JP2012211671A - Speed change transmission device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a speed change transmission device that can easily be suppressed and avoided in the enlargement of the device.SOLUTION: The speed change transmission device comprises: an input shaft 22 that is input with an engine drive force; a hydraulic continuous variable transmission 30 driven by the input shaft 22; a planetary transmission part 40 which synthesizes the drive force of the input shaft 22 and an output of the hydraulic continuous variable transmission 30, and outputs the synthesized drive force; and an output rotating body 24 which outputs power to a traveling device. The planetary transmission part 40 and the output rotating body 24 are arranged at the same side as a side at which the engine connecting side of the input shaft 22 is positioned with respect to the hydraulic continuous variable transmission 30. The drive force is inputted to the planetary transmission part 40 from a region between the engine connecting side of the input shaft 22 and the hydraulic continuous variable transmission side.

Description

  The present invention combines an input shaft for inputting engine driving force, a hydraulic continuously variable transmission driven by the input shaft, a driving force of the input shaft and an output of the hydraulic continuously variable transmission. The present invention relates to a speed change transmission device provided with a planetary transmission unit that outputs a composite driving force and an output rotating body that outputs a combined driving force.

  Conventionally, for example, there has been a speed change transmission device described in Patent Document 1. Patent Document 1 includes a pump shaft that penetrates a hydraulic pump of a continuously variable transmission (hydraulic continuously variable transmission), and is connected to a side projecting from the continuously variable transmission of the pump shaft from the engine. The driving force is input, the driving force of the pump shaft is transmitted to the composite planetary transmission portion from the side protruding from the continuously variable transmission portion of the pump shaft to the composite planetary transmission portion, and the continuously variable transmission portion is driven by the engine driving force. The power and the output from the continuously variable transmission unit are combined by a composite planetary transmission unit.

JP 2008-215499 A

  When the above-mentioned conventional technology is adopted, the distance from the part that inputs the engine driving force of the pump shaft to the part that outputs to the planetary transmission part becomes longer due to the hydraulic pump located between both parts, and the planetary transmission part It is necessary to increase the strength of the pump shaft so that the pump shaft is less likely to be distorted due to the driving load, and a large hydraulic continuously variable transmission such as a large pump shaft is provided to increase the strength of the pump shaft. It was necessary to adopt a machine.

  An object of the present invention is to provide a transmission device that can easily suppress or avoid an increase in size.

The first invention combines an input shaft for inputting engine driving force, a hydraulic continuously variable transmission driven by the input shaft, a driving force of the input shaft and an output of the hydraulic continuously variable transmission. In the transmission transmission device provided with a planetary transmission unit that outputs a combined driving force and an output rotating body that outputs to the traveling device,
The planetary transmission unit and the output rotating body are disposed on the same side as the side where the engine connection side of the input shaft is located with respect to the hydraulic continuously variable transmission, and the engine connection side of the input shaft is not hydraulically connected. A driving force is input to the planetary transmission unit from a portion between the step transmission and the transmission side.

  According to the configuration of the first aspect of the invention, the planetary transmission unit and the output rotating body are disposed on the same side as the side where the engine connection side of the input shaft is located with respect to the hydraulic continuously variable transmission, and the engine connection side of the input shaft Since the driving force is input to the planetary transmission part from the part between the transmission and the hydraulic continuously variable transmission, the transmission structure from the input shaft to the planetary transmission part can be made as simple as possible with a short transmission distance. . The driving force is input to the planetary transmission portion from the portion between the engine connecting side of the input shaft and the hydraulic continuously variable transmission connecting portion, and the portion that outputs the engine driving force of the input shaft to the planetary transmission portion Distance can be made as small as possible, distortion of the input shaft due to the driving load of the planetary transmission section can be made difficult to prevent or increase the size of the input shaft, and the driving load of the planetary transmission section can be used as the pump shaft It can be difficult to engage, and the increase in size of the hydraulic continuously variable transmission can be suppressed or avoided by suppressing or avoiding the increase in size of the pump shaft.

  Therefore, it is possible to obtain a compact state that suppresses or avoids an increase in size both in terms of the transmission structure that transmits power from the input shaft to the planetary transmission unit and also in terms of the input shaft and the hydraulic continuously variable transmission.

  In the second aspect of the present invention, the input shaft is coaxially arranged with respect to the pump shaft of the hydraulic continuously variable transmission and is connected to the pump shaft so as to be integrally rotatable, the sun gear of the planetary transmission unit, An output rotator is rotatably supported around a rotation axis that is coaxial with the motor axis of the hydraulic continuously variable transmission.

  According to the configuration of the second invention, the hydraulic continuously variable transmission can be driven by the input shaft with a compact interlocking structure in which the input shaft and the pump shaft are arranged coaxially. Furthermore, a compact interlocking structure in which the sun gear, the output rotator, and the motor shaft are coaxially arranged allows transmission from the hydraulic continuously variable transmission to the planetary transmission unit and transmission from the planetary transmission unit to the output rotator.

  Therefore, it is possible to obtain compactly from the aspect of driving the hydraulic continuously variable transmission by the input shaft, from the aspect of transmission from the hydraulic continuously variable transmission to the planetary transmission section and transmission from the planetary transmission section to the output rotating body. Can do.

  In the third aspect of the present invention, an input side clutch mechanism is provided for switching the planetary transmission unit between an interlocking state and an interlocking disengagement state with respect to the input shaft, and the output rotating body is in an interlocking state with respect to the motor shaft of the hydraulic continuously variable transmission. And an output side clutch mechanism for switching to the interlocking cut-off state.

  According to the configuration of the third aspect of the invention, the planetary transmission unit is switched to the interlocked state with respect to the input shaft, and the output rotating body is switched to the interlocked state with respect to the motor shaft. A shift by HST mode transmission can be performed so that the gear is output from the output rotating body after being shifted by the step transmission. By switching the planetary transmission unit to the interlocking state with respect to the input shaft and switching the output rotating body to the interlocking disconnection state with respect to the motor shaft, the engine driving force input by the input shaft is transmitted to the planetary transmission unit, and the engine driving force and hydraulic pressure Shift by HMT mode transmission can be performed so that the output from the continuously variable transmission is combined by the planetary transmission unit and the combined driving force is output from the output rotating body.

  Therefore, it is possible to easily stop running and switch between forward and backward movements simply by changing the operation of the hydraulic continuously variable transmission by performing output by HST mode transmission, and outputting by HMT mode transmission. Thus, it is possible to perform variable speed running with good transmission efficiency.

  In the fourth aspect of the invention, a charge pump for supplying hydraulic oil to the hydraulic continuously variable transmission is provided between the engine connecting side and the hydraulic continuously variable transmission connecting side of the input shaft.

  According to the configuration of the fourth aspect of the present invention, the drive load of the charge pump can be applied between the engine connecting side of the input shaft and the hydraulic continuously variable transmission connecting side, so that it is difficult to be applied to the pump shaft of the hydraulic continuously variable transmission. .

  Therefore, while the charge pump is driven by the driving force of the input shaft, an increase in the size of the pump shaft of the hydraulic continuously variable transmission can be suppressed, and a hydraulic continuously variable transmission can be advantageously obtained.

  In the fifth aspect of the invention, a charge pump for supplying hydraulic oil to the hydraulic continuously variable transmission is provided between the engine connecting side of the input shaft and the input side clutch mechanism.

  Between the engine connecting side of the input shaft and the input side clutch mechanism, there is no hydraulic continuously variable transmission and it is easy to secure a pump installation space. According to the configuration of the fifth aspect of the invention, the pump installation space is secured. A charge pump can be equipped compactly in an easy part.

  Accordingly, while the charge pump is driven by the driving force of the input shaft, the charge pump can be simply equipped with a compact.

It is a side view which shows the whole combine. It is a schematic front view which shows a transmission structure. It is a vertical front view which shows the speed change transmission apparatus in HMT mode transmission. It is a vertical front view which shows the speed change transmission apparatus in HST mode transmission. It is explanatory drawing which shows the relationship between the operation state of an input side clutch mechanism and an output side clutch mechanism, the operation state of a transmission switching clutch mechanism, and the transmission form of a transmission gearbox. It is explanatory drawing which shows the relationship between the speed change state of a hydraulic continuously variable transmission, and the output speed of a speed change transmission apparatus. It is a block diagram which shows a speed change operation apparatus. It is a vertical front view which shows the speed change transmission apparatus provided with the 1st another implementation structure. It is explanatory drawing which shows the relationship between the operation state of a hydraulic continuously variable transmission, a forward clutch, a reverse clutch, and an output side clutch mechanism, and the transmission form of a transmission gearbox. It is explanatory drawing which shows the output speed of the speed change transmission apparatus provided with the 1st another implementation structure. It is a block diagram which shows the speed change operation apparatus which carries out speed change operation of the speed change transmission apparatus provided with the 1st another implementation structure. It is a vertical front view which shows the speed change transmission apparatus provided with the 2nd another implementation structure. It is a vertical front view which shows the speed change transmission apparatus provided with the 3rd another implementation structure. It is a vertical front view which shows the transmission gear mechanism provided with the 4th another implementation structure. It is a vertical front view which shows the transmission gear mechanism provided with the 5th another implementation structure. It is a vertical front view which shows the speed change transmission apparatus provided with the 6th another implementation structure.

Hereinafter, based on the drawings, a description will be given of a case in which a transmission according to the present invention is installed in a combine.
As shown in FIG. 1, a combine is configured to be self-propelled by a pair of left and right crawler type traveling devices 1, 1, and is equipped with a riding type driving unit 2, and a body frame of the traveling body 3, a cutting part 4 connected to the front part of the machine frame 3, a threshing device 5 provided behind the cutting part 4 on the rear side of the machine body frame 3, And a grain tank 6 arranged and provided on the side, and harvesting rice, wheat and the like.

  That is, the cutting unit 4 includes a cutting unit frame 4a that extends from the front portion of the body frame 3 so as to be able to swing up and down in the forward direction. The weeding tool 4b provided at the front end of the mowing unit 4 moves up and down to a lowering work position where the weeding tool 4b is lowered near the ground, and a rising non-working position where the weeding tool 4b is raised from the ground. When the mowing unit 4 is lowered to the lowering work position and the traveling machine body is run, the mowing unit 4 causes the planted culm to be harvested by the weeding tool 4b to be introduced into the path, and the planting that has been induced and introduced into the path. While raising the standing cereal and raising it by the device 4c, it is cut by the clipper type reaping device 4d, and the chopped cereal is supplied to the threshing device 5 by the supply device 4e. The threshing device 5 sandwiches the stock side of the harvested cereal meal from the supply device 4e by the threshing feed chain 5a and conveys it toward the rear of the machine body, and supplies the tip side of the harvested cereal meal to the handling room (not shown). The threshing process is performed, and the threshing grain is fed into the grain tank 6.

  The engine 8 is provided below the driver seat 2 a provided in the driving unit 2, and the driving force output from the engine 8 is driven by a pair of left and right traveling by the transmission structure 10 including the transmission case 11 provided at the front end of the body frame 3. It is configured to transmit to the devices 1 and 1.

  FIG. 2 is a front view showing a schematic structure of the transmission structure 10. As shown in this figure, the transmission structure 10 is provided with the engine driving force from the output shaft 8a of the engine 8 on the lateral side of the upper end portion of the transmission case 11 via the transmission mechanism 12 provided with the transmission belt 12a. Input to the transmission transmission device 20 and the output of the transmission transmission device 20 is input to the traveling mission 13 housed in the mission case 11 to the left of the pair of left and right steering clutch mechanisms 14, 14 provided in the traveling mission 13. The power is transmitted from the steering clutch mechanism 14 to the drive shaft 1a of the left traveling device 1, and is transmitted from the right steering clutch mechanism 14 to the drive shaft 1a of the right traveling device 1.

  The transmission structure 10 includes a cutting mission 15 incorporated in the mission case 11, and the output of the transmission 20 is input to the cutting mission 15 and transmitted from the cutting output shaft 16 to the drive shaft 4 f of the cutting unit 4.

The transmission 20 will be described.
As shown in FIGS. 3 and 4, the transmission 20 is connected to the planetary transmission unit 20 </ b> A including a transmission case 21 having a lateral side connected to the upper end side of the transmission case 11, and to the transmission case 11 of the transmission case 21. And a hydraulic continuously variable transmission 30 having a casing 31 connected to the lateral side opposite to the side to be operated.

  The transmission case 21 houses a main case portion 21a that accommodates the planetary transmission unit 40 and the transmission mechanism 50, a coupling portion between the input shaft 22, the transmission shaft 23, and the hydraulic continuously variable transmission 30, and the transmission case 21 and the casing. The connection case part 21b which connects the 31 port blocks 34 is provided. The transmission case 21 is connected to the transmission case 11 at a bulging portion 21c that is bulged outwardly on the lateral side of the lower side surface where the output rotating body 24 of the main case portion 21a is located. The size of the connecting case portion 21b in the vertical direction of the traveling machine body is smaller than the size of the main case portion 21a in the vertical direction of the traveling machine body. The main case portion 21a is formed so that the longitudinal cross-sectional shape when viewed in the longitudinal direction of the fuselage is a longitudinally long shape, and the casing 31 is formed such that the longitudinal sectional shape when viewed in the longitudinal direction of the aircraft is longitudinally elongated. While the portion 20A and the hydraulic continuously variable transmission 30 are arranged in the lateral direction of the vehicle body, the lateral width of the vehicle body as a whole of the transmission transmission device 20 becomes small, and the transmission transmission device 20 does not protrude laterally outward so The direction is connected to the lateral side of the mission case 11 in a compact state. Further, the lower side surface of the casing 31 is formed with an inclined surface 31A inclined toward the inner side of the machine body at the lower end side, and a bulging portion 31B for supporting the bearing of the motor shaft 33a is formed on the inclined surface 31A. Is being made more compact. In addition, an oil filter 20F is disposed on the upper surface of the casing 31 so as to avoid protrusion of the oil filter 20F to the lateral outer side, thereby achieving further compactness.

  The planetary transmission unit 20A includes a laterally-facing input shaft 22 that is rotatably supported on the upper end side of the transmission case 21, and a transmission that is rotatably supported in parallel or substantially parallel to the input shaft 22 on the lower end side of the transmission case 21. A shaft 23 and a rotary shaft type output rotor 24; a planetary transmission unit 40 supported by the transmission shaft 23; and a transmission mechanism 50 provided across the input shaft 22 and the carrier 41 of the planetary transmission unit 40. Yes.

  The input shaft 22 is arranged so as to be aligned coaxially with the pump shaft 32 a of the hydraulic continuously variable transmission 30. The input shaft 22 is configured to be coupled to the output shaft 8a of the engine 8 via the transmission mechanism 12 on the side projecting laterally outward from the transmission case 21, and the joint on the opposite side to the side coupled to the engine 8 The hydraulic continuously variable transmission 30a is connected to the pump shaft 32a of the hydraulic continuously variable transmission 30 so as to be freely rotatable. The engine driving force is input via the transmission mechanism 12, and the hydraulic continuously variable transmission is driven by the engine driving force. The hydraulic pump 32 of the machine 30 is driven.

  The output rotating body 24 is arranged on the same side as the side where the engine connection side of the input shaft 22 is located with respect to the hydraulic continuously variable transmission 30 so as to be aligned coaxially with the motor shaft 33a of the hydraulic continuously variable transmission 30. Has been. The output rotator 24 is configured to be interlocked with the input portion of the traveling mission 11 on the side projecting laterally outward from the speed change case 21, and receives the driving force from the planetary transmission portion 40 and the hydraulic continuously variable transmission 30. Output to the pair of left and right traveling devices 1, 1 via the traveling mission 13.

  The hydraulic continuously variable transmission 30 includes a hydraulic pump 32 in which a pump shaft 32a is rotatably supported on an upper end side of a casing 31, and a hydraulic motor in which a motor shaft 33a is rotatably supported on a lower end side of the casing 31. 33. The hydraulic pump 32 is constituted by a variable displacement axial plunger pump, and the hydraulic motor 33 is constituted by an axial plunger motor. The hydraulic motor 33 is driven by pressure oil that is discharged by the hydraulic pump 32 and supplied through an oil passage formed inside the port block 34. The hydraulic continuously variable transmission 30 is supplied with supplementary hydraulic fluid by a charge pump 90 provided at the end of the pump shaft 32a. The charge pump 90 includes a rotor 90a that is attached to the pump shaft 32a so as to be integrally rotatable, and a pump casing 90b that is detachably connected to the casing 31.

  Therefore, the hydraulic continuously variable transmission 30 is switched to the forward transmission state, the reverse transmission state, and the neutral state by performing an angle changing operation of the swash plate 32b included in the hydraulic pump 32. When the hydraulic continuously variable transmission 30 is operated to switch to the forward transmission state, the engine driving force transmitted from the input shaft 22 to the pump shaft 32a is converted into the forward driving force and output from the motor shaft 33a for reverse transmission. When the operation is switched to the state, the engine driving force transmitted from the input shaft 22 to the pump shaft 32a is converted into the reverse driving force and output from the motor shaft 33a, and the engine is driven in both the forward transmission state and the reverse transmission state. The driving force is steplessly shifted and output. When the hydraulic continuously variable transmission 30 is switched to the neutral state, the output from the motor shaft 33a is stopped.

  The planetary transmission unit 40 is disposed on the same side as the side where the engine connection side of the input shaft 22 is positioned with respect to the hydraulic continuously variable transmission 30 and is positioned between the motor shaft 33 a and the output rotating body 24. . The planetary transmission unit 40 is configured to freely rotate a sun gear 42 supported by the transmission shaft 23, a plurality of planetary gears 43 that mesh with the sun gear 42, a ring gear 44 that meshes with each planetary gear 43, and a plurality of planetary gears 43. And a carrier 41 to be supported. The carrier 41 includes an arm portion 41a that rotatably supports the planetary gear 43 at the extended end portion, and a cylindrical shaft portion 41b to which the base end sides of the plurality of arm portions 41a are connected. The transmission shaft 23 is rotatably supported via a bearing.

  The transmission shaft 23 and the motor shaft 33a are connected so as to be integrally rotatable via a joint 23a, and the transmission shaft 23 and the sun gear 42 are connected so as to be integrally rotatable via a spline structure. The shaft 33a is interlocked with the shaft 33a so as to be integrally rotatable.

  The ring gear 44 and the output rotating body 24 are integrally rotatable by an annular planetary interlocking body 26 and an annular output side interlocking body 27 that are externally fitted to the transmission shaft 23 so as to be relatively rotatable side by side in the axial direction. It is linked to. That is, the planetary interlocking body 26 includes a plurality of engagement arm portions 26 a that extend radially and integrally from the outer peripheral portion of the planetary interlocking body 26. The plurality of engagement arm portions 26 a are engaged with a plurality of locations of the ring gear 44, and the planetary interlocking body 26 is interlocked with the ring gear 44 so as to be integrally rotatable. The output-side interlocking body 27 is engaged with the planetary-side interlocking body 26 so as to be integrally rotatable with an engaging claw 27a, and is integrally engaged with the output rotating body 24 with a spline structure. The interlocking body 26 and the output rotating body 24 are connected so as to be rotatable together. The planetary interlocking body 26 is supported on the transmission shaft 23 through a bearing so as to be relatively rotatable. The output side interlocking body 27 is rotatably supported by the transmission case 21 via a bearing.

  The transmission mechanism 50 is a transmission gear 52 that is supported on the input shaft 22 through a needle bearing so as to be relatively rotatable while meshing with an input gear 41c of the carrier 41 that is provided rotatably on the cylindrical shaft portion 41b of the carrier 41. And an input side clutch mechanism 55 provided across the transmission gear 52 and the input shaft 22.

  The input-side clutch mechanism 55 includes a clutch body 56 that is supported on the input shaft 22 so as to be integrally rotatable and slidable, and a clutch mechanism main body provided across one end side of the clutch body 56 and the lateral side portion of the transmission gear 52. 57. The clutch body 56 is slid and operated by a hydraulic piston 58 fitted in the end of the clutch body 56. The clutch mechanism main body 57 is configured as a meshing clutch so that the engagement claw provided on the clutch body 56 and the engagement claw provided on the transmission gear 52 are engaged and disengaged to switch between the on state and the off state. .

  The input-side clutch mechanism 50 is switched to the input state so that the input shaft 22 and the transmission gear 52 are interlocked so as to be integrally rotatable when the clutch mechanism main body 57 is switched to the engaged state. The carrier 41 is switched to the interlocked state with respect to the input shaft 22.

  The input-side clutch mechanism 50 is switched to the disconnected state so that the input shaft 22 and the transmission gear 52 are disengaged when the clutch mechanism main body 57 is switched to the disconnected state, and the carrier 41 of the planetary transmission unit 40 is moved. Switch to the interlocking cut-off state for the input shaft 22.

  Therefore, the planetary transmission unit 40 is switched from the portion located between the engine connecting side and the continuously variable transmission connecting side of the input shaft 22 by switching the input side clutch mechanism 50 to the on state. A driving force is input to the carrier 41 via the transmission mechanism 50. The planetary transmission unit 40 is disconnected from the input shaft 22 when the input side clutch mechanism 50 is switched to the disengaged state.

  An output side clutch mechanism 60 having a clutch body 61 fitted on the transmission shaft 23 is provided across the sun gear 42 of the planetary transmission unit 40 and the planetary side interlocking body 26.

  The clutch body 61 is slidably operated toward the sun gear 42 against the energizing spring 62 when pressure oil is supplied to an oil chamber formed on the inner peripheral side of the clutch body 61, so that the clutch body 61 is in the cut position. When the pressure oil is discharged from the oil chamber, the urging spring 62 is slid toward the planetary interlocking body 26 to switch to the entry position. When the clutch body 61 is switched to the entering position, the clutch pawl 61 a provided on the clutch body 61 and the clutch pawl provided on the planetary interlocking body 26 are engaged with each other, so that the clutch body 61 is integrated with the planetary interlocking body 26. Connect freely. The clutch body 61 is slid while maintaining a state in which the clutch body 61 is engaged with the sun gear 42 by the engaging claws 61b so as to be integrally rotatable. When the clutch body 61 is switched to the disengagement position, the clutch pawl 61a is disengaged from the planetary interlocking body 26.

  Therefore, the output-side clutch mechanism 60 disconnects the sun gear 42 and the planetary-side interlocking body 26 from being interlocked by switching the clutch body 61 to the disengagement position, thereby disconnecting the motor shaft 33a from the output rotating body 24. In this state, the first transmission state in which the ring gear 44 of the planetary transmission unit 40 and the output rotator 24 are interlocked so as to be integrally rotatable appears, and the combined driving force of the planetary transmission unit 40 can be output from the output rotator 24. To do.

  The output side clutch mechanism 60 rotates the motor shaft 33a integrally with the output rotating body 24 by interlocking the sun gear 42 and the planetary side interlocking body 26 so that the clutch body 61 is switched to the entering position. The second transmission state to be freely interlocked appears, the output of the output by the hydraulic continuously variable transmission 30 can be output from the output rotating body 24, and the sun gear 42 and the transmission shaft 23 are interlocked so as to be integrally rotatable. And the planetary-side interlocking body 26 are interlocked so as to be rotatable together, so that the sun gear 42, the planetary gear 43, and the ring gear 44 can rotate together with the motor shaft 33a so that the planetary gear 43 does not rotate. To do.

  The output-side clutch mechanism 60 keeps the ring gear 44 of the planetary transmission unit 40 and the output rotating body 24 in an interlocked state, while the sun gear 43 and the output rotating body 24 of the planetary transmission unit 40 are in an interlocked on state and an interlocked off state. Switch.

  Therefore, in the planetary transmission unit 40, the input side clutch mechanism 55 is switched to the on state and the output side clutch mechanism 60 is switched to the off state, so that the driving force of the input shaft 22 is transmitted via the transmission mechanism 50. Input to the carrier 41, the output from the motor shaft 33a of the hydraulic continuously variable transmission 30 is input to the sun gear 42 via the transmission shaft 23, and the driving force of the input shaft 22 and the output of the hydraulic continuously variable transmission 30 are combined. Then, a combined driving force is generated, and the generated combined driving force is output from the ring gear 44 to the output rotating body 24 via the planetary side interlocking body 26 and the output side interlocking body 27.

  An input side clutch mechanism 55 and an output side clutch mechanism 60 are provided to constitute a transmission switching clutch mechanism 70. The transmission switching clutch mechanism 70 is switched between the single transmission state and the combined transmission state when the input side clutch mechanism 55 and the output side crack mechanism 60 are switched.

  FIG. 5 is an explanatory diagram showing the relationship between the operation state of the input side clutch mechanism 55 and the output side clutch mechanism 60, the operation state of the transmission switching clutch mechanism 70, and the transmission mode of the speed change transmission device 20. “OFF” shown in FIG. 5 indicates the disengaged state of the input side clutch mechanism 55 and the output side clutch mechanism 60, and “ON” indicates the engaged state of the input side clutch mechanism 55 and the output side clutch mechanism 60. As shown in this figure, the transmission switching clutch mechanism 70 is switched to the single transmission state when the input side clutch mechanism 55 is switched to the disengaged state and the output side clutch mechanism 60 is switched to the on state. When the side clutch mechanism 55 is switched to the engaged state and the output side clutch mechanism 60 is switched to the disconnected state, the combined transmission state is switched.

  FIG. 3 is a longitudinal front view showing the transmission 20 in HMT mode transmission. As shown in this figure, when the transmission switching clutch mechanism 70 is switched to the combined transmission state, the driving force of the input shaft 22 and the output of the hydraulic continuously variable transmission 30 are combined by the planetary transmission unit 40, and the planetary transmission is performed. HMT mode transmission in which the combined driving force by the unit 40 is transmitted to the output rotator 24 is caused to appear on the transmission 20. When in the HMT mode transmission state, the transmission 20 shifts the engine driving force input to the input shaft 22 by both the hydraulic continuously variable transmission 30 and the planetary transmission unit 40, and transmits the driving force after the shift to the ring gear. 44 from the output rotator 24 to the pair of left and right traveling devices 1, 1.

  FIG. 4 is a longitudinal front view showing the transmission 20 in the HST mode transmission. As shown in this figure, when the transmission switching clutch mechanism 70 switches to the single transmission state, the output of the hydraulic continuously variable transmission 30 is not transmitted to the planetary transmission unit 40 alone and is transmitted to the output rotating body 24 alone. The HST mode transmission to be performed is made to appear on the transmission 20. When in the HST mode transmission state, the transmission 20 is not shifted by the planetary transmission unit 40 of the hydraulic continuously variable transmission 30 and the planetary transmission unit 40, and the hydraulic continuously variable transmission 30, the driving force after the shift is transmitted from the motor shaft 33a to the output rotating body 24 via the transmission shaft 23, the sun gear 42, the clutch body 61, the planetary side interlocking body 26 and the output side interlocking body 27, This is transmitted from the output rotating body 24 to the pair of left and right traveling devices 1 and 1.

  The transmission switching clutch mechanism 70 is in a state where transmission from the input shaft 22 to the carrier 41 of the planetary transmission unit 40 is cut off when the transmission 20 is operated in the HST mode transmission state, and the sun gear 42 is in the transmission shaft 23. The ring gear 44 is linked to the motor shaft 33a via the planetary side linkage body 26, the clutch body 61, the sun gear 42 and the transmission shaft 23 so as to be integrally rotatable. Therefore, the sun gear 42, the planetary gear 43 and the ring gear 44 of the planetary transmission unit 40 are operated so as to rotate integrally with the motor shaft 33a, and the transmission 20 is in a state in which the HST mode transmission appears. The planetary gear 43 does not rotate, that is, the relative rotation of the sun gear 42 and the planetary gear 43 and the planetary gear 43 and the Without causing relative rotation of the gear 44, for transmitting the output of the motor shaft 33a of the hydraulic continuously variable transmission 30 to the output rotor 24.

  FIG. 6 shows the state of the shift of the hydraulic continuously variable transmission 30 and the output speed of the output rotating body 24 of the transmission transmission 20 in a state where the engine 8 is accelerator-set so as to output a driving force at a set constant speed. It is explanatory drawing which shows a relationship. The horizontal axis in FIG. 6 indicates the shift state of the hydraulic continuously variable transmission 30, “n” indicates the neutral position of the hydraulic continuously variable transmission 30, and “−max” indicates the hydraulic continuously variable transmission. 30 indicates the highest speed position in the reverse transmission state, and “+ max” indicates the highest speed position in the forward transmission state of the hydraulic continuously variable transmission 30. The vertical axis in FIG. 6 indicates the output speed by the output rotating body 24. The solid line R and the solid line FL shown in FIG. 6 are operated when the input side clutch mechanism 55 is operated in the disengaged state and the output side clutch mechanism 60 is operated in the on state, that is, the transmission transmission 20 is operated in the HST mode transmission state. The change of the output speed in a case is shown. A solid line FH shown in FIG. 6 indicates an output when the input side clutch mechanism 55 is operated in the engaged state and the output side clutch mechanism 60 is operated in the disengaged state, that is, when the transmission transmission 20 is operated in the HMT mode transmission state. Indicates the change in speed.

  As indicated by the solid line R and the solid line FL, when the input side clutch mechanism 55 is maintained in the disengaged state and the output side clutch mechanism 60 is maintained in the on state, the hydraulic continuously variable transmission 30 is in the most reverse transmission state. When the high speed position “−max” is operated, the output speed becomes the reverse maximum speed “RVH”. As the hydraulic continuously variable transmission 30 is shifted from the highest speed position “−max” in the reverse transmission state toward the neutral position “n”, the reverse output speed is continuously reduced. When the hydraulic continuously variable transmission 30 reaches the neutral position “n”, the output speed becomes zero “0”. As the hydraulic continuously variable transmission 30 is shifted from the neutral position “n” toward the highest speed position “+ max” in the forward transmission state, the forward output speed increases steplessly. When the hydraulic continuously variable transmission 30 reaches the maximum speed position “+ max” in the forward transmission state, the output speed becomes the forward intermediate speed “FVM”.

  As indicated by the solid line FH, when the hydraulic continuously variable transmission 30 reaches the maximum speed position “+ max” in the forward transmission state, the input side clutch mechanism 55 is controlled to be switched from the disengaged state to the on state, and the output side clutch mechanism 60 is controlled. Is switched from the on state to the off state, the input side clutch mechanism 55 is maintained in the on state, and the output side clutch mechanism 60 is maintained in the disengaged state, the hydraulic continuously variable transmission 30 is in the forward transmission state. As a speed change operation is performed from the highest speed position “+ max” to the highest speed position “−max” in the reverse transmission state, the forward output speed increases steplessly. When the hydraulic continuously variable transmission 30 reaches the maximum speed position “+ max” in the reverse transmission state, the forward output speed becomes the maximum speed “FVH”.

  “N” shown in FIG. 6 indicates the horizontal axis when the solid line FH is extended beyond the maximum speed position “+ max” on the forward side of the hydraulic continuously variable transmission 30 to a point where the output rotation becomes zero “0”. Indicates the value. When the value of the horizontal axis of the maximum speed position “+ max” on the forward side of the hydraulic continuously variable transmission 30 is 1, N = 1.6 to 2.2. That is, the capacities of the hydraulic pump 32 and the hydraulic motor 33 in the hydraulic continuously variable transmission 30 and the transmission gear ratio of the planetary transmission unit 40 are set so that N = 1.6 to 2.2.

  FIG. 7 is a block diagram showing a speed change operation device 71 that changes the speed of the speed change transmission device 20. As shown in this figure, the speed change operation device 71 is a control device 72 linked to the speed change operation portion 30a of the hydraulic continuously variable transmission 30, the input side clutch mechanism 55, and the operation portions 55a and 60a of the output side clutch mechanism 60. And a shift detection sensor 73, an engine speed sensor 74, a transmission output speed sensor 75, and an output speed sensor 76 linked to the control device 72.

  The shift operation unit 30a is configured by an electric actuator or a hydraulic actuator that performs an angle changing operation of the swash plate 32b of the hydraulic pump 32 in the hydraulic continuously variable transmission 30. The operation portion 55a of the input side clutch mechanism 55 is constituted by an operation valve connected to the hydraulic piston 58 via an operation oil passage formed inside the input shaft 22, and the clutch body is operated by operating the hydraulic piston 58. By sliding operation 56, the input side clutch mechanism 55 is switched. The operation portion 60 a of the output side clutch mechanism 60 is configured by an operation valve connected to the oil chamber of the clutch body 61 via an operation oil passage formed inside the transmission shaft 23. By supplying and discharging the operating oil, the clutch body 61 is slid and the output side clutch mechanism 60 is switched.

  The shift detection sensor 73 detects the operation position of the shift lever 77 and outputs the detection result to the control device 72. The engine speed sensor 74 detects the speed of the engine 8 and outputs the detection result to the control device 72. The transmission output rotation speed sensor 75 detects the output rotation speed of the hydraulic continuously variable transmission 30 and outputs the detection result to the control device 72. The output speed sensor 76 detects the output speed of the transmission 20 and outputs the detection result to the controller 72.

  The control device 72 is configured using a microcomputer and includes a shift control means 78. The shift control means 78 is configured so that the shift state of the hydraulic continuously variable transmission 30 corresponds to the operation position of the shift lever 77 based on detection information from the shift detection sensor 73 and the transmission output rotation speed sensor 75. Then, the shift control unit 30a is operated to control the shift of the hydraulic continuously variable transmission 30.

  The shift control means 78 detects the rotational speed of the accelerator-set engine 8 on the basis of information detected by the engine rotational speed sensor 74 in addition to controlling the shift of the hydraulic continuously variable transmission 30, Based on the detection information by the detection sensor 73, the transmission output speed sensor 75, and the output speed sensor 76, as shown in FIGS. 5 and 6, the speed change transmission device 20 appears to transmit the HST mode transmission and the HMT mode transmission. Further, the input side clutch mechanism 55 and the output side clutch mechanism 60 are controlled to be switched at a predetermined timing by operating the operation unit 55a and the operation unit 60a.

[Another implementation structure]
FIG. 8 is a longitudinal front view showing the transmission device 20 having the first different embodiment structure. As shown in this figure, the speed change transmission device 20 provided with the first alternative embodiment includes a forward / reverse switching mechanism 80 provided across the input shaft 22 and the carrier 41 of the planetary transmission unit 40.

  In the transmission 20 having the first alternative structure, the engine connection side of the input shaft 22 and the forward clutch 82 are provided between the engine connection side of the input shaft 22 and the hydraulic continuously variable transmission connection side. The charge pump 90 is provided between the hydraulic continuously variable transmission 30 and the hydraulic pump continuously supplied to the hydraulic continuously variable transmission 30. The charge pump 90 includes a rotor 90 a that is connected to the input shaft 22 so as to be integrally rotatable, and a pump casing 90 b that is detachably attached to the transmission case 21.

  The forward / reverse switching mechanism 80 includes a forward transmission gear 81 rotatably supported on the input shaft 22 via a needle bearing, a forward clutch 82 provided across the forward transmission gear 81 and the input shaft 22, and the input shaft 22. Relative rotation to the reverse transmission shaft 83 in mesh with a reverse transmission shaft 83 that is rotatably supported by the transmission case 21 in a parallel or substantially parallel arrangement, and a transmission gear 84 that is rotatably supported integrally with the input shaft 22. A reverse input gear 85 supported, a reverse clutch 86 provided across the input gear 85 and the reverse transmission shaft 83, and a reverse transmission gear 87 provided on the reverse transmission shaft 83 so as to be integrally rotatable are configured. It is.

  The forward transmission gear 81 and the reverse transmission gear 87 are meshed with an input gear 41 c of the carrier 41 that is rotatably provided integrally with the cylindrical shaft portion 41 b of the carrier 41. The input gear 85 and the transmission gear 84 are located on the opposite side of the planetary transmission unit 40 from the side where the forward transmission gear 81 and the reverse transmission gear 87 are located. The forward transmission gear 81 and the reverse transmission gear 87 mesh with the input gear 41c of the planetary transmission unit 40 located on the opposite side of the sun gear 42 from the side where the input gear 85 and the transmission gear 84 are located.

  The forward clutch 82 is a clutch mechanism provided across the forward clutch body 82a supported on the input shaft 22 so as to be integrally rotatable and slidable, and one end side of the forward clutch body 82a and the lateral side portion of the forward transmission gear 81. And a main body 82b. The forward clutch body 82a is slidably operated by a hydraulic piston 88 fitted in the end of the forward clutch body 82a. The clutch mechanism main body 82b is configured as a mesh clutch so that the engagement claw provided on the forward clutch body 82a and the mesh claw provided on the forward transmission gear 81 are engaged and disengaged to switch between the on state and the off state. It is.

  The reverse clutch 86 includes a reverse clutch body 86 a that is supported by the reverse transmission shaft 83 so as to be integrally rotatable and slidable, and a clutch mechanism that is provided across one end side of the reverse clutch body 86 a and the lateral side portion of the input gear 85. And a main body 86b. The reverse clutch body 86a is slidably operated by a hydraulic piston 89 fitted in the end portion of the reverse clutch body 86a. The clutch mechanism main body 86b is configured as a meshing clutch so that the engagement claw provided on the reverse clutch body 86a and the engagement claw provided on the input gear 85 are engaged and disengaged to switch between the on state and the off state. is there.

  The forward / reverse switching mechanism 80 is in a forward transmission state when the forward clutch 82 is switched to the engaged state and the reverse clutch 86 is switched to the disengaged state, and is connected to the engine connection side of the input shaft 22 and a hydraulic stepless. The driving force of the input shaft 22 is input from the forward clutch body 82a located between the transmission connecting side, the driving force of the input shaft 22 is converted into the forward driving force, and transmitted from the forward transmission gear 81 to the carrier 41.

  The forward / reverse switching mechanism 80 is switched to the disengaged state of the forward clutch 82 and is switched to the engaged state of the reverse clutch 86 to be in the reverse transmission state. The drive force of the input shaft 22 is input from the transmission gear 84 located between the transmission connecting side, the drive force of the input shaft 22 is converted into the reverse drive force, and the carrier 41 of the planetary transmission unit 40 is converted from the reverse drive gear 87. To communicate.

  The forward / reverse switching mechanism 80 is in a neutral state when the forward clutch 82 and the reverse clutch 86 are switched to a disengaged state, and the input shaft 22 and the carrier 41 of the planetary transmission unit 40 are disconnected from each other.

  FIG. 9 is an explanatory diagram showing the relationship between the operation state of the hydraulic continuously variable transmission 30, the forward clutch 82, the reverse clutch 86, and the output-side clutch mechanism 60 and the transmission mode of the transmission 20. “Forward” shown in FIG. 9 indicates the forward transmission state of the hydraulic continuously variable transmission 30, and “reverse” indicates the reverse transmission state of the hydraulic continuously variable transmission 30. “OFF” shown in FIG. 9 indicates the disengagement state of the forward clutch 82, the reverse clutch 86 and the output-side clutch mechanism 60, and “ON” indicates the engagement of the forward clutch 82, the reverse clutch 86 and the output-side clutch mechanism 60. Indicates the state.

  When the forward clutch 82 and the reverse clutch 86 are switched to the disengaged state and the output side clutch mechanism 60 is switched to the on state, the speed change transmission device 20 is brought into a state where the HST mode transmission appears. When the transmission 20 is in the HST mode transmission state, the engine drive force input to the input shaft 22 is not transmitted to the planetary transmission unit 40, and the engine drive force input to the input shaft 22 is hydraulically stepped. The speed is changed by the machine 30, and the driving force after the speed change is transmitted from the motor shaft 33a to the output rotating body 24 through the transmission shaft 23, the sun gear 42, the clutch body 61, the planetary side interlocking body 26 and the output side interlocking body 27 for output. This is transmitted from the rotating body 24 to the pair of left and right traveling devices 1, 1.

  When the forward clutch 82 is controlled to be turned on and the reverse clutch 86 and the output side clutch mechanism 80 are controlled to be turned off, the transmission 20 is brought into a state in which the forward HMT mode transmission appears. . When the forward transmission side HMT mode transmission is established, the transmission device 20 converts the engine driving force input by the input shaft 20 into the forward driving force by the forward / reverse switching mechanism 80 and transmits the forward driving force to the planetary transmission unit 40, thereby transmitting the planetary transmission unit. 40, the forward drive force from the forward / reverse switching mechanism 80 and the output from the motor shaft 33 a of the hydraulic continuously variable transmission 30 are combined to generate the forward drive force, and the forward drive force generated is generated. Is transmitted from the ring gear 44 to the output rotating body 24 via the planetary-side interlocking body 26 and the output-side interlocking body 27 and from the output rotating body 24 to the pair of left and right traveling devices 1, 1.

  When the reverse clutch 86 is controlled to be turned on and the forward clutch 82 and the output side clutch mechanism 60 are controlled to be turned off, the transmission 20 is brought into a state in which the reverse side HMT mode transmission appears. . When the reverse transmission side HMT mode transmission is established, the transmission 20 is converted into a reverse drive force by the forward / reverse switching mechanism 80 and transmitted to the planetary transmission unit 40 by the forward / reverse switching mechanism 80, and the planetary transmission unit. 40, the reverse drive force from the forward / reverse switching mechanism 80 and the output from the motor shaft 33a of the hydraulic continuously variable transmission 30 are combined to generate the reverse drive force, and the reverse drive force generated is generated. Is transmitted from the ring gear 44 to the output rotating body 24 via the planetary-side interlocking body 26 and the output-side interlocking body 27 and from the output rotating body 24 to the pair of left and right traveling devices 1, 1.

  FIG. 10 is an explanatory view showing the output speed of the transmission 20 having the first alternative structure, and is hydraulic when the engine 8 is accelerator-set so as to output a set driving force at a constant speed. FIG. 4 is an explanatory diagram showing a relationship between a speed change state of a continuously variable transmission 30 and an output speed by an output rotating body 24 of the speed change transmission device 20. The horizontal axis in FIG. 10 indicates the shift state of the hydraulic continuously variable transmission 30, “n” indicates the neutral position of the hydraulic continuously variable transmission 30, and “−max” indicates the hydraulic continuously variable transmission. 30 indicates the highest speed position in the reverse transmission state, and “+ max” indicates the highest speed position in the forward transmission state of the hydraulic continuously variable transmission 30. The vertical axis in FIG. 10 indicates the output speed by the output rotating body 24. The solid line RL and the solid line FL shown in FIG. 10 indicate that the forward clutch 82 and the reverse clutch 86 are controlled to be switched to the disengaged state and the output side clutch mechanism 60 is controlled to be switched to the engaged state, that is, the transmission 20 is set to HST. It shows the change in output speed when operated in the mode transmission mode. Solid lines FM and FH shown in FIG. 10 indicate that the forward clutch 82 is controlled to be switched on and the reverse clutch 86 and the output side clutch mechanism 60 are controlled to be switched off, that is, the transmission 20 is connected to the forward side. The change of the output speed when operated in the state of HMT mode transmission is shown. The solid lines RM and RH shown in FIG. 10 indicate that the reverse clutch 86 is controlled to be turned on and the forward clutch 82 and the output-side clutch mechanism 60 are controlled to be turned off, that is, the transmission 20 is connected to the reverse side. The change of the output speed when operated in the state of HMT mode transmission is shown.

  As shown in FIG. 9 and as indicated by the solid line FL in FIG. 10, in the state where the forward clutch 82 and the reverse clutch 86 are controlled to be disengaged and the output side clutch mechanism 60 is controlled to be in the engaged state, When the continuously variable transmission 30 is operated to the neutral position “n”, the output becomes zero “0”.

  While the forward clutch 82 and the reverse clutch 86 are maintained in the disengaged state and the output-side clutch mechanism 60 is maintained in the engaged state, the hydraulic continuously variable transmission 30 moves from the neutral position “n” to the highest speed position “ When a speed change operation is performed toward “+ max”, the forward drive force is output. While the forward clutch 82 and the reverse clutch 86 are maintained in the disengaged state and the output-side clutch mechanism 60 is maintained in the engaged state, the hydraulic continuously variable transmission 30 moves from the neutral position “n” to the highest speed position “ As the speed change operation is performed toward “+ max”, the forward output increases steplessly. When the hydraulic continuously variable transmission 30 reaches the maximum speed position “+ max” in the forward transmission state, the output speed becomes the forward intermediate speed “FV1”.

  As shown in FIG. 9 and as indicated by solid lines FM and FH in FIG. 10, when the hydraulic continuously variable transmission 30 reaches the maximum speed position “+ max” in the forward transmission state, the forward clutch 82 is switched to the engaged state. The output-side clutch mechanism 60 is controlled to be switched off, the forward clutch 82 is maintained in the engaged state, and the reverse clutch 86 and the output-side clutch mechanism 60 are maintained in the disconnected state, while the hydraulic continuously variable transmission is performed. As the machine 30 is shifted from the highest speed position “+ max” in the forward transmission state toward the highest speed position “−max” in the reverse transmission state, the forward output is increased steplessly from the intermediate speed “FV1”. To do. When the hydraulic continuously variable transmission 30 reaches the maximum speed position “−max” in the reverse transmission state, the output becomes the maximum forward speed “FV2”.

  As shown in FIG. 9 and as indicated by the solid line RL in FIG. 10, the forward clutch 82 and the reverse clutch 86 are maintained in the disengaged state, and the output-side clutch mechanism 60 is maintained in the engaged state. When the transmission 30 is shifted from the neutral position “n” toward the highest speed position “−max” in the reverse transmission state, the reverse drive force is output. While the forward clutch 82 and the reverse clutch 86 are maintained in the disengaged state and the output-side clutch mechanism 60 is maintained in the engaged state, the hydraulic continuously variable transmission 30 moves from the neutral position “n” to the highest speed position “ As the speed change operation is performed toward “−max”, the reverse output increases steplessly. When the hydraulic continuously variable transmission 30 reaches the maximum speed position “−max” in the reverse transmission state, the output speed becomes the reverse intermediate speed “RV1”.

  As shown in FIG. 9 and as indicated by solid lines RM and RH in FIG. 10, when the hydraulic continuously variable transmission 30 reaches the maximum speed position “−max” in the reverse transmission state, the reverse clutch 86 is engaged. The switching is controlled, the output side clutch mechanism 80 is switched to the disengaged state, the reverse clutch 86 is maintained in the engaged state, and the forward clutch 82 and the output side clutch mechanism 60 are maintained in the disengaged state. As the transmission 30 is shifted from the highest speed position “−max” in the reverse transmission state to the highest speed position “+ max” in the forward transmission state, the reverse output increases steplessly from the intermediate speed “RV1”. Speed up. When the hydraulic continuously variable transmission 30 reaches the maximum speed position “+ max” in the forward transmission state, the output becomes the maximum reverse speed “RV2”.

  “N” shown in FIG. 10 indicates the horizontal line when the solid lines FH and FM are extended beyond the maximum speed position “+ max” on the forward side of the hydraulic continuously variable transmission 30 to a point where the output rotation becomes zero “0”. Indicates the axis value. When the value of the horizontal axis of the maximum speed position “+ max” on the forward side of the hydraulic continuously variable transmission 30 is 1, N = 1.6 to 2.2. That is, the capacities of the hydraulic pump 32 and the hydraulic motor 33 in the hydraulic continuously variable transmission 30 and the transmission gear ratio of the planetary transmission unit 40 are set so that N = 1.6 to 2.2.

  FIG. 11 is a block diagram showing a speed change operation device 91 that performs a speed change operation of the speed change transmission device 20 having the first different embodiment structure. As shown in this figure, the speed change operation device 91 is connected to the speed change operation portion 30a of the hydraulic continuously variable transmission 30, and the operation portions 82c, 86c and 60a of the forward clutch 82, the reverse clutch 86 and the output side clutch mechanism 60. A linked control device 72, a shift detection sensor 73 linked to the control device 72, an engine speed sensor 74, a transmission output speed sensor 75, and an output speed sensor 76 are provided.

  The shift operation unit 30a is configured by an electric actuator or a hydraulic actuator that performs an angle changing operation of the swash plate 32b of the hydraulic pump 32 in the hydraulic continuously variable transmission 30. The operation portion 82c of the forward clutch 82 is constituted by an operation valve connected to the hydraulic piston 88 via an operation oil passage formed inside the input shaft 22, and the forward clutch body 82a is operated by operating the hydraulic piston 88. The forward clutch 82 is switched by performing a sliding operation. The operation portion 86c of the reverse clutch 86 is constituted by an operation valve connected to the hydraulic piston 89 via an operation oil passage formed inside the reverse transmission shaft 83. The reverse clutch body is operated by operating the hydraulic piston 89. The reverse clutch 86 is switched by sliding the 86a. The operation portion 60 a of the output-side clutch mechanism 60 is configured by an operation valve connected to the oil chamber of the clutch body 61 via an operation oil passage formed inside the transmission shaft 23. By supplying and discharging the operating oil to and from the chamber, the clutch body 61 is slid and the output side clutch mechanism 60 is switched.

  The shift detection sensor 73 detects the operation position of the shift lever 77 and outputs the detection result to the control device 72. The engine speed sensor 74 detects the speed of the engine 8 and outputs the detection result to the control device 72. The transmission output rotation speed sensor 75 detects the output rotation speed of the hydraulic continuously variable transmission 30 and outputs the detection result to the control device 72. The output speed line 76 detects the output speed of the transmission 20 and outputs the detection result to the controller 72.

  The control device 72 is configured using a microcomputer and includes a shift control means 78. The shift control means 78 is configured so that the shift state of the hydraulic continuously variable transmission 30 corresponds to the operation position of the shift lever 77 based on detection information from the shift detection sensor 73 and the transmission output rotation speed sensor 75. Then, the shift control unit 30a is operated to control the shift of the hydraulic continuously variable transmission 30.

  The shift control means 78 detects the rotational speed of the accelerator-set engine 8 on the basis of information detected by the engine rotational speed sensor 74 in addition to controlling the shift of the hydraulic continuously variable transmission 30, Based on the detection information by the detection sensor 73, the transmission output speed sensor 75, and the output speed sensor 76, the transmission 20 is operated in the HST mode transmission, the forward HMT mode transmission, and the reverse side as shown in FIGS. The operation unit 82c, the operation unit 86c, and the operation unit 60a are operated to switch the forward clutch 82, the reverse clutch 86, and the output-side clutch mechanism 60 at a predetermined timing so that the HMT mode transmission appears.

  FIG. 12 is a longitudinal front view showing the transmission 20 having the second alternative structure. As shown in this figure, in the transmission 20 having the second alternative embodiment structure, the charge pump 90 for supplying hydraulic oil for supplement to the hydraulic continuously variable transmission 30 is connected to the engine coupling side of the input shaft 22. Between the engine connection side of the input shaft 22 and the input side clutch mechanism 55. The charge pump 90 includes a rotor 90 a that is connected to the input shaft 22 so as to be integrally rotatable, and a pump casing 90 b that is detachably connected to the transmission case 21.

  FIG. 13 is a longitudinal front view showing the transmission device 20 having the third alternative embodiment structure. As shown in this figure, in a transmission 20 having a third alternative embodiment structure, a hydraulic continuously variable transmission 30 includes a variable displacement hydraulic pump 32 and a variable displacement hydraulic motor 33. It is.

  FIG. 14 is a longitudinal front view showing the transmission 20 having the fourth alternative structure. As shown in this figure, in the transmission 20 having the fourth alternative structure, the output-side clutch mechanism 60 is provided on the support body 63 and the planetary-side interlocking body 26 that are provided to rotate integrally with the transmission shaft 23. A multi-plate friction clutch portion 64 provided over the clutch body portion is provided to constitute a friction clutch mechanism. In the output side clutch mechanism 60, when the friction clutch portion 64 is switched between the on state and the off state by the hydraulic piston 65 supported by the sun gear 42, the motor shaft 33a and the output rotating body 24 are interlocked with the interlocked on state. Switch to the off state.

  FIG. 15 is a longitudinal sectional front view showing the transmission device 20 having the fifth alternative embodiment structure. As shown in this figure, in the transmission 20 having the fifth alternative embodiment structure, the input side clutch mechanism 55 is integrally rotatable with the input shaft 22 and the support portion provided integrally with the transmission gear 52. A multi-plate type friction clutch portion 59 provided over the provided clutch body portion 59a is provided to constitute a friction type clutch mechanism. In the input side clutch mechanism 55, the friction clutch portion 59 is switched between an on state and a disengaged state by a hydraulic piston 59b built in the clutch body portion 59a, whereby the input shaft 22 and the transmission gear 52 are brought into an interlocked engaged state. Change over to the state where the interlocking is cut off.

  FIG. 16 is a longitudinal front view showing a transmission device 20 having a sixth different embodiment structure. As shown in this figure, in the transmission 20 having the sixth alternative embodiment structure, the output-side clutch mechanism 60 is integrated with the support portion 66 and the output-side interlocking body 27 that are provided so as to be integrally rotatable with the transmission shaft 23. A multi-plate friction clutch portion 67 provided over a rotatable clutch body 67a is provided to constitute a friction clutch mechanism. In the output side clutch mechanism 60, the friction clutch portion 67 is switched between an on state and a disengaged state by a hydraulic piston 67b built in the clutch body 67a, whereby the motor shaft 33a and the output rotating body 24 are brought into an interlocked engaged state. Switch to the linked cut-off state.

  The speed change transmission device 20 having the sixth alternative structure includes a friction clutch mechanism 79 that allows the ring gear 44 and the motor shaft 33a to be switched between an interlocking state and an interlocking disengagement state, and in the HST mode transmission, the sun gear 42 and the planetary gears. 43 and the ring gear 44 can be switched between a state of rotating integrally with the motor shaft 33a and a state of rotating the ring gear 44 in the HST mode transmission.

[Another Example]
(1) In the above embodiment, the driving force of the input shaft 22 is input to the carrier 41 of the planetary transmission unit 40, and the driving force of the ring gear 44 of the planetary transmission unit 40 is transmitted to the output rotating body 24. Although shown, the driving force of the input shaft 22 may be input to the ring gear 44 of the planetary transmission unit 40 and the driving force of the carrier 41 of the planetary transmission unit 40 may be transmitted to the output rotor 24.

(2) In the above-described embodiment, the input shaft 22 is formed separately from the pump shaft 32a and connected to the pump shaft 32a via the joint 22a, and the transmission shaft 23 is formed separately from the motor shaft 33a. Although an example in which the shaft 33a is connected via the joint 23a is shown, the input shaft 22 may be integrally formed with the pump shaft 32a, and the transmission shaft 23 may be integrally formed with the motor shaft 33a.

  The present invention can be used for various vehicles such as a rice transplanter and a transporter in addition to a combine.

DESCRIPTION OF SYMBOLS 1 Traveling device 22 Input shaft 24 Output rotary body 30 Hydraulic continuously variable transmission 32a Pump shaft 33a Motor shaft 40 Planetary transmission part 42 Sun gear 55 Input side clutch mechanism 60 Output side clutch mechanism 90 Charge pump

Claims (5)

An input shaft for inputting engine driving force, a hydraulic continuously variable transmission driven by the input shaft, and a combined driving force by combining the driving force of the input shaft and the output of the hydraulic continuously variable transmission. A transmission transmission device provided with an output planetary transmission section and an output rotating body output to the traveling device,
The planetary transmission unit and the output rotating body are disposed on the same side as the side where the engine connection side of the input shaft is located with respect to the hydraulic continuously variable transmission, and the engine connection side of the input shaft is not hydraulically connected. A transmission device configured to input a driving force to the planetary transmission unit from a portion between the step transmission and the transmission side. The input shaft is connected to the pump shaft so as to be integrally rotatable with the pump shaft of the hydraulic continuously variable transmission arranged coaxially.
2. The sun gear of the planetary transmission unit and the output rotating body are rotatably supported around a rotation shaft centered coaxially with respect to a motor shaft core of the hydraulic continuously variable transmission. Variable speed transmission.   An input-side clutch mechanism is provided for switching the planetary transmission portion between the interlocked state and the interlocked state with respect to the input shaft, and the output rotating body is switched between the interlocked state and the interlockingly disconnected state with respect to the motor shaft of the hydraulic continuously variable transmission. The transmission according to claim 1 or 2, wherein an output side clutch mechanism is provided.   The charge pump for supplying hydraulic oil to the hydraulic continuously variable transmission is provided between the engine connecting side and the hydraulic continuously variable transmission connecting side of the input shaft. A transmission gear according to claim 1.   4. The transmission according to claim 3, wherein a charge pump for supplying hydraulic oil to the hydraulic continuously variable transmission is provided between the engine coupling side of the input shaft and the input side clutch mechanism.

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