JP2001108083A - Transmission having planetary gear - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a transmission having a planetary gear that can downsize the transmission, simplify a structure, and facilitate the change of a transmission characteristic. SOLUTION: This transmission 1 has planetary gears 20, 40, 60 comprising respective three gears of ring gears 21, 41, 61, planetary gears 24, 44, 64, and sun gears 22, 42, 62. The sun gears 22, 42, 62 functioning as control members are supported on a fixing shaft 9 via one-way clutches 15, 16, 17. Hydraulic clutches are interposed between ring gears 21, 41, 61 functioning as input members and the planetary gears 24, 44, 64 functioning as output members, and oil pressure controlled so as to operate the hydraulic clutches and perform its intermittence is supplied to the hydraulic clutches through an oil feed passage 90 provided in a fixing shaft 9. The oil feed passage 90 is shared by the plurality of planetary gears 20, 40, 60, and a rotary valve 91 is rotated and controlled via an actuator 92 operated by a transmission control device.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a transmission equipped with a planetary gear, and more particularly to a transmission equipped with a planetary gear that facilitates downsizing of the transmission and easy change of shift characteristics.

[0002]

2. Description of the Related Art Conventionally, in a transmission equipped with a planetary gear set, a gear functioning as an input member among three gears of a ring gear, a planetary gear, and a sun gear constituting the planetary gear set. And a gear that functions as an output member, and a gear holding unit or a control unit that functions as a control member that controls power transmission between these two members is provided alongside the planetary gear device. Was becoming larger and more complicated. No. 109646).

The applicant of the present invention has solved the above-mentioned problems of the conventional transmission equipped with a planetary gear set, and has made it possible to reduce the size and the structure of the power transmission device and to change the transmission ratio. A transmission equipped with a planetary gear device that enables simplification and the like has been developed.
A patent application was filed as No. 2.

However, in the present invention, since the speed change characteristics of the planetary gear device are uniquely determined by the centrifugal force acting on the weight constituting the centrifugal clutch,
It was difficult to freely change the shifting characteristics depending on the running conditions.

Conventionally, there is a transmission having a planetary gear device, which shifts by switching hydraulic pressure. However, a solenoid or a piston for switching hydraulic pressure is used, and the structure is complicated. T (general 4 wheels A
T).

SUMMARY OF THE INVENTION The present invention solves the above-mentioned problems of a conventional transmission equipped with a planetary gear set, and makes it possible to reduce the size and structure of the transmission, simplify the structure of the transmission, and easily change the transmission characteristics. It is an object of the present invention to provide a transmission provided with a planetary gear device that enables the transmission.

[0007]

SUMMARY OF THE INVENTION The present invention relates to a transmission provided with a planetary gear unit which solves the above-mentioned problems. Of the three gears, a ring gear, a planetary gear, and a sun gear, which are arranged on a fixed shaft and constitute the planetary gear device, a gear functioning as a control member is supported by the fixed shaft via a one-way clutch. In a transmission including a planetary gear device, a hydraulic clutch is interposed between a gear functioning as an input member and a gear functioning as an output member among the three gears, and the hydraulic clutch includes A planetary gear unit wherein pressure oil controlled to operate and disconnect the hydraulic clutch is supplied through an oil supply passage provided in the fixed shaft. A transmission device provided with.

According to the first aspect of the present invention, the shift characteristic of the planetary gear device is determined by the supply timing of the pressure oil (hydraulic oil) for connecting and disconnecting the hydraulic clutch. As a result, by appropriately controlling the supply timing of the pressure oil in accordance with the running conditions, the shift characteristics of the planetary gear device can be appropriately changed in accordance with the running conditions, and the running performance can be improved.

The pressure oil for intermittently operating the hydraulic clutch is as follows:
Since the oil is supplied through the oil supply passage provided in the fixed shaft, the pressure oil can be supplied by effectively utilizing the empty space in the fixed shaft, and the outer diameter of the transmission can be reduced. Thus, the transmission can be downsized.

Further, by configuring the invention according to claim 1 as described in claim 2, the plurality of planetary gear devices are
Since the oil supply passage is shared by the plurality of planetary gear devices, the transmission device having the plurality of planetary gear devices can be downsized.

According to the third aspect of the present invention, the oil supply passage is communicated / blocked by a rotary valve coaxially arranged in a fixed shaft. By controlling the rotation of the rotary valve, it is possible to control the supply timing of the pressure oil to the hydraulic clutch, and the control becomes extremely easy. Further, the structure of the rotary valve is simple, and even if the number of gears is different, the structure change can be reduced.

Further, by constituting the invention of claim 3 as described in claim 4, the rotary valve is
The rotation is controlled by an actuator operated by a shift control device, and the actuator is coaxially arranged in a fixed shaft. As a result, the actuator can be arranged by effectively utilizing the empty space in the fixed shaft, and the transmission can be further reduced in size.

According to a fifth aspect of the present invention, the transmission having the planetary gear device is provided on the side of the vehicle wheels. Are arranged along the front-back direction. As a result,
The transmission in the vehicle can be miniaturized, and can be arranged close to the side of the rear wheel.

Further, according to the present invention, the gear functioning as a control member is a sun gear, and the gear functioning as an input member is provided. Are ring gears, and the gear functioning as an output member is a planetary gear. As a result, of the three gears constituting the planetary gear device, the sun gear which is the innermost gear is supported by the fixed shaft via the one-way clutch, so that the control is performed among the three gears constituting the planetary gear device. The configuration in which the gear functioning as a member is supported on the fixed shaft via the one-way clutch can be extremely simplified.

[0015]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS One embodiment of the invention described in claims 1 to 6 of the present application shown in FIGS. 1 to 6 will be described below. 1 is a longitudinal sectional view of a transmission equipped with a planetary gear device according to the present embodiment, FIGS. 2 and 3 are partially enlarged views of FIG. 1, and FIG. 4 is a planetary gear in one operation state of the transmission of FIG. FIG. 5 is a longitudinal sectional view of the gear device.
6 is an enlarged view of a shift rotary valve used in the transmission shown in FIG. 1, and FIG. 6 is an operation diagram of the shift rotary valve.

In FIG. 1 to FIG. 3, the transmission 1 including the planetary gear units 20, 40, 60 according to the present embodiment is used, for example, as a reduction gear of an internal combustion engine mounted on a motorcycle. The rotation of the crankshaft of the internal combustion engine (not shown) is input to the driven gear 2 arranged substantially at the center of the transmission 1 in FIG. 1, and is output from the output gear 3 arranged at the right end after being reduced in speed. You.

The driven gear 2 has a plurality of projections formed in a circumferential direction on a step portion of the rotary cylinder 4 having a large-diameter portion and a small-diameter portion, and a plurality of projections formed on the driven gear 2 corresponding to these projections. By fitting the circular holes into each other, the rotary cylinder 4 is integrally connected to the rotary cylinder 4.
The right small diameter portion 4b is spline-fitted to the inner 6a of the centrifugal start clutch 6 and is rotatably supported on the center shaft 9 via the needle bearings 7, 8. The boss portion of the output gear 3 is also rotatably supported on the center shaft 9 via a needle bearing 85. Needle bearing 8
Also rotatably supports the outer 6b of the centrifugal start clutch 6.

Between the driven gear 2 and the output gear 3,
In FIG. 1, a centrifugal start clutch 6, a second-speed shift clutch 12, a third-speed shift clutch 13, and a fourth-speed shift clutch 14 are arranged on the center shaft 9 in order from the left. The second-speed transmission clutch 12, the third-speed transmission clutch 13, and the fourth-speed transmission clutch 14 are rotatably supported on one side only on the center shaft 9 via one-way clutches 15 to 17, and are arranged respectively. I have.

The center shaft 9 is a fixed shaft, and its right end is not shown in detail in FIG. 1, but is non-rotatably fixed to a right case portion 10a of a case 10 such as a crankcase. Have been. FIG. 1 of the center shaft 9
The left end is supported by the bearing of the left case portion 10b.

Therefore, when the driven gear 2 is rotated by the crankshaft of the internal combustion engine through the meshing of the gears, the inner 6a of the centrifugal starting clutch 6 rotates integrally with the driven gear 2. When the rotation speed reaches the first predetermined rotation speed, the weight of the inner 6a comes into contact with the inner peripheral surface of the outer 6b of the centrifugal start clutch 6, and the centrifugal start clutch 6 is brought into the connected state.

Since the outer 6b of the centrifugal start clutch 6 is integrally connected to the outer 12a of the adjacent second speed transmission clutch 12 on the center shaft 9 by the rivet 18, the centrifugal start clutch 6 is connected as described above. In this connection, the outer 12a also rotates integrally with the driven gear 2.

The ring gear 21 of the first planetary gear set 20 is fitted to the inner peripheral edge of the outer cylindrical portion of the outer cylinder 12a of the rotary drum-shaped second speed transmission clutch 12. On the center shaft 9, a sun gear boss 22a integral with the sun gear 22 of the first planetary gear set 20 is rotatably supported on only one side via the one-way clutch 15 adjacent to the outer 12a. . The one-way clutch 15 is press-fitted between the center shaft 9 and the sun gear boss 22a.

A planetary gear 24 is interposed between the ring gear 21 and the sun gear 22 of the first planetary gear device 20 so as to mesh with these gears. The first planetary gear set 20 is constituted by the ring gear 21, the sun gear 22, and the planetary gear 24.

The outer 12a of the second-speed transmission clutch 12
A plurality of annular plate-shaped clutch clutches 25 are implanted on the inner peripheral surface of the outer cylindrical portion. The planetary gear boss 26a, which is a boss of the clutch center 26 that acts as a carrier of the planetary gear 24, faces the planetary gear 24.
The outer peripheral surface of the ring-shaped gearshift friction disc
A plurality of sheets 28 are slightly separated from the clutch plate 25 and are rotatably fitted thereto.

The outer 12a of the second-speed transmission clutch 12 has a boss portion 30 which is fitted on the center shaft 9 and rotates while sliding at the center thereof. Inner tubular portion 30 extended from the end in the same direction as the outer tubular portion
a. The inner cylindrical portion 30a and the sun gear boss 22
A needle bearing 31 is interposed between a and a. The boss portion 30 has a radially-directed through hole at equal intervals in the circumferential direction.
30b are formed in plurality.

The bottom of the outer 12a sandwiched between the outer cylindrical portion and the inner cylindrical portion 30a is a cylinder chamber 32, in which a piston 33 is slidably housed. I have. In the cylinder chamber 32, as will be described later,
When the rotation of 12a reaches the second predetermined number of rotations, hydraulic oil is supplied from the oil supply passage 90 provided in the center shaft 9 to the through hole 34a formed in the center shaft 9 and the above-described through hole 30b. Supplied.

Then, this hydraulic oil pushes the piston 33 rightward in FIG. 3 against the urging force of the wave spring 35 to bring the clutch plate 25 and the friction disk 28 into contact. In this way, the second speed transmission clutch 12
Is connected, and the clutch center 26 and the planetary gear 24 rotate integrally with the outer 12a of the second-speed transmission clutch 12. As a result, the entire first planetary gear device 20 rotates integrally with the outer 12a. As described above, the second speed transmission clutch 12 is configured as a hydraulic clutch that is intermittently operated by hydraulic pressure. 27 is a return spring.

Here, it can be seen that the inner part of the second speed transmission clutch 12 comprises the components of the first planetary gear device 20 excluding the ring gear 21 and the transmission clutch plate 28. These two-speed transmission clutch outer 12a
The second-speed transmission clutch 12 is constituted by the second-speed transmission clutch inner.

The second speed transmission clutch 12 operates as follows. First, the rotation speed of the driven gear 2 reaches a first predetermined rotation speed (LOW ratio), and the centrifugal start clutch 6
Is in the connected state, the outer 12
a rotates, the ring gear 21 integral with the outer 12a rotates, and the rotational power is input to the first planetary gear device 20. The ring gear 21 functions as an input member in the first planetary gear device 20.

In the first planetary gear set 20, the ring gear
When the 21 rotates, the sun gear 22 is fixed by the one-way clutch 15 so that it cannot rotate in the reverse direction, so that the planetary gear 24 revolves while rotating between the ring gear 21 and the sun gear 22.

Since the clutch center 26 of the planetary gear 24 is integrally connected to the outer 13a of the adjacent third-speed transmission clutch 13 on the center shaft 9, the planet gear 24 revolves through this integrated connection. The power is transmitted to the outer 13a of the third-speed transmission clutch 13. The number of revolutions of the planetary gear 24 is reduced with respect to the number of revolutions of the ring gear 21 based on a predetermined reduction ratio of the first planetary gear device 20.

The planetary gear 24 functions as an output member in the first planetary gear device 20. The sun gear 22 is located between the ring gear 21 functioning as an input member and the planetary gear 24 functioning as an output member, and functions as a control member for controlling the reduction ratio of the first planetary gear device 20.

When the rotation speed of the driven gear 2 further increases (LOW ratio → second speed ratio), the rotation speed of the ring gear 21 further increases, and the revolving speed of the planetary gear 24 also increases. When a predetermined rotational speed level is reached, pressurized oil is supplied into the cylinder chamber 32, and the piston 33 is pushed rightward in the drawing to bring the clutch plate 25 into contact with the friction disk. As a result, the second speed transmission clutch 12 is engaged, and the first planetary gear set 20
The entirety rotates integrally with the outer gear 12a of the second speed transmission clutch 12 and the driven gear 2. And this rotation is the first
The clutch centers 26 and 3 of the planetary gear 24 of the planetary gear set 20
The speed transmission clutch 13 is transmitted to the outer 13a without being decelerated via an integral connection with the outer 13a.

The structure of the third-speed transmission clutch 13 is basically the same as that of the second-speed transmission clutch 12. Therefore, a portion corresponding to each component 20 to 35 of the second-speed transmission clutch 12 includes
Reference numerals from 55 to 55 are attached, and the first digit and the subscript are indicated by matching each other, and the detailed description is omitted. The same applies to the configuration of the fourth-speed transmission clutch 14, and reference numerals 60 to 75 are assigned thereto, and the first-digit number and the suffix are indicated by matching each other, and detailed description is omitted. .

As described above, the second speed transmission clutch 12
The rotation of the outer 12a is the outer 13 of the third-speed transmission clutch 13.
If the speed is transmitted to a
The third-speed transmission clutch 13 operates in exactly the same manner as the second-speed transmission clutch 12, and applies rotation input to the outer 13a to the clutch center 46 of the planetary gear 44 of the second planetary gear unit 40 and the fourth-speed transmission clutch. The transmission is performed to the outer 14a with or without deceleration through the integral connection of the 14 with the outer 14a.

When the rotation input to the outer 13a is small (the number of rotations is low), the third-speed transmission clutch 13 transmits this rotation input to the outer 14a of the fourth-speed transmission clutch 14 at a reduced speed. Further, when the rotation input is large (the rotation speed is high) and reaches a third predetermined rotation speed (second speed ratio →
In the (third speed ratio), the third speed transmission clutch 13 is in the connected state, so that this rotation input is transmitted to the outer 14a of the fourth speed transmission clutch 14 without deceleration.

As described above, the third-speed transmission clutch 13
The rotation of the outer 13a is the outer 14 of the fourth-speed transmission clutch 14.
If the speed is transmitted to a
The fourth speed transmission clutch 14 operates in exactly the same manner as the third speed transmission clutch 13, and applies rotation input to the outer 14 a between the clutch center 66 of the planetary gear 64 of the third planetary gear unit 60 and the output plate 80. The power is transmitted to the output plate 80 via the integral connection with or without deceleration.

When the rotation input to the outer 14a is small, the fourth-speed transmission clutch 14 transmits the rotation input to the output plate 80 at a reduced speed. Also, when the rotation input is large and reaches the fourth predetermined rotation speed (3rd gear ratio →
In the fourth-speed ratio), the fourth-speed transmission clutch 14 is in the connected state, so that this rotation input is transmitted to the output plate 80 without deceleration.

Since the boss portion of the output plate 80 is integrated with the boss portion of the output gear 3, the rotation input transmitted to the output plate 80 is transmitted to the output gear 3 at the same speed, and this output is output. Output from gear 3.

As described above, each of the centrifugal start clutch 6, the second-speed shift clutch 12, the third-speed shift clutch 13, and the fourth-speed shift clutch 14 disposed between the driven gear 2 and the output gear 3 is provided. Of the rotation input transmitted to the driven gear 2 by the action of
The output is shifted from the output gear 3 in multiple stages according to

That is, when the rotation input transmitted to the driven gear 2 is within the range until the second speed transmission clutch 12 is connected, only the centrifugal start clutch 6 is in the connected state, and the rotation input is the transmission clutch. The speed is reduced to three stages by 12 to 14 and output from the output gear 3 (LOW ratio).

When the rotation increases and becomes lower than the rotational speed at which the third-speed transmission clutch 13 is connected, the centrifugal start clutch 6 and the second-speed transmission clutch 12 are in the connected state, and the rotation input is The speed is reduced in two stages by the clutches 13 and 14 (second speed ratio).

Further, when the rotation increases and becomes lower than the rotation speed at which the fourth-speed transmission clutch 14 is connected, the centrifugal start clutch 6, the second-speed transmission clutch 12 and the third-speed transmission clutch 13 are connected. In this case, the speed is reduced to one stage only by the fourth speed transmission clutch 14 (third speed ratio).

Further, when the rotation speed increases and reaches the rotation speed at which the fourth-speed transmission clutch 14 is connected, all of the centrifugal start clutch 6 and the transmission clutches 12 to 14 are in the connected state, and the rotation transmitted to the driven gear 2 is transmitted. The input is transmitted as it is to the output plate 80 at high speed, and is output from the output gear 3 (fourth ratio).

As described above, the transmission 1 in the present embodiment changes the rotation input transmitted to the driven gear 2 by the action of the transmission clutches 12 to 14 according to the magnitude (the magnitude of the number of rotations). The output is decelerated in three stages. Since the number of speed reduction steps depends on the number of transmission clutches formed of the same module, it is easy to change the speed ratio (reduction ratio).

Here, when the number of rotations of the driven gear 2 reaches a predetermined second to fourth number of rotations, each of the cylinder chambers 32, 52,
72 is supplied to the shift clutches 12 to 14 in sequence.
The supply structure of the pressure oil for sequentially connecting the
This will be described in detail with reference to FIG.

The center shaft 9 is formed of a hollow pipe, and the hollow portion serves as an oil supply passage 90 for supplying pressure oil to each of the cylinder chambers 32, 52, 72 of the transmission clutches 12 to 14. A rotary valve 91 is provided in the oil supply passage 90.
And an oil valve shaft 92 as an actuator for controlling the rotation of the rotary valve 91. The rotary valve 91 and the oil valve shaft 92 have their ends connected by pins. The right end of the center shaft 9 in FIG.
Blocked by 4.

Each of the cylinder chambers 32, 52,
The pressure oil supplied to the valve 72 is communicated / blocked by the rotation of the rotary valve 91, and the transmission clutches 12 to 14 are disconnected. For this purpose, the rotary valve 91 is provided with a number of valve ports 93a, 94a, 95a corresponding to the speed change clutches 12 to 14 at intervals in the axial direction and shifted in phase in the circumferential direction (FIG. 5, see FIG. 6).

When the number of rotations of the driven gear 2 reaches a predetermined second number of rotations, the first valve port 93a is brought into communication with the through hole 34a formed in the center shaft 9, and Is supplied to the cylinder chamber 32. As a result, the piston 33 pushes the clutch plate 25 against the urging force of the wave spring 35, and the transmission clutch 12 is brought into the connected state. Wave spring 35, shifting clutch
12 works to reduce shift shock when connected. 27 is a return spring.

When the rotation speed of the driven gear 2 reaches a predetermined third rotation speed, the second valve port 94a is brought into communication with the through hole 54a formed in the center shaft 9, and the second valve port 94a Is supplied to the cylinder chamber 52. As a result, the piston 53 pushes the clutch plate 45 against the urging force of the wave spring 55, and the transmission clutch 13 is connected. At this time, the transmission clutch 12 maintains the connected state.

When the number of rotations of the driven gear 2 reaches a predetermined fourth number of rotations (TOP), the third valve port 95a is brought into communication with a through hole 74a formed in the center shaft 9, and The pressure oil in the valve 91 is supplied to the cylinder chamber 72. Accordingly, the piston 73 pushes the clutch plate 65 against the urging force of the wave spring 75, and the transmission clutch 14 is brought into the connected state. At this time, the transmission clutch 12 and the transmission clutch 13 maintain the connected state. Therefore, all three shift clutches 12 to 14 are in the connected state.

The above-described rotation control of the rotary valve 91 is performed by a shift control device 100 (see FIGS. 1 and 2) via an oil valve shaft 92 functioning as an actuator. The shift control device 100 is a shift motor.
101, control gear 102, potentiometer 103,
It comprises a stopper pin 104 and the like. Hereinafter, the structure and operation of the shift control device 100 will be described.

In FIGS. 1 and 2, the oil valve shaft 92 protrudes from the left end of the center shaft 9 in FIG. 1 to extend, and is fixed to the left case portion 10b.
105, and control gear 102 at its end.
Is fitted. The control gear 102 is a motor mounting case 10 similarly fixed to the left case 10b.
6 meshes with the gear at the end of the rotating shaft of the speed change motor 101 attached to 6 and when the speed change motor 101 rotates a predetermined angle,
The rotation is transmitted to the rotary valve 91 via the control gear 102 and the oil valve shaft 92.

Reference numeral 103 denotes a potentiometer for detecting the rotation angle of the rotary valve 91, and a gear 109 thereof.
Are engaged with the control gear 102. 104 is a stopper pin provided with a plurality of rotary valves.
Position 91. Due to the positioning function of the stopper pin 104, the speed change motor 101
Since the power required for holding the position is unnecessary, the speed change motor 101 can be downsized.

The slide member 107 for holding the stopper pin 104 is slidably fitted on the shaft of the gear 109, and is always resiliently pushed toward the bearing plate 105 by the coil spring 108, and is formed on the bearing plate 105. The rotary valve 91 is stably held by falling into the recessed portion.

Signals from various sensors for detecting the running state of the vehicle are input to the speed change motor 101. For example, when a vehicle speed signal is input and the vehicle speed reaches a rotational speed at which the clutches of the centrifugal start clutch 6 and the second and third speed shift clutches 12 to 14 are connected and disconnected, the speed change motor 101
Rotates forward or backward by a predetermined angle to rotate or reversely rotate the rotary valve 91 via the oil valve shaft 92. Then, the combination of connection and disconnection of these clutches is changed to various types. Note that such rotation control of the rotary valve 91 may be performed by a manual operation without using the speed change motor 101.

In the portion of the center shaft 9 where the left end in FIG. 1 is supported by the bearing of the left case portion 10b, the inward portion of the bearing is hollowed out, and the flange lid member 11 is formed.
1 and the supply chamber for hydraulic oil (pressure oil)
0 is formed. Hydraulic oil pumped by an oil pump (not shown) is received by the supply chamber 110, and then flows into an oil supply passage 90 in the center shaft 9 through a through hole 112 formed in the center shaft 9. And
Fill the inside of the rotary valve 91.

The planetary gear train constructed as described above
The transmission 1 including 20, 40, and 60 is disposed, for example, on the side of a wheel 113 (see FIG. 1) of a motorcycle along the longitudinal direction of the vehicle. As described above, since the transmission 1 is miniaturized, it does not protrude greatly in the vehicle width direction.

When the internal combustion engine is started, a starting torque is input to a starting gear 81 (see FIG. 1) by a starting motor or a kick mechanism (not shown) through meshing of gears of a predetermined ratio.

As shown in FIG. 1, the starting gear 81 rotates via a starting one-way clutch 83 provided between the boss 81a and the large diameter portion 4a of the rotary cylinder 4. Cylinder 4
It is connected to. The boss 81a is rotatably supported on the center shaft 9 via a needle bearing 84.

Therefore, when the starting torque is input to the starting gear 81, the rotation input is transmitted to the driven gear 2 via the starting one-way clutch 83 and the rotary cylinder 4, and the rotation input is transmitted from the driven gear 2. Is output. Then, the crankshaft is rotated via a gear (not shown) that meshes with the driven gear 2, and the internal combustion engine is started.

Since the present embodiment is configured as described above, the following effects can be obtained. The planetary gear units 20, 40, 60 are arranged on a center shaft (fixed shaft) 9, and the ring gear 2 constituting the planetary gear units 20, 40, 60
1, 41, 61, planet gears 24, 44, 64, sun gear 22, 42, 62
Of the three gears, the sun gears 22, 42, and 62 functioning as control members are provided with the one-way clutches 15, 1 on the center shaft 9.
Planetary gear units 20, 40, 60 supported via 6, 17
In the transmission 1 provided with the three gears,
Between the ring gears 21, 41, 61 functioning as input members and the planetary gears 24, 44, 64 functioning as output members, a hydraulic clutch (the hydraulic clutch of the planetary gear device 20 includes a clutch plate 25, a friction disk 28, Cylinder chamber 32,
It comprises a piston 33 and a return spring 27. The hydraulic clutches of the planetary gear units 40 and 60 are also made of similar members (see FIG. 3). ) Are interposed, and the hydraulic oil is supplied to the hydraulic clutch via an oil supply passage 90 provided in the center shaft 9 so as to operate the hydraulic clutch and to perform the on / off operation. It has become.

As a result, the shift characteristics of the planetary gear units 20, 40, and 60 can be determined by the supply timing of the pressure oil for intermittently connecting the respective hydraulic clutches. By appropriately controlling, the gear shift characteristics of the planetary gear devices 20, 40, and 60 can be appropriately changed according to running conditions, and running performance can be improved.

The pressure oil for intermittently operating the hydraulic clutch is as follows:
Since the oil is supplied through the oil supply passage 90 provided in the center shaft 9, the pressure oil can be supplied by effectively using the empty space in the center shaft 9, and the outer diameter of the transmission 1 can be reduced. be able to. Thereby, the transmission 1 can be reduced in size.

Further, the plurality of planetary gear units 20, 40, 60
The oil supply passage 90 is arranged and transmitted on the center shaft 9.
Is shared by the plurality of planetary gear units 20, 40, 60, so that the transmission 1 including the plurality of planetary gear units 20, 40, 60
Can be reduced in size.

Further, since the oil supply passage 90 is communicated / blocked by a rotary valve 91 coaxially arranged in the center shaft 9, the rotary valve 91
, The timing of supply of pressure oil to each hydraulic clutch can be controlled, and the control becomes extremely easy. Further, the structure of the rotary valve 91 is simple, and even if the number of gears is different, the structure change can be reduced.

The rotation of the rotary valve 91 is controlled by an oil valve shaft 92 (actuator) operated by the transmission control device 100. The oil valve shaft 92 is coaxially arranged in the center shaft 9. Therefore, the oil valve shaft 92 can be disposed by effectively utilizing the empty space in the center shaft 9, and the transmission 1 can be further downsized.

Further, since the transmission 1 including the planetary gear units 20, 40, and 60 is disposed on the side of the vehicle wheels 113 along the front-rear direction of the vehicle, the transmission in the vehicle can be reduced in size. And can be arranged close to the side of the rear wheel, so that it does not overhang in the vehicle width direction.

Further, the gears functioning as control members are sun gears 22, 42, 62, the gears functioning as input members are ring gears 21, 41, 61, and the gears functioning as output members are planetary gears. 24, 44, and 64, the sun gears 22, 42, and 62, which are the innermost gears, of the three gears that constitute the planetary gear units 20, 40, and 60 are provided with the one-way clutch 15, The gears functioning as control members among the three gears constituting the planetary gear units 20, 40, 60 are supported by the one-way clutches 15, 16, 17 on the center shaft 9. The structure supported by the via can be greatly simplified.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view of a transmission provided with a planetary gear device according to an embodiment of the invention described in claims 1 to 6 of the present application.

FIG. 2 is a partially enlarged view of FIG.

FIG. 3 is a partially enlarged view of FIG. 1;

FIG. 4 is a longitudinal sectional view of the planetary gear device in one operation state of the transmission of FIG. 1;

FIG. 5 is an enlarged view of a shift rotary valve used in the transmission of FIG. 1;

FIG. 6 is an operation diagram of the speed change rotary valve.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 ... Transmission device, 2 ... Driven gear, 3 ... Output gear, 4 ...
Rotating cylindrical body, 4a: large diameter part, 4b: small diameter part, 6: centrifugal start clutch, 6a: inner, 6b: outer, 7, 8, needle bearing, 9: center shaft (fixed shaft), 10: case,
10a: Right case section, 10b: Left case section, 12: 2nd-speed transmission clutch, 12a: Outer, 13: 3rd-speed transmission clutch, 13a: Outer, 14: 4th-speed transmission clutch, 14a: Outer, 15 to 17: one-way clutch, 18: rivet, 20: first planetary gear set, 21: ring gear, 22: sun gear, 22a
… Sun gear boss, 24… Planetary gear, 25… Shift clutch plate, 26… Clutch center, 26a… Planetary gear boss,
27: Return spring, 28: Friction disk for speed change, 30: Outer boss, 30a: Inner cylindrical part, 30b: Through hole, 31: Needle bearing, 32: Cylinder chamber, 33: Piston, 34a, 34b: Through hole , 35 ... Wave spring, 40 ...
2nd planetary gear set, 41 ... ring gear, 42 ... sun gear, 42
a ... sun gear boss, 44 ... planetary gear, 45 ... shift clutch plate, 46 ... clutch center, 46a ... planetary gear boss, 47 ... return spring, 48 ... shift friction disc, 50 ... outer boss part, 50a ... inner cylindrical part , 50b
… Through hole, 51… needle bearing, 52… cylinder chamber, 53… piston, 54a, 54b… through hole, 55… wave spring, 60
... third planetary gear set, 61 ... ring gear, 62 ... sun gear,
62a: sun gear boss, 64: planetary gear, 65: shift clutch plate, 66: clutch center, 66a: planetary gear boss, 67: return spring, 68: shift friction disc, 70: outer boss, 70a: inner cylindrical part , 70b
… Through hole, 71… needle bearing, 72… cylinder chamber, 73… piston, 74a, 74b… through hole, 75… wave spring, 80
... output plate, 81 ... starting gear, 81a ... boss, 83 ... one-way clutch for starting, 84, 85 ... needle bearing, 90 ... oil supply passage, 91 ... rotary valve, 92 ... oil valve shaft, 93a ... valve port, 93b ... pore, 94a ... valve mouth, 94b ... pore, 95a ... valve mouth, 95b ... pore, 96-98 ... relief groove, 100
... Transmission control device, 101 ... Transmission motor, 102 ... Control gear, 103 ... Potentiometer, 104 ... Stopper pin, 105 ... Bearing plate, 106 ... Motor mounting case, 107
... Slide member, 108 ... Coil spring, 109 ... Gear, 110 ... Hydraulic oil (pressure oil) supply chamber, 111 ... Flange lid member, 112 ... Through hole, 113 ... Wheel, 114 ... Closing member.

Claims (6)

[Claims] 1. A planetary gear device is disposed on a fixed shaft, and among the three gears of the planetary gear device, a ring gear, a planetary gear, and a sun gear, one of the gears functioning as a control member is provided on the fixed shaft. In a transmission having a planetary gear set supported via a direction clutch, a hydraulic clutch is interposed between a gear functioning as an input member and a gear functioning as an output member among the three gears. Operating the hydraulic clutch to the hydraulic clutch;
A transmission equipped with a planetary gear set, characterized in that pressure oil controlled so as to cause the interruption is supplied through an oil supply passage provided in the fixed shaft. 2. The plurality of planetary gear devices are arranged and transmitted and connected on the fixed shaft, and the oil supply passage is shared by the plurality of planetary gear devices. A transmission equipped with a planetary gear set. 3. The planetary gear device according to claim 1, wherein the oil supply passage is communicated and blocked by a rotary valve coaxially arranged in the fixed shaft. Transmission equipped. 4. The rotary valve according to claim 3, wherein the rotation of the rotary valve is controlled by an actuator operated by a shift control device, and the actuator is coaxially arranged in the fixed shaft. A transmission equipped with a planetary gear set. 5. A transmission equipped with the planetary gear set,
A transmission equipped with the planetary gear device according to any one of claims 1 to 4, wherein the transmission is arranged on a side of a wheel of the vehicle along a front-rear direction of the vehicle. 6. The gear that functions as the control member is a sun gear, the gear that functions as an input member is a ring gear, and the gear that functions as an output member is a planetary gear. A transmission comprising the planetary gear set according to any one of claims 1 to 5.