutral state is established. If the auxiliary transmission 215 is operated in the high speed shifting state, the cutting operation can be performed at high speed, and if it is operated in the low speed shifting state, the cutting operation can be performed at low speed. That is, by operating the auxiliary transmission 215 to change the traveling speed, the traveling speed can be changed to a speed according to the working state.
  • the main transmission lever 237 for shifting the main transmission 214 is prevented from being operated in a high speed range that is equal to or higher than the set value.
  • a checking means (not shown) that releases the check and allows the main transmission lever 237 to be operated to a high speed range equal to or higher than a set value.
  • the main speed change lever 237 is not operated in the high speed range above the set value by the check operation by the check means, and the speed change operation can be performed in the operation range lower than the set value.
  • the sub-transmission lever 256 is operated to operate the sub-transmission device 215 to the high-speed shift state, the cutting operation on the high-speed side is possible. Work is possible.
  • the main speed change lever 237 can be operated in a high speed range that is equal to or higher than the set value, and can travel at a speed higher than the work speed.
  • the steering transmission mechanism 219 will be described. As shown in FIGS. 19 and 20, the steering transmission mechanism 219 rotates integrally with the side clutch shaft 263 supported by the transmission case 216 in a posture parallel to the transmission output shaft 240 and near the center of the side clutch shaft 263.
  • the center gear 264 is fixed to the left and right sides, the left and right clutch sleeves 265 inserted on the side clutch shaft 263 so as to be relatively rotatable and slidable on both the left and right sides of the center gear 264, and the clutch sleeve 265 being pressed.
  • a shifter 267 that moves the left and right clutch sleeves 265 separately or simultaneously to the friction disk 266 side.
  • the center gear 264 is engaged with the driving gear 246 in the auxiliary transmission 215 and interlocked with the center gear 264 to transmit the power after shifting. Accordingly, the center gear 264 corresponds to the lower transmission gear.
  • a meshing portion 268 is formed on the inner end side of the clutch sleeve 265 (the left and right center side of the transmission case 216) and on both sides of the center gear 264, and the meshing portions 268 on both sides constitute a so-called dog clutch. Further, the left and right clutch sleeves 265 are provided with side gears 270 that always mesh with an intermediate gear 272 (described later) of the intermediate gear mechanism 220.
  • a “clutch engaged state (transmission state)” is established, and the clutch sleeve 265 rotates integrally with the center gear 264 to perform main shift.
  • the power shifted by the device 214 and the auxiliary transmission 215 is transmitted to the traveling device 202 via the intermediate gear mechanism 220.
  • the clutch sleeve 265 slides in a direction away from the center gear 264, and the engagement between the center gear 264 and the clutch sleeve 265 is released, so that a "clutch disengaged state (disengaged state)" Transmission of power to the traveling device 202 is cut off. Further, when the clutch sleeve 265 presses the friction disk 266, a braking force is applied to the clutch sleeve 265, and the traveling device 202 is braked.
  • the vehicle body can be turned by sliding the left or right clutch sleeve 265, and the travel can be stopped by simultaneously sliding the left and right clutch sleeves 265.
  • the intermediate gear mechanism 220 has an intermediate shaft 271 supported by the transmission case 216 in a posture parallel to the side clutch shaft 263, and an intermediate shaft 271 that is relatively rotatable and non-slidable.
  • the left and right intermediate gears 272 are provided.
  • the left and right intermediate gears 272 include a large-diameter gear portion 272A that always meshes with the left and right side gears 270, and a small-diameter gear portion 272B that meshes with a final gear 276 provided on the axle 221.
  • the power transmitted from the steering transmission mechanism 219 is transmitted to the left and right traveling devices 202 via the left and right intermediate gears 272.
  • a pair of left and right axles 221 that transmit the power shifted by the main transmission 214 and the auxiliary transmission 215 to the left and right traveling devices 202 are fixedly extended from the transmission case 216. It is provided in a state of being inserted through the axle cases 273 on the left and right sides.
  • the pair of left and right axles 221 includes a small-diameter power transmission portion 221A at the inner side in the lateral direction of the fuselage, and a large-diameter laterally extending outwardly in the lateral direction of the fuselage.
  • the portion 221C is configured to include the portion 221B, and the continuous portion 221C between the power transmission portion 221A and the laterally extending portion 221B has a larger diameter from the power transmission portion 221A toward the outer side in the lateral direction of the body. It is formed in a taper shape.
  • a spline portion 274 is formed on the outer periphery of the power transmission portion 221A, and a final gear 276 that meshes with a small-diameter gear 275 that rotates integrally with the intermediate gear 272 is externally attached to the spline portion 274. Further, the laterally extending portion 221 ⁇ / b> B is provided with a large diameter in order to increase the support strength, and the gap between the inner peripheral surface of the axle case 273 is narrow.
  • the connecting portion 221C between the power transmission portion 221A and the laterally extending portion 221B is formed in a tapered shape, the circulating oil stored in the transmission case 216 is supported by the bearing 277 that supports the axle 221. From the wide space between the power transmission part 221A and the axle case 273, the taper-like gap makes it easy to flow into the gap between the laterally extending part 221B and the inner peripheral surface of the axle case 273. ing.
  • the output shaft 229 of the main transmission 214 may be integrally formed over the entire length in the axial direction.
  • the arrangement configuration of the input gear 241, the high-speed drive gear 243, and the low-speed drive gear 242 provided in the transmission input shaft 239 is not limited to the configuration of the above embodiment, and is close to the input gear 241, for example.
  • the low speed drive gear 242 may be provided on the side, and the high speed drive gear 243 may be provided on the side far from the input gear 241.
  • the arrangement configuration of the high-speed driven gear 245, the low-speed driven gear 244, and the driving gear 246 provided in the transmission output shaft 240 may be changed as appropriate.
  • the auxiliary transmission 215 includes the high-speed drive gear 243 and the low-speed drive gear 242 that are not provided with the shifter 247, but are provided on the transmission input shaft 239 so as to be integrally rotatable and slidable integrally in the axial direction. It is good also as a structure which performs gear shifting by sliding these gears.
  • the transmission output shaft 240 is provided with the high-speed driven gear 245 and the low-speed driven gear 244 so that they can rotate integrally and cannot slide in the axial direction.
  • the auxiliary transmission 215 is provided with a high-speed driven gear 245 and a low-speed driven gear 244 that are not provided with the shifter 247 but are provided on the transmission output shaft 240 so as to be integrally rotatable and slidable in the axial direction. It is good also as a structure which shifts by sliding.
  • the speed change input shaft 239 is provided with the high speed drive gear 243 and the low speed drive gear so as to be integrally rotatable and not slidable in the axial direction.
  • the collar member 280 for axial alignment is provided in the connection surface of the main transmission case 226 and the connection surface of the transmission case 216 at the position where the output shaft 229 is inserted.
  • a configuration without the collar member 280 may also be adopted.
  • the continuous portion 221C between the small-diameter power transmission portion 221A and the large-diameter laterally extending portion 221B in the axle 221 is formed in a tapered shape.
  • a stepped stepped portion may be formed.
  • the hydrostatic continuously variable transmission is used as the main transmission 214, but the present invention is not limited to this.
  • the main transmission 214 may be a hydraulic mechanical continuously variable transmission (HMT) or other CVT.
  • a normal combine is shown as the harvesting machine, but a self-removing combine may be used, and other types of harvesting machines such as a corn harvesting machine may be used.
  • the combine includes a self-propelled traveling machine body 301, a crawler-type traveling apparatus 302 that enables self-running, and a cutting part that is supported on the front part of the traveling machine body 301 so as to be swingable up and down. 303, a threshing device 304, a Glen tank 305 arranged next to the threshing device 304, and an unloader 306 connected to the rear lower part of the Glen tank 305.
  • the cutting unit 303 includes a reel 303A, a reel 303A, an auger 303C, and a feeder 303D.
  • the planted cereal is scraped by the reel 303A and cut by the reel 303A.
  • the harvested grains are collected in front of the feeder 303D by the auger 303C, scraped into the feeder 303D, and conveyed to the threshing device 304 by the feeder 303D.
  • the harvested culm is threshed and sorted by the threshing device 304, and the threshed grain is conveyed to the glen tank 305 and stored.
  • the stored grain is discharged to the outside by the unloader 306.
  • the driving unit 307 is disposed on one side (right side) of the front portion of the traveling machine body 301.
  • the threshing device 304 is disposed on the opposite side of the driving unit 307 in the rear part of the traveling machine body 301, the Glen tank 305 is disposed on the same side as the driving unit 307, and the threshing device 304 and the Glen tank 305 are arranged side by side. It is out.
  • the front end portion of the threshing device 304 overlaps the rear portion of the operation unit 307 in the front-rear direction.
  • an engine 308 is provided in the lower part of the driving unit 307, and a transmission 309 is provided in front of the engine 308.
  • the transmission 309 is equipped with a hydrostatic continuously variable transmission 309A (hereinafter referred to as “HST 309A”) as a main transmission of the present invention, an auxiliary transmission 309C, and other reduction gears.
  • the transmission case 309B is connected to the transmission case 309B.
  • the driving force from the engine 308 is input to the HST 309A from the HST input shaft 311 and is shifted forward and backward continuously by the HST 309A.
  • the driving force shifted by the HST 309A is output from the HST output shaft 312 to the transmission case 309B, shifted by the auxiliary transmission 309C, and finally transmitted to the left and right driving sprockets 302A (see FIG. 23).
  • the left and right traveling devices 302 are driven by the left and right sprockets.
  • the driving force from the engine 308 is transmitted to the mowing unit 303 and the threshing device 304 through a route different from the transmission route to the HST input shaft 311.
  • the auxiliary transmission 309C is a two-stage switching and gear transmission.
  • the auxiliary transmission 309C includes an auxiliary transmission input shaft 313, an auxiliary transmission output shaft 316, a small diameter gear 314, a large diameter gear 315, a large diameter fixed gear 317, and a small diameter fixed gear 318 that constitute the “gear train” of the present invention. And a shifter 319.
  • the sub-transmission input shaft 313 and the sub-transmission output shaft 316 are supported by the mission case 309B so as to be rotatable along the left-right direction.
  • the small-diameter gear 314 and the large-diameter gear 315 are extrapolated to the auxiliary transmission input shaft 313 in a state in which they can rotate relative to each other but cannot slide.
  • the large-diameter fixed gear 317 and the small-diameter fixed gear 318 are externally fitted to the auxiliary transmission output shaft 316 in a state where relative rotation is impossible and sliding is impossible.
  • the small-diameter gear 314 and the large-diameter fixed gear 317 are positioned in the left-right direction so that they always mesh, and the large-diameter gear 315 and the small-diameter fixed gear 318 are positioned in the left-right direction so that they always mesh. Yes.
  • the shifter 319 is externally fitted (for example, spline fitted) to the auxiliary transmission input shaft 313 in a state where relative rotation is impossible and sliding is possible between the small diameter gear 314 and the large diameter gear 315.
  • the shifter 319 moves in the left-right direction and meshes with the inner diameter portion of the small-diameter gear 314, meshes with the inner diameter portion of the large-diameter gear 315, or meshes with both the small-diameter gear 314 and the large-diameter gear 315. It is possible to switch to a state that is not.
  • the sub-transmission device 309C causes the small-diameter gear 314 and the large-diameter fixed gear 317 to transmit the driving force that is shifted by the HST 309A and input to the sub-transmission input shaft 313 by the movement of the shifter 319 via the shifter 319.
  • the driving force can be switched in two stages.
  • the traveling speed is changed within the respective speed regions by selecting the high speed shift state or the low speed shift state by the speed change operation of the sub-transmission device 309C and greatly changing the speed range (a large change in the reduction ratio). And appearing after speed adjustment. Therefore, if the sub-transmission device 309C is operated in the high speed shift state, the cutting operation can be performed at high speed, and if the sub transmission device 309C is operated in the low speed transmission state, the cutting operation can be performed at low speed. That is, the traveling speed can be efficiently changed to a speed corresponding to the working state by operating the auxiliary transmission device 309C.
  • the driver 307 includes a driver seat 323, a front panel 321 positioned in front of the driver seat 323, and a left side of the driver seat 323 from the left end of the front panel 321. And a side panel 322 extending rearward.
  • the front panel 321 is provided with a reel lifting / lowering lever 334, a steering lever 331, a meter panel 332, and a water temperature meter 333 in this order from the right outer side to the inner side of the body.
  • a reel lifting / lowering lever 334 When the steering lever 331 is swung left and right, the traveling machine body 301 turns left and right.
  • the cutting unit 303 swings up and down.
  • the reel lift lever 334 is swung back and forth, the reel 303A swings up and down.
  • the water thermometer 333 is provided with a temperature indicator 333a as a region indicating the water temperature, and the water temperature is represented by the position where the needle 333c points to the temperature indicator 333a. Further, when the water temperature reaches an allowable upper limit temperature (for example, 115 ° C.), an alarm sound is generated from a buzzer (not shown). Further, a warning sign part 333b is provided adjacent to the high temperature side end of the temperature sign part 333a for performing a preliminary warning before the water temperature reaches the allowable upper limit temperature. The extreme end position of the warning sign portion 333b is set to the allowable upper limit temperature, and the needle 333c points to the area of the warning sign portion 333b to visually notify that the water temperature is approaching the allowable upper limit temperature.
  • an allowable upper limit temperature for example, 115 ° C.
  • an alarm sound is generated from a buzzer (not shown).
  • a warning sign part 333b is provided adjacent to the high temperature side end of the temperature sign part 333a for performing
  • the side panel 322 includes a lever guide 324, a lever guide 325, a lever guide 326, and a lever guide 327.
  • the lever guide 324 is formed in the front part of the side panel 322 in a state located in the vicinity of the center in the left-right direction and substantially along the front-rear direction.
  • the lever guide 325 is formed in the front portion of the side panel 322 in a state located right next to the lever guide 325 and along the front-rear direction.
  • the lever guide 326 is formed in a state of being located behind the lever guide 325 and in a state along the front-rear direction at the center portion in the front-rear direction of the side panel 322.
  • the lever guide 327 is formed at the center of the side panel 322 in the front-rear direction, in a state positioned behind the lever guide 324, in a state adjacent to the left side of the lever guide 326, and in a state along the front-rear direction.
  • a main transmission lever 341 as a “main transmission operation tool” of the present invention is inserted into the lever guide 324 so as to be able to swing back and forth.
  • a trunnion shaft (not shown) in the HST 309A is rotated, and a swash plate angle (not shown) is changed. That is, the HST 309A can be shifted by operating the main shift lever 341.
  • the lever guide 324 is displaced to the left in the left-right direction with respect to the forward-side operation path 324a on the forward-side operation path 324a along the front-rear direction and on the rear side of the forward-side operation path 324a.
  • the reverse operation path 324c in the state along the front-rear direction, and the neutral path 324b in the state along the left-right direction so as to connect the rear end of the forward operation path 324a and the front end of the reverse operation path 324c
  • the “neutral position” of the present invention is formed.
  • the main speed change lever 341 is operated to the front end side in the forward operation path 324a
  • the forward speed increases
  • the main speed change lever 341 is operated to the rear end side in the reverse operation path 324c
  • the reverse speed is increased.
  • Increases speed When the main transmission lever 341 is operated to the neutral path 324b, the speed becomes “0”.
  • a sub-transmission lever 342 as the “sub-transmission operating tool” of the present invention is inserted so as to be swingable back and forth.
  • the shifter 319 described above is operated by operating the auxiliary transmission lever 342.
  • the auxiliary transmission 309C can be switched to the low speed shift state, the neutral state, and the high speed shift state.
  • a “clutch operating tool” and a “clutch lever” 343 as a “clutch lever” of the present invention are inserted in a swingable manner.
  • the cutting clutch 310A see FIG. 25
  • the cutting clutch 310A see FIG. 25
  • the driving force of the engine 308 is transmitted to the harvesting unit 303.
  • the mowing clutch lever 343 can swing back and forth around the swing axis X located at the lower end.
  • a “clutch disengagement position (see FIG. 27A)” is set on the rear end side of the lever guide 326, and a “clutch engagement position (see FIG. 27B)” is on the front end side of the lever guide 326. Is set.
  • the cutting clutch lever 343 When the cutting clutch lever 343 is operated to the clutch engagement position, it moves further forward by contacting the front end 326a of the lever guide 326, that is, the clutch disengagement position from the clutch engagement position. Movement to the opposite side is restricted. That is, the front end portion 326a corresponds to the “restricting portion” of the present invention.
  • a threshing clutch lever 344 is inserted so as to be able to swing back and forth.
  • the threshing clutch 310B (see FIG. 25) can be switched between the on state and the off state.
  • the driving force of the engine 308 is transmitted to the threshing device 304.
  • the power transmission path to the mowing unit 303 is provided in series on the lower side of the power transmission path from the engine 308 to the threshing device 304, when the threshing clutch 310B is in the disengaged state, the mowing clutch 310A is Even in the on state, the cutting unit 303 is not driven. That is, when the “threshing clutch 310B is engaged and the reaping clutch 310A is engaged”, the threshing device 304 and the reaping portion 303 are driven, and “the threshing clutch 310B is engaged and the reaping clutch is disengaged”. In this case, only the threshing device 304 is driven, and when the threshing clutch 310B is in the disengaged state, the threshing device 304 and the reaping unit 303 are not driven regardless of the state of the reaping clutch.
  • the check mechanism 345 is provided with a check portion 351 and a link portion 352.
  • the check part 351 can be moved out and out of the forward operation path 324a.
  • the link part 352 links the check part 351 and the cutting clutch lever 343, and when the cutting clutch lever 343 is operated to the clutch engagement position, the check part 351 moves to a predetermined command position in the forward operation path 324a. Project to the corresponding position. As a result, even if the main transmission lever 341 is moved further forward (front end side), it cannot be moved in contact with the check portion 351.
  • the restraining portion 351 is provided with a guide member 351a and a protruding member 351b.
  • the guide member 351a extends along the forward operation path 324a at a position deviated downward from the forward operation path 324a (lever guide 324) and is slidable along the front-rear direction.
  • the protruding member 351b is provided at the distal end of the guide member 351a and can protrude into the forward operation path 324a.
  • the guide member 351a and the protruding member 351b are formed by bending the tip of a single bar-like member (for example, a round bar).
  • a bracket 346 corresponding to the “support bracket” of the present invention and a bracket 347 corresponding to “another support bracket” of the present invention are attached to the bottom surface of the side panel 322.
  • the bracket 346 is provided between the lever guide 324 and the lever guide 325 in a plan view.
  • the bracket 346 is formed by bending a single plate into a U shape when viewed from the side, and further bending both upper ends into a hook shape on the front side and the rear side.
  • the bracket 346 is fixed to the bottom surface of the side panel 322 via the flanges at the front and rear ends.
  • the front surface portion and the rear surface portion of the bracket 346 are located at different positions along the front-rear direction, and a through hole 346a is formed in each.
  • the two through holes 346a are formed so as to overlap when viewed in the front-rear direction.
  • the guide member 351a passes through the two through holes 346a, and is supported by the bracket 346 so as to be slidable in the front-rear direction (slidable).
  • the bracket 347 is provided on the left side of the forward operation path 324a, that is, on the opposite side of the bracket 346 across the forward operation path 324a in plan view. As shown in FIGS. 27 and 28, the bracket 347 is formed by bending a single plate into an L shape in front view. The bracket 347 is fixed to the bottom surface of the side panel 322 via an L-shaped one side. A long hole 347a is formed in the L-shaped other side of the bracket 347 along the front-rear direction.
  • the leading end of the projecting member 351b is penetrated through the long hole 347a, and one end of the projecting member 351b is supported by the guide member 351a, and the other end (tip section) is slidable in the front-rear direction (slidable). In this state, the bracket 347 is supported.
  • the bracket 347 has a front end of the long hole 347a positioned at least ahead of the front end of the forward operation path 324a by at least the radial length of the protruding member 351b, and a rear end of the long hole 347a is restrained. It is configured and positioned so as to be positioned rearward by the radial length of the protruding member 351b from the position.
  • the link part 352 is provided with an arm member 352a and a rod member 352b.
  • the arm portion is coupled and fixed to the lower end portion of the cutting clutch lever 343 and can swing around the swing axis X together with the cutting clutch lever 343.
  • the rod portion extends in the front-rear direction, the rear end portion is linked to the arm member 352a so as to be rotatable about the first axis Y1, and the front end portion is a second axis center with respect to the rear end portion of the guide member 351a. It is linked so as to be rotatable around Y2.
  • the rod member 352b is a rod-like member (for example, a round bar) that is bent downward at an intermediate portion slightly closer to the front end.
  • the arm portion extends downward and slightly forward from the swing axis X in the side view, and the cutting clutch lever 343 is When the clutch is engaged (see FIG. 27 (b)), it is in a state extending rearward and slightly upward from the swing axis X in a side view.
  • the rod member 352b has a front end connected to a guide member 351a that slides in the front-rear direction, so that the cutting clutch lever 343 moves from the clutch disengagement position (see FIG. 27A) to the clutch engagement position (see FIG. 27). 27 (b)), it moves rearward while maintaining the vertical position of the front end, and the rear end swings upward about the second axis Y2.
  • the link portion 352 has a swinging axis X in a side view when the cutting clutch lever 343 is operated from the clutch disengagement position (see FIG. 27A) to the clutch engagement position (see FIG. 27B).
  • the first axis Y1 passes the rear side of the swing axis X, and the straight line L connecting the first axis Y1 and the second axis Y2 is the swing axis. It is configured to move across the heart X. Accordingly, when the cutting clutch lever 343 is operated to the clutch engagement position (see FIG. 27B), when a force pulling forward is applied to the rod member 352b, the arm portion is moved by the rod member 352b. Pulled forward, trying to rotate counterclockwise in left side view. However, as described above, the cutting clutch lever 343 to which the arm member 352a is connected and fixed is in contact with the front end portion 326a of the lever guide 326 and cannot rotate counterclockwise. It cannot move further forward.
  • the protruding member 351b is in a state of being retracted to the front side of the forward operation path 324a when the cutting clutch lever 343 is operated to the clutch disengagement position, and the cutting clutch lever 343 is operated to the clutch engagement position. Then, the guide member 351a is pulled backward by the swing of the arm member 352a via the rod member 352b and slides, and the protruding member 351b protrudes to the check position of the forward operation path 324a. Therefore, as shown in FIG.
  • the main speed change lever 341 is checked even if it moves from the neutral path 324b side to the forward side. At the position, it abuts against the protruding member 351b and cannot be operated further forward. However, even when the cutting clutch 310A is operated, the main speed change lever 341 can be freely operated in the forward side operation path 324a between the check position and the neutral path 324b and in the reverse side operation path 324c.
  • the traveling speed region on the forward side is that the cutting clutch 310A is in the “disengaged state” (the check mechanism 345 is in the “non-check state”).
  • the check mechanism 345 is in the “non-check state”.
  • Pattern A when “0” to “V1 (maximum speed)” are set and the reaping clutch 310A is in the “engaged state” (the restraining mechanism 345 is in the “restraining state”), “pattern C” is obtained.
  • “0” to “V3 (maximum speed) k ⁇ V1”.
  • “k” is a coefficient satisfying “0 ⁇ k ⁇ 1”.
  • the check mechanism 345 As described above, by providing the check mechanism 345, two types of speed regions appear on condition that the cutting clutch 310A is turned on and off, and four traveling speed regions that are twice the number of speed change regions of the auxiliary transmission 309C appear. It becomes possible to go out. Therefore, compared with the gear-type sub-transmission device 309C having four gear trains, the left and right widths of the transmission case 309B are designed to be smaller, and the gear thickness is increased to improve the durability of the sub-transmission device 309C. You can make it. Further, since the traveling speed is not shifted to a certain traveling speed (V3, V4) or more in a state where the cutting unit 303 is driven, the traveling device 302 does not exceed the appropriate traveling speed due to an erroneous operation. It is possible to prevent a high load on 308.
  • the check mechanism 345 there are other ways to use the check mechanism 345.
  • the sub-transmission device 309C when the sub-transmission device 309C is operated in the low speed shift state and travels at a low speed, the reaping clutch 303 is driven when the mowing unit 303 is driven and the travel speed is considerably higher than the current speed.
  • the auxiliary transmission device 309C is operated in the high speed shifting state after the 310A is operated in the on state, the speed can be efficiently increased to the appropriate traveling speed.
  • the user forgets to operate the auxiliary transmission 309C in the high speed transmission state.
  • the check mechanism 345 is provided, even if the main speed change lever 341 is operated forward to increase the speed, the speed change side cannot be operated from the check position, and the sub-transmission device 309C is provided to the driver. It can be noticed that it is in the low speed shift state, and can be urged to operate the auxiliary transmission 309C to the high speed shift state.
  • the traveling speed region on the forward side is “pattern A” when the cutting clutch 310A is in the “disengaged state” (the restraint mechanism 345 is in the “non-restraint state”).
  • “k” is a coefficient satisfying “0 ⁇ k ⁇ 1”.
  • the check mechanism 345 does not operate. Therefore, in the traveling speed range on the forward side, the cutting clutch 310A is in the “cut state” (the check mechanism 345 is in the “non-check state”). ) Or “entering state” (the restraining mechanism 345 is “restraining state”), as indicated by “pattern B”, “0” to “V2 (maximum speed)”.
  • the main transmission device 309C when the sub-transmission device 309C is in a high-speed transmission state and the engine 308 is in a high-load state where a working unit that requires a large driving force is driven, the main transmission device is on the high-speed side. Thus, it is possible to prevent a situation in which the engine 308 is further loaded by the operation.
  • the harvesting clutch 310A and the harvesting clutch lever are provided as the working clutch and the working clutch lever.
  • the present invention is not limited thereto.
  • the threshing clutch 310B and the threshing clutch lever 344 may be selected as the working clutch and the working clutch lever, and when there are other clutches and clutch levers, they may be selected.
  • the power transmission path to the traveling device 302 and the power transmission path to the mowing unit 303 and the threshing device 304 may be branched into two in the mission case 309B (for example, the HST output shaft 312).
  • the power transmission path to the mowing unit 303 and the power transmission path to the threshing device 304 are not provided in series, and may be configured as different routes.
  • auxiliary transmission device 309C can be switched between the two states of the high speed shift state and the low speed shift state. It may be configured to be switchable to a state.
  • the magnitude relationship between the speeds “V1” to “V4” in the above-described embodiment is not limited to that shown in FIG. 29 and FIG.
  • “V2” may be a value greater than “V3”
  • “V4” may be a value greater than “V3”.
  • the coefficient “k” is not necessarily a common value in the “high speed shift state” and the “low speed shift state”.
  • bracket 346 having two through-holes 346a is provided as the “support bracket” is shown.
  • two brackets having one through-hole are arranged side by side. It may be installed.
  • the main transmission may be, for example, an HMT (hydraulic mechanical continuously variable transmission) or other CVT.
  • the lever type is provided as the auxiliary transmission operation tool and the clutch operation tool.
  • a push button type switch or the like may be used.
  • the main transmission operating tool may be a sliding lever or a switch instead of a rocking lever.
  • the present invention can be applied not only to a full throw-in type combine, but also to a self-removing combine, and only a harvester that travels with a steering lever type harvester or a crawler type traveling device.
  • the present invention can also be applied to a harvesting machine that travels by a steering wheel type harvesting machine or a wheel type traveling device.
  • a transmission device for a working machine such as a transmission device for a harvester according to the present invention includes, for example, a harvester such as a normal combine harvester, a self-removing combine harvester, a carrot harvester, a corn harvester, a transport vehicle, and a tractor. , Etc.
  • traveling device 34 output shaft 43 transmission case 43A opening 43B opening 44 input shaft 45 driven shaft 45A spline shaft portion 45B predetermined spline shaft portion 46 side clutch shaft 47 transmission 49 reduction mechanism 50 traveling drive shaft 61B spline boss portion 63 driven gear 63A gear portion 63B spline boss portion 65 driven gear 65A gear portion 65B spline boss portion 66 shift mechanism 74 spline boss 74a spline 81 output rotating body 82 transmission rotating body 83 side clutch 84 side brake 85 cylinder shaft 85A spline shaft portion 85C stepped portion 85D Engagement groove 85E Engagement part 86 Moving side Rolling body (driven rotating body) 86A Engagement part 86C Press part 86E Diameter expansion part 87 Fixed side rotary body (drive side rotary body) 87A Engaged part 88 Compression spring 89 Stopper (retaining ring) 90 Spring receiver 91 Sliding unit 92 Gear (drive gear, interlocking rotating body) 94 Brake hub 95 Separat

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Environmental Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • General Engineering & Computer Science (AREA)
  • Arrangement Of Transmissions (AREA)
  • Structure Of Transmissions (AREA)
  • Harvester Elements (AREA)
  • General Details Of Gearings (AREA)

Abstract

La présente invention concerne un dispositif de transmission destiné à une moissonneuse et comprenant, à l'intérieur d'une boîte (43) de transmission: un arbre récepteur (45) horizontal qui est installé de façon adjacente et dans une orientation parallèle à un arbre (44) d'entrée de la boîte (43) de transmission; un horizontal arbre (46) d'embrayage latéral muni d'un rotor (82) de transmission qui est en prise avec un rotor (81) de sortie installé sur l'arbre récepteur (45); une transmission (47) sélective à engrenages servant à réorienter une force motrice provenant de l'arbre (44) d'entrée; et une paire d'embrayages latéraux (83) qui sont positionnés sur l'arbre (46) d'embrayage latéral de façon à connecter/à déconnecter individuellement la transmission de la force motrice du rotor (82) de transmission à des dispositifs d'avance droit et gauche. L'arbre (44) d'entrée est installé sur un arbre (34) de sortie horizontal, qui est installé sur un dispositif extérieur (A) relié à la boîte (43) de transmission, de façon à tourner solidairement avec l'arbre (34) de sortie autour du centre axial de l'arbre (34) de sortie. La transmission (47) est configurée pour transmettre la force motrice de l'arbre (44) d'entrée à l'arbre récepteur (45) et est placée de façon à s'étendre de l'arbre (44) d'entrée à l'arbre récepteur (45).
PCT/JP2014/052998 2013-06-28 2014-02-10 Dispositif de transmission pour engin de travaux, et moissonneuse WO2014208117A1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
CN202010067316.8A CN111066488B (zh) 2013-06-28 2014-02-10 传动装置以及收割机
CN201480032975.0A CN105283339B (zh) 2013-06-28 2014-02-10 收割机用的传动装置
KR1020157032539A KR101799175B1 (ko) 2013-06-28 2014-02-10 작업기용의 전동 장치 및 수확기
KR1020177032617A KR102048136B1 (ko) 2013-06-28 2014-02-10 수확기
PH12015502618A PH12015502618A1 (en) 2013-06-28 2015-11-24 Power transmission apparatus for work machine, and harvester

Applications Claiming Priority (8)

Application Number Priority Date Filing Date Title
JP2013-136519 2013-06-28
JP2013136520A JP6095506B2 (ja) 2013-06-28 2013-06-28 収穫機
JP2013136519A JP6095505B2 (ja) 2013-06-28 2013-06-28 収穫機
JP2013-136520 2013-06-28
JP2013189765A JP6104110B2 (ja) 2013-09-12 2013-09-12 収穫機用の伝動装置
JP2013189767A JP6029556B2 (ja) 2013-09-12 2013-09-12 作業機用の伝動装置
JP2013-189767 2013-09-12
JP2013-189765 2013-09-12

Publications (1)

Publication Number Publication Date
WO2014208117A1 true WO2014208117A1 (fr) 2014-12-31

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PCT/JP2014/052998 WO2014208117A1 (fr) 2013-06-28 2014-02-10 Dispositif de transmission pour engin de travaux, et moissonneuse

Country Status (4)

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KR (2) KR101799175B1 (fr)
CN (3) CN111066488B (fr)
PH (1) PH12015502618A1 (fr)
WO (1) WO2014208117A1 (fr)

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CN107087450B (zh) * 2017-03-29 2022-11-11 星光农机股份有限公司 无级变速传动结构
CN108162692A (zh) * 2018-02-05 2018-06-15 温岭市明华齿轮有限公司 收获机前驱动桥总成
DE102019206829A1 (de) * 2019-05-10 2020-11-12 Deere & Company Antriebssystem für eine Erntemaschine
CN112173746B (zh) * 2020-09-04 2022-06-21 南京朗禾智能控制研究院有限公司 一种用于农作物软管吸粮机的进料装置
CN112026513B (zh) * 2020-09-07 2022-02-15 中国第一汽车股份有限公司 一种断开装置及同轴电驱动系统
CN115180261B (zh) * 2021-08-25 2024-09-06 江苏富勤机械制造有限公司 一种管材转运设备的使用方法
JP7536124B2 (ja) * 2023-01-24 2024-08-19 本田技研工業株式会社 パワーユニット構造

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US11430272B2 (en) 2017-01-20 2022-08-30 Polaris Industries Inc. Diagnostic systems and methods of a continuously variable transmission
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KR101799175B1 (ko) 2017-12-20
KR102048136B1 (ko) 2019-11-22
CN105283339B (zh) 2018-12-04
CN105283339A (zh) 2016-01-27
CN107521337B (zh) 2020-02-14
PH12015502618B1 (en) 2016-02-29
CN111066488B (zh) 2022-07-15
PH12015502618A1 (en) 2016-02-29
KR20170127575A (ko) 2017-11-21
CN107521337A (zh) 2017-12-29
KR20160025496A (ko) 2016-03-08
CN111066488A (zh) 2020-04-28

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