JPS62159835A - Transmission - Google Patents

Abstract

PURPOSE:To get rid of a neutral state during a speed changing process by mounting a clutch which makes direct connection of a carrier to a sun gear during no speed change and making speed changing operation to disengage the clutch only during the process of deceleration and simultaneously braking the sun gear to be fixed. CONSTITUTION:When the speed is changed from a high speed range to a low speed range, a change shaft 28 is operated to make the cam face 29 thereof push a hollow shaft 23 to the left. A brake disk 24 is then pushed to the left to make frictional contact with the friction face 21 of a clutch inner 20. When the brake disk 24 is further pushed to the left, the clutch inner 20 is moved to the left on a hollow rod 14 so that the frictional contact between the friction face 21 and the friction contact part 18 is released. Consequently, a clutch outer 17 can be turned independently from the clutch inner 20 so that a carrier 15 can be turned on the hollow rod 14 and the clutch inner 20 is braked by the brake disk 24, whereby fixing the hollow rod 14 and a sun gear 13 unified therewith.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a compact transmission consisting of a planetary gear mechanism for motorcycles and the like, and particularly to a transmission that does not produce a neutral state during a gear change operation.

[Prior Art] Planetary gear mechanisms are used as transmissions for two-wheeled motor vehicles, three-wheeled motor vehicles, and various other power devices. A single planetary gear mechanism enables two-stage speed change on the high-speed side and low-speed side. This shift operation is performed using a band brake, clutch,
This is usually done by selectively operating a one-way clutch or the like. Since the planetary gear mechanism can be made relatively compact, it is advantageous as a transmission for motorcycles and the like.

[Problems to be Solved by the Invention] By the way, when a speed change operation is performed, a neutral state usually occurs during the operation. For example, when the clutch is released to fix one of the components with the brake, the vehicle becomes neutral at that moment. When the vehicle is in the neutral state, the engine tends to run dry, which tends to reduce fuel efficiency. Furthermore, even with a planetary gear mechanism, it requires a band brake mechanism, one-way clutch, etc. to switch between high and low speeds, which makes the device complicated, making the transmission larger and more expensive. . SUMMARY OF THE INVENTION The present invention aims to solve these problems, and provides a compact transmission that is hardly in a neutral state during gear shifting operations.

[Means for Solving the Problems] The transmission of the present invention has the following configuration. That is, a ring gear with internal teeth that connects to the input shaft, a planetary gear that meshes with the internal teeth of the ring gear, a carrier that rotatably supports the planetary gear and also serves as an output shaft, and a sun gear that meshes with the planetary gear. In the transmission having a planetary gear mechanism, a clutch outer is fixed to the end of the carrier, a clutch inner is attached to the end of the rotating shaft of the sun gear so as to be movable in the axial direction but not rotatable in the circumferential direction, and the clutch inner is attached to the end of the rotating shaft of the sun gear. An elastic means is provided, and the elastic means constantly urges the clutch inner in a direction in which the clutch inner is brought into pressure contact with the clutch outer and is frictionally coupled, so that the sun gear and the carrier are directly connected, and the clutch inner is frictionally coupled with the clutch outer. A brake plate that can be frictionally coupled to a surface by pressure contact is provided to be movable in the axial direction and non-rotatable, and when the brake plate comes in pressure contact with the clutch inner, it is frictionally coupled to the clutch inner and stops its rotation, It is characterized in that the connection with the clutch outer is cut off at the same time.

[Operation of the invention] Power input from the input shaft to the ring gear is output to the output shaft integrated with the carrier. When not shifting, the clutch outer is pressed against the clutch inner and frictionally coupled, so the carrier and sun gear are directly connected, the output of the drive gear is not shifted, and the shifting state is a high speed gear with a gear ratio of 1:1. Become. Further, when the brake plate is pressed into contact with the clutch inner, the clutch inner is frictionally connected, and at the same time, the clutch inner is pushed and moved in the axial direction, and the frictional connection with the clutch outer is released.

As a result, the sun gear is fixed, and the carrier is rotated at a reduced speed in the same direction as the ring gear. Therefore, the output of the output shaft, which is integrated with the carrier, is decelerated without being in a neutral state, and the speed change state becomes a deceleration stage. When the brake plate stops pressing against the clutch inner, the clutch inner moves in the axial direction and engages with the clutch outer again, and at the same time, the connection with the brake plate is released and the clutch returns to the high speed side again.

[Embodiment] FIG. 1 shows the entire power transmission system to which this embodiment is applied. In other words, the power of the engine 1 is transmitted from the crankshaft 2 to the main transmission Tm to the sub-transmission Ts to the final reduction Fr.
→It is transmitted through the path of the rear wheels 39. The main transmission Tm is a known V-belt type continuously variable transmission, and is constructed by wrapping a V-belt 4 around a drive pulley 3 and a driven pulley 5.

Driven pulley 5 is also equipped with a known centrifugal starting clutch C.
1 is provided. The sub-transmission Ts is a planetary gear mechanism Gp
It is a two-stage transmission device consisting of a conical clutch C2, and can be switched to a high speed side or a low speed side. The main transmission Tm is connected to the sub-transmission Ts through the main shaft 1°,
This sub-transmission Ts greatly expands the speed change width.

As will be described later, the conical clutch C2 includes a clutch inner 20 having a conical surface, a latch outer 17 that can be frictionally coupled to the clutch inner 20, and a brake plate 24.

The power shifted by the sub-shift N&Ts passes through the countershaft 31 and undergoes final deceleration by the final gear 35.
The signal is transmitted to the final shaft 34 and the rear wheels 39 are driven.

FIG. 2 shows the detailed structure after the driven pulley 5. The driven pulley 5 is fixed to one end of a cam cylinder 6, which is a hollow shaft. The cam cylinder 6 is provided with a known torque cam mechanism. A weight 7 is fixed to the other end of the cam cylinder 6 so as to be expandable. The weight 7 is the clutch outer 8 when expanded.
integrated into the lining 9 fixed to the inner periphery of the
The rotation of the driven pulley 5 is transmitted to the clutch outer 8. A main shaft 10 is located in the center of the clutch outer 8.
is fixed to the cam cylinder 6 and passes through the inside of the cam cylinder 6 to form an input shaft of the sub-transmission Ts. The sub-transmission TS and the final reduction Fr are provided in the same mission chamber M. A ring gear 11 having internal teeth is spline-coupled to the main shaft 10 entered into the mission chamber M, and a planetary gear 12 and a sun gear 13 are meshed with this. The sun gear 13 has a hollow shaft 14 extending in the axial direction along the main shaft 10, and is rotatably supported on the outside of the main shaft 10. The planetary gear 12 is pivotally connected to the carrier 15, and the carrier 1
5 is fixed to one end of a drive gear 16 formed on an output shaft that is rotatable around the planetary gear 12. At the other end of the drive gear 16 is a clutch outer 1.
7 is fixed, and a sliding contact portion 18 that forms a frictional contact surface with a frictional surface 21, which will be described later, is fixed to the tip end thereof.

A spline is formed at the end 19 of the hollow shaft 14, and the clutch inner 20 is connected to the spline so as to be movable in the axial direction. The side surface of the clutch inner 20 has a conical surface inclined in the axial direction, and a fading material is fixed to this surface to form a friction surface 21. Also clutch inner 20
is a return spring (disc spring) which is an example of elastic means.
22, it is urged to move to the right in the figure, and the friction surface 21 is pressed against the sliding contact portion 18 and frictionally coupled thereto.

The end of the main shaft 10 is hollow, and a hollow shaft 23 is fitted into the open end so as to be freely removable. A brake plate 24 is fixed to the hollow shaft 23.
The tip thereof is a sliding contact portion 25 that is bent so as to be able to come into sliding contact with the friction surface 21 . Hollow shaft 23 is return spring 2
6 to the outside (to the right in the figure), and normally the tip of the brake plate 24 is kept out of contact with the friction surface 21. Further, a rotation stopper 27 is attached to the brake plate 24, and the rotation stopper 27 cannot rotate with respect to the right side wall surface of the mission chamber M and is axially fixed.

It is supported so that it can slide in the direction. (However, illustration of the wall surface of the portion that supports the bottle 27 is omitted). The hollow shaft 23 is moved in and out by a change shaft 28. The change shaft 28 is formed with a cam surface 29 that is in contact with the top of the shaft 23, and is prevented from being removed by a bolt 30 fixed to the right side wall of the transmission chamber.

A counter shaft 31 is rotatably supported at both ends between the left and right walls of the mission chamber M and is parallel to the main shaft 10.
is provided. A counter gear 32 is attached to the counter shaft 31 so that it cannot move in the axial direction and the counter gear 32 is attached to the counter shaft 31.
1, and is engaged with the drive gear 16. Further, a small-diameter gear 33 is formed on the countershaft 31, and meshes with a final gear 35 mounted on a final shaft 34 provided parallel to the countershaft 31.
1 rotation is transmitted to the final shaft 34. A collar 36 is splined to the end of the final shaft 34 and fastened with bolts 37. One end of a spoke 38 is fixed to the collar 36, and a rear wheel 39 is attached to the other end of the spoke 38.

Next, the operation of this embodiment will be explained.

High-speed side> In FIG. 2, the power transmitted from the V-belt 4 to the driven pulley 5 is input to the main shaft 10 by press-welding the weight 7 to the lining 9 as the cam cylinder 6 rotates. . When the main shaft 10 rotates, the ring gear 11 spline-coupled thereto is also rotated together. At this time, the planetary gear 12 that meshes with the ring gear 11 and the carrier 15 also try to rotate around the hollow shaft 14. However, the clutch outer 17 is frictionally coupled with the clutch inner 20 and rotated together. Therefore, the carrier 15 is integrated with the clutch outer 17, and the sun gear 13 is integrated with the clutch inner 20.
are directly connected, and the drive gear 16 is rotated at the same rotation as the main shaft 10. That is, the sub-transmission Ts is in a high-speed gear position with a gear ratio of 1:1,
The input to the main shaft 10 is rotationally outputted from the drive gear 16, which is an output shaft, without being changed in speed. Therefore, the subsequent power path is drive gear 16 → counter gear 32 → counter shaft 31 → gear 33 → final gear 35 → final shaft 34 → spoke 38.
→Transmitted to the rear wheel 39.

Low Speed Side> In the high speed side state, the change shaft 28 is operated and its cam surface 29 pushes the hollow shaft 23 to the left in the figure against the return spring 26. Then, the brake plate 24 is pushed to the left in the figure, and the clutch inner 2
It is frictionally coupled with the friction surface 21 of 0. When the brake plate 24 is further pushed to the left in this state, the clutch inner 20 moves to the left on the spline of the hollow shaft 14 against the return spring 22, and the friction surface 21 and the sliding contact portion 18 are frictionally connected. is solved. As a result, the clutch outer 17 can be rotated separately from the clutch inner 20, and the carrier 15 can be rotated around the hollow shaft 14. Also, the brake plate 2
4 stops the rotation of the clutch inner 20,
A hollow shaft 14 spline-coupled to the brake plate 24 and a sun gear 13 integral therewith are fixed.

As a result, the planetary gear 12 revolves around the sun gear 13 while rotating, and the carrier 15 and the drive gear 16 integrated therewith decelerate and rotate around the hollow shaft 14 in the same direction as the rotation direction of the ring gear 11. It will be done. That is, the gear is on the low speed side, and the gear ratio R at this time is given by R=(M+N)/M, where M is the number of teeth of the ring gear and N is the number of teeth of the sun gear. Therefore, the speed change output of the main transmission Tm is further reduced in speed by the speed ratio R by the sub-transmission Ts, and is output from the drive gear 16. Thereafter, the power path is transmitted through the final reduction Fr to the rear wheels 39 in the same manner as described above.

Furthermore, excluding the force applied to the change shaft 28,
Due to the restoring forces of the return springs 22 and 26, the clutch inner 20 and the brake plate 24 are pushed back to the right in the figure and returned to their normal positions. As a result, the frictional connection between the friction surface 21 and the brake plate 24 is released, and at the same time, the sliding contact portion 18 and the friction surface 21 are frictionally connected, and the clutch inner 20 and the clutch outer 17 are again switched to the high speed side where they are integrated. .

Fixing the sun gear as in this embodiment has the advantage that the capacity of the clutch can be reduced. That is, when the sun gear is fixed, it is given by (sun gear torque)=(input torque)XN7M. Note that the number of teeth of the ring gear is M, and the number of teeth of the sun gear is N.

[Effects of the invention] A clutch is provided in which the carrier and sun gear are directly connected when not shifting, and the gear is shifted only when decelerating, the clutch is released, and the sun gear is braked and fixed at the same time. A neutral state of meaning does not occur. Therefore, the engine will not run dry and fuel efficiency will improve. Furthermore, since both high-speed and low-speed gear shifting operations are performed by frictional coupling, the impact force during gear shifting can be alleviated, and durability is good, and the device can be made smaller and lighter. In addition, shifting shock is reduced, and gears can be shifted both when stopped and when driving. Additionally, since the sun gear is fixed during deceleration, the clutch capacity can be reduced. Furthermore, since the high speed gear is often used during normal driving, fuel efficiency is good in this respect as well.

[Brief explanation of drawings]

1 and 2 show an embodiment of the present invention, FIG. 1 is a system diagram of the entire power transmission system to which the present invention is applied, and FIG. 2 is a cross-sectional view of the main parts. (Explanation of symbols) Tm...Main transmission, Ts...Sub-transmission, Fr...
Final reduction, Gp...planetary gear mechanism, 1
0... Main shaft, 11... Ring gear, 12
...Planetary gear, 13...Sun gear, 14...
- Hollow shaft, 15...Carrier, 16...Drive gear, 17...Clutch outer, 20...Clutch inner, 24...Brake plate.

Claims (1)

[Claims] A planet consisting of a ring gear with internal teeth connected to an input shaft, a planetary gear meshing with the internal teeth of the ring gear, a carrier rotatably attached to the planetary gear and serving as an output shaft, and a sun gear meshing with the planetary gear. In a transmission having a gear mechanism, a clutch outer is fixed to an end of the carrier, a clutch inner is attached to an end of the rotating shaft of the sun gear so as to be movable in an axial direction but not rotatable in a circumferential direction, and an elastic means is attached to the clutch inner. is provided, and the elastic means constantly biases the clutch inner in the direction of pressure contact and frictional connection between the clutch inner and the clutch outer to directly connect the sun gear and the carrier, and on the surface of the clutch inner with which the clutch outer is frictionally connected. A brake plate that can be pressed and frictionally coupled is provided so as to be movable in the axial direction and non-rotatable, and when the brake plate comes in pressure contact with the clutch inner, it is frictionally coupled to the clutch inner and stops its rotation, and at the same time A transmission characterized by disconnecting from the clutch outer.