JP2012149769A - Variable speed transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a compact variable speed transmission that outputs power with continuously variable speed over a wide shift range only through a simple shift operation.SOLUTION: The variable speed transmission includes a first output gear 81 and other output gears 82, 83, and 84 which are different from the first output gear 81 as an output gear for outputting a synthetic driving force from a planetary transmission part P concentrically with sun gears 62 and 72 of planetary transmission mechanisms 60 and 70. Two transmission shafts 95 and 96 are provided for transmitting the synthetic driving force from the planetary transmission part P to an output rotary body 30 by switching the output gear for outputting the synthetic driving force and converting it into a driving force of multiple speed ranges by switching a plurality of speed range setting clutches 101, 102, 103, and 104. The transmission gear 109 to be engaged with the output gears 107b and 108b provided in the two transmission shafts 95 and 96 is provided integrally with output rotary bodies 30. The two transmission shafts 95 and 96 are arranged side by side in parallel.

Description

  The present invention includes a continuously variable transmission unit or an electric motor to which an engine driving force is input, and outputs an output of the continuously variable transmission unit and an engine driving force not subjected to a shifting action by the continuously variable transmission unit, or the electric motor. The planetary transmission unit that combines the output of the engine and the engine driving force by a plurality of planetary transmission mechanisms, the combined driving force from the planetary transmission unit is divided into a plurality of speed ranges, The present invention relates to a speed change transmission device configured to change continuously and output from an output rotating body.

The above-described shift transmission device performs a shift operation of the continuously variable transmission unit or the electric motor, thereby combining the driving force of the engine output and the output of the continuously variable transmission unit, or the combination of the engine output and the output of the electric motor. The driving force is divided into multiple speed ranges, and the driving force that is steplessly shifted in each speed range is output. If used for driving the traveling device, the shifting can be performed smoothly and the shifting operation can be performed easily. It can be transmitted.
As this type of transmission, a device described in Patent Document 1 was first developed.
Patent Document 1 describes three types of transmission gears. In one of the three types of transmission gears (the one described in FIG. 2 of Patent Document 1), a continuously variable transmission (corresponding to a continuously variable transmission unit), a planetary transmission unit, a clutch unit, and a third planetary transmission mechanism And a brake acting on the third planetary transmission mechanism.

  The continuously variable transmission includes a variable displacement hydraulic pump whose pump shaft is linked to an output shaft of an engine via a main clutch, and a hydraulic motor driven by pressure oil from the hydraulic pump.

  The planetary transmission unit includes a first planetary transmission mechanism and a second planetary transmission mechanism. The planetary gear of the first planetary transmission mechanism and the planetary gear of the second planetary transmission mechanism are interlocked by meshing of interlocking gear portions provided in each planetary gear. The planetary gear of the first planetary transmission mechanism and the planetary gear of the second planetary transmission mechanism are supported by a carrier common to the first planetary transmission mechanism and the second planetary transmission mechanism.

  The clutch unit includes a first clutch, a second clutch, a third clutch, and a fourth clutch. The input side rotation member of the first clutch is interlocked with the ring gear of the second planetary transmission mechanism via the interlock mechanism. The input side rotation member of the second clutch is interlocked with the sun gear of the second planetary transmission mechanism via the rotation shaft. The input side rotating member of the third clutch is interlocked with the carrier of the planetary transmission unit via an interlocking mechanism.

  The interlocking mechanism that interlocks the input-side rotating member of the first clutch and the ring gear of the second planetary transmission mechanism includes a clutch-side transmission gear that meshes with the input-side rotating member of the first clutch, and the second planetary transmission mechanism. A planetary transmission gear meshed with a ring gear; and a rotary shaft connected to the clutch transmission gear and the planetary transmission gear. The interlocking mechanism that interlocks the input side rotation member of the third clutch and the carrier of the planetary transmission unit includes a clutch side transmission gear that meshes with the input side rotation member of the third clutch, and a planetary side transmission that meshes with the carrier. A gear, and a rotary shaft connected to the clutch side transmission gear and the planetary side transmission gear.

  The sun gear of the third planetary transmission mechanism is interlocked with the output side rotation member of the first clutch and the second clutch and the input side rotation member of the third clutch. The carrier of the third planetary transmission mechanism is interlocked with output side rotating members of the third clutch and the fourth clutch.

  The brake can be switched between an on state where the braking action is applied to the ring gear of the third planetary transmission mechanism and a cut state where the braking action on the ring gear is released.

  2, the output of the continuously variable transmission and the driving force of the pump shaft of the continuously variable transmission (the engine driving force that is not subjected to the shifting action by the continuously variable transmission) are provided. Synthesized by planetary transmission unit. Synthetic drive output from the planetary transmission unit when the continuously variable transmission is operated for shifting, and the first to fourth clutches and the brake are appropriately switched between the engaged state and the disengaged state in conjunction with the shifting operation. The force is stepped from the first speed range to the fourth speed range and continuously variable in each speed range, and output from the carrier shaft of the third planetary transmission mechanism.

  Another one of the three types of transmission gears described in Patent Document 1 (described in FIG. 12 of Patent Document 1) and another one (described in FIG. 16 of Patent Document 1) In the present invention, a continuously variable transmission (corresponding to a continuously variable transmission), a planetary transmission unit, a clutch unit, and an auxiliary transmission are provided.

  The continuously variable transmission and the planetary transmission unit have the same configuration as the continuously variable transmission and planetary transmission unit of the transmission described in FIG.

  The clutch unit includes a first clutch and a second clutch. The input side rotation member of the first clutch is linked to the ring gear of the second planetary transmission mechanism of the planetary transmission unit via the linkage mechanism. The interlocking mechanism includes a planetary transmission gear meshed with the ring gear of the second planetary transmission mechanism, a clutch transmission gear meshed with the gear portion of the input side rotating member of the first clutch, the planetary transmission gear, and the clutch transmission. A rotation interlocking shaft connected to the gear.

  The auxiliary transmission includes a high speed clutch and a low speed clutch. In the auxiliary transmission device described in FIG. 16 of Patent Document 1, the high speed clutch and the low speed clutch are meshing clutches.

  12 and FIG. 16 of the cited document 1, the output of the continuously variable transmission and the driving force of the pump shaft of the continuously variable transmission (the engine drive that is not subjected to the shifting action by the continuously variable transmission). Force) is synthesized by the planetary transmission unit. When the continuously variable transmission is operated to change gears, the first clutch, the second clutch, the high-speed clutch, and the low-speed clutch are appropriately switched between the on-state and the off-state according to the speed-change operation. The composite driving force to be output is divided into stages from the first speed range to the fourth speed range, and continuously variable in each speed range and output from the output shaft of the auxiliary transmission.

JP 2007-92949 A

  In the case of the speed change transmission device adopting the above-described conventional technology, the first to fourth clutches provided to divide the combined driving force from the planetary transmission unit into a plurality of speed ranges and transmit it to the output rotating body, or The first, second clutch, high speed, and low speed clutch are arranged in the front-rear direction of the transmission case, and the size of the transmission in the front-rear direction of the transmission case tends to increase.

  An object of the present invention is to provide a speed change transmission device that can be obtained in a compact manner while an output with a stepless change in speed over a wide speed change range can be obtained only by performing a simple speed change operation.

The first invention includes a continuously variable transmission unit or an electric motor to which engine driving force is input,
A planetary transmission unit configured to combine an output of the continuously variable transmission unit and an engine driving force not subjected to a shifting action by the continuously variable transmission unit, or an output of the electric motor and an engine driving force by a plurality of planetary transmission mechanisms; ,
In the transmission device configured to divide the combined driving force from the planetary transmission unit into a plurality of speed ranges, and to change the speed steplessly in each step speed range and output from the output rotating body,
A plurality of transmission shafts that convert the combined driving force from the planetary transmission unit into a driving force of the plurality of speed ranges by switching a plurality of speed range setting clutches and transmit the driving force to the output rotating body,
The plurality of transmission shafts are arranged in parallel and in parallel.

  According to the configuration of the first aspect of the present invention, when the plurality of speed range setting clutches are appropriately switched in accordance with the speed change operation of the continuously variable transmission unit or the electric motor, the combined driving force from the planetary transmission unit is a speed range of a plurality of stages. The speed is steplessly changed at each speed range and transmitted to the output rotating body.

  According to the configuration of the first aspect of the present invention, a plurality of transmission shafts are provided so that transmission from the planetary transmission unit to the output rotating body is performed by a transmission shaft corresponding to the transmission speed range, and the plurality of transmission shafts are arranged in parallel. Since the transmission parts are arranged in parallel and in parallel, the size of the transmission portion in the longitudinal direction of the transmission case can be made smaller than the size of the conventional transmission gear transmission.

  Therefore, if a simple shift operation is performed by simply shifting the continuously variable transmission unit or the electric motor, an output that changes steplessly over a wide shift range can be obtained. Thus, a shift transmission device that is easy to use, such as being easily mounted on a small vehicle, can be obtained.

  In the second aspect of the invention, two of the transmission shafts are provided, and the plurality of speed range setting clutches are distributed to the two transmission shafts.

  According to the configuration of the second aspect of the present invention, two transmission shafts can be used, and the transmission shaft and the speed range setting clutch are arranged together to obtain a transmission unit that transmits power from the planetary transmission unit to the output rotating body more compactly. Can do.

  Accordingly, it is possible to obtain a speed change transmission device that is more compact and easy to use because it is more compact in terms of the size of the transmission portion from the planetary transmission portion to the output rotating body.

  In the third aspect of the invention, the planetary transmission unit includes a pair of planetary transmission mechanisms in which planetary gears mesh with each other, and the plurality of transmission shafts are arranged in parallel over the entire length.

  According to the configuration of the third aspect of the invention, since the plurality of transmission shafts are arranged in parallel over the entire length, the output transmission from the planetary transmission unit is rotated as compared with the case where the plurality of transmission shafts are arranged in parallel in a state shifted in the longitudinal direction of the transmission case. The length of the transmission part to the body in the front-rear direction of the mission case can be reduced.

  Accordingly, it is possible to obtain a transmission device that is easy to use, such as being more compact and easier to design in terms of the size of the transmission portion from the planetary transmission portion to the output rotor in the longitudinal direction of the transmission case.

  In the fourth invention, the plurality of speed range setting clutches are meshing clutches.

According to the configuration of the fourth invention, since the speed range setting clutch is a meshing clutch, the speed range setting clutch can be obtained lighter and more compact than when a friction clutch is employed as the speed range setting clutch.

  Therefore, the speed range setting clutch is light and inexpensive in terms of the weight and size of the speed range setting clutch, and it is possible to obtain a speed change transmission device that is easy to use from the viewpoint of weight and cost.

Diagram of traveling transmission device of tractor equipped with the transmission device of the first embodiment Sectional view of planetary transmission section, speed range setting section, odd range transmission clutch and even range transmission clutch Planetary gear layout Shaft layout of the transmission Explanatory drawing of action state of speed range setting part Explanatory drawing which shows the relationship between the speed change state of a continuously variable transmission part, the output speed of a gear transmission, and a speed range. Explanatory drawing of clutch operating state by control means at the time of speed range switching Block diagram of operating device Diagram of a traveling transmission device for a tractor equipped with the speed change transmission device of the second embodiment Sectional drawing of the planetary transmission part and speed range setting part of the speed change transmission apparatus of 2nd Example Sectional drawing of the forward / reverse switching device of the traveling transmission device equipped with the speed change transmission device of the second embodiment. Diagram of traveling transmission device of tractor equipped with transmission gearing device of third embodiment Sectional drawing of the planetary transmission part and speed range setting part of the speed change transmission apparatus of 3rd Example Sectional drawing of the forward / reverse switching device of the traveling transmission equipped with the transmission of the third embodiment. Diagram of the driving transmission equipped with the transmission gear of the fourth embodiment

Embodiments of the present invention will be described below with reference to the drawings.
FIG. 1 is a diagram of a traveling transmission device for a tractor equipped with a transmission gear transmission A according to a first embodiment of the present invention. As shown in this figure, the tractor travel transmission device includes a main clutch 2 for inputting an output from an output shaft 1a of the engine 1, and a forward / reverse switching device 10 for inputting an output of the main clutch 2 by an input shaft 11. The transmission gear A according to the first embodiment of the present invention in which the input shaft 22 is interlocked with the output gear 12 of the forward / reverse switching device 10 via the gear 21, and the output rotating body of the transmission gear A. A rear wheel differential mechanism 32 in which an input gear 31 is connected to a rear end portion of the output shaft 30 so as to be integrally rotatable, and an input shaft 41 is integrally rotatable to a front end portion of the output shaft 30 via a joint 33. And a front wheel differential mechanism 35 to which an output from the output shaft 42 of the front wheel transmission 40 is input via the rotation transmission shaft 34.

  The forward / reverse switching device 10, the transmission device A, the rear wheel differential mechanism 32, and the front wheel transmission device 40 are accommodated in the same mission case 36.

  As shown in FIG. 1, a power take-out shaft 37 protruding rearward from the mission case 36 transmits driving force to various working devices such as a rotary tiller connected to the tractor. The power take-out shaft 37 is interlocked with the input shaft 11 of the forward / reverse switching device 10 via an interlocking shaft 38 and a work clutch 39.

  As shown in FIG. 1, the forward / reverse switching device 10 includes the input shaft 11 and the output gear 12, an input-side rotating body 13 provided on the input shaft 11 so as to be integrally rotatable, A multi-plate forward friction clutch 14 provided across one end of the rotating body 13 and the output gear 12 is provided. The forward / reverse switching device 10 further includes a transmission gear 15 that is positioned on the opposite side of the output gear 12 with respect to the input-side rotator 13 and is supported on the input shaft 11 so as to be relatively rotatable. A multi-plate reverse friction clutch 16 provided over the gear 15 and the other end of the input side rotating body 13, a reverse gear 17 meshed with the transmission gear 15, and the reverse gear 17 are linked to the output gear 12. The interlocking shaft 18 is provided.

  In the forward / reverse switching device 10, operating hydraulic pressure is supplied to the forward piston of the forward piston and the backward piston provided in the input side rotator 13, and the forward piston pressurizes the forward friction clutch 14 into the engaged state. By operating it, it will be in the forward state, and the hydraulic pressure will be supplied to the reverse piston, and the reverse piston will be in the reverse state by pressurizing the reverse friction clutch 16 into the engaged state.

  When the forward / reverse switching device 10 is in the forward movement state, the driving force of the input shaft 11 is converted into the forward driving force by the input side rotating body 13, the forward friction clutch 14, and the output gear 12, and the continuously variable transmission unit is converted from the output gear 12. 20 and the planetary transmission part P. When the forward / reverse switching device 10 enters the reverse state, the drive force of the input shaft 11 is converted into the reverse drive force by the input side rotating body 13, the reverse friction clutch 16, the transmission gear 15, the reverse gear 17, and the transmission shaft 18. The power is transmitted to the output gear 12 and is output from the output gear 12 to the continuously variable transmission 20 and the planetary transmission unit P.

  As shown in FIG. 1, a transmission A according to a first embodiment of the present invention includes the input shaft 22 and the output shaft 30, the continuously variable transmission unit 20, and the continuously variable transmission unit 20. The first input gear 91 meshes with the planetary transmission portion P in which the sun gear shaft 61 is interlocked with the motor shaft 23 via the gear 50 and the gear 51, and the first output gear 81 of the planetary transmission portion P. The speed range setting unit 90 is provided.

  As shown in FIG. 1, the continuously variable transmission 20 includes an axial plunger type and variable displacement type hydraulic pump 24 having the input shaft 22 as a pump shaft (hereinafter, the input shaft is referred to as a pump shaft 22). And an axial plunger type hydraulic motor 25 driven by the pressure oil from the hydraulic pump 24. The hydraulic motor 25 includes the motor shaft 23.

  That is, the continuously variable transmission unit 20 is a hydrostatic continuously variable transmission unit, and is changed into a forward rotation transmission state, a neutral state, and a reverse rotation transmission state by changing the swash plate angle of the hydraulic pump 24. Switch. The continuously variable transmission unit 20 changes the swash plate angle of the hydraulic pump 24 in the forward rotation transmission state, thereby transferring the engine driving force transmitted to the pump shaft 22 via the forward / reverse switching device 10 in the forward rotation direction. It is converted into a driving force and is steplessly shifted and output from the motor shaft 23. The continuously variable transmission unit 20 changes the swash plate angle of the hydraulic pump 24 in the reverse rotation transmission state, thereby transferring the engine driving force transmitted to the pump shaft 22 via the forward / reverse switching device 10 in the reverse rotation direction. It is converted into a driving force and is steplessly shifted and output from the motor shaft 23. The continuously variable transmission 20 stops the output from the motor shaft 23 in the neutral state.

  FIG. 2 shows a cross-sectional structure of the planetary transmission portion P. As shown in FIG. 1 and FIG. 1, the planetary transmission unit P transmits a driving force input from the continuously variable transmission unit 20 and the forward / reverse switching device 10 to the speed range setting unit 90. And a planetary transmission mechanism 60 (hereinafter abbreviated as the upper planetary mechanism 60) positioned on the upper side and a planetary transmission mechanism 70 (hereinafter abbreviated as the lower planetary mechanism 70) positioned on the lower side. It is configured.

  The upper planetary mechanism 60 is provided with a sun gear 62 provided at one end of the sun gear shaft 61 so as to be rotatable together with the sun gear 62, and is distributed in the circumferential direction of the sun gear 62 on the outer peripheral side of the sun gear 62 and meshed with the sun gear 62. Three planetary gears 63, a carrier 64 that freely supports the three planetary gears 63, and a ring gear 65 that meshes with the three planetary gears 63 are provided. The sun gear 62 and the sun gear shaft 61 are integrally formed.

  The lower planetary mechanism 70 includes a sun gear 72 that is rotatably positioned around the same axis as the sun gear 62 on the lower side in the transmission direction of the sun gear 62 of the upper planetary mechanism 60, and a sun gear 72 on the outer peripheral side of the sun gear 72. Three planetary gears 73 that are distributed in the circumferential direction and meshed with the sun gear 72, a carrier 64 that supports the three planetary gears 73 in a freely rotating manner, and meshed with the three planetary gears 73. Ring gear 75.

  FIG. 3 is an arrangement view of the planetary gear 63 of the upper planetary mechanism 60 and the planetary gear 73 of the lower planetary mechanism 70. As shown in FIG. 2 and FIG. 2, the three planetary gears 63 of the upper planetary mechanism 60 and the three planetary gears 73 of the lower planetary mechanism 70 are combined with one planetary gear 63 of the upper planetary mechanism 60. One planetary gear 73 of the lower planetary mechanism 70 forms one gear pair that faces the circumferential direction of the sun gears 62, 72, and the other planetary gear 63 of the upper planetary mechanism 60 and the other planetary mechanism 70. One planetary gear 73 forms one gear pair that faces the circumferential direction of the sun gears 62, 72, and the remaining planetary gear 63 of the upper planetary mechanism 60 and the remaining planetary gear 73 of the lower planetary mechanism 70 In this arrangement, the sun gears 62 and 72 are arranged in a pair of gears close to each other in the circumferential direction. The planetary gear 63 of the upper planetary mechanism 60 and the planetary gear 73 of the lower planetary mechanism 70 in each gear pair are the ends of the planetary gears 63 and 73 opposite to the side meshed with the sun gears 62 and 72. Interlocking with each other.

  In two adjacent gear pairs, the tooth tip portions of the planetary gears 63 and 73 of one gear pair are inserted between the tooth tip portions of the planetary gears 63 and 73 of the other gear pair. However, in the two adjacent gear pairs, the planetary gears 63 and 73 of one gear pair and the planetary gears 63 and 73 of the other gear pair are not interlocked. By adopting an arrangement in which the tooth tip portions of the planetary gears 63 and 73 are inserted between the tooth tip portions in this way, the sun gears 62 and 72 and the ring gear 65, The diameter of 75 can be suppressed small, and the planetary transmission part P can be obtained in a compact state with a small outer diameter.

  As shown in FIG. 3, the planetary gear 63 of the upper planetary mechanism 60 is rotatably supported by the support shaft 64a of the carrier 64, and the planetary gear 73 of the lower planetary mechanism 70 rotates about the support shaft 64b of the carrier 64. It is supported freely. That is, the carrier 64 is a carrier common to the upper planetary mechanism 60 and the lower planetary mechanism 70. That is, the carrier 64 revolves around the sun gear 62 while rotating while the planetary gears 63 of the upper planetary mechanism 60 mesh with the planetary gears 73 of the lower planetary mechanism 70 forming a gear pair with the carrier planetary mechanism 70. Each planetary gear 73 supports the planetary gears 63 and 73 so as to revolve around the sun gear 72 while rotating with the planetary gear 63 of the upper planetary mechanism 60 forming a gear pair with the planetary gear 73.

  The ring gear 65 of the upper planetary mechanism 60 is connected to an interlocking member 66 that is connected to the ring gear 65 so as to be integrally rotatable, and is connected to the end of the interlocking member 66 so as to be integrally rotatable by spline engagement. The output gear 12 is linked to the output gear 12 through a transmission gear 67 configured to mesh with the output gear 12. The ring gear 65 and the interlocking member 66 are integrally formed. The sun gear 62 of the upper planetary mechanism 60 is linked to the motor shaft 23 of the continuously variable transmission 20 via the sun gear shaft 61, the gear 51, and the gear 50.

  The planetary transmission portion P includes the first output gear 81, and also includes a second output gear 82 and a third output gear 83 that are positioned side by side in the longitudinal direction of the transmission case on the rear side of the transmission case with respect to the first output gear 81. And a fourth output gear 84.

  The first output gear 81 is linked to the ring gear 75 of the lower planetary mechanism 70 so as to be integrally rotatable via an interlocking member 76 whose one end is connected to the first output gear 81 by spline engagement. . The interlocking member 76 and the ring gear 75 are integrally formed.

  A rotation support shaft 85 that supports the second output gear 82 and the fourth output gear 84 so as to rotate together and a sun gear shaft 71 that supports the sun gear 72 of the lower planetary mechanism 70 so as to rotate together are formed by spline engagement. They are connected so that they can rotate together. As a result, the second output gear 82 and the fourth output gear 84 are integrally rotated and interlocked with the sun gear 72 of the lower planetary mechanism 70 so as to be integrally rotatable.

  The third output gear 83 is connected to the other end of a rotating shaft 86, one end of which is connected to the carrier 64 so as to be integrally rotatable by spline engagement. Thus, the third output gear 83 is connected to the carrier 64 via the rotary shaft 86 so as to be integrally rotatable.

  That is, the planetary transmission unit P inputs the output from the motor shaft 23 of the continuously variable transmission unit 20 to which the engine driving force is input to the sun gear 62 of the upper planetary mechanism 60 through the gear 50, the gear 51, and the sun gear shaft 61. The driving force of the output gear 12 of the forward / reverse switching device 10 as the engine driving force that is not subjected to the shifting action by the continuously variable transmission unit 20 is input to the ring gear 65 of the upper planetary mechanism 60 by the gear 67 and the interlocking member 66, The output of the transmission unit 20 and the engine driving force that is not subjected to the shifting action of the continuously variable transmission unit 20 are combined by the upper planetary mechanism 60 and the lower planetary mechanism 70, and the combined driving force is first, second, third, Output from the fourth output gears 81, 82, 83, 84 to the speed range setting unit 90.

  FIG. 2 shows a cross-sectional structure of the speed range setting unit 90. As shown in FIG. 1 and FIG. 1, the speed range setting unit 90 includes the first input gear 91, the second output gear 82, the third output gear 83, and the fourth output gear 84. Are provided with a second input gear 92, a third input gear 93, and a fourth input gear 94, and a transmission shaft that supports the first input gear 91 and the third input gear 93 in a relatively rotatable manner. And an even range transmission shaft 96 as a transmission shaft for supporting the second input gear 92 and the fourth input gear 94 in a relatively rotatable manner.

  FIG. 4 is a layout diagram of each axis in the cross section of the transmission gearbox A. As shown in FIG. 2 and FIG. 2, the odd-range transmission shaft 95 and the even-range transmission shaft 96 are arranged in parallel with each other in the vertical direction of the transmission case 36 over the entire length and in parallel with each other. Thus, the size of the speed range setting unit 90 in the front-rear direction of the mission case is reduced.

  The odd range transmission shaft 95 includes a first clutch 101 provided across the transmission cylinder portion 91a and the odd range transmission shaft 95 of the first input gear 91, and an odd range transmission of the transmission cylinder portion 93a of the third input gear 93. A third clutch 103 provided across the shaft 95 and an odd range transmission clutch 107 provided at the end of the odd range transmission shaft 95 opposite to the end where the first input gear 91 is located are provided.

  The even range transmission shaft 96 includes a second clutch 102 provided across one side portion of the second input gear 92 and the even range transmission shaft 96, and one side portion of the fourth input gear 94 and the even range transmission shaft 96. And an even range transmission clutch 108 provided at the end of the even range transmission shaft 96 opposite to the end where the second input gear 92 is located.

  FIG. 2 shows a sectional structure of the first clutch 101, the second clutch 102, the third clutch 103, and the fourth clutch 104. As shown in this figure, the first clutch 101, the second clutch 102, the third clutch 103, and the fourth clutch 104 are provided with holders 105a and 106a attached to an odd range transmission shaft 95 or an even range transmission shaft 96. Shift gears 105 and 106 supported so as to be integrally rotatable and freely slidable via the transmission cylinder portions 91a and 93a or gears 101a, 102a and 103a of the corresponding input gears 91, 92, 93 and 94. , 104a, and is a meshing clutch.

  That is, the first clutch 101, the second clutch 102, the third clutch 103, and the fourth clutch 104 are coupled to the shift gears 105 and 106 via a shifter and are provided with hydraulic pistons 111 and 112 provided outside the transmission case 36. , And the shift gears 105 and 106 are slid with respect to the holders 105a and 106a to engage the holders 105a and 106a with the gears 101a, 102a, 103a, and 104a, whereby the input gears 91, 92, 93, The driving force 94 is transmitted to the odd range transmission shaft 95 or the even range transmission shaft 96 via the shift gears 105 and 106 and the holders 105a and 106a, and the input gears 91 and 93 and the odd range transmission shaft 95 are input. Gears 92 and 94 and even range transmission shaft 96 are integrated. A state enters so as to.

  The first clutch 101, the second clutch 102, the third clutch 103, and the fourth clutch 104 are disengaged from the gears 101a, 102a, 103a, 104a when the shift gears 105, 106 are slid with respect to the holders 105a, 106a. As a result, the input gears 91 and 93 and the odd range transmission shaft 95 are turned or the input gears 92 and 94 and the even range transmission shaft 96 are rotated relative to each other.

  FIG. 2 shows a cross-sectional structure of the odd range transmission clutch 107 and the even range transmission clutch 108. As shown in this figure, the odd range transmission clutch 107 and the even range transmission clutch 108 are input side rotating members 107a, 108a provided on the odd range transmission shaft 95 or the even range transmission shaft 96 so as to be integrally rotatable, The output gears 107b and 108b provided to be rotatable relative to the odd range transmission shaft 95 or the even range transmission shaft 96, and a multi-plate type provided over one side of the output gears 107b and 108b and the input side rotation members 107a and 108a. The friction clutch main bodies 107c and 108c are configured as friction clutches.

  The output gear 107b of the odd-number range transmission clutch 107 is interlocked with the output shaft 30 via a transmission gear 109 that is configured to mesh with the output gear 107b and is integrally rotatable with the output shaft 30. . The output gear 108 b of the even range transmission clutch 108 meshes with the transmission gear 109, and is linked to the output shaft 30 via the transmission gear 109.

  That is, the odd range transmission clutch 107 and the even range transmission clutch 108 are supplied with operating hydraulic pressure from the operating oil passages 116 and 117 to the hydraulic pistons 114 and 115 slidably provided inside the input side rotating members 107a and 108a. Then, the hydraulic pistons 114 and 115 pressurize the friction clutch bodies 107c and 108c into the engaged state, so that the input side rotation members 107a and 108a and the output gears 107b and 108b can be integrally rotated by the friction clutch bodies 107c and 108c. It enters the state to be interlocked. In the odd range transmission clutch 107 and the even range transmission clutch 108, the operating oil pressure is discharged from the hydraulic pistons 114 and 115, and the pressurizing operation of the friction clutch bodies 107c and 108c by the hydraulic pistons 114 and 115 is released, and the friction clutch body 107c. , 108c are turned off so that the input side rotating members 107a, 108a and the output gears 107b, 108b are rotated relative to each other.

  As a result, the odd range transmission clutch 107 is operated in the engaged state to transmit the driving force of the odd range transmission shaft 95 to the output gear 107b, and the transmission from the odd range transmission shaft 95 to the output shaft 30 enters. In this way, the transmission from the odd range transmission shaft 95 to the output shaft 30 is turned off by being operated in the cut state.

  When the even range transmission clutch 108 is operated to be in the engaged state, the driving force of the even range transmission shaft 96 is transmitted to the output gear 108b, and the transmission from the even range transmission shaft 96 to the output shaft 30 is turned on and off. By operating to the state, the transmission from the even range transmission shaft 96 to the output shaft 30 is cut off.

  FIG. 5 is an explanatory diagram showing the operating state of the speed range setting unit 90. “On” shown in FIG. 5 indicates an on state of the first, second, third, and fourth clutches 101, 102, 103, 104, the odd range transmission clutch 107, and the even range transmission clutch 108. “-” Shown in FIG. 5 indicates the disengaged state of the first, second, third, and fourth clutches 101, 102, 103, 104, the odd range transmission clutch 107, and the even range transmission clutch 108.

  As shown in this figure, the speed range setting unit 90 shifts speed by operating the first clutch 101 in the engaged state and operating the second, third, and fourth clutches 102, 103, and 104 in the disengaged state. Set transmission A to the first speed range. Then, the transmission device A shifts the combined driving force output from the planetary transmission unit P by the first output gear 81 by the first output gear 81 and the first input gear 91, and the odd-number range via the first clutch 101. It is transmitted to the transmission shaft 95. At this time, when the odd range transmission clutch 107 is operated to be engaged, the transmission device A transmits the driving force of the odd range transmission shaft 95 to the output shaft 30 by the odd range transmission clutch 107 and the transmission gear 109. .

  The speed range setting unit 90 operates the transmission device A in the second speed range by operating the second clutch 102 in the engaged state and operating the first, third, and fourth clutches 101, 103, and 104 in the disengaged state. Set to. Then, the transmission device A shifts the combined driving force output from the planetary transmission unit P by the second output gear 82 by the second output gear 82 and the second input gear 92, and the even number range via the second clutch 102. It is transmitted to the transmission shaft 96. At this time, when the even range transmission clutch 108 is operated to be in the engaged state, the transmission device A transmits the driving force of the even range transmission shaft 96 to the output shaft 30 by the even range transmission clutch 108 and the transmission gear 109. .

  The speed range setting unit 90 operates the transmission A in the third speed range by operating the third clutch 103 in the engaged state and operating the first, second, and fourth clutches 101, 102, and 104 in the disengaged state. Set to. Then, the transmission device A shifts the combined driving force output from the planetary transmission unit P by the third output gear 83 by using the third output gear 83 and the third input gear 93, and the odd-number range via the third clutch 103. It is transmitted to the transmission shaft 95. At this time, when the odd range transmission clutch 107 is operated to be engaged, the transmission device A transmits the driving force of the odd range transmission shaft 95 to the output shaft 30 by the odd range transmission clutch 107 and the transmission gear 109. .

  The speed range setting unit 90 operates the transmission device A in the fourth speed range by operating the fourth clutch 104 in the engaged state and operating the first, second, and third clutches 101, 1012, and 103 in the disengaged state. Set to. Then, the transmission device A shifts the combined driving force output from the planetary transmission unit P by the fourth output gear 84 by the fourth output gear 84 and the fourth input gear 94, and the even range via the fourth clutch 104. It is transmitted to the transmission shaft 96. At this time, when the even range transmission clutch 108 is operated to be in the engaged state, the transmission device A transmits the driving force of the even range transmission shaft 96 to the output shaft 30 by the even range transmission clutch 108 and the transmission gear 109. .

  FIG. 8 is a block diagram of an operating device equipped on the tractor to operate the traveling transmission device. As shown in this figure, this operating device includes a speed change lever 120, a speed change operation detecting means 121, an engine output sensor 122, a continuously variable transmission output sensor 123, a vehicle speed sensor 124, a forward / reverse lever 125, It includes a forward / reverse detection means 126, a shift detection means 127, and a control means 128 linked to the detection means 121, 126, 127 and the sensors 122, 123, 124.

  The control means 128 is linked to an operation unit (not shown) of an actuator (not shown) that changes the swash plate angle of the hydraulic pump 24 of the continuously variable transmission unit 20. The control means 128 operates the hydraulic pistons 111, 112, 114, 115 of the first clutch 101, the second clutch 102, the third clutch 103, the fourth clutch 104, the odd range transmission clutch 107, and the even range transmission clutch 108. Connected to an operation valve (not shown). The control means 128 is linked to an actuator (not shown) that switches between the forward friction clutch 14 and the reverse friction clutch 16.

  As shown in FIG. 8, the shift lever 120 swings the operation range from the neutral position N to the maximum speed position max. A portion from the neutral position N to the intermediate position M in this operation area is a low speed area L. A portion from the intermediate position M to the highest speed position max in the operation area is a high speed area H.

  The shift operation detecting means 121 is constituted by a rotary potentiometer linked to the shift lever 120. The shift operation detecting means 121 detects the operation position of the shift lever 120 and outputs the detection result to the control means 128.

  The engine output sensor 122, the continuously variable transmission output sensor 123, and the vehicle speed sensor 124 are constituted by rotation sensors. The engine output sensor 122 detects the output speed of the engine 1 and outputs the detection result to the control means 128. The continuously variable transmission output sensor 123 detects the output speed of the continuously variable transmission 20 from the motor shaft 23 and outputs the detection result to the control means 128. The vehicle speed sensor 124 detects the rotational speed of the output shaft 30 as the vehicle speed, and outputs the detection result to the control means 128. The shift detection unit 127 detects the shift state of the continuously variable transmission unit 20 and feeds back the detection result to the control unit 128.

  The forward / reverse lever 125 is switched to a neutral position N, a forward position F, and a reverse position R by a swing operation. The forward / reverse detection means 126 is constituted by a rotary potentiometer linked to the forward / reverse lever 125. The forward / reverse detection means 126 detects the operation position of the forward / reverse lever 125 and outputs the detection result to the control means 128.

  The control means 128 is configured using a microcomputer. The control means 128 shifts the speed change gear A so that the output shaft 30 is driven at a rotational speed corresponding to the operation position of the speed change lever 120 in a speed range as an operation state corresponding to the operation position of the speed change lever 120. First, second, third, and fourth clutches 101, 102, and 103 based on information detected by operation detection means 121, shift detection means 127, engine output sensor 122, continuously variable transmission output sensor 123, and vehicle speed sensor 124. 104, odd range transmission clutch 107 and even range transmission clutch 108 are operated. The control means 128 operates the forward friction clutch 14 and the reverse friction clutch 16 based on the information detected by the forward / reverse detection means 126 so that the forward / reverse switching device 10 is in an operation state corresponding to the operation position of the forward / reverse lever 125. To do.

  As a result, when the tractor operates the speed change lever 120 and the forward / reverse lever 125, the operation position of the speed change lever 120 and the output speed of the engine 1 are changed in the forward or backward direction corresponding to the operation position of the forward / backward movement lever 125. Drive at the corresponding vehicle speed.

  That is, FIG. 6 shows the relationship between the speed change state of the continuously variable transmission 20, the output speed of the output shaft 30 of the transmission A, and the speed range set by the speed range setting unit 90 of the transmission A. It is explanatory drawing. The vertical axis shown in FIG. 6 indicates the number of rotations of the output shaft 30 (hereinafter referred to as output speed). The horizontal axis shown in FIG. 6 indicates the speed change state of the continuously variable transmission unit 20. “−MAX” on the horizontal axis indicates the maximum speed of the continuously variable transmission unit 20 in the reverse rotation transmission state. “0” on the horizontal axis indicates a neutral state of the continuously variable transmission 20. “+ MAX” on the horizontal axis indicates the maximum speed of the continuously variable transmission unit 20 in the normal rotation transmission state.

  As shown in FIG. 5, FIG. 5 and FIG. 8, the portion of the speed change lever 120 from the neutral position N to the intermediate position Lm of the low speed area L (hereinafter referred to as the low speed intermediate position Lm) in the low speed area L. The control means 128 operates the first clutch 101 in the engaged state, operates the second, third, and fourth clutches 102, 103, and 104 in the disengaged state. Become a range. At this time, the control means 128 operates the odd range transmission clutch 107 to the on state and operates the even range transmission clutch 108 to the disengagement state. Thereby, the transmission device A transmits the driving force of the first output gear 81 of the planetary transmission portion P to the odd range transmission shaft 95 by the first input gear 91 and the first clutch 101, and this odd range transmission shaft 95. Is transmitted to the output shaft 30 by the odd range transmission clutch 107 and the transmission gear 109. Then, as the shift lever 120 is operated from the neutral position N toward the low speed intermediate position Lm, the control means 128 shifts the continuously variable transmission 20 from “−MAX” to “+ MAX”, and outputs the output speed. Increases continuously from “0”. When the speed change lever 120 reaches the low speed intermediate position Lm, the control means 128 operates the continuously variable transmission 20 to “+ MAX”, and the output speed becomes “V1”.

  When the speed change lever 120 is operated to a portion from the low speed intermediate position Lm to the intermediate position M in the low speed range L, the control means 128 operates the second clutch 102 to be in the engaged state, and the first, third and fourth clutches. By operating 101, 103, and 104 in the cut-off state, the transmission device A is in the second speed range. At this time, the control means 128 operates the even range transmission clutch 108 to the engaged state and operates the odd range transmission clutch 107 to the disengaged state. Thus, the transmission device A transmits the driving force of the second output gear 82 of the planetary transmission unit P to the even range transmission shaft 96 by the second input gear 92 and the second clutch 102, and this even range transmission shaft 96. Is transmitted to the output shaft 30 by the even range transmission clutch 108 and the transmission gear 109. Then, as the shift lever 120 is operated from the low speed intermediate position Lm toward the intermediate position M, the control means 128 shifts the continuously variable transmission unit 20 from “+ MAX” to “−MAX”, and the output speed Increases continuously from “V1”. When the speed change lever 120 reaches the intermediate position M, the control means 128 operates the continuously variable transmission 20 to “−MAX”, and the output speed becomes “V2”.

  When the speed change lever 120 is operated in a portion of the high speed range H from the neutral position N to the intermediate position Hm of the high speed range H (hereinafter referred to as the high speed intermediate position Hm), the control means 128 causes the third clutch 103 to move. By operating to the on state and operating the first, second, and fourth clutches 101, 102, and 104 to the disengaged state, the transmission A is in the third speed range. At this time, the control means 128 operates the odd range transmission clutch 107 to the on state and operates the even range transmission clutch 108 to the disengagement state. Thus, the transmission A transmits the driving force of the third output gear 83 of the planetary transmission portion P to the odd range transmission shaft 95 via the third input gear 93 and the third clutch 103, and the odd range transmission shaft. The driving force of 95 is transmitted to the output shaft 30 by the odd range transmission clutch 107 and the transmission gear 109. Then, as the shift lever 120 is operated from the intermediate position M toward the high speed intermediate position Hm, the control means 128 shifts the continuously variable transmission unit 20 from “−MAX” to “+ MAX”, and the output speed Increases continuously from “V2”. When the speed change lever 120 reaches the high speed intermediate position Mm, the control means 128 operates the continuously variable transmission 20 to “+ MAX” and the output speed becomes “V3”.

  When the speed change lever 120 is operated to a portion from the high speed intermediate position Hm to the maximum speed position max in the high speed range H, the control means 128 operates the fourth clutch 104 to the engaged state, and the first, second, third By operating the clutches 101, 102, 103 in the disengaged state, the transmission device A is in the fourth speed range. At this time, the control means 128 operates the even range transmission clutch 108 to the engaged state and operates the odd range transmission clutch 107 to the disengaged state. Thus, the transmission device A transmits the driving force of the fourth output gear 84 of the planetary transmission unit P to the even range transmission shaft 96 by the fourth input gear 94 and the fourth clutch 104, and The driving force is transmitted to the output shaft 30 by the even range transmission clutch 108 and the transmission gear 109. Then, as the shift lever 120 is operated from the high speed intermediate position Hm toward the maximum speed position max, the control means 128 shifts the continuously variable transmission 20 from “+ MAX” to “−MAX” and outputs it. The speed increases steplessly from “V3”. When the speed change lever 120 reaches the maximum speed position max, the control means 128 operates the continuously variable transmission 20 to “−MAX” and the output speed becomes “V4”.

  When the forward / reverse lever 125 is operated to the forward position F, the control means 128 operates the forward friction clutch 14 to the on state, operates the reverse friction clutch 16 to the disengaged state, and the forward / reverse switching device 10 enters the forward transmission state. . Then, the forward / reverse switching device 10 converts the driving force input from the engine 1 as a forward driving force and transmits it from the output gear 12 to the continuously variable transmission unit 20 and the planetary transmission unit P, and the transmission device A transmits the forward driving force. The tractor travels forward by transmitting to the front wheel differential mechanism 35 and the rear wheel differential mechanism 32.

  When the forward / reverse lever 125 is operated to the reverse position R, the control means 128 operates the forward friction clutch 14 to the disengaged state, operates the reverse friction clutch 16 to the on state, and the forward / reverse switching device 10 enters the reverse transmission state. . Then, the forward / reverse switching device 10 converts the driving force input from the engine 1 as a reverse driving force and transmits it from the output gear 12 to the continuously variable transmission unit 20 and the planetary transmission unit P, and the transmission device A transmits the reverse driving force to the front wheels. The tractor travels backward by transmitting to the differential mechanism 35 for the rear wheel and the differential mechanism 32 for the rear wheel.

  When the forward / reverse lever 125 is operated to the neutral position N, the control unit 128 operates the forward friction clutch 14 and the reverse friction clutch 16 to be disconnected, and the forward / reverse switching device 10 is in the neutral state. Then, the forward / reverse switching device 10 does not transmit power to the continuously variable transmission unit 20 and the planetary transmission unit P, and the transmission transmission device A blocks transmission to the front wheel actuation mechanism 35 and the rear wheel differential mechanism 32. The tractor stops.

  FIG. 7 is an explanatory diagram showing the operating states of the first, second, third, and fourth clutches 101, 102, 103, and 104 by the control means 128 when the speed range of the transmission device A is switched. “Increase” shown in FIG. 7 indicates that the output speed of the output shaft 30 changes at an increased speed for switching the speed range. “Decrease” shown in FIG. 7 indicates that the output speed of the output shaft 30 is decelerated and changed for switching the speed range.

  As shown in this figure, when switching the speed range of the transmission A, the control means 128 temporarily turns both the odd range transmission shaft 95 and the even range transmission shaft 96 into the planetary transmission section. Each clutch 101, so that a double transmission state in which power is transmitted from the P to the output shaft 30 via the odd transmission system having the odd range transmission shaft 95 and the even transmission system having the even range transmission shaft 96 occurs. 102, 103, 104, 107, 108 are operated.

  That is, when the transmission device A is switched from the first speed range to the second speed range, the control means 128 switches the second clutch 102 to the engaged state before switching the first clutch 101 to the disconnected state. After the clutch 102 is switched to the engaged state, the first clutch 101 is switched to the disconnected state. At this time, the control means 128 switches the even range transmission clutch 108 to the on state before switching the odd range transmission clutch 107 to the disengaged state, and after the even range transmission clutch 108 switches to the on state, The transmission clutch 107 is switched to the disengaged state.

  When the transmission device A is switched from the second speed range to the third speed range, the control means 128 switches the third clutch 103 to the on state before switching the second clutch 102 to the disengaged state. After switching to the engaged state, the second clutch 102 is switched to the disconnected state. At this time, the control means 128 switches the odd range transmission clutch 107 to the on state before switching the even range transmission clutch 108 to the disengaged state, and after the odd range transmission clutch 107 switches to the on state, The transmission clutch 108 is switched to the disengaged state.

  When the transmission device A is switched from the third speed range to the fourth speed range, the control means 128 switches the fourth clutch 104 to the on state before switching the third clutch 103 to the disengaged state. After switching to the engaged state, the third clutch 103 is switched to the disconnected state. At this time, the control means 128 switches the even range transmission clutch 108 to the on state before switching the odd range transmission clutch 107 to the disengaged state, and after the even range transmission clutch 108 switches to the on state, The transmission clutch 107 is switched to the disengaged state.

  When the transmission device A is switched from the fourth speed range to the third speed range, the control means 128 switches the third clutch 103 to the on state before switching the fourth clutch 104 to the disengaged state. After switching to the engaged state, the fourth clutch 104 is switched to the disconnected state. At this time, the control means 128 switches the odd range transmission clutch 107 to the on state before switching the even range transmission clutch 108 to the disengaged state, and after the odd range transmission clutch 107 switches to the on state, The transmission clutch 108 is switched to the disengaged state.

  When the transmission device A is switched from the third speed range to the second speed range, the control means 128 switches the second clutch 102 to the on state before switching the third clutch 103 to the disengaged state. After switching to the engaged state, the third clutch 103 is switched to the disconnected state. At this time, the control means 128 switches the even range transmission clutch 108 to the on state before switching the odd range transmission clutch 107 to the disengaged state, and after the even range transmission clutch 108 switches to the on state, The transmission clutch 107 is switched to the disengaged state.

  When the transmission device A is switched from the second speed range to the first speed range, the control means 128 switches the first clutch 101 to the on state before switching the second clutch 102 to the disengaged state. After switching to the engaged state, the second clutch 102 is switched to the disconnected state. At this time, the control means 128 switches the odd range transmission clutch 107 to the on state before switching the even range transmission clutch 108 to the disengaged state, and after the odd range transmission clutch 107 switches to the on state, The transmission clutch 108 is switched to the disengaged state.

  When the control unit 128 generates a double transmission state in which both the odd range transmission shaft 95 and the even range transmission shaft 96 are driven, the odd range transmission clutch 107 and the even range transmission clutch 108 are in a half transmission state. To operate. That is, even if torque fluctuation occurs in the double transmission state, the continuously variable transmission unit 20 absorbs the torque fluctuation due to the slippage of the hydraulic oil. In addition to this, the control means 128 causes the odd range transmission clutch 107 and the even range transmission clutch 108 to slip to absorb torque fluctuations.

  As shown in FIG. 1, the front wheel transmission 40 includes a standard gear transmission mechanism 45 having a standard transmission clutch 44 and a speed increasing transmission clutch 46 in addition to the input shaft 41 and the output shaft 42. A speed increasing gear transmission mechanism 47 is provided across the input shaft 41 and the output shaft 42.

  When the standard transmission clutch 44 is operated in the engaged state and the speed increasing transmission clutch 46 is operated in the disengaged state, the front wheel transmission 40 transmits the driving force of the input shaft 41 to the output shaft 42 by the standard gear transmission mechanism 45. It will be in the standard transmission state. Then, the front wheel transmission device 40 drives the left and right front wheels so that the average peripheral speed of the left and right front wheels is equal to the average peripheral speed of the left and right rear wheels.

  When the standard transmission clutch 44 is operated in the disengaged state and the speed increasing transmission clutch 46 is operated in the engaged state, the front wheel transmission 40 transmits the driving force of the input shaft 41 to the output shaft 47 by the speed increasing gear transmission mechanism 47. It will be in the state of speed increase transmission. Then, the front wheel transmission device 40 drives the left and right front wheels so that the average peripheral speed of the left and right front wheels is approximately twice the average peripheral speed of the left and right rear wheels.

  FIG. 9 is a diagram of a traveling transmission device for a tractor equipped with a transmission gear transmission A according to a second embodiment of the present invention.

  In the tractor traveling transmission device equipped with the transmission gear transmission A according to the second embodiment of the present invention, the output from the output shaft 30 as the output rotating body of the transmission transmission device A is transmitted via the forward / reverse switching device 10. This is transmitted to the wheel differential mechanism 32 and the front wheel transmission 40.

  As shown in FIGS. 9, 10, and 11, the forward / reverse switching device 10 is positioned on the input side rotator 13 that is integrally rotatable with the output shaft 30, and on the front and rear sides of the input side rotator 13. Over the output gears 19a, 19b, the forward friction clutch 14 provided across one end side of the input side rotator 13 and the front output gear 19a, and over the other end side of the input side rotator 13 and the rear output gear 19b. A reverse friction clutch 16 provided and a reverse gear 17 meshed with the rear output gear 19b are provided.

  The front output gear 19 a is interlocked with the input gear 31 of the rear wheel differential mechanism 32 and the input shaft 41 of the front wheel transmission 40 via a transmission gear 130 and a transmission shaft 131. The reverse gear 17 is linked to the input gear 31 of the rear wheel differential mechanism 32 and the input shaft 41 of the front wheel transmission 40 via the transmission gear 132 and the transmission shaft 131.

  When the transmission A according to the second embodiment is compared with the transmission A according to the first embodiment, the output of the continuously variable transmission 20 to which the engine driving force is input and the continuously variable transmission 20 The engine drive force not subjected to the speed change action is synthesized by the planetary transmission portion P, and the composite drive force from the planetary transmission portion P is changed by switching the first, second, third, and fourth clutches 101, 102, 103, and 104. It has the same configuration in that it is converted to a driving force in a four-stage speed range and is transmitted to the output shaft 30 as an output rotating body by two transmission shafts of an odd range transmission shaft 95 and an even range transmission shaft 96. And has a different configuration in terms of the planetary transmission portion P. This difference will be described.

  As shown in FIGS. 9 and 10, the planetary transmission unit P in the speed change transmission device A according to the second embodiment includes a first planetary transmission mechanism 140, a second planetary transmission mechanism 150, and a third planetary transmission mechanism 160. It is prepared.

  As shown in FIG. 10, the first planetary transmission mechanism 140, the second planetary transmission mechanism 150, and the third planetary transmission mechanism 160 include one sun gear 141, 151, 161, and a plurality of planetary gears 142, 152, 162. , Ring gears 143, 153, and 163 and carriers 144, 154, and 164 are provided.

  The sun gear 141 of the first planetary transmission mechanism 140 is interlocked with the motor shaft 23 of the continuously variable transmission 20 via the sun gear shaft 145, the gear 170, and the gear 171. The carrier 144 of the first planetary transmission mechanism 140, the ring gear 153 of the second planetary transmission mechanism 150, and the carrier 164 of the third planetary transmission mechanism 160 are interlocked so as to be rotatable together. The ring gear 143 of the first planetary transmission mechanism 140 and the carrier 154 of the second planetary transmission mechanism 150 are interlocked so as to be integrally rotatable, and can be integrally rotated to the pump shaft 22 of the continuously variable transmission unit 20 via the interlocking shaft 172. It is linked. The sun gear 151 of the second planetary transmission mechanism 150 and the sun gear 161 of the third planetary transmission mechanism 160 are interlocked so as to be integrally rotatable.

  The planetary transmission unit P includes a first output gear 81 that is linked to the carrier 144 of the first planetary transmission mechanism 140 so as to be integrally rotatable. The planetary transmission unit P is rotatable integrally with the sun gears 151 and 161 of the second and third planetary transmission mechanisms 150 and 160. The second output gear 82 and the fourth output gear 84 linked to each other, and the third output gear 83 linked to the ring gear 163 of the third planetary transmission mechanism 160 so as to be integrally rotatable.

  The planetary transmission unit P inputs the output from the motor shaft 23 of the continuously variable transmission unit 20 to the sun gear 141 of the first planetary transmission mechanism 140, and is continuously variable as an engine driving force that is not subjected to a shifting action by the continuously variable transmission unit 20. The driving force of the pump shaft 22 of the transmission unit 20 is input to the ring gear 143 of the first planetary transmission mechanism 140 and the carrier 154 of the second planetary transmission mechanism 150, and the input driving force of the continuously variable transmission unit 20 and the driving of the engine 1 are input. The force is combined by the first planetary gear mechanism 140, the second planetary transmission mechanism 150, and the third planetary transmission mechanism 160. The combined driving force is transmitted from the first output gear 81 to the first input gear 91 of the odd range transmission shaft 95, and from the second output gear 82 to the second input gear 92 of the even range transmission shaft 96, and the third output gear. 83 is transmitted to the third input gear 93 of the odd range transmission shaft 95, and is transmitted from the fourth output gear 84 to the fourth input gear 94 of the even range transmission shaft 96.

  The first output gear 81 and the first input gear 91 are interlocked with each other at a transmission ratio at which the rotational speed of the first input gear 91 is twice the rotational speed of the first output gear 81. The second output gear 82 and the second input gear 92 are interlocked with each other at a transmission ratio at which the rotational speed of the second input gear 92 is twice the rotational speed of the second output gear 82. The third output gear 83 and the third input gear 93 are interlocked with each other at a transmission ratio in which the rotation speed of the third input gear 93 is ½ of the rotation speed of the third output gear 83. The fourth output gear 84 and the fourth input gear 94 are interlocked with each other at a transmission ratio in which the rotation speed of the fourth input gear 94 is ½ of the rotation speed of the fourth output gear 84. The output gear 107b of the odd number range transmission clutch 107 and the passive gear 173 of the output shaft 30 are interlocked with each other at a transmission ratio in which the rotational speed of the output shaft 30 is ½ of the rotational speed of the output gear 107b. The output gear 108b of the even range transmission clutch 108 and the passive gear 174 of the output shaft 30 are interlocked with each other at a transmission ratio in which the rotational speed of the output shaft 30 is ½ of the rotational speed of the output gear 108b.

As a result, the driving force of the third output gear 83 is transmitted to the output shaft 30 by decelerating it to 1/4 of the rotational speed, and between the third output gear 83 and the odd range transmission shaft 95, the output gear 107b. And the output shaft 30 are divided into two portions and decelerated. In order to transmit the driving force of the fourth output gear 84 to the output shaft 30 by decelerating to 1/4 of the number of revolutions, the fourth output gear 84 and the even range transmission shaft 96, the output gear 108b and the output shaft It will be decelerated in two places between 30. Then, 1/4 speed reduction can be performed while reducing the size of the speed range setting unit 90.

  FIG. 12 is a diagram of a traveling transmission device for a tractor equipped with a transmission gear transmission A according to a third embodiment of the present invention.

  In the tractor traveling transmission device equipped with the transmission gear transmission A according to the third embodiment of the present invention, the output from the output shaft 30 as the output rotating body of the transmission transmission device A is transmitted via the forward / reverse switching device 10. This is transmitted to the wheel differential mechanism 32 and the front wheel transmission 40.

  As shown in FIGS. 12, 13, and 14, the forward / reverse switching device 10 in the traveling transmission device equipped with the transmission transmission A according to the third embodiment is the transmission transmission A according to the second embodiment. Is provided with the same configuration as the forward / reverse switching device 10 in the traveling transmission device.

  When the transmission A according to the third embodiment is compared with the transmission A according to the first embodiment, the output of the continuously variable transmission 20 to which the engine driving force is input and the continuously variable transmission 20 The engine drive force not subjected to the speed change action is synthesized by the planetary transmission portion P, and the composite drive force from the planetary transmission portion P is changed by switching the first, second, third, and fourth clutches 101, 102, 103, and 104. It has the same configuration in that it is converted to a driving force in a four-stage speed range and is transmitted to the output shaft 30 as an output rotating body by two transmission shafts of an odd range transmission shaft 95 and an even range transmission shaft 96. In this respect, the planetary transmission unit P and the speed range setting unit 90 have different configurations.

  As shown in FIGS. 12 and 13, the planetary transmission portion P in the transmission transmission A according to the third embodiment has the same configuration as the planetary transmission portion P in the transmission transmission A according to the second embodiment. Yes.

  As shown in FIGS. 12 and 13, the speed range setting unit 90 in the transmission transmission A according to the third embodiment and the speed range setting unit 90 in the transmission transmission A according to the first embodiment are odd numbers. This is the same in that the range transmission shaft 95 and the even range transmission shaft 96 are arranged in parallel in parallel.

  The speed range setting unit 90 in the speed change transmission device A according to the third embodiment and the speed range setting portion 90 in the speed change transmission device A according to the first embodiment include an odd range transmission shaft 95 and a planetary transmission portion P. The first input gear 91 meshed with the first output gear 81 and the third input gear 93 meshed with the third output gear 83 of the planetary transmission portion P are freely rotatable, and the even range transmission shaft 96 is And a third input gear 93 meshed with the second output gear 83 of the planetary transmission portion P and a fourth input gear 94 meshed with the fourth output gear 84 of the planetary transmission portion P, which are freely rotatable. The driving force of one input gear 91 is transmitted to the odd range transmission shaft 95 by the first clutch 101, the driving force of the second input gear 92 is transmitted to the even range transmission shaft 96 by the second clutch 102, and the third input gear 93 is transmitted. The driving force of the third clutch 103 In that transmitted to the number range transmission shaft 95, transmitting the driving force of the fourth input gear 94 by the fourth clutch 104 to the even-range transmission shaft 96 have the same configuration.

In the speed range setting unit 90 in the speed change transmission device A according to the third embodiment, an output gear 95a in which the driving force of the odd range transmission shaft 95 is rotatably provided integrally with the rear end portion of the odd range transmission shaft 95; This is transmitted to the output shaft 30 via an input gear 30a that is rotatably provided integrally with the front end portion of the output shaft 30 while being engaged with the output gear 95a. The output shaft 30 is connected to the drive force of the even-range transmission shaft 96 via an output gear 96a that is provided so as to be rotatable integrally with the rear end portion of the even-range transmission shaft 96 and the input gear 30a meshed with the output gear 96a. To communicate.
The output gear 95a of the odd range transmission shaft 95 and the output gear 96a of the even range transmission shaft 96 are engaged with the same input gear 30a when transmitting to the output shaft 30, and this transmission structure includes a speed range setting unit 90. Keep the size in the front-rear direction small.

In the speed range setting unit 90 in the transmission A according to the third embodiment, the first clutch 101, the second clutch 102, the third clutch 103, and the fourth clutch 104 are connected to the input gears 91, 92, 93, 94. A clutch disk provided so as to be integrally rotatable, a clutch disk provided so as to be integrally rotatable and slidable on the odd range transmission shaft 95 or the even range transmission shaft 96, and hydraulic pistons 101b, 102b, 103b, 104b. It is a good clutch.
That is, when the hydraulic pistons 101b, 102b, 103b, and 104b press and operate both clutch disks, the clutch disks interlock with each other by engagement of clutch protrusions provided on side surfaces facing each other.

  The speed range setting unit 90 of the third embodiment includes a clutch of the odd range transmission shaft 95 (first clutch 101, third clutch 103) and a clutch of the even range transmission shaft 96 (second clutch 102, fourth clutch 104). ) In the first clutch 101, the third clutch 103, the second clutch 102, and the fourth clutch 104, the hydraulic pistons 101b, 102b, 103b, 104b Due to the pressure oil acting on the clutch, slip occurs between both clutch discs and absorbs torque fluctuations in the double transmission state. As a result, the speed range setting unit 90 of the third embodiment includes the odd range transmission clutch 107 and the even range transmission clutch 108 employed in the speed range setting unit 90 of the first embodiment and the second embodiment. Is omitted, and the transmission efficiency is increased and the speed range setting unit 90 is made compact.

  FIG. 15 is a diagram of a traveling transmission device for a tractor equipped with a transmission gear transmission A according to a fourth embodiment of the present invention. When the transmission gear transmission A according to the fourth embodiment is compared with the transmission transmission device A according to the first embodiment, the planetary transmission section P and the speed range setting section 90 have the same configuration, and are continuously variable. In the configuration for inputting a variable driving force, the transmission A according to the fourth embodiment is different from the transmission A according to the first embodiment. This difference will be described next.

  The transmission device A according to the fourth embodiment includes an electric motor 180. The planetary transmission unit P inputs the output from the output shaft 180 a of the electric motor 180 to the sun gear 62 of the upper planetary mechanism 60 through the transmission gear 181, the transmission gear 182, and the sun gear shaft 61. The planetary transmission unit P inputs the output from the output shaft 1 a of the engine 1 to the ring gear 65 of the upper planetary mechanism 60 via the main clutch 2, the forward / reverse switching device 10 and the gear 67. The planetary transmission unit P inputs and combines the driving force of the engine 1 and the driving force of the electric motor 180, and combines this combined driving force from the first output gear 81 and the third output gear 83 of the speed range setting unit 90. Transmission to the odd range transmission shaft 95 and transmission from the second output gear 82 and the fourth output gear 84 to the even range transmission shaft 96 of the speed range setting unit 90.

  The electric motor 180 changes the drive rotational speed steplessly by a speed change operation by the driver 183. The electric motor 180 is shifted, and the first, second, third, and fourth clutches 101, 102, 103, and 104, the odd range transmission clutch 107, and the even range transmission clutch 108 are switched in accordance with the shifting operation. By operating, the output shaft 30 is divided into four speed ranges from the first speed range to the fourth speed range, and infinitely in each speed range, as in the transmission A according to the first embodiment. It is driven with a shift.

[Another Example]
In place of the above-described embodiments, the odd-range transmission shaft 95 is divided into a transmission shaft that includes the first clutch 101 and is linked to the output shaft 30, and a transmission shaft that includes the third clutch 103 and is linked to the output shaft 30. The even-range transmission shaft 96 is divided into a transmission shaft that includes the second clutch 102 and that is linked to the output shaft 30, and a transmission shaft that includes the fourth clutch 104 and that is linked to the output shaft 30. And you may implement by providing the structure which has arrange | positioned each transmission shaft in parallel in parallel. In addition, the transmission shaft includes one transmission shaft having the first clutch 101 and the second clutch 102, and one transmission shaft having the third clutch 103 and the fourth clutch 104, and both the transmission shafts are arranged in parallel. Alternatively, a parallel arrangement may be adopted. In either case, the object of the present invention can be achieved.

20 continuously variable transmission 30 output rotor 60, 70, 140, 150, 160 planetary transmission mechanism 62, 72 sun gear 95, 96 transmission shaft 101, 102, 103, 104 speed setting clutch 180 electric motor P planetary transmission unit

  The present invention includes a continuously variable transmission unit or an electric motor to which an engine driving force is input, and outputs an output of the continuously variable transmission unit and an engine driving force not subjected to a shifting action by the continuously variable transmission unit, or the electric motor. The planetary transmission unit that combines the output of the engine and the engine driving force by a plurality of planetary transmission mechanisms, the combined driving force from the planetary transmission unit is divided into a plurality of speed ranges, The present invention relates to a speed change transmission device configured to change continuously and output from an output rotating body.

The above-described shift transmission device performs a shift operation of the continuously variable transmission unit or the electric motor, thereby combining the driving force of the engine output and the output of the continuously variable transmission unit, or the combination of the engine output and the output of the electric motor. The driving force is divided into multiple speed ranges, and the driving force that is steplessly shifted in each speed range is output. If used for driving the traveling device, the shifting can be performed smoothly and the shifting operation can be performed easily. It can be transmitted.
As this type of transmission, a device described in Patent Document 1 was first developed.
Patent Document 1 describes three types of transmission gears. In one of the three types of transmission gears (the one described in FIG. 2 of Patent Document 1), a continuously variable transmission (corresponding to a continuously variable transmission unit), a planetary transmission unit, a clutch unit, and a third planetary transmission mechanism And a brake acting on the third planetary transmission mechanism.

  The continuously variable transmission includes a variable displacement hydraulic pump whose pump shaft is linked to an output shaft of an engine via a main clutch, and a hydraulic motor driven by pressure oil from the hydraulic pump.

  The planetary transmission unit includes a first planetary transmission mechanism and a second planetary transmission mechanism. The planetary gear of the first planetary transmission mechanism and the planetary gear of the second planetary transmission mechanism are interlocked by meshing of interlocking gear portions provided in each planetary gear. The planetary gear of the first planetary transmission mechanism and the planetary gear of the second planetary transmission mechanism are supported by a carrier common to the first planetary transmission mechanism and the second planetary transmission mechanism.

  The clutch unit includes a first clutch, a second clutch, a third clutch, and a fourth clutch. The input side rotation member of the first clutch is interlocked with the ring gear of the second planetary transmission mechanism via the interlock mechanism. The input side rotation member of the second clutch is interlocked with the sun gear of the second planetary transmission mechanism via the rotation shaft. The input side rotating member of the third clutch is interlocked with the carrier of the planetary transmission unit via an interlocking mechanism.

  The interlocking mechanism that interlocks the input-side rotating member of the first clutch and the ring gear of the second planetary transmission mechanism includes a clutch-side transmission gear that meshes with the input-side rotating member of the first clutch, and the second planetary transmission mechanism. A planetary transmission gear meshed with a ring gear; and a rotary shaft connected to the clutch transmission gear and the planetary transmission gear. The interlocking mechanism that interlocks the input side rotation member of the third clutch and the carrier of the planetary transmission unit includes a clutch side transmission gear that meshes with the input side rotation member of the third clutch, and a planetary side transmission that meshes with the carrier. A gear, and a rotary shaft connected to the clutch side transmission gear and the planetary side transmission gear.

  The sun gear of the third planetary transmission mechanism is interlocked with the output side rotation member of the first clutch and the second clutch and the input side rotation member of the third clutch. The carrier of the third planetary transmission mechanism is interlocked with output side rotating members of the third clutch and the fourth clutch.

  The brake can be switched between an on state where the braking action is applied to the ring gear of the third planetary transmission mechanism and a cut state where the braking action on the ring gear is released.

  2, the output of the continuously variable transmission and the driving force of the pump shaft of the continuously variable transmission (the engine driving force that is not subjected to the shifting action by the continuously variable transmission) are provided. Synthesized by planetary transmission unit. Synthetic drive output from the planetary transmission unit when the continuously variable transmission is operated for shifting, and the first to fourth clutches and the brake are appropriately switched between the engaged state and the disengaged state in conjunction with the shifting operation. The force is stepped from the first speed range to the fourth speed range and continuously variable in each speed range, and output from the carrier shaft of the third planetary transmission mechanism.

  Another one of the three types of transmission gears described in Patent Document 1 (described in FIG. 12 of Patent Document 1) and another one (described in FIG. 16 of Patent Document 1) In the present invention, a continuously variable transmission (corresponding to a continuously variable transmission), a planetary transmission unit, a clutch unit, and an auxiliary transmission are provided.

  The continuously variable transmission and the planetary transmission unit have the same configuration as the continuously variable transmission and planetary transmission unit of the transmission described in FIG.

  The clutch unit includes a first clutch and a second clutch. The input side rotation member of the first clutch is linked to the ring gear of the second planetary transmission mechanism of the planetary transmission unit via the linkage mechanism. The interlocking mechanism includes a planetary transmission gear meshed with the ring gear of the second planetary transmission mechanism, a clutch transmission gear meshed with the gear portion of the input side rotating member of the first clutch, the planetary transmission gear, and the clutch transmission. A rotation interlocking shaft connected to the gear.

  The auxiliary transmission includes a high speed clutch and a low speed clutch. In the auxiliary transmission device described in FIG. 16 of Patent Document 1, the high speed clutch and the low speed clutch are meshing clutches.

  12 and FIG. 16 of the cited document 1, the output of the continuously variable transmission and the driving force of the pump shaft of the continuously variable transmission (the engine drive that is not subjected to the shifting action by the continuously variable transmission). Force) is synthesized by the planetary transmission unit. When the continuously variable transmission is operated to change gears, the first clutch, the second clutch, the high-speed clutch, and the low-speed clutch are appropriately switched between the on-state and the off-state according to the speed-change operation. The composite driving force to be output is divided into stages from the first speed range to the fourth speed range, and continuously variable in each speed range and output from the output shaft of the auxiliary transmission.

JP 2007-92949 A

  In the case of the speed change transmission device adopting the above-described conventional technology, the first to fourth clutches provided to divide the combined driving force from the planetary transmission unit into a plurality of speed ranges and transmit it to the output rotating body, or The first, second clutch, high speed, and low speed clutch are arranged in the front-rear direction of the transmission case, and the size of the transmission in the front-rear direction of the transmission case tends to increase.

  An object of the present invention is to provide a speed change transmission device that can be obtained in a compact manner while an output with a stepless change in speed over a wide speed change range can be obtained only by performing a simple speed change operation.

The first invention includes a continuously variable transmission unit or an electric motor to which engine driving force is input,
A planetary transmission unit configured to combine an output of the continuously variable transmission unit and an engine driving force not subjected to a shifting action by the continuously variable transmission unit, or an output of the electric motor and an engine driving force by a plurality of planetary transmission mechanisms; ,
In the transmission device configured to divide the combined driving force from the planetary transmission unit into a plurality of speed ranges, and to change the speed steplessly in each step speed range and output from the output rotating body,
As an output gear that outputs a combined driving force from the planetary transmission unit, a first output gear and another output gear different from the first output gear are provided concentrically with the sun gear of the planetary transmission mechanism,
Two transmissions that switch the output gear that outputs the combined driving force from the planetary transmission unit by switching a plurality of speed range setting clutches , convert the output gear to the driving force of the plurality of speed ranges, and transmit it to the output rotating body With a shaft,
A transmission gear meshing with an output gear provided on each of the two transmission shafts is provided in the output rotating body so as to be integrally rotatable,
The two transmission shafts are arranged in parallel and in parallel.

  According to the configuration of the first aspect of the present invention, when the plurality of speed range setting clutches are appropriately switched in accordance with the speed change operation of the continuously variable transmission unit or the electric motor, the combined driving force from the planetary transmission unit is a speed range of a plurality of stages. The speed is steplessly changed at each speed range and transmitted to the output rotating body.

According to the construction of the first invention, it comprises two transmission shafts so as to perform the transmission shaft corresponding to transmission from the planetary transmission section to the output rotary member in the speed range of the transmission, two a transmission shaft parallel Since the transmission parts are arranged in parallel and in parallel, the size of the transmission portion in the longitudinal direction of the transmission case can be made smaller than the size of the conventional transmission gear transmission.

  Therefore, if a simple shift operation is performed by simply shifting the continuously variable transmission unit or the electric motor, an output that changes steplessly over a wide shift range can be obtained. Thus, a shift transmission device that is easy to use, such as being easily mounted on a small vehicle, can be obtained.

In the second aspect of the invention, the planetary transmission unit includes a pair of planetary transmission mechanisms in which planetary gears mesh with each other, and the plurality of transmission shafts are arranged in parallel over the entire length.

According to the configuration of the second aspect of the invention, since the plurality of transmission shafts are arranged in parallel over the entire length, the output transmission from the planetary transmission unit is rotated as compared with the case where the plurality of transmission shafts are arranged in parallel in a state shifted in the longitudinal direction of the transmission case. The length of the transmission part to the body in the front-rear direction of the mission case can be reduced.

  Accordingly, it is possible to obtain a transmission device that is easy to use, such as being more compact and easier to design in terms of the size of the transmission portion from the planetary transmission portion to the output rotor in the longitudinal direction of the transmission case.

In the third aspect of the invention , the second output gear, the third output gear, and the fourth output gear are provided as another output gear that outputs the combined driving force from the planetary transmission unit.
A first input gear meshing with the first output gear and a third input gear meshing with the third output gear are supported on one of the two transmission shafts,
A second input gear meshing with the second output gear and a fourth input gear meshing with the fourth output gear are supported on the other of the two transmission shafts,
Ri clutch der meshing said plurality of speed range setting clutch,
As the speed range setting clutch, one speed range setting clutch arranged corresponding to one of the two transmission shafts and the other speed range setting arranged corresponding to the other of the two transmission shafts With a clutch,
The one speed range setting clutch includes a first engaged state in which the first input gear and one of the two transmission shafts are integrally rotated, and the first input gear and one of the two transmission shafts. Of the third input gear and the two transmission shafts, a first cut-off state in which the third input gear and one of the two transmission shafts are integrally rotated, Is switchable to a third cut-off state in which one of them is relatively rotated,
The other speed range setting clutch includes a second engagement state in which the second input gear and the other of the two transmission shafts are integrally rotated, and the second input gear and the other of the two transmission shafts. Of the fourth input gear and the two transmission shafts, a second cutting state in which the fourth input gear and the other of the two transmission shafts are integrally rotated, It is possible to switch to a fourth cutting state in which the other is relatively rotated.

According to the configuration of the third invention, since the speed range setting clutch is a meshing clutch, the speed range setting clutch can be obtained lighter and more compact than when a friction clutch is employed as the speed range setting clutch.

  Therefore, the speed range setting clutch is light and inexpensive in terms of the weight and size of the speed range setting clutch, and it is possible to obtain a speed change transmission device that is easy to use from the viewpoint of weight and cost.

Diagram of traveling transmission device of tractor equipped with the transmission device of the first embodiment Sectional view of planetary transmission section, speed range setting section, odd range transmission clutch and even range transmission clutch Planetary gear layout Shaft layout of the transmission Explanatory drawing of action state of speed range setting part Explanatory drawing which shows the relationship between the speed change state of a continuously variable transmission part, the output speed of a gear transmission, and a speed range. Explanatory drawing of clutch operating state by control means at the time of speed range switching Block diagram of operating device Diagram of a traveling transmission device for a tractor equipped with the speed change transmission device of the second embodiment Sectional drawing of the planetary transmission part and speed range setting part of the speed change transmission apparatus of 2nd Example Sectional drawing of the forward / reverse switching device of the traveling transmission device equipped with the speed change transmission device of the second embodiment. Diagram of traveling transmission device of tractor equipped with transmission gearing device of third embodiment Sectional drawing of the planetary transmission part and speed range setting part of the speed change transmission apparatus of 3rd Example Sectional drawing of the forward / reverse switching device of the traveling transmission equipped with the transmission of the third embodiment. Diagram of the driving transmission equipped with the transmission gear of the fourth embodiment

Embodiments of the present invention will be described below with reference to the drawings.
FIG. 1 is a diagram of a traveling transmission device for a tractor equipped with a transmission gear transmission A according to a first embodiment of the present invention. As shown in this figure, the tractor travel transmission device includes a main clutch 2 for inputting an output from an output shaft 1a of the engine 1, and a forward / reverse switching device 10 for inputting an output of the main clutch 2 by an input shaft 11. The transmission gear A according to the first embodiment of the present invention in which the input shaft 22 is interlocked with the output gear 12 of the forward / reverse switching device 10 via the gear 21, and the output rotating body of the transmission gear A. A rear wheel differential mechanism 32 in which an input gear 31 is connected to a rear end portion of the output shaft 30 so as to be integrally rotatable, and an input shaft 41 is integrally rotatable to a front end portion of the output shaft 30 via a joint 33. And a front wheel differential mechanism 35 to which an output from the output shaft 42 of the front wheel transmission 40 is input via the rotation transmission shaft 34.

  The forward / reverse switching device 10, the transmission device A, the rear wheel differential mechanism 32, and the front wheel transmission device 40 are accommodated in the same mission case 36.

  As shown in FIG. 1, a power take-out shaft 37 protruding rearward from the mission case 36 transmits driving force to various working devices such as a rotary tiller connected to the tractor. The power take-out shaft 37 is interlocked with the input shaft 11 of the forward / reverse switching device 10 via an interlocking shaft 38 and a work clutch 39.

  As shown in FIG. 1, the forward / reverse switching device 10 includes the input shaft 11 and the output gear 12, an input-side rotating body 13 provided on the input shaft 11 so as to be integrally rotatable, A multi-plate forward friction clutch 14 provided across one end of the rotating body 13 and the output gear 12 is provided. The forward / reverse switching device 10 further includes a transmission gear 15 that is positioned on the opposite side of the output gear 12 with respect to the input-side rotator 13 and is supported on the input shaft 11 so as to be relatively rotatable. A multi-plate reverse friction clutch 16 provided over the gear 15 and the other end of the input side rotating body 13, a reverse gear 17 meshed with the transmission gear 15, and the reverse gear 17 are linked to the output gear 12. The interlocking shaft 18 is provided.

  In the forward / reverse switching device 10, operating hydraulic pressure is supplied to the forward piston of the forward piston and the backward piston provided in the input side rotator 13, and the forward piston pressurizes the forward friction clutch 14 into the engaged state. By operating it, it will be in the forward state, and the hydraulic pressure will be supplied to the reverse piston, and the reverse piston will be in the reverse state by pressurizing the reverse friction clutch 16 into the engaged state.

  When the forward / reverse switching device 10 is in the forward movement state, the driving force of the input shaft 11 is converted into the forward driving force by the input side rotating body 13, the forward friction clutch 14, and the output gear 12, and the continuously variable transmission unit is converted from the output gear 12. 20 and the planetary transmission part P. When the forward / reverse switching device 10 enters the reverse state, the drive force of the input shaft 11 is converted into the reverse drive force by the input side rotating body 13, the reverse friction clutch 16, the transmission gear 15, the reverse gear 17, and the transmission shaft 18. The power is transmitted to the output gear 12 and is output from the output gear 12 to the continuously variable transmission 20 and the planetary transmission unit P.

  As shown in FIG. 1, a transmission A according to a first embodiment of the present invention includes the input shaft 22 and the output shaft 30, the continuously variable transmission unit 20, and the continuously variable transmission unit 20. The first input gear 91 meshes with the planetary transmission portion P in which the sun gear shaft 61 is interlocked with the motor shaft 23 via the gear 50 and the gear 51, and the first output gear 81 of the planetary transmission portion P. The speed range setting unit 90 is provided.

  As shown in FIG. 1, the continuously variable transmission 20 includes an axial plunger type and variable displacement type hydraulic pump 24 having the input shaft 22 as a pump shaft (hereinafter, the input shaft is referred to as a pump shaft 22). And an axial plunger type hydraulic motor 25 driven by the pressure oil from the hydraulic pump 24. The hydraulic motor 25 includes the motor shaft 23.

  That is, the continuously variable transmission unit 20 is a hydrostatic continuously variable transmission unit, and is changed into a forward rotation transmission state, a neutral state, and a reverse rotation transmission state by changing the swash plate angle of the hydraulic pump 24. Switch. The continuously variable transmission unit 20 changes the swash plate angle of the hydraulic pump 24 in the forward rotation transmission state, thereby transferring the engine driving force transmitted to the pump shaft 22 via the forward / reverse switching device 10 in the forward rotation direction. It is converted into a driving force and is steplessly shifted and output from the motor shaft 23. The continuously variable transmission unit 20 changes the swash plate angle of the hydraulic pump 24 in the reverse rotation transmission state, thereby transferring the engine driving force transmitted to the pump shaft 22 via the forward / reverse switching device 10 in the reverse rotation direction. It is converted into a driving force and is steplessly shifted and output from the motor shaft 23. The continuously variable transmission 20 stops the output from the motor shaft 23 in the neutral state.

  FIG. 2 shows a cross-sectional structure of the planetary transmission portion P. As shown in FIG. 1 and FIG. 1, the planetary transmission unit P transmits a driving force input from the continuously variable transmission unit 20 and the forward / reverse switching device 10 to the speed range setting unit 90. And a planetary transmission mechanism 60 (hereinafter abbreviated as the upper planetary mechanism 60) positioned on the upper side and a planetary transmission mechanism 70 (hereinafter abbreviated as the lower planetary mechanism 70) positioned on the lower side. It is configured.

  The upper planetary mechanism 60 is provided with a sun gear 62 provided at one end of the sun gear shaft 61 so as to be rotatable together with the sun gear 62, and is distributed in the circumferential direction of the sun gear 62 on the outer peripheral side of the sun gear 62 and meshed with the sun gear 62. Three planetary gears 63, a carrier 64 that freely supports the three planetary gears 63, and a ring gear 65 that meshes with the three planetary gears 63 are provided. The sun gear 62 and the sun gear shaft 61 are integrally formed.

  The lower planetary mechanism 70 includes a sun gear 72 that is rotatably positioned around the same axis as the sun gear 62 on the lower side in the transmission direction of the sun gear 62 of the upper planetary mechanism 60, and a sun gear 72 on the outer peripheral side of the sun gear 72. Three planetary gears 73 that are distributed in the circumferential direction and meshed with the sun gear 72, a carrier 64 that supports the three planetary gears 73 in a freely rotating manner, and meshed with the three planetary gears 73. Ring gear 75.

  FIG. 3 is an arrangement view of the planetary gear 63 of the upper planetary mechanism 60 and the planetary gear 73 of the lower planetary mechanism 70. As shown in FIG. 2 and FIG. 2, the three planetary gears 63 of the upper planetary mechanism 60 and the three planetary gears 73 of the lower planetary mechanism 70 are combined with one planetary gear 63 of the upper planetary mechanism 60. One planetary gear 73 of the lower planetary mechanism 70 forms one gear pair that faces the circumferential direction of the sun gears 62, 72, and the other planetary gear 63 of the upper planetary mechanism 60 and the other planetary mechanism 70. One planetary gear 73 forms one gear pair that faces the circumferential direction of the sun gears 62, 72, and the remaining planetary gear 63 of the upper planetary mechanism 60 and the remaining planetary gear 73 of the lower planetary mechanism 70 In this arrangement, the sun gears 62 and 72 are arranged in a pair of gears close to each other in the circumferential direction. The planetary gear 63 of the upper planetary mechanism 60 and the planetary gear 73 of the lower planetary mechanism 70 in each gear pair are the ends of the planetary gears 63 and 73 opposite to the side meshed with the sun gears 62 and 72. Interlocking with each other.

  In two adjacent gear pairs, the tooth tip portions of the planetary gears 63 and 73 of one gear pair are inserted between the tooth tip portions of the planetary gears 63 and 73 of the other gear pair. However, in the two adjacent gear pairs, the planetary gears 63 and 73 of one gear pair and the planetary gears 63 and 73 of the other gear pair are not interlocked. By adopting an arrangement in which the tooth tip portions of the planetary gears 63 and 73 are inserted between the tooth tip portions in this way, the sun gears 62 and 72 and the ring gear 65, The diameter of 75 can be suppressed small, and the planetary transmission part P can be obtained in a compact state with a small outer diameter.

  As shown in FIG. 3, the planetary gear 63 of the upper planetary mechanism 60 is rotatably supported by the support shaft 64a of the carrier 64, and the planetary gear 73 of the lower planetary mechanism 70 rotates about the support shaft 64b of the carrier 64. It is supported freely. That is, the carrier 64 is a carrier common to the upper planetary mechanism 60 and the lower planetary mechanism 70. That is, the carrier 64 revolves around the sun gear 62 while rotating while the planetary gears 63 of the upper planetary mechanism 60 mesh with the planetary gears 73 of the lower planetary mechanism 70 forming a gear pair with the carrier planetary mechanism 70. Each planetary gear 73 supports the planetary gears 63 and 73 so as to revolve around the sun gear 72 while rotating with the planetary gear 63 of the upper planetary mechanism 60 forming a gear pair with the planetary gear 73.

  The ring gear 65 of the upper planetary mechanism 60 is connected to an interlocking member 66 that is connected to the ring gear 65 so as to be integrally rotatable, and is connected to the end of the interlocking member 66 so as to be integrally rotatable by spline engagement. The output gear 12 is linked to the output gear 12 through a transmission gear 67 configured to mesh with the output gear 12. The ring gear 65 and the interlocking member 66 are integrally formed. The sun gear 62 of the upper planetary mechanism 60 is linked to the motor shaft 23 of the continuously variable transmission 20 via the sun gear shaft 61, the gear 51, and the gear 50.

  The planetary transmission portion P includes the first output gear 81, and also includes a second output gear 82 and a third output gear 83 that are positioned side by side in the longitudinal direction of the transmission case on the rear side of the transmission case with respect to the first output gear 81. And a fourth output gear 84.

  The first output gear 81 is linked to the ring gear 75 of the lower planetary mechanism 70 so as to be integrally rotatable via an interlocking member 76 whose one end is connected to the first output gear 81 by spline engagement. . The interlocking member 76 and the ring gear 75 are integrally formed.

  A rotation support shaft 85 that supports the second output gear 82 and the fourth output gear 84 so as to rotate together and a sun gear shaft 71 that supports the sun gear 72 of the lower planetary mechanism 70 so as to rotate together are formed by spline engagement. They are connected so that they can rotate together. As a result, the second output gear 82 and the fourth output gear 84 are integrally rotated and interlocked with the sun gear 72 of the lower planetary mechanism 70 so as to be integrally rotatable.

  The third output gear 83 is connected to the other end of a rotating shaft 86, one end of which is connected to the carrier 64 so as to be integrally rotatable by spline engagement. Thus, the third output gear 83 is connected to the carrier 64 via the rotary shaft 86 so as to be integrally rotatable.

  That is, the planetary transmission unit P inputs the output from the motor shaft 23 of the continuously variable transmission unit 20 to which the engine driving force is input to the sun gear 62 of the upper planetary mechanism 60 through the gear 50, the gear 51, and the sun gear shaft 61. The driving force of the output gear 12 of the forward / reverse switching device 10 as the engine driving force that is not subjected to the shifting action by the continuously variable transmission unit 20 is input to the ring gear 65 of the upper planetary mechanism 60 by the gear 67 and the interlocking member 66, The output of the transmission unit 20 and the engine driving force that is not subjected to the shifting action of the continuously variable transmission unit 20 are combined by the upper planetary mechanism 60 and the lower planetary mechanism 70, and the combined driving force is first, second, third, Output from the fourth output gears 81, 82, 83, 84 to the speed range setting unit 90.

  FIG. 2 shows a cross-sectional structure of the speed range setting unit 90. As shown in FIG. 1 and FIG. 1, the speed range setting unit 90 includes the first input gear 91, the second output gear 82, the third output gear 83, and the fourth output gear 84. Are provided with a second input gear 92, a third input gear 93, and a fourth input gear 94, and a transmission shaft that supports the first input gear 91 and the third input gear 93 in a relatively rotatable manner. And an even range transmission shaft 96 as a transmission shaft for supporting the second input gear 92 and the fourth input gear 94 in a relatively rotatable manner.

  FIG. 4 is a layout diagram of each axis in the cross section of the transmission gearbox A. As shown in FIG. 2 and FIG. 2, the odd-range transmission shaft 95 and the even-range transmission shaft 96 are arranged in parallel with each other in the vertical direction of the transmission case 36 over the entire length and in parallel with each other. Thus, the size of the speed range setting unit 90 in the front-rear direction of the mission case is reduced.

  The odd range transmission shaft 95 includes a first clutch 101 provided across the transmission cylinder portion 91a and the odd range transmission shaft 95 of the first input gear 91, and an odd range transmission of the transmission cylinder portion 93a of the third input gear 93. A third clutch 103 provided across the shaft 95 and an odd range transmission clutch 107 provided at the end of the odd range transmission shaft 95 opposite to the end where the first input gear 91 is located are provided.

  The even range transmission shaft 96 includes a second clutch 102 provided across one side portion of the second input gear 92 and the even range transmission shaft 96, and one side portion of the fourth input gear 94 and the even range transmission shaft 96. And an even range transmission clutch 108 provided at the end of the even range transmission shaft 96 opposite to the end where the second input gear 92 is located.

  FIG. 2 shows a sectional structure of the first clutch 101, the second clutch 102, the third clutch 103, and the fourth clutch 104. As shown in this figure, the first clutch 101, the second clutch 102, the third clutch 103, and the fourth clutch 104 are provided with holders 105a and 106a attached to an odd range transmission shaft 95 or an even range transmission shaft 96. Shift gears 105 and 106 supported so as to be integrally rotatable and freely slidable via the transmission cylinder portions 91a and 93a or gears 101a, 102a and 103a of the corresponding input gears 91, 92, 93 and 94. , 104a, and is a meshing clutch.

  That is, the first clutch 101, the second clutch 102, the third clutch 103, and the fourth clutch 104 are coupled to the shift gears 105 and 106 via a shifter and are provided with hydraulic pistons 111 and 112 provided outside the transmission case 36. , And the shift gears 105 and 106 are slid with respect to the holders 105a and 106a to engage the holders 105a and 106a with the gears 101a, 102a, 103a, and 104a, whereby the input gears 91, 92, 93, The driving force 94 is transmitted to the odd range transmission shaft 95 or the even range transmission shaft 96 via the shift gears 105 and 106 and the holders 105a and 106a, and the input gears 91 and 93 and the odd range transmission shaft 95 are input. Gears 92 and 94 and even range transmission shaft 96 are integrated. A state enters so as to.

  The first clutch 101, the second clutch 102, the third clutch 103, and the fourth clutch 104 are disengaged from the gears 101a, 102a, 103a, 104a when the shift gears 105, 106 are slid with respect to the holders 105a, 106a. As a result, the input gears 91 and 93 and the odd range transmission shaft 95 are turned or the input gears 92 and 94 and the even range transmission shaft 96 are rotated relative to each other.

  FIG. 2 shows a cross-sectional structure of the odd range transmission clutch 107 and the even range transmission clutch 108. As shown in this figure, the odd range transmission clutch 107 and the even range transmission clutch 108 are input side rotating members 107a, 108a provided on the odd range transmission shaft 95 or the even range transmission shaft 96 so as to be integrally rotatable, The output gears 107b and 108b provided to be rotatable relative to the odd range transmission shaft 95 or the even range transmission shaft 96, and a multi-plate type provided over one side of the output gears 107b and 108b and the input side rotation members 107a and 108a. The friction clutch main bodies 107c and 108c are configured as friction clutches.

  The output gear 107b of the odd-number range transmission clutch 107 is interlocked with the output shaft 30 via a transmission gear 109 that is configured to mesh with the output gear 107b and is integrally rotatable with the output shaft 30. . The output gear 108 b of the even range transmission clutch 108 meshes with the transmission gear 109, and is linked to the output shaft 30 via the transmission gear 109.

  That is, the odd range transmission clutch 107 and the even range transmission clutch 108 are supplied with operating hydraulic pressure from the operating oil passages 116 and 117 to the hydraulic pistons 114 and 115 slidably provided inside the input side rotating members 107a and 108a. Then, the hydraulic pistons 114 and 115 pressurize the friction clutch bodies 107c and 108c into the engaged state, so that the input side rotation members 107a and 108a and the output gears 107b and 108b can be integrally rotated by the friction clutch bodies 107c and 108c. It enters the state to be interlocked. In the odd range transmission clutch 107 and the even range transmission clutch 108, the operating oil pressure is discharged from the hydraulic pistons 114 and 115, and the pressurizing operation of the friction clutch bodies 107c and 108c by the hydraulic pistons 114 and 115 is released, and the friction clutch body 107c. , 108c are turned off so that the input side rotating members 107a, 108a and the output gears 107b, 108b are rotated relative to each other.

  As a result, the odd range transmission clutch 107 is operated in the engaged state to transmit the driving force of the odd range transmission shaft 95 to the output gear 107b, and the transmission from the odd range transmission shaft 95 to the output shaft 30 enters. In this way, the transmission from the odd range transmission shaft 95 to the output shaft 30 is turned off by being operated in the cut state.

  When the even range transmission clutch 108 is operated to be in the engaged state, the driving force of the even range transmission shaft 96 is transmitted to the output gear 108b, and the transmission from the even range transmission shaft 96 to the output shaft 30 is turned on and off. By operating to the state, the transmission from the even range transmission shaft 96 to the output shaft 30 is cut off.

  FIG. 5 is an explanatory diagram showing the operating state of the speed range setting unit 90. “On” shown in FIG. 5 indicates an on state of the first, second, third, and fourth clutches 101, 102, 103, 104, the odd range transmission clutch 107, and the even range transmission clutch 108. “-” Shown in FIG. 5 indicates the disengaged state of the first, second, third, and fourth clutches 101, 102, 103, 104, the odd range transmission clutch 107, and the even range transmission clutch 108.

  As shown in this figure, the speed range setting unit 90 shifts speed by operating the first clutch 101 in the engaged state and operating the second, third, and fourth clutches 102, 103, and 104 in the disengaged state. Set transmission A to the first speed range. Then, the transmission device A shifts the combined driving force output from the planetary transmission unit P by the first output gear 81 by the first output gear 81 and the first input gear 91, and the odd-number range via the first clutch 101. It is transmitted to the transmission shaft 95. At this time, when the odd range transmission clutch 107 is operated to be engaged, the transmission device A transmits the driving force of the odd range transmission shaft 95 to the output shaft 30 by the odd range transmission clutch 107 and the transmission gear 109. .

  The speed range setting unit 90 operates the transmission device A in the second speed range by operating the second clutch 102 in the engaged state and operating the first, third, and fourth clutches 101, 103, and 104 in the disengaged state. Set to. Then, the transmission device A shifts the combined driving force output from the planetary transmission unit P by the second output gear 82 by the second output gear 82 and the second input gear 92, and the even number range via the second clutch 102. It is transmitted to the transmission shaft 96. At this time, when the even range transmission clutch 108 is operated to be in the engaged state, the transmission device A transmits the driving force of the even range transmission shaft 96 to the output shaft 30 by the even range transmission clutch 108 and the transmission gear 109. .

  The speed range setting unit 90 operates the transmission A in the third speed range by operating the third clutch 103 in the engaged state and operating the first, second, and fourth clutches 101, 102, and 104 in the disengaged state. Set to. Then, the transmission device A shifts the combined driving force output from the planetary transmission unit P by the third output gear 83 by using the third output gear 83 and the third input gear 93, and the odd-number range via the third clutch 103. It is transmitted to the transmission shaft 95. At this time, when the odd range transmission clutch 107 is operated to be engaged, the transmission device A transmits the driving force of the odd range transmission shaft 95 to the output shaft 30 by the odd range transmission clutch 107 and the transmission gear 109. .

  The speed range setting unit 90 operates the transmission device A in the fourth speed range by operating the fourth clutch 104 in the engaged state and operating the first, second, and third clutches 101, 1012, and 103 in the disengaged state. Set to. Then, the transmission device A shifts the combined driving force output from the planetary transmission unit P by the fourth output gear 84 by the fourth output gear 84 and the fourth input gear 94, and the even range via the fourth clutch 104. It is transmitted to the transmission shaft 96. At this time, when the even range transmission clutch 108 is operated to be in the engaged state, the transmission device A transmits the driving force of the even range transmission shaft 96 to the output shaft 30 by the even range transmission clutch 108 and the transmission gear 109. .

  FIG. 8 is a block diagram of an operating device equipped on the tractor to operate the traveling transmission device. As shown in this figure, this operating device includes a speed change lever 120, a speed change operation detecting means 121, an engine output sensor 122, a continuously variable transmission output sensor 123, a vehicle speed sensor 124, a forward / reverse lever 125, It includes a forward / reverse detection means 126, a shift detection means 127, and a control means 128 linked to the detection means 121, 126, 127 and the sensors 122, 123, 124.

  The control means 128 is linked to an operation unit (not shown) of an actuator (not shown) that changes the swash plate angle of the hydraulic pump 24 of the continuously variable transmission unit 20. The control means 128 operates the hydraulic pistons 111, 112, 114, 115 of the first clutch 101, the second clutch 102, the third clutch 103, the fourth clutch 104, the odd range transmission clutch 107, and the even range transmission clutch 108. Connected to an operation valve (not shown). The control means 128 is linked to an actuator (not shown) that switches between the forward friction clutch 14 and the reverse friction clutch 16.

  As shown in FIG. 8, the shift lever 120 swings the operation range from the neutral position N to the maximum speed position max. A portion from the neutral position N to the intermediate position M in this operation area is a low speed area L. A portion from the intermediate position M to the highest speed position max in the operation area is a high speed area H.

  The shift operation detecting means 121 is constituted by a rotary potentiometer linked to the shift lever 120. The shift operation detecting means 121 detects the operation position of the shift lever 120 and outputs the detection result to the control means 128.

  The engine output sensor 122, the continuously variable transmission output sensor 123, and the vehicle speed sensor 124 are constituted by rotation sensors. The engine output sensor 122 detects the output speed of the engine 1 and outputs the detection result to the control means 128. The continuously variable transmission output sensor 123 detects the output speed of the continuously variable transmission 20 from the motor shaft 23 and outputs the detection result to the control means 128. The vehicle speed sensor 124 detects the rotational speed of the output shaft 30 as the vehicle speed, and outputs the detection result to the control means 128. The shift detection unit 127 detects the shift state of the continuously variable transmission unit 20 and feeds back the detection result to the control unit 128.

  The forward / reverse lever 125 is switched to a neutral position N, a forward position F, and a reverse position R by a swing operation. The forward / reverse detection means 126 is constituted by a rotary potentiometer linked to the forward / reverse lever 125. The forward / reverse detection means 126 detects the operation position of the forward / reverse lever 125 and outputs the detection result to the control means 128.

  The control means 128 is configured using a microcomputer. The control means 128 shifts the speed change gear A so that the output shaft 30 is driven at a rotational speed corresponding to the operation position of the speed change lever 120 in a speed range as an operation state corresponding to the operation position of the speed change lever 120. First, second, third, and fourth clutches 101, 102, and 103 based on information detected by operation detection means 121, shift detection means 127, engine output sensor 122, continuously variable transmission output sensor 123, and vehicle speed sensor 124. 104, odd range transmission clutch 107 and even range transmission clutch 108 are operated. The control means 128 operates the forward friction clutch 14 and the reverse friction clutch 16 based on the information detected by the forward / reverse detection means 126 so that the forward / reverse switching device 10 is in an operation state corresponding to the operation position of the forward / reverse lever 125. To do.

  As a result, when the tractor operates the speed change lever 120 and the forward / reverse lever 125, the operation position of the speed change lever 120 and the output speed of the engine 1 are changed in the forward or backward direction corresponding to the operation position of the forward / backward movement lever 125. Drive at the corresponding vehicle speed.

  That is, FIG. 6 shows the relationship between the speed change state of the continuously variable transmission 20, the output speed of the output shaft 30 of the transmission A, and the speed range set by the speed range setting unit 90 of the transmission A. It is explanatory drawing. The vertical axis shown in FIG. 6 indicates the number of rotations of the output shaft 30 (hereinafter referred to as output speed). The horizontal axis shown in FIG. 6 indicates the speed change state of the continuously variable transmission unit 20. “−MAX” on the horizontal axis indicates the maximum speed of the continuously variable transmission unit 20 in the reverse rotation transmission state. “0” on the horizontal axis indicates a neutral state of the continuously variable transmission 20. “+ MAX” on the horizontal axis indicates the maximum speed of the continuously variable transmission unit 20 in the normal rotation transmission state.

  As shown in FIG. 5, FIG. 5 and FIG. 8, the portion of the speed change lever 120 from the neutral position N to the intermediate position Lm of the low speed area L (hereinafter referred to as the low speed intermediate position Lm) in the low speed area L. The control means 128 operates the first clutch 101 in the engaged state, operates the second, third, and fourth clutches 102, 103, and 104 in the disengaged state. Become a range. At this time, the control means 128 operates the odd range transmission clutch 107 to the on state and operates the even range transmission clutch 108 to the disengagement state. Thereby, the transmission device A transmits the driving force of the first output gear 81 of the planetary transmission portion P to the odd range transmission shaft 95 by the first input gear 91 and the first clutch 101, and this odd range transmission shaft 95. Is transmitted to the output shaft 30 by the odd range transmission clutch 107 and the transmission gear 109. Then, as the shift lever 120 is operated from the neutral position N toward the low speed intermediate position Lm, the control means 128 shifts the continuously variable transmission 20 from “−MAX” to “+ MAX”, and outputs the output speed. Increases continuously from “0”. When the speed change lever 120 reaches the low speed intermediate position Lm, the control means 128 operates the continuously variable transmission 20 to “+ MAX”, and the output speed becomes “V1”.

  When the speed change lever 120 is operated to a portion from the low speed intermediate position Lm to the intermediate position M in the low speed range L, the control means 128 operates the second clutch 102 to be in the engaged state, and the first, third and fourth clutches. By operating 101, 103, and 104 in the cut-off state, the transmission device A is in the second speed range. At this time, the control means 128 operates the even range transmission clutch 108 to the engaged state and operates the odd range transmission clutch 107 to the disengaged state. Thus, the transmission device A transmits the driving force of the second output gear 82 of the planetary transmission unit P to the even range transmission shaft 96 by the second input gear 92 and the second clutch 102, and this even range transmission shaft 96. Is transmitted to the output shaft 30 by the even range transmission clutch 108 and the transmission gear 109. Then, as the shift lever 120 is operated from the low speed intermediate position Lm toward the intermediate position M, the control means 128 shifts the continuously variable transmission unit 20 from “+ MAX” to “−MAX”, and the output speed Increases continuously from “V1”. When the speed change lever 120 reaches the intermediate position M, the control means 128 operates the continuously variable transmission 20 to “−MAX”, and the output speed becomes “V2”.

  When the speed change lever 120 is operated in a portion of the high speed range H from the neutral position N to the intermediate position Hm of the high speed range H (hereinafter referred to as the high speed intermediate position Hm), the control means 128 causes the third clutch 103 to move. By operating to the on state and operating the first, second, and fourth clutches 101, 102, and 104 to the disengaged state, the transmission A is in the third speed range. At this time, the control means 128 operates the odd range transmission clutch 107 to the on state and operates the even range transmission clutch 108 to the disengagement state. Thus, the transmission A transmits the driving force of the third output gear 83 of the planetary transmission portion P to the odd range transmission shaft 95 via the third input gear 93 and the third clutch 103, and the odd range transmission shaft. The driving force of 95 is transmitted to the output shaft 30 by the odd range transmission clutch 107 and the transmission gear 109. Then, as the shift lever 120 is operated from the intermediate position M toward the high speed intermediate position Hm, the control means 128 shifts the continuously variable transmission unit 20 from “−MAX” to “+ MAX”, and the output speed Increases continuously from “V2”. When the speed change lever 120 reaches the high speed intermediate position Mm, the control means 128 operates the continuously variable transmission 20 to “+ MAX” and the output speed becomes “V3”.

  When the speed change lever 120 is operated to a portion from the high speed intermediate position Hm to the maximum speed position max in the high speed range H, the control means 128 operates the fourth clutch 104 to the engaged state, and the first, second, third By operating the clutches 101, 102, 103 in the disengaged state, the transmission device A is in the fourth speed range. At this time, the control means 128 operates the even range transmission clutch 108 to the engaged state and operates the odd range transmission clutch 107 to the disengaged state. Thus, the transmission device A transmits the driving force of the fourth output gear 84 of the planetary transmission unit P to the even range transmission shaft 96 by the fourth input gear 94 and the fourth clutch 104, and The driving force is transmitted to the output shaft 30 by the even range transmission clutch 108 and the transmission gear 109. Then, as the shift lever 120 is operated from the high speed intermediate position Hm toward the maximum speed position max, the control means 128 shifts the continuously variable transmission 20 from “+ MAX” to “−MAX” and outputs it. The speed increases steplessly from “V3”. When the speed change lever 120 reaches the maximum speed position max, the control means 128 operates the continuously variable transmission 20 to “−MAX” and the output speed becomes “V4”.

  When the forward / reverse lever 125 is operated to the forward position F, the control means 128 operates the forward friction clutch 14 to the on state, operates the reverse friction clutch 16 to the disengaged state, and the forward / reverse switching device 10 enters the forward transmission state. . Then, the forward / reverse switching device 10 converts the driving force input from the engine 1 as a forward driving force and transmits it from the output gear 12 to the continuously variable transmission unit 20 and the planetary transmission unit P, and the transmission device A transmits the forward driving force. The tractor travels forward by transmitting to the front wheel differential mechanism 35 and the rear wheel differential mechanism 32.

  When the forward / reverse lever 125 is operated to the reverse position R, the control means 128 operates the forward friction clutch 14 to the disengaged state, operates the reverse friction clutch 16 to the on state, and the forward / reverse switching device 10 enters the reverse transmission state. . Then, the forward / reverse switching device 10 converts the driving force input from the engine 1 as a reverse driving force and transmits it from the output gear 12 to the continuously variable transmission unit 20 and the planetary transmission unit P, and the transmission device A transmits the reverse driving force to the front wheels. The tractor travels backward by transmitting to the differential mechanism 35 for the rear wheel and the differential mechanism 32 for the rear wheel.

  When the forward / reverse lever 125 is operated to the neutral position N, the control unit 128 operates the forward friction clutch 14 and the reverse friction clutch 16 to be disconnected, and the forward / reverse switching device 10 is in the neutral state. Then, the forward / reverse switching device 10 does not transmit power to the continuously variable transmission unit 20 and the planetary transmission unit P, and the transmission transmission device A blocks transmission to the front wheel actuation mechanism 35 and the rear wheel differential mechanism 32. The tractor stops.

  FIG. 7 is an explanatory diagram showing the operating states of the first, second, third, and fourth clutches 101, 102, 103, and 104 by the control means 128 when the speed range of the transmission device A is switched. “Increase” shown in FIG. 7 indicates that the output speed of the output shaft 30 changes at an increased speed for switching the speed range. “Decrease” shown in FIG. 7 indicates that the output speed of the output shaft 30 is decelerated and changed for switching the speed range.

  As shown in this figure, when switching the speed range of the transmission A, the control means 128 temporarily turns both the odd range transmission shaft 95 and the even range transmission shaft 96 into the planetary transmission section. Each clutch 101, so that a double transmission state in which power is transmitted from the P to the output shaft 30 via the odd transmission system having the odd range transmission shaft 95 and the even transmission system having the even range transmission shaft 96 occurs. 102, 103, 104, 107, 108 are operated.

  That is, when the transmission device A is switched from the first speed range to the second speed range, the control means 128 switches the second clutch 102 to the engaged state before switching the first clutch 101 to the disconnected state. After the clutch 102 is switched to the engaged state, the first clutch 101 is switched to the disconnected state. At this time, the control means 128 switches the even range transmission clutch 108 to the on state before switching the odd range transmission clutch 107 to the disengaged state, and after the even range transmission clutch 108 switches to the on state, The transmission clutch 107 is switched to the disengaged state.

  When the transmission device A is switched from the second speed range to the third speed range, the control means 128 switches the third clutch 103 to the on state before switching the second clutch 102 to the disengaged state. After switching to the engaged state, the second clutch 102 is switched to the disconnected state. At this time, the control means 128 switches the odd range transmission clutch 107 to the on state before switching the even range transmission clutch 108 to the disengaged state, and after the odd range transmission clutch 107 switches to the on state, The transmission clutch 108 is switched to the disengaged state.

  When the transmission device A is switched from the third speed range to the fourth speed range, the control means 128 switches the fourth clutch 104 to the on state before switching the third clutch 103 to the disengaged state. After switching to the engaged state, the third clutch 103 is switched to the disconnected state. At this time, the control means 128 switches the even range transmission clutch 108 to the on state before switching the odd range transmission clutch 107 to the disengaged state, and after the even range transmission clutch 108 switches to the on state, The transmission clutch 107 is switched to the disengaged state.

  When the transmission device A is switched from the fourth speed range to the third speed range, the control means 128 switches the third clutch 103 to the on state before switching the fourth clutch 104 to the disengaged state. After switching to the engaged state, the fourth clutch 104 is switched to the disconnected state. At this time, the control means 128 switches the odd range transmission clutch 107 to the on state before switching the even range transmission clutch 108 to the disengaged state, and after the odd range transmission clutch 107 switches to the on state, The transmission clutch 108 is switched to the disengaged state.

  When the transmission device A is switched from the third speed range to the second speed range, the control means 128 switches the second clutch 102 to the on state before switching the third clutch 103 to the disengaged state. After switching to the engaged state, the third clutch 103 is switched to the disconnected state. At this time, the control means 128 switches the even range transmission clutch 108 to the on state before switching the odd range transmission clutch 107 to the disengaged state, and after the even range transmission clutch 108 switches to the on state, The transmission clutch 107 is switched to the disengaged state.

  When the transmission device A is switched from the second speed range to the first speed range, the control means 128 switches the first clutch 101 to the on state before switching the second clutch 102 to the disengaged state. After switching to the engaged state, the second clutch 102 is switched to the disconnected state. At this time, the control means 128 switches the odd range transmission clutch 107 to the on state before switching the even range transmission clutch 108 to the disengaged state, and after the odd range transmission clutch 107 switches to the on state, The transmission clutch 108 is switched to the disengaged state.

  When the control unit 128 generates a double transmission state in which both the odd range transmission shaft 95 and the even range transmission shaft 96 are driven, the odd range transmission clutch 107 and the even range transmission clutch 108 are in a half transmission state. To operate. That is, even if torque fluctuation occurs in the double transmission state, the continuously variable transmission unit 20 absorbs the torque fluctuation due to the slippage of the hydraulic oil. In addition to this, the control means 128 causes the odd range transmission clutch 107 and the even range transmission clutch 108 to slip to absorb torque fluctuations.

  As shown in FIG. 1, the front wheel transmission 40 includes a standard gear transmission mechanism 45 having a standard transmission clutch 44 and a speed increasing transmission clutch 46 in addition to the input shaft 41 and the output shaft 42. A speed increasing gear transmission mechanism 47 is provided across the input shaft 41 and the output shaft 42.

  When the standard transmission clutch 44 is operated in the engaged state and the speed increasing transmission clutch 46 is operated in the disengaged state, the front wheel transmission 40 transmits the driving force of the input shaft 41 to the output shaft 42 by the standard gear transmission mechanism 45. It will be in the standard transmission state. Then, the front wheel transmission device 40 drives the left and right front wheels so that the average peripheral speed of the left and right front wheels is equal to the average peripheral speed of the left and right rear wheels.

  When the standard transmission clutch 44 is operated in the disengaged state and the speed increasing transmission clutch 46 is operated in the engaged state, the front wheel transmission 40 transmits the driving force of the input shaft 41 to the output shaft 47 by the speed increasing gear transmission mechanism 47. It will be in the state of speed increase transmission. Then, the front wheel transmission device 40 drives the left and right front wheels so that the average peripheral speed of the left and right front wheels is approximately twice the average peripheral speed of the left and right rear wheels.

  FIG. 9 is a diagram of a traveling transmission device for a tractor equipped with a transmission gear transmission A according to a second embodiment of the present invention.

  In the tractor traveling transmission device equipped with the transmission gear transmission A according to the second embodiment of the present invention, the output from the output shaft 30 as the output rotating body of the transmission transmission device A is transmitted via the forward / reverse switching device 10. This is transmitted to the wheel differential mechanism 32 and the front wheel transmission 40.

  As shown in FIGS. 9, 10, and 11, the forward / reverse switching device 10 is positioned on the input side rotator 13 that is integrally rotatable with the output shaft 30, and on the front and rear sides of the input side rotator 13. Over the output gears 19a, 19b, the forward friction clutch 14 provided across one end side of the input side rotator 13 and the front output gear 19a, and over the other end side of the input side rotator 13 and the rear output gear 19b. A reverse friction clutch 16 provided and a reverse gear 17 meshed with the rear output gear 19b are provided.

  The front output gear 19 a is interlocked with the input gear 31 of the rear wheel differential mechanism 32 and the input shaft 41 of the front wheel transmission 40 via a transmission gear 130 and a transmission shaft 131. The reverse gear 17 is linked to the input gear 31 of the rear wheel differential mechanism 32 and the input shaft 41 of the front wheel transmission 40 via the transmission gear 132 and the transmission shaft 131.

  When the transmission A according to the second embodiment is compared with the transmission A according to the first embodiment, the output of the continuously variable transmission 20 to which the engine driving force is input and the continuously variable transmission 20 The engine drive force not subjected to the speed change action is synthesized by the planetary transmission portion P, and the composite drive force from the planetary transmission portion P is changed by switching the first, second, third, and fourth clutches 101, 102, 103, and 104. It has the same configuration in that it is converted to a driving force in a four-stage speed range and is transmitted to the output shaft 30 as an output rotating body by two transmission shafts of an odd range transmission shaft 95 and an even range transmission shaft 96. And has a different configuration in terms of the planetary transmission portion P. This difference will be described.

  As shown in FIGS. 9 and 10, the planetary transmission unit P in the speed change transmission device A according to the second embodiment includes a first planetary transmission mechanism 140, a second planetary transmission mechanism 150, and a third planetary transmission mechanism 160. It is prepared.

  As shown in FIG. 10, the first planetary transmission mechanism 140, the second planetary transmission mechanism 150, and the third planetary transmission mechanism 160 include one sun gear 141, 151, 161, and a plurality of planetary gears 142, 152, 162. , Ring gears 143, 153, and 163 and carriers 144, 154, and 164 are provided.

  The sun gear 141 of the first planetary transmission mechanism 140 is interlocked with the motor shaft 23 of the continuously variable transmission 20 via the sun gear shaft 145, the gear 170, and the gear 171. The carrier 144 of the first planetary transmission mechanism 140, the ring gear 153 of the second planetary transmission mechanism 150, and the carrier 164 of the third planetary transmission mechanism 160 are interlocked so as to be rotatable together. The ring gear 143 of the first planetary transmission mechanism 140 and the carrier 154 of the second planetary transmission mechanism 150 are interlocked so as to be integrally rotatable, and can be integrally rotated to the pump shaft 22 of the continuously variable transmission unit 20 via the interlocking shaft 172. It is linked. The sun gear 151 of the second planetary transmission mechanism 150 and the sun gear 161 of the third planetary transmission mechanism 160 are interlocked so as to be integrally rotatable.

  The planetary transmission unit P includes a first output gear 81 that is linked to the carrier 144 of the first planetary transmission mechanism 140 so as to be integrally rotatable. The planetary transmission unit P is rotatable integrally with the sun gears 151 and 161 of the second and third planetary transmission mechanisms 150 and 160. The second output gear 82 and the fourth output gear 84 linked to each other, and the third output gear 83 linked to the ring gear 163 of the third planetary transmission mechanism 160 so as to be integrally rotatable.

  The planetary transmission unit P inputs the output from the motor shaft 23 of the continuously variable transmission unit 20 to the sun gear 141 of the first planetary transmission mechanism 140, and is continuously variable as an engine driving force that is not subjected to a shifting action by the continuously variable transmission unit 20. The driving force of the pump shaft 22 of the transmission unit 20 is input to the ring gear 143 of the first planetary transmission mechanism 140 and the carrier 154 of the second planetary transmission mechanism 150, and the input driving force of the continuously variable transmission unit 20 and the driving of the engine 1 are input. The force is combined by the first planetary gear mechanism 140, the second planetary transmission mechanism 150, and the third planetary transmission mechanism 160. The combined driving force is transmitted from the first output gear 81 to the first input gear 91 of the odd range transmission shaft 95, and from the second output gear 82 to the second input gear 92 of the even range transmission shaft 96, and the third output gear. 83 is transmitted to the third input gear 93 of the odd range transmission shaft 95, and is transmitted from the fourth output gear 84 to the fourth input gear 94 of the even range transmission shaft 96.

The first output gear 81 and the first input gear 91 are interlocked with each other at a transmission ratio at which the rotational speed of the first input gear 91 is twice the rotational speed of the first output gear 81. The second output gear 82 and the second input gear 92 are interlocked with each other at a transmission ratio at which the rotational speed of the second input gear 92 is twice the rotational speed of the second output gear 82. The third output gear 83 and the third input gear 93 are interlocked with each other at a transmission ratio in which the rotation speed of the third input gear 93 is ½ of the rotation speed of the third output gear 83. The fourth output gear 84 and the fourth input gear 94 are interlocked with each other at a transmission ratio in which the rotation speed of the fourth input gear 94 is ½ of the rotation speed of the fourth output gear 84. The output gear 107b of the odd range transmission clutch 107 and the passive gear 173 (corresponding to the transmission gear) of the output shaft 30 have a transmission ratio in which the rotational speed of the output shaft 30 is ½ of the rotational speed of the output gear 107b. It is linked. The output gear 108b of the even range transmission clutch 108 and the passive gear 174 (corresponding to the transmission gear) of the output shaft 30 are linked with a transmission ratio in which the rotation speed of the output shaft 30 is ½ of the rotation speed of the output gear 108b. is doing.

  As a result, the driving force of the third output gear 83 is transmitted to the output shaft 30 by decelerating it to 1/4 of the rotational speed, and between the third output gear 83 and the odd range transmission shaft 95, the output gear 107b. And the output shaft 30 are divided into two portions and decelerated. In order to transmit the driving force of the fourth output gear 84 to the output shaft 30 by decelerating to 1/4 of the number of revolutions, the fourth output gear 84 and the even range transmission shaft 96, the output gear 108b and the output shaft It will be decelerated in two places between 30. Then, 1/4 speed reduction can be performed while reducing the size of the speed range setting unit 90.

  FIG. 12 is a diagram of a traveling transmission device for a tractor equipped with a transmission gear transmission A according to a third embodiment of the present invention.

  In the tractor traveling transmission device equipped with the transmission gear transmission A according to the third embodiment of the present invention, the output from the output shaft 30 as the output rotating body of the transmission transmission device A is transmitted via the forward / reverse switching device 10. This is transmitted to the wheel differential mechanism 32 and the front wheel transmission 40.

  As shown in FIGS. 12, 13, and 14, the forward / reverse switching device 10 in the traveling transmission device equipped with the transmission transmission A according to the third embodiment is the transmission transmission A according to the second embodiment. Is provided with the same configuration as the forward / reverse switching device 10 in the traveling transmission device.

  When the transmission A according to the third embodiment is compared with the transmission A according to the first embodiment, the output of the continuously variable transmission 20 to which the engine driving force is input and the continuously variable transmission 20 The engine drive force not subjected to the speed change action is synthesized by the planetary transmission portion P, and the composite drive force from the planetary transmission portion P is changed by switching the first, second, third, and fourth clutches 101, 102, 103, and 104. It has the same configuration in that it is converted to a driving force in a four-stage speed range and is transmitted to the output shaft 30 as an output rotating body by two transmission shafts of an odd range transmission shaft 95 and an even range transmission shaft 96. In this respect, the planetary transmission unit P and the speed range setting unit 90 have different configurations.

  As shown in FIGS. 12 and 13, the planetary transmission portion P in the transmission transmission A according to the third embodiment has the same configuration as the planetary transmission portion P in the transmission transmission A according to the second embodiment. Yes.

  As shown in FIGS. 12 and 13, the speed range setting unit 90 in the transmission transmission A according to the third embodiment and the speed range setting unit 90 in the transmission transmission A according to the first embodiment are odd numbers. This is the same in that the range transmission shaft 95 and the even range transmission shaft 96 are arranged in parallel in parallel.

  The speed range setting unit 90 in the speed change transmission device A according to the third embodiment and the speed range setting portion 90 in the speed change transmission device A according to the first embodiment include an odd range transmission shaft 95 and a planetary transmission portion P. The first input gear 91 meshed with the first output gear 81 and the third input gear 93 meshed with the third output gear 83 of the planetary transmission portion P are freely rotatable, and the even range transmission shaft 96 is And a third input gear 93 meshed with the second output gear 83 of the planetary transmission portion P and a fourth input gear 94 meshed with the fourth output gear 84 of the planetary transmission portion P, which are freely rotatable. The driving force of one input gear 91 is transmitted to the odd range transmission shaft 95 by the first clutch 101, the driving force of the second input gear 92 is transmitted to the even range transmission shaft 96 by the second clutch 102, and the third input gear 93 is transmitted. The driving force of the third clutch 103 In that transmitted to the number range transmission shaft 95, transmitting the driving force of the fourth input gear 94 by the fourth clutch 104 to the even-range transmission shaft 96 have the same configuration.

In the speed range setting unit 90 in the speed change transmission device A according to the third embodiment, an output gear 95a in which the driving force of the odd range transmission shaft 95 is rotatably provided integrally with the rear end portion of the odd range transmission shaft 95; This is transmitted to the output shaft 30 via an input gear 30a (corresponding to a transmission gear) provided so as to rotate integrally with the front end portion of the output shaft 30 in a state of meshing with the output gear 95a. The output shaft 30 is connected to the drive force of the even-range transmission shaft 96 via an output gear 96a that is provided so as to be rotatable integrally with the rear end portion of the even-range transmission shaft 96 and the input gear 30a meshed with the output gear 96a. To communicate.
The output gear 95a of the odd range transmission shaft 95 and the output gear 96a of the even range transmission shaft 96 are engaged with the same input gear 30a when transmitting to the output shaft 30, and this transmission structure includes a speed range setting unit 90. Keep the size in the front-rear direction small.

In the speed range setting unit 90 of the speed change transmission apparatus A according to the third embodiment, the first clutch 101 and second clutch 102 and the third clutch 103 and the fourth clutch 104, the odd-range transmission shaft 95 or even number range hydraulic piston 101b which is provided to be rotatable therewith and sliding on the transmission shaft 96, 102b, 103b, have become dog clutch equipped with 104b.
That is, hydraulic piston 101b, 102b, 103b, 104b are opposed to each other physician interlocked by engagement of the engagement float latching projection.

The speed range setting unit 90 of the third embodiment includes a clutch of the odd range transmission shaft 95 (first clutch 101 or third clutch 103) and a clutch of the even range transmission shaft 96 (second clutch 102 or fourth clutch 104). ), The torque is changed in the double transmission state when the double transmission state appears. As a result, the speed range setting unit 90 of the third embodiment includes the odd range transmission clutch 107 and the even range transmission clutch 108 employed in the speed range setting unit 90 of the first embodiment and the second embodiment. Is omitted, and the transmission efficiency is increased and the speed range setting unit 90 is made compact.

  FIG. 15 is a diagram of a traveling transmission device for a tractor equipped with a transmission gear transmission A according to a fourth embodiment of the present invention. When the transmission gear transmission A according to the fourth embodiment is compared with the transmission transmission device A according to the first embodiment, the planetary transmission section P and the speed range setting section 90 have the same configuration, and are continuously variable. In the configuration for inputting a variable driving force, the transmission A according to the fourth embodiment is different from the transmission A according to the first embodiment. This difference will be described next.

  The transmission device A according to the fourth embodiment includes an electric motor 180. The planetary transmission unit P inputs the output from the output shaft 180 a of the electric motor 180 to the sun gear 62 of the upper planetary mechanism 60 through the transmission gear 181, the transmission gear 182, and the sun gear shaft 61. The planetary transmission unit P inputs the output from the output shaft 1 a of the engine 1 to the ring gear 65 of the upper planetary mechanism 60 via the main clutch 2, the forward / reverse switching device 10 and the gear 67. The planetary transmission unit P inputs and combines the driving force of the engine 1 and the driving force of the electric motor 180, and combines this combined driving force from the first output gear 81 and the third output gear 83 of the speed range setting unit 90. Transmission to the odd range transmission shaft 95 and transmission from the second output gear 82 and the fourth output gear 84 to the even range transmission shaft 96 of the speed range setting unit 90.

  The electric motor 180 changes the drive rotational speed steplessly by a speed change operation by the driver 183. The electric motor 180 is shifted, and the first, second, third, and fourth clutches 101, 102, 103, and 104, the odd range transmission clutch 107, and the even range transmission clutch 108 are switched in accordance with the shifting operation. By operating, the output shaft 30 is divided into four speed ranges from the first speed range to the fourth speed range, and infinitely in each speed range, as in the transmission A according to the first embodiment. It is driven with a shift.

[Another Example]
In place of the above-described embodiments, the odd-range transmission shaft 95 is divided into a transmission shaft that includes the first clutch 101 and is linked to the output shaft 30, and a transmission shaft that includes the third clutch 103 and is linked to the output shaft 30. The even-range transmission shaft 96 is divided into a transmission shaft that includes the second clutch 102 and that is linked to the output shaft 30, and a transmission shaft that includes the fourth clutch 104 and that is linked to the output shaft 30. And you may implement by providing the structure which has arrange | positioned each transmission shaft in parallel in parallel. In addition, the transmission shaft includes one transmission shaft having the first clutch 101 and the second clutch 102, and one transmission shaft having the third clutch 103 and the fourth clutch 104, and both the transmission shafts are arranged in parallel. Alternatively, a parallel arrangement may be adopted. In either case, the object of the present invention can be achieved.

20 continuously variable transmission 30 output rotor
30a transmission gear 60, 70, 140, 150, 160 planetary transmission mechanism 62, 72 sun gear
81 1st output gear
82 Second output gear 83 Third output gear 84 Fourth output gear 91 First input gear 92 Second input gear 93 Third input gear 94 Fourth input gears 95, 96 Transmission shaft
95a, 95b Output gear 101, 102, 103, 104 Speed setting clutch
107b, 108b output gear
109 transmission gear
173,174 Transmission gear 180 Electric motor P Planetary transmission part

Claims (3)

A continuously variable transmission or an electric motor to which engine driving force is input;
A planetary transmission unit configured to combine an output of the continuously variable transmission unit and an engine driving force not subjected to a shifting action by the continuously variable transmission unit, or an output of the electric motor and an engine driving force by a plurality of planetary transmission mechanisms; ,
A transmission transmission device configured to divide the combined driving force from the planetary transmission unit into a plurality of speed ranges, and to change the speed steplessly in each step speed range and output from the output rotating body,
As an output gear that outputs a combined driving force from the planetary transmission unit, a first output gear and another output gear different from the first output gear are provided concentrically with the sun gear of the planetary transmission mechanism,
Two transmissions that switch the output gear that outputs the combined driving force from the planetary transmission unit by switching a plurality of speed range setting clutches, convert the output gear to the driving force of the plurality of speed ranges, and transmit it to the output rotating body With a shaft,
A transmission gear meshing with an output gear provided on each of the two transmission shafts is provided in the output rotating body so as to be integrally rotatable,
A transmission device in which the two transmission shafts are arranged in parallel and in parallel. The planetary transmission unit includes a pair of planetary transmission mechanisms in which planetary gears mesh with each other,
2. The transmission according to claim 1, wherein the two transmission shafts are arranged in parallel over the entire length. As another output gear that outputs the combined driving force from the planetary transmission unit, a second output gear, a third output gear, and a fourth output gear are provided.
A first input gear meshing with the first output gear and a third input gear meshing with the third output gear are supported on one of the two transmission shafts,
A second input gear meshing with the second output gear and a fourth input gear meshing with the fourth output gear are supported on the other of the two transmission shafts,
The plurality of speed range setting clutches are meshing clutches;
As the speed range setting clutch, one speed range setting clutch arranged corresponding to one of the two transmission shafts and the other speed range setting arranged corresponding to the other of the two transmission shafts With a clutch,
The one speed range setting clutch includes a first engaged state in which the first input gear and one of the two transmission shafts are integrally rotated, and the first input gear and one of the two transmission shafts. Of the third input gear and the two transmission shafts, a first cut-off state in which the third input gear and one of the two transmission shafts are integrally rotated, Is switchable to a third cut-off state in which one of them is relatively rotated,
The other speed range setting clutch includes a second engagement state in which the second input gear and the other of the two transmission shafts are integrally rotated, and the second input gear and the other of the two transmission shafts. Of the fourth input gear and the two transmission shafts, a second cutting state in which the fourth input gear and the other of the two transmission shafts are integrally rotated, The transmission according to claim 1 or 2, wherein the transmission can be switched to a fourth cut-off state in which the other is rotated relative to the other.

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