JPS6157497B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a clutch operating device that makes clutch operation easier without reducing clutch capacity.

[Prior art] Friction clutches used in motorcycles, etc.
It is preferable to use a clutch that requires less force to engage and disengage, and also has a shorter stroke because it facilitates operation.

[Problems to be Solved by the Invention] However, reducing the capacity of the clutch, that is, the amount of torque that can be transmitted,
This must be avoided as it will reduce the vehicle's power performance.

In addition, increasing the operating force by increasing the size of members such as the clutch actuating arm must be avoided since this increases the size of the clutch. Particularly in motorcycles, a large clutch not only increases the weight of the vehicle, but also increases the width of the vehicle, making it difficult to maintain a large bank angle. Therefore,
From the standpoint of improving running performance, it is desirable to make the clutch as small as possible.

[Means for Solving the Problems] The present invention was made in view of the above circumstances, and provides a clutch operation that can reduce the clutch operation force without reducing the clutch capacity or increasing the clutch size. It provides equipment. In the clutch operating device according to the present invention, the other end of the auxiliary spring, one end of which is locked to the rotational end of the clutch actuating arm, is connected to the other end of the auxiliary spring when the line connecting the rotational center of the auxiliary spring and the one end is in the connected state of the clutch. A connecting member is fixed so as to pass over the center of rotation of the clutch actuating arm, and has a concave portion between the center of rotation of the auxiliary spring and the other end of the auxiliary spring, from which the center of rotation of the clutch actuating arm faces. It was an intervention.

[Function] In the present invention, when the clutch actuating arm rotates from the connected state of the clutch, the line connecting one end of the auxiliary spring and the center of rotation gradually separates from the center of rotation of the clutch actuating arm. The rotational direction component of the clutch operating arm due to the contractile force gradually increases. Further, since the connecting member prevents the auxiliary spring and the clutch actuating arm from overlapping in the axial direction, the auxiliary spring is prevented from protruding to the side of the clutch actuating arm.

[Example] Hereinafter, an example of the present invention will be described in detail with reference to the drawings. FIG. 1 is a sectional view showing an embodiment in which a clutch operating device according to the present invention is applied to a clutch of a motorcycle, and FIG. 2 is a side view of the main parts thereof. 1st
In the figure, numeral 1 is a crankcase, 2 is an intermediate shaft supported by the crankcase 1, and the intermediate shaft 2 is driven by a crankshaft (not shown). A starting gear 3 and a driving gear 4 are mounted on the intermediate shaft 2 on the inside and outside of the crankcase 1, respectively. In particular, the driving gear 4 and the intermediate shaft 2 are spline-coupled and are integrally formed. Rotate to .
Reference numeral 5 denotes a clutch shaft, which is supported by the crankcase 1 so as to be parallel to the intermediate shaft 2. One end of the clutch shaft 5 protrudes from the crankcase 1 toward the drive gear 4, and a wet multi-plate clutch 6 is mounted thereon. Reference numeral 7 designates a clutch housing constituting this clutch 6, which is formed into a substantially cylindrical shape with one end open, and this cylindrical portion 7a is provided with a large number of notches 7b in the axial direction.
A gear 8 is integrally connected to the clutch housing 7. This gear 8 is rotatably supported on the clutch shaft 5 via a spacer 9, and the clutch housing 7 is open to the outside (to the right in FIG. 1). A clutch boss 10 is inserted into the clutch housing 7 and connected to the clutch shaft 5 by a spline. This clutch boss 10 has a cylindrical portion 10a facing the cylindrical portion 7a of the clutch housing 7 with a constant gap therebetween, and a flange-shaped pressing portion 10b formed to close this gap from the outside. A large number of grooves 10c are formed in the axial direction on the outer peripheral surface of the portion 10a. Reference numeral 11 designates a second pressure plate, which is interposed between the clutch housing 7 and the clutch boss 10, and includes a pressing portion 11a facing the gap between the cylindrical portions 7a and 10a, and a plurality of pressing portions 11a extending outward through the clutch boss. The columnar portion 11b is provided. Cylindrical part 7a
A large number of clutch plates 12 and friction plates 13 are alternately stacked in the gap between the clutch plates 12 and 10a.
engages with the notch 7b of the clutch housing 7,
Each friction plate 13 is engaged with a groove 10c of the clutch boss 10. Reference numeral 14 designates a first pressure plate, which is screwed onto the tip of each columnar portion 11b of the second pressure plate 11. Each columnar part 1
A coil spring 15 is attached to 1b, and this spring 1
Both ends of the clutch boss 5 are in contact with the first pressure plate 14 and the clutch boss 10 so as to separate them from each other in a compressed state. Therefore, in FIG. 1, normally the second pressure plate 11 is urged to the right (outside) together with the first pressure plate 14, and each clutch plate 12 and friction plate 13 are pressed against the pressure portions 10b and 11a. There is close contact between That is, this clutch 6 is in a connected state.

Next, the operating device for this clutch 6 will be explained.

A crankcase cover 16 is firmly fixed to the crankcase 1. The case cover 16 is formed to cover the clutch 6, and the portion of the clutch 6 facing the first pressure plate 14 has a concave portion 16a recessed so as to be close to the first pressure plate 14. It is formed. A substantially umbrella-shaped push screw 17 is supported coaxially with the clutch shaft 5 in this recess 16a. This Pushyu Screw 17
The umbrella portion 17a is located on the first pressure plate 14 side. A push screw housing 18 is attached to the inner surface of the case cover 16 so as to face the umbrella portion 17a, and its position is determined by a dowel pin 33. Push screw housing 18 and umbrella portion 17 of push screw 17
A plurality of cam grooves 17b, 18a whose depths gradually change on the same radius are formed on the opposing surfaces of the cam grooves a, and a ball 19 is interposed between the cam grooves 17b, 18a. Accordingly, the rotation of the push screw 17 causes the push screw 17 to move in the left-right direction in FIG. 1 on the same axis as the clutch shaft 5.
20 is a push screw 17 and a case cover 1
This is a seal that prevents oil leakage between 6 and 6.

Reference numeral 21 denotes a bearing, the outer race of which is fixed to the first pressure plate 14, and a substantially hat-shaped push piece 22 fitted into the inner race from the outside. An adjustment screw 23 is screwed through the push screw 17, and its inner tip abuts the push piece 22, and its outer end projects beyond the push screw 17. Note that there is an O between the adjustment screw 23 and the push screw 17.
A ring 24 is attached to prevent oil leakage.

Reference numeral 25 designates a push lever as a clutch operating arm, which engages with a notch 26 formed in the externally projecting end of the push screw 17 and rotates together with the push screw 17. This push lever 25 is fixed by a washer and a nut 27 attached to the adjustment screw 23. A clutch wire 28 is connected to the rotating end 25a of the push lever 25.
One end of the is attached. This clutch wire 2
The other end of 8 is engaged with a clutch lever (not shown),
By squeezing the clutch lever, the clutch wire 28 is pulled toward the clutch lever, and the push lever 25 is rotated to the position shown by the imaginary line in FIG. Note that the solid line in FIG. 2 indicates the connected state of the clutch 6. Rotating end 2 of this push lever 25
One end 29a of the auxiliary spring 29 is locked to 5a. Note that although the pivoting end of the push lever 25 is bifurcated, there is no difference in that one end 29a of the auxiliary spring 29 is locked to the pivoting end 25a. 30 is a pin implanted in the recess 16a of the case cover 16, and a line connecting this pin 30, one end of the auxiliary spring 29, and the adjusting screw 23, which is the center of rotation of the push lever 25, is connected to the clutch 6.
The position of the pin 30 is determined so that it forms a straight line when it is in the connected state, that is, at the solid line position in FIG. A connecting member 31 having a concave portion facing the pivoting center of the push lever 25 in order to avoid contact with the push lever 25 is rotatably held on this pin 30, and the auxiliary spring is attached to the pivoting end of the connecting member 31. The other end of 29 is attached. In this embodiment, the concave portion is formed by forming the connecting member 31 into a semicircular arc shape. Therefore, when the push lever 25 rotates, the auxiliary spring 29 is pressed against the pin 30.
Since the pin 30 rotates around the center, this pin 30 also serves as the center of rotation of the auxiliary spring 29. That is,
The connecting member 31 is interposed between a pin 30 that is the center of rotation of the auxiliary spring 29 and the other end of the auxiliary spring 29, and locks the other end of the auxiliary spring 29 to the pin 30. Note that a clutch cover 32 is placed over the recess 16a of the case cover 16 in which these operating devices are housed.

Now, push lever 2 is used as the clutch operating arm.
In the clutch connected state where 5 is in the solid line position in FIG. 2, the push screw 17 is in a position approaching the case cover 16, in other words, in a position away from the first pressure plate 14. At this time, the first pressure plate 14 is pushed to the right (outside) in FIG.
The pressing portion 11a of the pressure plate 11 is also on the right side in the figure. As a result, each clutch plate 12 and friction plate 13 are pressed between the two pressing parts 10b and 11a, and the rotation of the crankshaft is caused by the intermediate shaft 2, drive gear 4, gear 8, clutch housing 7, clutch plate 12, and friction plate. 13, is transmitted to the clutch shaft 5 via the clutch boss 10. The rotation of the clutch shaft 5 is transmitted to the rear wheels via a transmission (not shown).

When the clutch lever attached to the handle is squeezed to disengage the clutch 6, the push lever 2
5 rotates to the position indicated by the imaginary line in FIG. 2, and the push screw 17 moves toward the first pressure plate 14. For this reason, since the adjustment screw 23 presses the push piece 22, the first and second pressure plates 14, 11 resist the elastic force of the spring 15 and
Move to the left in the diagram. As a result, the pressing force between the clutch plate 12 and the friction plate 13 is released, so that the clutch becomes in the disconnected state.

Note that the push lever 25 is operated by the return force of the spring 15 of the first pressure plate 14, which is applied to the cam groove 1.
Due to the rotational force converted by the clutch lever 7b, 18a and the ball 19, the clutch lever automatically returns to the solid line position in FIG. 2 when the clutch lever is released.
Further, the engagement and disengagement of the clutch 6 and the rotational position of the push lever 25 can be adjusted by loosening the nut 27, rotating the adjusting screw 23, and then tightening the nut 27 to lock it.

At the solid line position in FIG. 2, the auxiliary spring 29 is in a stretched state and its tension is at its maximum;
Since the line connecting the one end 29a and the pin 30 is located on the center of rotation of the push lever 25, no urging force is generated in the rotation direction of the push lever 25.
Therefore, the capacity of the clutch 6 is not reduced in the least.

As the push lever 25 rotates to the imaginary line position in FIG. 2, the auxiliary spring 29 gradually contracts. Since the push lever 25 gradually moves away from the center of rotation, a component in the rotation direction of the push lever 25 due to the contraction force of the spring 29 is generated and gradually increases. Fig. 3 is a graph showing the relationship between the stroke of the clutch lever and the grip force required for its operation, and A in the figure indicates this auxiliary spring 29.
indicates the amount of force that contributes to the decrease in grip strength. Therefore, the gripping force required to operate the clutch lever is reduced as shown by curve C compared to the conventional clutch lever shown in FIG.

Further, a connecting member 31 having a concave portion facing the rotating center of the push lever 25 is interposed between the auxiliary spring 29 and the pin 30 which is the center of rotation thereof, and the other end of the auxiliary spring 29 is connected to the pin 30 through the connecting member 31. Pin 3
0, the auxiliary spring 29 and push lever 25 are prevented from overlapping in the axial direction.

Therefore, the auxiliary spring 29
5 can be prevented from protruding laterally, and the device can be prevented from elongating in the direction of the clutch shaft 5. In other words, compared to the case where the other end of the auxiliary spring 29 is directly engaged with the pin 30, the length in the direction of the clutch shaft 5 can be shortened, and the entire structure can be made compact.

The present invention can also be applied to release levers such as dry single-plate clutches widely used in automobiles. That is, the clutch operating arm of the present invention may be a release lever that is pivotally supported by the clutch cover and interposed between the release bearing and the pressure plate.

[Effects of the Invention] As explained above, according to the present invention, the line connecting the other end of the auxiliary spring, one end of which is locked to the rotational end of the clutch actuating arm, and the rotational center of the auxiliary spring and the one end. is locked so that it passes over the center of rotation of the clutch actuating arm when the clutch is in the connected state, so when the clutch actuating arm rotates from the connected state, the line connecting one end of the auxiliary spring and the center of rotation Since the clutch actuating arm gradually moves away from the center of rotation, the component in the rotational direction of the clutch actuating arm due to the contraction force of the auxiliary spring gradually increases.

Furthermore, since a connecting member having a concave portion facing the rotational center of the clutch operating arm is interposed between the rotational center of the auxiliary spring and the other end of the auxiliary spring, the auxiliary spring can be connected to the auxiliary spring by the connecting member. This prevents the clutch actuating arm from overlapping in the axial direction.

Therefore, the rotation of the clutch actuating arm can be assisted only when the clutch actuating arm is rotated from the connected state by means of an auxiliary spring that does not pose the risk of lengthening the device in the axial direction, thereby reducing the clutch capacity or
The clutch operation force can be reduced without increasing the size of the clutch.

[Brief explanation of the drawing]

Fig. 1 is a sectional view showing an embodiment of the clutch operating device according to the present invention applied to a clutch of a motorcycle, Fig. 2 is a side view of its main parts, and Fig. 3 shows the stroke of the clutch lever and its operation. It is a graph showing the relationship with the required grip strength. 6...Clutch, 23...Adjustment screw as the center of rotation of the clutch operating arm, 25...Push lever as the clutch operating arm, 25a... Rotation end,
29...Auxiliary spring, 29a...One end, 30...A pin serving as the center of rotation of the auxiliary spring.

Claims (1)

[Claims] 1 In a clutch that is engaged and disconnected by rotating the clutch operating arm 25, an auxiliary spring 2 whose one end is locked to the rotating end of the clutch operating arm 25 is used.
9, and the other end of the auxiliary spring 29 is locked such that a line connecting the rotation center of the auxiliary spring 29 and the one end passes over the rotation center of the clutch operating arm 25 when the clutch is connected. A clutch operating device characterized in that a connecting member 31 having a concave portion facing the rotation center of the clutch operating arm 25 is interposed between the rotation center of the auxiliary spring 29 and the other end of the auxiliary spring 29. .