JP2001082573A - Transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To solve such a problem that a conventional multistage transmission needs a large-sized mission case, and that it is difficult to obtain a neutral position by using a transmission adopting a split pulley continuous transmission device. SOLUTION: A planetary gear device 3 and two continuous transmission devices 4, 5 are arranged inside a mission case. Power from an input shaft 20 is respectively outputted to the continuous transmission devices 4, 5. Output of the continuous transmission device 4 is transmitted to a sun gear 61 of the planetary gear device 3, while output of the continuous transmission device 5 is transmitted to a ring gear 63 of the planetary gear device 3. Power is transmitted to an output shaft 26 via a carrier 24 which pivots planetary gears 62, 62, etc., of the planetary gear device 3.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a transmission having a small shift shock and capable of smoothly switching between forward and reverse.

[0002]

2. Description of the Related Art Conventionally, there has been known a technique for changing a traveling speed or a working speed by using a gear type transmission or a hydraulic stepless transmission as a transmission of an agricultural work vehicle such as a tractor or a combine. It has become.

[0003]

However, in the case of a gear-sliding type transmission, a gear and a slider are required on a transmission shaft, and a shaft and a gear on the driven side are also required for the transmission gear. As the number of gears increased, the size of the transmission case became larger, making it more difficult to reduce the size of the transmission. In addition, skill was required to operate the clutch in order to reduce shift shock. Further, the hydraulic continuously variable transmission can reduce the shift shock, but because of the configuration in which the hydraulic pump and the hydraulic motor are fluidly connected, the hydraulic oil leaks and the transmission efficiency is poor.

[0004]

The problems to be solved by the present invention are as described above. Next, means for solving the problems will be described.

That is, in the first aspect, the planetary gear device and the two continuously variable transmissions are arranged in a transmission case,
The power from the input shaft is input to each of the two continuously variable transmissions, and the output of one continuously variable transmission is transmitted to the sun gear of the planetary gear unit, and the output of the other continuously variable transmission is the ring gear of the planetary gear unit. And power is transmitted to an output shaft from a carrier that pivotally supports a planetary gear of the planetary gear device.

According to a second aspect of the present invention, the two continuously variable transmissions are continuously variable transmissions using a split pulley and a belt.

According to a third aspect of the present invention, the effective diameter of the split pulley is changed by hydraulic control.

According to a fourth aspect of the present invention, in the transmission according to any one of the first to third aspects, when the shift operation means is set to the "neutral" position, the two continuously variable transmissions are sun gears. And the speed ratio of the ring gear is controlled so that the rotational speed of the ring gear does not revolve around the planetary gear.

According to a fifth aspect of the present invention, a planetary gear set, a pair of clutches, and two continuously variable transmissions are arranged in a transmission case, and power from an input shaft is transmitted to an input side of each clutch. The output side of the clutch is operatively connected to the input side of each of the two continuously variable transmissions, the output of one continuously variable transmission is transmitted to the sun gear of the planetary gear set, and the output of the other continuously variable transmission is connected to the planetary gear. The power is transmitted to the ring gear, and the power is transmitted to the output shaft from the carrier that supports the planetary gear of the planetary gear device.The output side of the other clutch is connected to the output shaft without passing through the continuously variable transmission. They are linked and linked.

[0010]

Next, embodiments of the present invention will be described. FIG. 1 is a skeleton diagram of a transmission according to one embodiment of the present invention, FIG. 2 is a schematic side view showing meshing of gears, and FIG. 3 is a cross-sectional view taken along line XX in FIG. FIG. 4 is a sectional view taken along the line YY. FIG. 5 is a sectional view taken along the line ZZ. FIG. 6 is a front view showing the appearance of the transmission, and FIG. 7 is a side view of the transmission.

The transmission 1 is a transmission for a vehicle. As shown in FIGS. 3 to 5, a planetary gear device 3 and a plurality of shafts and gears for transmitting power are provided in a transmission case 2 as shown in FIGS. Split pulley type continuously variable transmission 4
5 and differential device 7 for differentially connecting the left and right axles
Is stored. As shown in FIGS. 3 to 6, the transmission case 2 is configured by joining a plurality of right and left divided cases 2a, 2b, and 2c. As described above, the transmission mechanism, the speed reduction mechanism, and the differential gear are collectively housed in the transmission case 2, thereby making the transmission case 2 compact.

At the center position of the transmission case 2,
As shown in FIG. 2, the first transmission shaft 21 is supported laterally in the left-right direction, and the second transmission shaft 22, the third transmission shaft 23, the fourth transmission shaft 24, and the fifth transmission are parallel to the first transmission shaft 21. The shaft 25 and the output shaft 26 are supported in the left-right direction. The first to fifth transmission shafts 21, 22, 23, 24, 25 are arranged around the output shaft 26 as shown in FIG. 2, and the input shaft 20 and the first transmission shaft Reference numeral 21 is located just above the output shaft 26.

At one end of the first transmission shaft 21 (the left end in the present embodiment, the right side in FIG. 3), an input shaft 20 is disposed on the same axis and protrudes outward from the transmission case 2. Power is input by being connected to an external engine. One end of a cylindrical clutch case 30 is fixed to an end of the input shaft 20 inside the transmission case 2, and supports one end of the first transmission shaft 21 inside the clutch case 30. Also, as shown in FIG.
At the inner end of the clutch case 30, a clutch boss 32 is integrally fixed to the outer periphery thereof, and friction plates 33 are provided on the clutch boss 32. Friction plates 34
And the friction plates 33 and 34 are arranged alternately.

A gear 35 is loosely fitted on an intermediate portion of the first transmission shaft 21 (FIG. 3), and a cylindrical boss 35a formed integrally with the gear 35 is inserted into the clutch case 30. Are externally fitted on the boss portion 35a, and friction plates 37
37 is fitted inside, and the friction plates 36 and 37 are alternately arranged. The friction plates 33 and 34 and the friction plates 36.3
The double-acting piston 38 is arranged on the first transmission shaft 21 during the period 7.

The first transmission shaft 21 is a hollow shaft. A hollow pipe shaft 39 is inserted into the hollow portion, and the inner peripheral surface of the first transmission shaft 21 and the outer peripheral surface of the pipe shaft 39 are connected to each other. The space between them is a control oil passage 90 for pushing the piston 38 leftward (rightward in FIG. 3), and pushes the piston 38 rightward (leftward in FIG. 3) inside the pipe shaft 39. Control oil passage 91 for the control. One end of the control oil passage 90 communicates with a port B provided in the transmission case 2, and one end of the control oil passage 91 communicates with a port A. First transmission shaft 2
A gear 43 is fixed on the rear of the vehicle 1 so as not to rotate relatively. As a result, the first hydraulic clutch 11 is formed in the left half of the clutch case 30, the second hydraulic clutch 12 is formed in the right half, and hydraulic oil is supplied to one of the two ports A and B. Is supplied, the corresponding hydraulic clutch (11 or 12) is alternatively engaged, so that the gear 43 or the gear 35 can be selectively driven.

Further, a second transmission shaft 22 is supported in parallel with the first transmission shaft 21 (FIG. 4). On the second transmission shaft 22, there is provided a split pulley type continuously variable transmission. A split pulley 41 on the driving side of the continuously variable transmission 4 is provided. The split pulley 41 has two halves 41a and 41b.
The half portion 41a is formed integrally with the second transmission shaft 22, and the other half portion 41b is provided on the second transmission shaft 22 so as to be relatively non-rotatable and slidable in the axial direction. A gear 79 is formed on the outer peripheral surface of the half portion 41a, and the gear 79 is meshed with the gear 43 on the first transmission shaft 21. Above half 4
A control oil passage 49 is formed in the second transmission shaft 22 to push the shaft 1b in the axial direction (FIG. 4).
The end of 9 is in communication with port C. Therefore, when pressure oil is input to the port C, the half portion 41b is pushed in the direction approaching the other half portion 41a, and the split pulley 4
1 is increased.

A fifth transmission shaft 25 is supported in parallel with the second transmission shaft 22. On the fifth transmission shaft 25, the split pulley 42 of the first continuously variable transmission 4 on the driven side is provided. Is provided (FIGS. 3 and 4). The split pulley 42 has substantially the same configuration as the split pulley 41 on the driving side, and includes a half 42 a integrally formed with the fifth transmission shaft 25, And a half portion 42b slidably provided in the direction. Further, a control oil passage 50 for pushing the half portion 42b in the axial direction is formed in the fifth transmission shaft 25, and one end of the oil passage 50 is communicated with the port D. Therefore, when pressure oil is input to the port D, the half 42b is pushed in a direction approaching the other half 42a, and the effective diameter of the split pulley 42 is increased. .

The split pulleys 41, 42 having such a configuration
The belt 44 is wound between the second transmission shaft 2
The first continuously variable transmission 4 connects the second transmission shaft 25 with the fifth transmission shaft 25, and supplies or stops supply of pressure oil to both ports C and D, or changes the pressure to change the speed. The ratio can be changed continuously. The speed-changed rotation is input to a sun gear 61 of the planetary gear device 3 described later.

Further, a third transmission shaft 23 is supported in parallel with the first transmission shaft 21. On the third transmission shaft 23, the second continuously variable transmission, which is a split pulley type continuously variable transmission, is provided. The split pulley 51 on the driving side of the device 5 is provided. The split pulley 51 includes two halves 51a and 51b, and the halves 51a are integrally fixed to the third transmission shaft 23,
The other half 51b is provided on the third transmission shaft 23 so as to be relatively non-rotatable and slidable in the axial direction. A gear 80 is formed on the outer peripheral surface of the half portion 51a, and the gear 80 is meshed with the gear 43 on the first transmission shaft 21. A control oil passage 59 is formed in the third transmission shaft 23 to push the half portion 51b in the axial direction, and an end of the control oil passage 59 communicates with the port E. Therefore, when pressure oil is input to the port E, the half portion 51b is pushed in a direction approaching the other half portion 51a, and the effective diameter of the split pulley 51 is increased. .

A fourth transmission shaft 24 is supported in parallel with the third transmission shaft 23. On the fourth transmission shaft 24, the driven side split pulley 52 of the second continuously variable transmission 5 is mounted. Is arranged. The split pulley 52 has substantially the same configuration as that of the split pulley 51 on the prime mover side, and includes a half portion 52 a formed integrally with the fourth transmission shaft 24, Half 52 slidably provided in direction
b. Further, a control oil passage 60 for pushing the half portion 52b in the axial direction is formed in the fourth transmission shaft 24, and one end of the oil passage 60 is communicated with the port F. Therefore,
When pressure oil is input to the port F, the half 52b is pushed in a direction approaching the other half 52a, and the effective diameter of the split pulley 52 is increased.

Split pulleys 51 and 52 having such a configuration
The belt 54 is wound between the third transmission shaft 2
A second continuously variable transmission 5 that connects the third transmission shaft 24 and the fourth transmission shaft 24 is configured to supply and stop supply of pressure oil to both ports E and F, or to change the pressure ratio thereof. It can be changed continuously. An output gear 71 is fixed on the fourth transmission shaft 24 so as not to rotate relatively, and the speed-changed rotation is input to the later-described planetary gear device 3 via the output gear 71. .

A pump output gear 73 is formed on the outer peripheral surface of the clutch case 30.
The pump shaft 27 is supported on the same axis as the pump shaft 3, and a pump drive gear 70 is integrally formed with the pump shaft 27 and meshes with the pump output gear 73. The hydraulic pump 6 is mounted on the pump shaft 27. The hydraulic pump 6 is provided so as to supply pressure oil to the ports A, B, C, D, E and F as needed.

Next, the above-mentioned planetary gear device 3 will be described. That is, the planetary gear device 3 includes a sun gear 61 integrally fixed on the fifth transmission shaft 25, and a plurality of planetary gears 62 that are disposed around the sun gear 61 and mesh with the sun gear 61. A ring gear 63 in which an internal gear meshing with the planetary gear 62 is engraved on its inner peripheral surface; and a ring gear 63 rotatably supported on the end of the fifth transmission shaft 25, and the planetary gear 62 is rotatably supported on the side surface thereof. And a supporting carrier 64. A plurality of support shafts 65 are radially projected on the carrier 64 at equal intervals, one end of the support shaft 65 is fixed to the carrier 64, and the other end is disposed on the same axis. It is fixed to a disk-shaped support plate 66. A support pipe 67 for rotatably supporting the planetary gear 62 is fitted on the support shaft 65 and is rotatably supported. The support pipe 67 has a large-diameter portion and a small-diameter portion. The above-described planetary gear 62 is externally fitted to the small-diameter portion to rotatably support the inner peripheral surface of the ring gear 63 in the large-diameter portion. In support, it will also serve as a floating mediation wheel. The ring gear 63 is disposed at a position sandwiched between the carrier 64 and the support plate 66, and its axial displacement is regulated by the both 64 and 66. The gear 77 on the outer peripheral surface of the ring gear 63 is connected to the output gear 7 on the fourth transmission shaft 24.
1 is engaged. A gear 78 is also engraved on the outer peripheral surface of the carrier 64, and the gear 78
The gear 35 meshes with the gear 35 supported above.

An output shaft 26 is integrally formed at the front end of the carrier 64 on the same axis. An output gear 72 is fixed on the output shaft 26 so as not to rotate relatively. The left and right axles 10L and 10R are supported in parallel with the output shaft 26, and the outer ends of the left and right axles 10L and 10R are projected out of the transmission case 2.
A differential device 7 is provided between 0L and 10R, and differentially connects the two axles 10L and 10R. The differential device 7
The ring gear 81 is meshed with the output gear 72 described above.
With this configuration, the rotation of the output shaft 26 is
The transmission is transmitted from the output gear 72 on the gear 6 to the ring gear 81 of the differential device 7, and the axles 10L and 10R are driven.

The state of power transmission by this configuration will be described. That is, when the pressure oil is supplied to the port A, the first hydraulic clutch 11 is engaged, and the engine power input to the input shaft 20 is transmitted to the clutch case 30 → the clutch boss 32 → the first transmission shaft 21. Then, the gear 43 is driven. Since the gear 43 meshes with the gear 79 and the gear 80, the power of the gear 43 is transmitted to both the gears 79 and 80.
Is branched and input. The power of the gear 79 is transmitted from the second transmission shaft 22 → the first continuously variable transmission 4 → the fifth transmission shaft 25, and is input to the sun gear 61 of the planetary gear device 3 to rotate the sun gear 61 forward. The second transmission shaft 22, the first continuously variable transmission 4, and the fifth transmission shaft 25 constitute a first transmission path T1 for driving the sun gear with continuously variable transmission. On the other hand, the power of the gear 80 is transmitted from the third transmission shaft 23 → the second continuously variable transmission 5 → the fourth transmission shaft 24, and finally from the output gear 71 to the ring gear 63 of the planetary gear device 3. The ring gear 63 is rotated in the forward direction.
The third transmission shaft 23, the second continuously variable transmission 5, and the fourth transmission shaft 24 constitute a second transmission path T2 for continuously driving the ring gear.

The planetary gears 62.6 of the planetary gear set 3
Are simultaneously meshed with the sun gear 61 and the internal gear integrally formed on the inner peripheral surface of the ring gear 63. Accordingly, the power transmitted through the first continuously variable transmission 4 when continuously transmitted from the second transmission shaft 22 to the fifth transmission shaft 25 and the third transmission shaft 23 are transmitted to the planetary gear 62. When the power is transmitted to the fourth transmission shaft 24, both the powers that have been continuously variable by the second continuously variable transmission 5 are input. The forward rotation of the sun gear 61 acts to revolve the planetary gear 62 in the forward direction, while the ring gear 6 rotates.
The forward rotation of No. 3 causes the planetary gear 62 to revolve in the reverse direction. Therefore, the rotation direction and the speed of the carrier 64 pivotally supporting the planetary gear 62 depend on the sun gear 6.
1. The rotation of the carrier 64 is differentially determined according to the magnitude of the forward rotation of the ring gear 63, and the rotation of the carrier 64 is transmitted to the axles 10L and 10R via the output gear 72 and the differential device 7, and It drives 10L and 10R.

Here, the rotation speed of the sun gear 61 is:
The gear ratio of the first continuously variable transmission 4, that is, port C / port D
The rotation speed of the ring gear 63 is determined by the hydraulic pressure of the hydraulic oil supplied to the second continuously variable transmission 5,
That is, it is determined by the hydraulic pressure of the hydraulic oil supplied to the ports E and F. The ports A, B, C, D, E and F are respectively connected to switching valves and proportional valves (not shown) through piping,
These valves are switched by operating a main shift lever (not shown), so that the hydraulic oil from the hydraulic pump 6 is supplied. Therefore, by operating the main transmission lever, the transmission ratio of the first and second continuously variable transmissions 4 and 5 can be changed through the supply of hydraulic oil to the ports C, D, E, and F, the supply stop, and the change in hydraulic pressure. The control for changing the rotation direction and the rotation speed of the carrier 64 can be arbitrarily changed.

When pressure oil is supplied to the port B, the first hydraulic clutch 11 is disengaged, the second hydraulic clutch 12 is engaged, and the gear 35 is driven. You. Here, the carrier 6 of the planetary gear set 3
4 is directly meshed with the gear 35 by the gear 78, the carrier 64 is directly driven by the gear 35 without passing through the above-described continuously variable transmissions 4, 5 and the like, and the axles 10L, 10L
R will be driven.

Next, the manner of shifting using this mechanism will be outlined. That is, before starting the engine, the hydraulic pump 6 is not driven and the pressure oil is not supplied to the ports A and B, so that the first and second hydraulic clutches 11 and 12 are disengaged. The main shift lever is "neutral"
Position. When the engine is driven from this state and the pressure oil is supplied to the port A, the first hydraulic clutch 11 is engaged, the gear 43 is driven, and the gears 79 and 80 meshed with the gear 43 are rotated. . Here, as described above, the main shift lever is set to the "neutral" position. When the main shift lever is in the "neutral" position, the pressure oil is not supplied to the ports C and E, while the pressure oil is supplied to the ports D and F. The valve is set so that is supplied. Accordingly, in both the first and second continuously variable transmissions 4, 5, the effective diameter of the driving side split pulleys (41, 51) is the smallest, and the effective diameter of the driven side split pulleys (42, 52) is the largest. Is in a state. The rotation of the gear 79 is based on the first transmission path T1 described above.
, And the rotation of the gear 80 is input to the ring gear 63 via the above-described second transmission path T2.

Here, as described above, the first and second continuously variable transmissions 4 and 5 are both driven-side split pulleys (4 and 5).
When the effective diameter of the driven pulley (42.52) is the largest and the effective diameter of the driven pulley (42.52) is the largest, the power input to the sun gear 61 corrects the planetary gear 62. The action of revolving in the forward direction (hereinafter referred to as “forward revolving action”) and the action of the power input to the ring gear 63 revolving the planetary gear 62 in the reverse direction (hereinafter “reverse revolving action”) are balanced. The gear ratio of the continuously variable transmissions 4 and 5, the sun gear 61 and the ring gear 6 are set so that the gear 62 rotates and does not revolve.
3. The number of teeth of the internal gear 62 and the like are set. Therefore, in this case, since the planetary gear 62 does not revolve,
The carrier 64 is not driven, and the axles 10L and 10R are not driven (neutral state).

Next, the operation when the operator tilts the shift lever from the above-mentioned "neutral" position to the "forward" side will be described. That is, when the shift lever is tilted to the "forward" side, the valve is switched, the supply of pressure oil to the port C is started, and the hydraulic pressure is increased according to the tilt operation amount of the shift lever. On the other hand, the pressure of the port D is reduced, and the oil pressure is reduced according to the amount of tilt operation of the shift lever. The ports E and F are the same as in the above-described neutral case. The port E is not supplied with pressure oil, while the port F is supplied with pressure oil. Accordingly, the speed ratio of the first continuously variable transmission 4 is changed to increase the speed of the sun gear 61, and the forward revolving action of the sun gear increases to exceed the reverse revolving action of the ring gear 63, so that the planetary gear 62 moves in the forward direction. Then, the carrier 64 is driven in the forward direction, and the neutral state is broken, and the vehicle travels forward. Here, the speed-up of the vehicle is continuously performed up to a speed corresponding to the position of the shift lever. For example, when the shift lever is set to the “third forward speed” position, the speed increase is gradually performed until the vehicle finally reaches a speed equivalent to the third speed. The degree of acceleration (acceleration) can be adjusted, for example, by providing a throttle in a circuit for supplying pressure oil to the ports C and D.

When the shift lever is further tilted to the "high-speed forward" position, the supply of pressure oil to ports A and C is stopped, and the supply of pressure oil to port B is started instead. Next, the valve is switched. Accordingly, the engagement of the first hydraulic clutch 11 is released and the gear 43 is not driven, and the sun gear 61 and the ring gear 63 are not driven.
Is stopped, the second hydraulic clutch 12 is fitted, the gear 35 is driven, and the carrier 64, which is interlocked to the gear 35 via the gear 78, is directly driven, and the axles 10L and 10R The vehicle is driven at a high speed in the forward direction, and the vehicle travels at a high speed equivalent to the fourth speed.

In this case, the first and second continuously variable transmissions 4 and 5 are free, and the disengaged first hydraulic clutches 11 idle at substantially the same rotational speed in the same direction. , Output loss can be reduced. That is, since the input sides of the two hydraulic clutches 11 and 12 are simultaneously driven and the rotation direction during shifting is not changed, the shock during shifting is large and the loss can be reduced.

On the other hand, the operation when the operator tilts the shift lever from the above-mentioned "neutral" position to the "reverse" side will be described. That is, when the shift lever is tilted to the "reverse" side, the valve is switched to start supplying the pressure oil to the port E, and the supply of the pressure oil to the port F is released (depressurized). The ports C and D are the same as in the above-described neutral case. The supply of the pressure oil is not supplied to the port C, and the pressure oil is supplied to the port D. Therefore, the speed ratio of the second continuously variable transmission 5 is changed, and the speed of the ring gear 63 is increased.
, The planetary gear 62 is revolved in the reverse direction, the carrier 64 is driven in the reverse direction, and the vehicle travels rearward. Note that, as in the present embodiment, the transmission 1
When the vehicle is used in reverse, the vehicle speed is generally limited to a certain speed or less. For this reason, in the present embodiment, the restriction ring 99 is fitted to the split pulley 51 on the driving side of the second continuously variable transmission 5 so that the minimum value of the effective diameter of the split pulley 51 becomes equal to or more than a certain value. Set to achieve the above objectives.

Next, an example of a configuration for decelerating the vehicle will be described. That is, for example, the shift lever is set to the “third forward speed” position, the pressure oil is supplied to the port C as described above, and the supply of the pressure oil is released to the port D, so that the vehicle corresponds to the third speed. It is assumed that the speed has been increased to the speed shown in FIG. When the shift lever is operated to "second speed" from this state, the speed is also reduced by depressurizing the port C and restarting the supply of the pressurized oil to the port D (that is, by changing the speed ratio of the first transmission 4). Can be performed, but pressure oil is supplied to the port E while the state of the ports C and D remains unchanged.
The deceleration can also be performed by a method of releasing the supply of the pressure oil to the motor (ie, a method of changing the speed ratio of the second transmission 5). That is, by changing the gear ratio of the second continuously variable transmission 5 to increase the speed of the ring gear 63 while maintaining the state where the sun gear 61 is increased in speed by the first continuously variable transmission 4, By reducing the revolving speed of the planetary gear 62, the vehicle can be decelerated.

The configuration of the transmission described above is an example, and the present invention is not limited to this configuration. For example, it may be configured as in a modified example described below. Hereinafter, this configuration will be described. FIG. 8 is a skeleton diagram of a transmission according to a modification, FIG. 9 is a schematic side view showing meshing of gears, and FIG.
FIG. 11 is a sectional view taken along the line YY, and FIG. 12 is a sectional view taken along the line ZZ. FIG. 13 is a front view showing the appearance of the transmission, and FIG. 14 is a side view of the transmission.

Hereinafter, a specific configuration of a transmission 1 'according to this modified example will be described. That is, as shown in FIGS. 10 to 12, a planetary gear device 3, a plurality of shafts and gears for power transmission, and first and second split pulley type continuously variable transmissions 4, 5 are provided in a transmission case 2. Is stored. Transmission case 2 is shown in FIGS.
As shown above, the case 2a
2b and 2c are joined.

The configuration of power transmission of this transmission 1 'is substantially the same as that of the above-described transmission 1, but
It mainly has some differences in the layout of each transmission path. Hereinafter, the different point will be mainly described. That is, the transmission 1 ′ according to this modification does not have a configuration in which a differential device is provided inside the transmission case 2, and the output shaft 26 is provided on the side surface opposite to the input shaft 21. Further, a pump drive shaft (reference numeral 27 shown in FIG. 1), a pump output gear, and a pump drive gear (reference numerals 73 and 70) provided for driving the hydraulic pump are omitted,
Instead, the hydraulic pump 6 is arranged in a middle part of the input shaft 20 (FIGS. 8 and 10). Further, the gear meshing with the gear 43 on the first transmission shaft 21 is not a gear integrally provided on a half of the split pulley as in the transmission 1 described above, but is a spur gear separately provided on the shaft. (Reference numerals 79 and 80 shown in FIGS. 8, 10 and 11). The split pulleys (41, 42) of both continuously variable transmissions 4, 5
The position where the (51) and (52) are disposed is opposite to the input shaft 20 in the transmission 1 described above.
In this transmission 1 ', the position is closer to the input shaft 20.

The planetary gear 6 of the planetary gear device 3
The carrier 64 that pivotally supports 2 is disposed at a position opposite to the input shaft 20 with the planetary gear 62 interposed therebetween, and the output shaft 26 formed integrally with the carrier 64 is opposite to the input shaft 20. The transmission case 2 protrudes outward from the side surface. The fifth transmission shaft 25 for driving the sun gear 61 of the planetary gear device 3 is supported on the opposite side of the transmission 1, that is, on the position closer to the input shaft 20 than the sun gear 61, and the fifth transmission shaft The split pulley 41 on the driven side of the first continuously variable transmission 4 disposed at 25 is also disposed at a position closer to the input shaft 20 than the sun gear 61.

Transmission 1 'according to this modified example
Is constructed as described above, but the method of shifting by the transmission 1 'is exactly the same as the method of shifting by the transmission 1 described above. That is, port A
When pressure oil is supplied to the port C, D, E, F
By supplying and canceling the supply of pressurized oil to the gears, the gear ratios of the first and second continuously variable transmissions 4 and 5 are changed, and the magnitude of the forward and reverse revolutions of the planetary gears is increased. Is changed to control the rotational direction and rotational speed of the carrier 64 that is differentially driven, and the rotation obtained by this is output from the output shaft 26. When pressure oil is supplied to the port B, the carrier 64 of the planetary gear device 3 is directly driven by the gear 35 on the first transmission shaft 21, and the driving force is output from the output shaft 26. The Rukoto.

Although the embodiments of the present invention have been described above, the technical scope of the present invention is not limited to the above-described embodiments, and the present invention will be apparent from the matters described in the present specification and drawings. It covers a whole range of technical ideas that are truly intended.

[0042]

The present invention is configured as described above.
The following effects are obtained.

That is, as set forth in claim 1, a planetary gear set and two continuously variable transmissions are arranged in a transmission case,
The power from the input shaft is input to each of the two continuously variable transmissions, and the output of one continuously variable transmission is transmitted to the sun gear of the planetary gear unit, and the output of the other continuously variable transmission is the ring gear of the planetary gear unit. Power is transmitted to the output shaft from the carrier that supports the planetary gears of the planetary gear device, so that the carrier is differentially driven using two continuously variable transmissions, so Shift control can be easily performed, and the transmission case can be easily made compact.

According to a second aspect of the present invention, since the two continuously variable transmissions are continuously variable transmissions using a split pulley and a belt, a neutral output mechanism is provided by canceling the outputs of the two. Neutral can be easily achieved. That is, when only one split pulley type continuously variable transmission is used, it is difficult to achieve neutrality because the engine is always running when the engine is driven. Since the shift is performed by differentially extracting the output of the pulley-type continuously variable transmission, the neutral state can be easily achieved. Therefore, switching from the neutral state to driving (for example, switching from stop to start when used in a vehicle) can be performed smoothly without special skill.

Since the effective diameter of the split pulley is changed by hydraulic control as described in claim 3, once a throttle is set in a circuit for performing the hydraulic control, the speed ratio of the continuously variable transmission can be changed. Can be easily and stably controlled.
That is, smooth shifting can be performed with a simple operation.

According to a fourth aspect, in the transmission according to any one of the first to third aspects, when the shift operation means is set to the "neutral" position, the two continuously variable transmissions are: Since the gear ratio is controlled so that the rotational speeds of the sun gear and the ring gear do not cause the planetary gear to revolve, neutralization can be easily achieved.

According to a fifth aspect of the present invention, a planetary gear set, a pair of clutches and two continuously variable transmissions are arranged in a transmission case, and power from an input shaft is transmitted to the input side of each clutch. The output side of the clutch is linked to the input side of each of the two continuously variable transmissions, the output of one continuously variable transmission is transmitted to the sun gear of the planetary gear unit, and the output of the other continuously variable transmission is the planetary gear. Is transmitted to a ring gear of the planetary gear device, and power is transmitted from a carrier pivotally supporting a planetary gear of the planetary gear device to an output shaft, and an output side of another clutch is connected to the output shaft without passing through the continuously variable transmission. , So that it is possible to easily switch between continuously variable transmission and gear type transmission. Further, since the input sides of the two clutches are simultaneously driven and the rotation directions of the clutches are not reversed in the forward and reverse directions even at the time of the switching, the shock at the time of shifting can be reduced and the loss of output can be reduced.

[Brief description of the drawings]

FIG. 1 is a skeleton diagram of a transmission according to one embodiment of the present invention.

FIG. 2 is a schematic side view showing meshing of gears.

FIG. 3 is a sectional view taken along line XX in FIG. 2;

FIG. 4 is a sectional view taken along the line YY.

FIG. 5 is a sectional view taken along the line ZZ.

FIG. 6 is a front view showing the appearance of the transmission.

FIG. 7 is a side view of the same.

FIG. 8 is a skeleton diagram of a transmission according to a modification.

FIG. 9 is a schematic side view showing meshing of gears.

FIG. 10 is a sectional view taken along line XX in FIG. 9;

FIG. 11 is a sectional view taken along the line YY.

FIG. 12 is a sectional view taken along the line ZZ.

FIG. 13 is a front view showing the appearance of the transmission.

FIG. 14 is a side view of the same.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Transmission 2 Transmission case 3 Planetary gear device 4 1st continuously variable transmission 5 2nd continuously variable transmission 10 Axle 20 Input shaft 26 Output shaft 61 Sun gear 62 Planetary gear 63 Ring gear 64 Carrier

 ──────────────────────────────────────────────────続 き Continued on the front page F term (reference) 3J028 EA21 EA25 EB44 FA06 FB05 FB12 FC13 FC23 FC32 FC42 FC67 GA13 GA14 3J050 AA02 AB03 BA04 BB12 CD01 CE08 DA06

Claims (5)

[Claims] 1. A planetary gear set and two continuously variable transmissions are arranged in a transmission case, and power from an input shaft is input to each of the two continuously variable transmissions, and the output of one continuously variable transmission is a planet. The output of the other continuously variable transmission is transmitted to the sun gear of the gear device, and the output of the other continuously variable transmission is transmitted to the ring gear of the planetary gear device,
A transmission configured to transmit power to an output shaft from a carrier pivotally supporting a planetary gear of a planetary gear device. 2. The transmission according to claim 1, wherein the two continuously variable transmissions are continuously variable transmissions using a split pulley and a belt. 3. The transmission according to claim 2, wherein the effective diameter of the split pulley is changed by hydraulic control. 4. The transmission according to any one of claims 1 to 3, wherein when the shift operation means is set to a "neutral" position, the two continuously variable transmissions include a sun gear and a ring gear. A transmission characterized in that the transmission gear ratio is controlled so that the number of revolutions is such that the planetary gear does not revolve. 5. A planetary gear set, a pair of clutches, and two continuously variable transmissions are arranged in a transmission case, and power from an input shaft is transmitted to an input side of each clutch, and an output side of one clutch is provided. Is linked to the input of each of the two continuously variable transmissions, the output of one continuously variable transmission is transmitted to the sun gear of the planetary gear unit, and the output of the other continuously variable transmission is transmitted to the ring gear of the planetary gear. The planetary gear device is configured to transmit power to the output shaft from a carrier pivotally supporting the planetary gear, and the output side of the other clutch is interlocked to the output shaft without passing through the continuously variable transmission. The transmission of claim 1, wherein: