JPS59231217A - Friction clutch equipment - Google Patents

Abstract

PURPOSE:To absorb and moderate a reverse load if it is applied from the side of a driven shaft by providing, between a clutch member and the driven shaft, a movable member which advances toward a press member in said case. CONSTITUTION:An annular movable member 35 is mounted movably in the axial direction inside the central through hole 34 of an intermediate member 32 which is provided radially outside of a clutch boss 31 and coaxially therewith. The internal peripheral face of the center opening 38 of the movable member 35 is engaged on a twisted spline 37 which is cut on the external peripheral face of the clutch boss 31 on the side of a press member 29. The movable member 35 is designed such that when a reverse load is applied on an intermediate shaft 12, the movable member 35 advance on the side of the press member 29. An initially coned disc spring 41 which is interposed between the spring receiver 36 of the movable member 35 and the supporting projection 40 formed on the back face of the press member 29 presses the projection in the direction reverse to the pressing direction of a diaphragm spring 30. The pressing force F1 of the spring 41 is set lower than the pressing force F2 of the spring 30.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a friction clutch device in which drive-side clutch plates and driven-side clutch plates that are stacked alternately are pressed together by a suppressor, and power is transmitted by the frictional force thereof.

This type of friction clutch device is built into the power transmission system of motorcycles, etc., but when an excessive reverse load (pack torque) is applied from the driven shaft side due to sudden engine braking, for example, this reverse load will cause the Since it is added to the engine and power transmission system, there is a risk that it will have an adverse effect on both.

As a countermeasure to this, conventionally, as shown in Japanese Patent Publication No. 51-31893, the clutch member connected to the driven shaft is divided in the axial direction, and one part is directly connected to the moving shaft.
A one-sided clutch is provided on the other side that allows power transmission only from the drive source side, and when a reverse load is applied as described above,
A clutch is known that absorbs reverse load by causing slippage between the clutch plates.

However, with this configuration, even when slippage occurs between the clutch plates as described above, the clutch plates remain pressed together by the clutch spring and suppressor (clutch outer) in the same way as when normal power is reached. Because of this condition, there are problems such as a large load being applied to the clutch plate and easy wear.

The present invention was made based on these circumstances, and
It is an object of the present invention to provide a friction clutch device that can weaken the frictional force between clutch plates when an excessive reverse load is applied from the driven shaft side, can reliably absorb and alleviate the reverse load, and can also prevent premature wear of the clutch plates. purpose.

That is, in order to achieve the above object, the present invention provides a movable member that advances toward the suppressor side when a reverse load is applied from the driven shaft side between the clutch member and the driven shaft,
A spring member is interposed between the movable member and the suppressing body to press and bias the suppressing body in a direction opposite to the biasing direction of the clutch spring, and the biasing force of the spring member is greater than the biasing force of the clutch spring. By setting it to a small value, the biasing force of the suppressor toward the clutch plate side (
It is characterized by reducing the load (1) and causing slippage between the clutch plates.

An embodiment of the present invention will be described below based on drawings in which the present invention is applied to a motorcycle.

In FIG. 1, 1 is a frame, 2 is an engine, 3 is a front fork, 4 is a fuel tank, 5 is a seat, and 6 is a rear wheel. The engine 2 of this embodiment has a V-type engine in which a front cylinder 8 and a rear cylinder 9 are arranged in a substantially V shape on a crankcase 7.
The crank case 7 houses a crank IIIll11 driven by the pistons 10 of the valley cylinders 8 and 9, an intermediate shaft 12 as a driven shaft, and an output shaft 13 in parallel with each other.

A driven gear 1 is connected to one end of the middle shaft 12 via a bearing 14.
5 is rotatably supported by a shaft, and this driven gear 15 is always engaged with the drive gear groove of the crankshaft 1). In between again! A friction clutch device 17 is attached to the 1III 112 adjacent to the driven gear 15, and when this friction clutch device 17 is connected, the crank 44Il
1) is transmitted to the intermediate shaft 12 via the drive gear J6 and the driven gear 15. Then, the rotation of the intermediate m12 is selectively reduced in multiple stages by the constantly meshing gear mechanism 18 and then transmitted to the output shaft 13, and the rotation of the output shaft J3 is further transmitted via the bevel gears 19 and 19. The power is transmitted to the drive shaft 2 in the rear arm 20, and the rear wheel 6 is driven by this drive 14@21.

The details of the friction clutch device 17 are shown in FIG. 3. That is, 22 is a substantially cylindrical clutch housing, which is coaxially fixed to one end surface of the driven gear 15 and rotated in conjunction with the crankshaft 11.

A clutch member 23, which is connected to the intermediate shaft 2, is housed in the clutch housing 22 so as to be rotatable relative to the intermediate shaft 2. A plurality of drive side clutch plates 24... and driven side clutch plates 25... are provided on the inner circumference of the clutch housing 22 and the outer circumference of the clutch member 23.
are installed, these clutch plates 24...
25 are alternately overlapped within the clutch housing 22. Further, a release 26 is provided at one end of the intermediate shaft 12 and is movable in the axial direction of the intermediate shaft 12, and the release 26 is moved in the above direction by a bushing rod 27 inserted through the intermediate shaft 12. . A substantially disk-shaped pressing body 29 is attached to the outer periphery of the release 26 via a bearing 28, and this pressing body 29 rotates together with the clutch member 23. The pressing body 29 is urged by a diaphragm spring 30 serving as a clutch spring disposed coaxially on the outer surface of one end thereof in a direction in which the clutch plates 24, 25, etc. are frictionally engaged with each other. The shift latch plates 24..., 25... are pressed together by this biasing force.

6- However, a clutch disk 31 is provided between the intermediate shaft 2 and the clutch member 23, and this clutch disk 3
is directly connected to the intermediate shaft 12 by straight spline engagement with the outer periphery of the intermediate shaft 12. An annular intermediate member 32 is coaxially provided on the radially outer side of the clutch gear 3, and this intermediate member 32 is fixed to the clutch member 23 via a rivet 33.

An annular movable member 35 is engaged with a straight spline in the through hole 34 at the center of the intermediate member 32 .
An annular spring receiver 36 is fitted to the outer peripheral portion of the movable member 35 on the side of the suppressor 29 so as to be slidable in the axial direction. A torsion spline 3 is provided on the outer circumferential surface of the pressing body 29 at the position where the clutch is located.
7 is carved, and the inner circumferential surface of the opening 38 of the movable member 35 is engaged on this torsion spline 37.

Therefore, when a reverse load is applied to the intermediate shaft 12 due to sudden engine braking, for example, and the rotational speed of the intermediate shaft 12 exceeds the rotational speed of the clutch housing 22, there is a speed difference between the clutch member 23 and the clutch post 3. Because of this difference, the movable member 35 is moved toward the suppressor 29 by the action of the torsion spline 37. In addition, the reference numeral 39 in FIG. 3 is a stock for positioning the movable member 35, and is rotatably attached to the outer periphery of the clutch disk 3. A disc spring 4 serving as a spring member is interposed between the spring receiver 36 of the movable member 35 and a support protrusion 40 protruding from the back surface of the pressing body 29. The disc spring 4 presses and biases the pressing body 29 in the opposite direction to the biasing direction by the diaphragm spring 30,
The biasing force F1 of the disc spring 4 in this interposed state is also set to be smaller than the biasing force F2 of the diaphragm spring 30. Therefore, when the movable member 35 is advanced toward the suppressing body 29 due to the action of a reverse load, the disc spring 4 is compressed and biases the pressing body 29 with a force F3 that is larger than the biasing force Fl. It has become. In addition, the movable member 35 and the spring receiver 3
6, a return disc spring 42 is interposed in a compressed state. This return disc spring 42 biases the movable member 35 in the opposite direction to the above-mentioned moving direction, and this biasing force F4 is set smaller than the biasing force F3 when the disc spring 4 is compressed. .

With this configuration, the disc spring 4 is not compressed significantly during normal power transmission, so the clutch plate 24...
, 25... is the pressing force F of the suppressing body 29 as described above F2
-Fl. For this reason, the clutch plates 24..., 25.
...They are not pressed against each other by the above-mentioned pressing force F, and the 220 rotations of the clutch ring connected to the crankshaft 1 are caused by the frictional force generated between the clutch plates 24..., 25... 23, and from this clutch member 23 to intermediate member 32. It is transmitted to the intermediate shaft 12 through the movable member 35 and the clutch post 31f. In this state, if an excessive reverse load is applied from the intermediate shaft 12 side due to the action of engine braking due to an accident, for example, the movable member 35 will be pushed toward the pressure body 29 side by the action of the torsion spline 37 as described above. The plate spring 4 is compressed between it and the suppressor 29. In this case, the biasing force F3 by which the disc spring 41 tries to push back the suppressing body 29 becomes a dog, so the pressing force F' of the pressing body 29 against the clutch plates 24..., 25... becomes F2-F3. Also, the pressing force F during the above-mentioned normal power transmission is also smaller. Therefore, the clutch plate 24.
Since the frictional force between the clutch plates 24..., 25... is reduced, a space is created between the clutch plates 24..., 25...
When a reverse load is applied, the power transmission capacity is substantially reduced.

Therefore, the reverse load can be reliably absorbed and alleviated, and the speed change gear mechanism 18
This can prevent negative effects on the engine 2.

Moreover, when a reverse load is applied, the clutch plate 24...

25... Since the force pressing against each other is weakened, the clutch plates 24..., 25... can be easily removed, and the load on the clutch plates 24..., 25... can be reduced. , the clutch plates 24..., 25... have the advantage of being able to prevent early wear.

Also, when the clutch is turned OFF, the release 26 is released from the pressing body 2.
9 is pressed in a direction opposite to the biasing direction of the diaphragm spring 3o, the disc spring 4 returns to its free state and its biasing force F approaches O. If this happens, there is a risk that the movable member 35 will move toward the suppressor 29 as the intermediate shaft 12 rotates, but in the above configuration, when the biasing force of the disc spring 4 decreases, the movable member 35 will be moved by the biasing force of the return disc spring 42. 35 is pressed in the opposite direction, this movable member 3
5 can be prevented from moving.

Note that the present invention is not limited to the embodiments described above. For example, the spring member interposed between the movable member and the suppressing body is not limited to a disc spring, but a coil spring may be used, and a coil spring may be used instead of a diaphragm spring that biases the suppressing body.

According to the present invention described in detail above, when an excessive reverse load is applied from the driven shaft side, the biasing force of the suppressor against the clutch plate is weakened and the frictional force between the clutch plates is reduced, so that slippage between the clutch plates is reduced. occurs, and the above-mentioned reverse load can be absorbed and alleviated. Moreover, since the force pressing the clutch plates together can be weakened, the load on the clutch plates can be reduced, and there is an advantage that premature wear can be prevented.

[Brief explanation of drawings]

The drawings show one embodiment of the present invention, in which Fig. 1 is a side view of a motorcycle, Fig. 2 is a partially sectional plan view of the engine, and Fig. 3 is a side view of a motorcycle.
The figure is a sectional view. DESCRIPTION OF SYMBOLS 12... Driven shaft (intermediate shaft), 22... Clutch housing, 23... Clutch member, 24.25... Clutch plate, 29... Pressing body, 30... Clutch spring (diaphragm spring) ), 35... Movable member, 4... Spring member (plate spring). Applicant's agent Patent attorney Takehiko Suzue Figure 2 JP-A-59-231217 (5) Figure 3 r' -1qg

Claims (1)

[Claims] A clutch member connected to a movable shaft is relatively rotatably accommodated in a clutch housing that is rotationally driven by power transmission from a drive source, and a clutch plate and a clutch provided in the clutch housing are mounted on one end of the clutch housing in the axial direction. A friction mechanism in which a suppressing body is arranged to press a clutch plate provided on a member to each other, and the suppressing body is urged in the pressing direction by a clutch spring, and power is transmitted by the frictional force generated between the clutch plates. In the clutch device, a movable member is provided between the clutch member and the driven shaft that advances toward the suppressor when a reverse load is applied from the driven shaft, and a movable member is provided between the movable member and the suppressor. 7, characterized in that a spring member is interposed to press and bias the suppressing body in a direction opposite to the direction of the biasing force by the clutch spring, and the biasing force of the spring member is set to be smaller than the biasing force of the clutch spring. Friction clutch device.