JPS6334347A - Gear shift clutch - Google Patents

Abstract

PURPOSE:To eliminate a shock following a back load by connecting a low-speed side clutch part to a fixed element via a one-way clutch, and arranging the one-way clutch so that it can be made free from a reversing torque by the back load. CONSTITUTION:Cam grooves are formed at regular intervals along around a low-speed side clutch inner 23, a one-way clutch is formed with the cam grooves and rollers by providing the rollers in the cam grooves, and the one-way clutch is arranged so that it can be free from a reversing torque. Now, when an engine brake is applied in a state where a planetary gear type transmission Gp connecting the engine 1 to the rear wheel 39 of a vehicle is shifted to the low-speed, side, a back load transmitted from the rear wheel 39 to the engine 1 is inputted from the output side of the planetary gear type transmission Gp, so a reversing torque is generated against a fixed element. Whereupon, a power transfer in the low-speed side clutch part is cut and a shock following the back load can be eliminated, as the one-way clutch in the low-speed side clutch part is made free.

Description

[Detailed Description of the Invention] [Field of Industrial Application] This invention relates to a speed change clutch that switches a planetary gear type transmission that connects the engine and wheels of a vehicle to two stages, high and low. Regarding something that reduces the accompanying shock.

[Background of the Invention] In a speed change clutch for a planetary gear transmission that connects the engine and wheels of a vehicle, the clutch inner is a substantially truncated cone, and the high-speed side tarlatch outer is in sliding contact with the large diameter side, and the clutch is in sliding contact with the small diameter side. An application has been filed for a device in which a low-speed clutch outer is provided in contact with each other, and the gear is shifted to the high-speed side under normal conditions, and the gear can be switched to the low-speed side when appropriate.
No. 9091).

By the way, in a shift clutch that does not have a neutral state and is always connected on either the high-speed side or the low-speed side, when engine braking is applied, a backload is applied from the wheels to the engine, causing a relatively large shock. occurs. Particularly when engine braking is applied while shifting at low speeds, a large shock occurs. This is because the clutch has a large latch capacity capable of transmitting driving torque, so when the torque is small, such as during engine braking, the clutch slip time becomes extremely short. SUMMARY OF THE INVENTION Therefore, an object of the present invention is to provide a speed change clutch that can alleviate the shock caused by back loading.

[Means for solving problems] The speed change clutch of the present invention has the following configuration.

That is, it is a speed change clutch that switches a planetary gear type transmission that connects the engine and wheels of a vehicle to either a high speed side or a low speed side, and by fixing any one element of the planetary gear type transmission. In things that slow down,
The speed change clutch is composed of a high-speed side clutch section and a low-speed side clutch section, and the low-speed side clutch section is connected to the fixed element via a one-way clutch, and is capable of handling reverse rotation torque due to the back rotor transmitted from the wheels to the engine. The present invention is characterized in that the one-way clutch is disposed so as to be free.

[Operation of the invention] When the engine brake is applied with the planetary gear type transmission that connects the engine and wheels of the vehicle switched to the low speed side,
Since a backload transmitted from the wheels to the engine is input from the output side of the planetary gear transmission, a reverse torque is generated on the fixed element. Then, the one-way clutch in the low-speed clutch section becomes free. Therefore, power transmission at the low-speed clutch section is cut off, and no shock occurs due to backrotation.

[Example code] A first embodiment according to the present invention is shown in FIGS. 1 to 5.

FIG. 1 shows an overview of the entire power transmission system to which the present invention 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 F.
It is transmitted along the route r→rear wheel 39.

The main transmission Tm is a known V-belt type continuously variable transmission,
It is constructed by wrapping a V-belt 4 around a drive pulley 3 and a driven pulley 5. The driven pulley 5 is provided with a known centrifugal starting clutch C1. The main transmission Tm is connected to the sub-transmission Ts at a main shaft angle of 1°, and the speed change width is greatly expanded by the sub-transmission Ts. The sub-transmission Ts is a two-stage transmission consisting of a planetary gear type transmission Gp, and can be switched to a high speed side or a low speed side by a speed change clutch C2. The speed change clutch c2 is a two-stage switching type conical clutch, as will be described in detail later. This clutch does not have a neutral state and is always in either a high speed side or a low speed side.

In this embodiment, the fixed element of the planetary gear type transmission is a sun gear. That is, a high speed stage in which the high speed side clutch inner 21 and the high speed side clutch outer 26 are brought into sliding contact to directly connect the sun gear and the carrier, and a low speed side clutch inner 2
3 and a low speed stage in which the sun gear is fixed by slidingly contacting the low speed side clutch outer 27. The high-speed side clutch inner 21 and the low-speed side clutch inner 23 are connected via a one-way clutch C3. The fixing direction of the one-way clutch C3 coincides with the normal rotation direction of the high-speed side clutch inner 21. A one-way clutch is installed to alleviate the shock caused by backroading. In addition,
24 is a single-plate clutch that connects the high-speed side clutch inner 21 and the low-speed side clutch inner 23. The effective diameter of this single-plate clutch can be changed as needed, so it can be set arbitrarily to transmit only the necessary engine braking torque and release any torque beyond that.

The speed change output by the planetary gear type transmission Gp is transmitted to the final reduction Fr. Final reduction F
r is a gear train consisting of counter gears 34, 35 and final gear 36. The output of the planetary gear type transmission Gp is finally reduced here, and the rear wheel 39 is driven through the final shaft 37, hub and spokes 38.

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 comes into sliding contact with a lining 9 fixed to the inner periphery of the clutch outer 8 when expanded. A main shaft 10 is fixed to the center of the clutch outer 8. The main shaft 10 passes through the inside of the cam cylinder 6 and forms an input shaft of the planetary gear type transmission Gp.

The planetary gear type transmission Gp has an internally toothed ring gear 11.
It consists of a planetary gear 12, a sun gear 13, a carrier 14, etc., and are meshed with each other. The ring gear 11 is spline-coupled to the main shaft 10 that enters the mission chamber M. Sun gear 13 has a sun gear shaft 15 . Sun gear shaft 15 is rotatably supported externally by main shaft 10 and extends in the axial direction. The planetary gear 12 is rotatably attached to the carrier 14 via a shaft 16 . Further, the carrier 14 is fixed to one end of the output shaft 17. The output shaft 17 is rotatably mounted around the sun gear shaft 15. A drive gear 18 is formed around the output shaft 17.

Next, the speed change clutch C2 will be explained. A spline 19 is formed on the free end side of the sun gear shaft 15, and a clutch inner 20 is spline-coupled to the spline 19. clutch inner 20
is a large-diameter high-speed side clutch inner 21 extending in the radial direction.
has. The high-speed side clutch inner 21 is provided with a boss portion 22 extending in the axial direction from the center portion to the side surface. A small-diameter low-speed side clutch inner 23 is fitted onto the outer periphery of the boss portion 22 via a one-way clutch C3. The fixing direction of the one-way clutch coincides with the normal rotation direction of the high-speed side clutch inner 21. Further, a single-plate clutch 24 is provided on the side surface of the low-speed clutch inner 23 on the high-speed clutch inner 21 side.

The clutch inner 20 is also provided with a return spring 25 made of a disc spring and extending obliquely upward from one end thereof. The high-speed side clutch inner 21 is urged upward in the figure by the return spring 25.

On the other hand, the high-speed side clutch outer 26 is fixed to the end of the output shaft 17 and extends in the radial direction, and a friction ring 26a is attached to its tip flange. The friction ring 26 is capable of slidingly contacting the outer peripheral surface of the high-speed side clutch inner 21 in circumferential contact.

High-speed side clutch outer 26 and high-speed side clutch inner 21
This constitutes a high-speed side clutch section.

The low speed side clutch outer 27 is also the low speed side clutch inner 23.
is provided so as to be able to come into contact with and separate from the outer periphery of the

Low speed clutch outer 27 and low speed clutch inner 23
The low-speed side clutch section is configured by: A guide pin 28 is attached to the center of the low speed side clutch outer 27.

The guide pin 28 fits into a shaft hole 29 formed in the center of the main shaft 10, and is movable in the axial direction inside this hole. A return spring is disposed within the shaft hole 29. Further, the low-speed side clutch outer 27 is non-rotatably attached to the wall portion 30 of the mission chamber M by a fixing pin 31. One end of the guide pin 28 is connected to a change shaft 32
comes into contact with the cam surface 33 of. The change shaft 32 is rotatably supported within the wall portion 30. When the change shaft 32 rotates, the cam surface 33 moves the guide bin 28 in the axial direction.

Incidentally, the process after the final reduction Fr is as described in FIG. 1, and only the reference numerals are shown in the figure and the explanation will be omitted.

Next, details of the speed change clutch C2 and the one-way clutch C3 are shown in FIG. FIG. 3 is an assembly drawing. The clutch inner 20 consists of a high-speed side clutch inner 21 and a boss portion 22. The high-speed side clutch inner 21 is provided with a spline portion 40 in its center that can be coupled to the spline portion 19 of the sun gear shaft (see FIG. 2). A friction material is pasted on the outer periphery to form a friction surface 41. On the other hand, the low speed side clutch inner 2
A friction material is also pasted on the outer periphery of 3 to form a friction surface 42.

Further, the center portion thereof is an opening portion 43 into which the boss portion 22 of the high-speed side clutch inner 21 can be fitted. Furthermore, cam grooves 44 are formed at equal intervals along the periphery of the low-speed side clutch inner 23. A roller 45 is disposed within the cam groove.

Therefore, the cam groove 44 and the roller 45 form a one-way clutch C3. The fixing direction of the one-way clutch C3 is the normal rotation direction of the high-speed side clutch inner 21 (arrow A
direction). A single-plate clutch 24 is provided on the side surface 46 of the low-speed clutch inner 23 on the high-speed clutch inner 21 side, if necessary, and when the high-speed clutch inner 21 and the low-speed clutch inch 23 are integrated, a predetermined clutch can be inserted between them. form a capacity.

Next, the operation of this embodiment will be explained based on FIGS. 1 to 3.

(High-speed stage) Since the return spring 25 presses the friction surface 41 on the outer circumference of the high-speed side clutch inner 21 and the high-speed side clutch outer 26, the high-speed side clutch portion is connected. As a result, the sun gear shaft 15 and the output shaft 17 are connected, so that the sun gear 13 and the carrier 14 at both ends thereof are directly connected, and the output is output from the drive gear 18 at the same speed as the input.

(Low speed gear) The low speed side clutch outer 27 is connected to the low speed side clutch inner 23.
When the low speed side clutch outer 27 is moved in the direction, the low speed side clutch outer 27 comes into pressure contact with the friction surface 42 on the outer peripheral part of the low speed side clutch inner 23, and the low speed side clutch portion is connected. At the same time, the friction surface 41 of the high-speed side clutch inner 21 is connected to the high-speed side clutch outer 26.
, and disconnect the high-speed side clutch. At this time, since the sun gear shaft 15 still tries to rotate in the normal direction, normal rotation torque is applied to the boss portion 22 of the high-speed side clutch inner 21. Then, the one-way clutch C3 operates to stop the rotation of the high-speed side clutch inner 21, and as a result, the sun gear shaft 15 and the sun gear 13 are fixed. As a result, the planetary gear type transmission GP is shifted to a low gear, and the carrier 14 is decelerated and output from the output shaft 17 and the drive gear 18.

(At the time of backload) When the engine throttle valve is returned to the engine braking state in a low speed gear, a backload is applied to the engine from the direction of the rear wheels 39. This backload is input from the output shaft 17 in the opposite manner to the previous case. As a result, the sun gear 13 tries to rotate in the opposite direction, and the sun gear shaft 15
A reverse rotational torque is applied to the boss portion 22 via the high-speed side clutch inner 21. Then, since the fixing direction of the one-way clutch C3 matches the forward rotation direction of the boss portion 22,
One-way clutch C3 becomes free and sun gear 13
In addition, the sun gear shaft 15, high-speed side clutch inch 21, etc. become rotatable. However, since the high-speed side clutch inner 21 and the low-speed side clutch inner 23 are connected by the single-plate clutch 24, rotation is restricted by a predetermined clutch capacity. Therefore, while maintaining some degree of engine braking by the single-plate clutch 24, more backload torque is not transmitted. Therefore, you hardly feel the shock of backroading. Note that if the single-plate clutch 24 is eliminated, the shock associated with backroading can be completely eliminated, but engine braking will also become ineffective.

Fig. 4 compares the degree of shock during engine braking, where curve X shows this embodiment with a one-way clutch and a single-plate clutch, curve Y shows another embodiment with only one-way clutch, and curve Z shows the case of another embodiment with one-way clutch. Each characteristic of a comparative example without the above is shown. As is clear from this, according to this embodiment, the shock associated with backloading, that is, the G value, which is the acceleration during deceleration, can be suppressed to an extremely low level. Therefore, the shock can be alleviated or almost eliminated.

In addition, in this embodiment, by providing the single-plate clutch 24 in addition to the one-way clutch C3, it is advantageous that engine braking can be appropriately applied. However, it goes without saying that the balance point between the effectiveness of the engine brake and the magnitude of the shock can be changed and set arbitrarily.

Furthermore, the present invention is not limited to the above embodiments, and can be applied in many other ways. For example, the input side, output side, and fixed side elements of a planetary gear type transmission can be freely combined.

[Effects of the Invention] Since the speed change clutch according to the present invention is provided with a one-way clutch in the low-speed clutch portion, when a backload is applied, the one-way clutch can release the backload torque transmitted from the wheels to the engine without being transmitted. can. Therefore, the shock caused by backroading can be alleviated or almost eliminated, and smooth and comfortable driving can be achieved.

[BRIEF DESCRIPTION OF THE DRAWINGS] Figures 1 to 4 show embodiments of the present invention. Figure 1 is a system diagram of the entire power transmission system, Figure 2 is a sectional view of the main parts, and Figure 3 is the main parts. The assembly diagram of the part and FIG. 4 are characteristic diagrams. (Explanation of symbols) Gp... Planetary gear type transmission, C2... Speed change clutch, C3... One-way clutch, 17... Output shaft,
20...Clutch inch, 21...High speed side clutch inner, 23...Low speed side clutch inner, 26...
High-speed side clutch outer, 27...low-speed side clutch outer. Patent applicant: Agent for Honda Motor Co., Ltd.
Patent Attorney Kiyomitsu Komatsu Figure 5 Figure 6 G Yodo 5I Tewa℃ne fl-3 formal text (method) % formula % 2 Title of invention Speed clutch 3 Relationship to the person making the amendment Patent applicant address Tokyo 2-1-1 Minami Aoyama, Miyakominato-ku Name
Honda Motor Co., Ltd. 4 Agent Room C, 8th floor, Rose Bay Ikebukuro Building, 2-39-8 Nishiikebukuro, Toshima-ku, Tokyo September 30, 1986 6 Drawings subject to amendment 7 Contents of amendment Drawings 5 and 6 Delete the diagram.

Claims (1)

[Claims] A speed change clutch that switches a planetary gear type transmission that connects the engine and wheels of a vehicle to either a high speed side or a low speed side, and decelerates by fixing any one element of the planetary gear type transmission. The speed change clutch is composed of a high-speed side clutch section and a low-speed side clutch section, and the low-speed side clutch section is connected to the fixed element through a one-way clutch, and is connected to the fixed element through a one-way clutch, and is configured to handle reverse rotation torque due to backload transmitted from the wheels to the engine. A speed change clutch, characterized in that the one-way clutch is disposed so as to be free.