JPS62165021A - Back torque reducing device - Google Patents

Abstract

PURPOSE:To reduce the clutch capacity to back torque and to reliably release back torque by disposing an intermediate member where a clutch spring bolt is fixed through a cam mechanism between a clutch center and a transmission shaft. CONSTITUTION:A clutch center 6 is rotatably disposed on a transmission shaft 1 through a sleeve 1a, and an intermediate member 10 provided with a dog tooth 7 and a dog recess portion 11 is loosely fitted to the clutch center 6 through a cam member 13. A clutch spring bolt 9 threaded on the clutch center 6 is loosely fitted to a pressure plate 15, and the pressure plate 15 is urged by a clutch spring 16 to press a clutch disc 5 and a clutch plate 8 to each other. Accordingly, at the time of disconnecting a clutch, the restoring force of the clutch spring 16' is decreased to reduce the operating force of a clutch lever and the clutch capacity, so that back torque can be released.

Description

[Detailed description of the invention] [Industrial application field] The present invention relates to a backtorque reduction device.

[Prior art]

For example, when a motorcycle, etc., suddenly downshifts while driving, the rotation speed of the rear wheels and the engine rotation speed are not synchronized due to the penetration of the vehicle body, and the engine receives a large torque from the rear wheels ( (generally referred to as bank torque)
This may cause the rear wheels to lock and cause the vehicle to jump on the road, a so-called hopping phenomenon. As a measure to prevent the above-mentioned hopping phenomenon, there is a damper installed in the power transmission path from the engine to the rear wheels to absorb torque fluctuations from the engine side, which attempts to absorb back torque. It is not possible to absorb bank torque sufficiently, and
When a special means for releasing back torque is used in the transmission, there is a disadvantage that the structure becomes complicated.

[Purpose of the invention]

In view of the above-mentioned circumstances, an object of the present invention is to provide a back torque reduction device that has a simple structure and can effectively release back torque.

[Structure of the invention]

Therefore, in the present invention, a clutch center in a multi-disc clutch is rotatably disposed on a mission shaft, and an intermediate member interlocked with one of them via a cam mechanism is provided between the clutch center and the mission shaft. The clutch spring bolt is loosely fitted and fixed to this intermediate member, and during normal power transmission, the rotational force of the clutch center is transmitted to the mission shaft via the intermediate member, and the rotational force of the clutch center is transmitted to the transmission shaft via the intermediate member, and the clutch spring bolt is fixed to this intermediate member. The intermediate member moved by the cam action moves the clutch spring bolt in the direction of increasing the biasing force of the clutch spring, and when back torque occurs, the cam action of the cam mechanism moves the clutch spring bolt to increase the biasing force of the clutch spring. By moving the clutch in a direction where the biasing force is weakened, the capacity of the clutch is reduced when back torque is generated, thereby achieving the above objective.

〔Example〕

DESCRIPTION OF THE PREFERRED EMBODIMENTS A specific configuration of the present invention will be described below in detail based on drawings showing one embodiment.

Fig. 1 shows an example in which the back torque reduction device according to the present invention is incorporated into a multi-disc clutch mounted on a motorcycle. It is fitted. The side plate 3 constituting the damper mechanism is a clutch outer 4
A plurality of clutch discs 5 are disposed on the clutch outer 4 as is well known. Further, on the right side of the drive gear 2, a clutch center 6 is rotatably disposed in a sleeve la that is integrally splined with the mission shaft 1, and dog teeth 7 are formed on the base 6a of the clutch center 6. . (See Figures 2 and 3) A clutch plate 8 is disposed in the clutch center 6 so as to sequentially overlap the clutch disc 5.
Furthermore, a clutch spring bolt 9, which will be described in detail later, is screwed into the clutch center 6. An intermediate member 10 is fitted to the clutch center 6, particularly to the right of the base 6a, so as to be rotatable relative to the mission shaft 1 and movable along the axial direction of the mission shaft 1. As shown in FIGS. 2 and 3, a recess 11 (hereinafter referred to as the dog recess 11) for fitting a dog is formed in the left edge 10a of the dog tooth 7. is stuck. Also, this intermediate member 10
A cam recess 12 is formed in the right edge 10b. Further to the right of the intermediate member 10, a cam member 13 is immovably splined to the sleeve 1a. This cam member 13 is formed with a cam protrusion 14 that fits into the cam recess 12 of the intermediate member IO.
O is disposed between the cam member 13 and the clutch center 6 so as to be movable left and right. The above cam convex portion 1
4 is formed with a cam surface 14a that is downward to the left in FIGS.
A cam receiver corresponding to 4a and also downward to the left is formed with a surface 12a. These cam recesses 12 and cam protrusions 14
The cam mechanism 100 is configured by the following. Further, a pressure plate 15 is disposed on the right side of the clutch outer 4i6 and the clutch center 6, and a clutch spring bolt 9 screwed onto the clutch center 6 is loosely fitted into the pressure plate 15. The pressure plate 15 is biased to the left in the figure by the elastic restoring force of a clutch spring 16 interposed between the spring bolt 9 and the pressure plate 15. Although not particularly shown, the clutch spring bolts 9 are arranged at three locations on the same circumference centered on the axis of the mission shaft 1, each having an equal center angle.

Clutch spring poles 1-9', 9', 9' are similarly disposed at intermediate positions between the respective clutch spring bolts 9, 9.9 on the circumference.

This clutch spring bolt 9' is different from the clutch spring bolt 9 described above, and is different from the clutch spring bolt 9 described above.
5, and its tip is screwed onto an arm portion 10C protruding from the outer periphery of the intermediate member 10. A clutch spring 16' is also interposed between the clutch spring bolt 9' and the pressure plate 15, and the pressure plate 15 is moved to the left in the figure by the cooperative action of the clutch springs 16 and 16'. The clutch is biased toward the connected state. In the figure, reference numeral 17 is a clutch rod, 18 is a clutch lifter,
19 is a clutch cover.

When the engine (not shown) starts operating and the drive gear 2 rotates counterclockwise (direction of arrow A in FIG. 2) when viewed from the right in FIG. 1, the rotational force is applied to the damper spring. The vibration is transmitted from the side plate 3 to the clutch outer 4 via the damper mechanism 22, which includes a damper mechanism 22a, a pin 22b, a collar 22C, etc., and is further transmitted to the clutch center 6 via the clutch disc 5 and clutch plate 8. The rotational force transmitted to the clutch center 6 is transmitted to the intermediate member 1 via the dog teeth 7 and the dog recess 11 that are fitted into each other.
The rotational force of the drive gear 2 is transmitted to the mission shaft 1 by rotating the cam member 13 via the cam recess 12 and the cam protrusion 14.

By the way, at the beginning of rotation, the clutch center 6 moves relative to the cam member 13 in the direction of arrow A in FIG. The cam receiver moves to the left by the mutual cam action of the surface 12a and the cam surface 14a of the cam convex portion 14, and occupies the leftward limit position shown in the figure.

As the intermediate member 10 moves to the left, the clutch spring bolt 9' fixed to the intermediate member 10 also moves to the left in FIG. At this time, as is clear from Figure #c1, the clutch spring 16' is compressed by the leftward movement of the clutch spring bolt 9'. The pressure plate 15 moves to the left in the figure due to the cooperative action of the elastic return force of the clutch spring 16' and the elastic return force of the clutch spring 16 moored to the clutch spring bolt 9 fixed to the clutch center 6. The clutch disk 5 and the clutch plate 8 are thus pressed into contact with each other reliably. On the other hand, when the passenger operates a clutch lever (not shown), the clutch lifter 18 moves to the right via the clutch rod 17, thereby causing the pressure plate 15 to generate a clutch spring +/force 'I C1c'/
-rXJ=hML+lr Lse I -r +ri;=
G 7 J. From this point, the pressure contact between the clutch disc 5 and the clutch plate 8 is released, the clutch becomes disconnected, and the transmission of power between the drive gear 2 and the transmission shaft 1 is cut off. . Note that as the pressure plate 15 moves to the right, the clutch center 6
There is no relative movement between the intermediate member 10 and the intermediate member 10, and thereby no cam action occurs between the cam recess 12 and the cam protrusion 14. In this way, the intermediate member 10 is biased by the clutch spring 16' via the clutch spring bolt 9' and moves to the right in FIG.
The elastic return force of ' is extremely weak. Therefore, in order to disengage the clutch, only the force required to move the pressure plate to the right against the biasing force of the clutch spring 16 that is anchored to the clutch spring bolt 9 screwed into the clutch center 6 is required. Therefore, the operating force of the clutch lever when the clutch is disengaged is reduced.

By the way, when the rider suddenly releases the accelerator pedal while the motorcycle of this example is running, the cam fixed to the transmission shaft 1 The member 13 is forcibly rotated at a higher rotation speed than the clutch center 6 by the rear wheels, which continue to rotate due to the inertia of the vehicle body that was traveling at the speed before the accelerator was released. Therefore, the cam member 13 moves in the direction of arrow A' (FIG. 2) relative to the clutch center 6. Therefore, the cam convex portion 14 moves from the position shown by the solid line in the figure to the position shown by the two-dot chain line, thereby allowing the intermediate member 1O to freely move to the right in the figure. As a result, the intermediate member 10 is moved to the right by the biasing force of the clutch spring 16'. In addition,
It goes without saying that the movement of the cam member 13 and the movement of the intermediate member 10 are performed continuously while the cam surface 14a and the surface 12a of the cam receiver are always in contact with each other. Intermediate member 10
As it is clear from FIG. 1, the installation length of the clutch spring 16' between the clutch spring bolt 9' and the pressure plate 15 is extended by moving to the right, so that the elastic return force of the clutch spring 16' is increased. In other words, the urging force applied to the pressure plate 15 becomes weaker. By doing so, the pressure contact force between the clutch disc 5 and the clutch plate 8, that is, the capacity of the clutch is reduced L.
, the back torque transmitted from the mission shaft 1 is released. After that, the traveling speed of the vehicle body decreases due to inertia, and when the transmission shaft 1 is again driven by the rotational force of the drive gear 2, the intermediate member 10 moves relative to the cam member 13 in the direction of arrow A'' in FIG. By moving, the intermediate member 10 moves to the left due to the cam action of the cam convex portion 14 and the cam concave portion 12. As a result, the pressure plate 15 is again urged by the clutch spring bolts 16 and 16', and the first The rotational force of the drive gear 2 is transmitted to the mission shaft 1 in accordance with the operation mode in the normal clutch connected state described in .

It goes without saying that the above-mentioned back torque release operating force f1 is also performed when a sudden downshift is performed.

In addition, in this example, a multi-disc clutch with a total of six clutch springs was illustrated, and an example was described in which three of the six clutch spring bolts were fixed to an intermediate member, but the number of clutch springs is Of course, the number of clutch spring bolts fixed to the intermediate member is not limited to this, and some or all of the clutch spring bolts provided in the multi-disc clutch may be attached to the intermediate member. Needless to say, it's a good thing.

In addition, in this example, a cam mechanism 100 consisting of a cam recess 12 and a cam protrusion 14 is provided between the intermediate member lO and the cam member 13.
However, the object of the present invention can also be achieved by providing a cam mechanism between the intermediate member 10 and the clutch center 6, or between the intermediate member 10 and the clutch center 6, and between the intermediate member 10 and the cam member 13. can be achieved.

〔Effect of the invention〕

As described in detail above, according to the back torque reduction device according to the present invention, the clutch center is rotatably arranged with respect to the transmission shaft, and the intermediate member is interposed between the clutch center and the transmission shaft via the cam mechanism. arranged,
Furthermore, a clutch spring bolt is fixed to this intermediate member, so that when back torque is applied to the clutch, the clutch spring bolt is moved by the cam action of the intermediate member, reducing the clutch capacity. This makes it possible to reliably release the space, and also makes it possible to make the entire device more compact.

[Brief explanation of drawings]

FIG. 1 is a side sectional view of a multi-disc clutch incorporating a back torque reducing device according to the present invention, and FIGS. 2 and 3 are exploded views of essential parts showing the operating mode of the back torque reducing device according to the present invention. . 1...Mission shaft, 2...Drive gear,
4...Clutch outer, 6...Clutch center, 7
...Dog tooth, 9,9'...Clutch spring bolt, 10...Intermediate member, IOC...Arm part, 11...
・Doc recess, 12...Cam recess, 12a--Cam receiver is surface, 13...Cam member, 14...Cam protrusion, 14
a...Cam surface, 15...Pressure plate, 16.
16'...Clutch spring, 100...Cam mechanism. Applicant Suzuki Motor Co., Ltd. Representative Patent Attorney
Takahisa Kimura: Figure 3 Procedures Neill Official Book September 11, 1985 1, Indication of Case I11 Patent Application No. 2988 of 1985 2, Name of Invention Back Torque Reduction Device 3, Make Amendment Special W [Applicant (20111) Suzuki Ji 111) iguchi Kogyo Co., Ltd. 4, Agent (104) February 6th floor, Ginza Daisaku Building, 2-11 Ginza, Chuo-ku, Tokyo Telephone 03-545 -3508 (Representative) 6
, Contents of amendment (1) Book III of the present application, page 7, line 14 to 1
In the 6th line, change ``And that......'' to ``
Moreover, its tip is screwed onto a support member 10c that is integrally assembled to the intermediate member 10. ” he corrected. (2) Insert "[via support member 10c]" before "fixed" in the 6th line of page 9. (3) "Clutch spring bolt 16" on page 12, lines 13 to 14 of the same page as "clutch spring 16"
and correct it. (4) Insert "via the support member 10c" before "intermediate member" in the second line of page 13. (5) Same, page 14, line 18 MOc...
・Correct "arm part" to "1oC...support member". (6) Amend Figure 1 of the drawing as per the attached drawing.

Claims (1)

[Claims] A clutch center is rotatably disposed on a mission shaft in a multi-disc clutch that transmits power by pressing a clutch disc and a clutch plate into contact with each other by applying the biasing force of a clutch spring interposed between a clutch spring bolt and a pressure plate. At the same time, an intermediate member is loosely fitted between the mission shaft and the clutch center, and the clutch spring bolt provided in the multi-disc clutch is fixed to the intermediate member, and the clutch center and the clutch center are fixedly connected to the clutch spring bolt. A cam mechanism is provided between the intermediate members or at least one between the intermediate member and the mission shaft, and when the clutch center rotates with respect to the mission shaft, the rotational force of the clutch center is transmitted to the above through the intermediate member. The clutch spring bolt is moved in a direction in which the biasing force of the clutch spring toward the pressure plate is increased by the intermediate member, which is transmitted to the mission shaft and is moved by a cam action caused by relative displacement between the mission shaft and the clutch center. On the other hand, when a relative displacement occurs between the mission shaft and the clutch center in a direction opposite to the relative displacement, the cam action of the cam mechanism moves the clutch spring bolt in a direction where the biasing force of the clutch spring is weakened. A back torque reducing device characterized in that the device is configured to move the back torque.