ES2371346T3 - CLUTCH AND VEHICLE OPERATING DEVICE EQUIPPED WITH THE SAME. - Google Patents

Abstract

Clutch operating device having a friction clutch (18) with a clutch spring (27), and an operating element (9) connected to the friction clutch (18) by transmission components (43a, 43b) and being manually operable against the pushing force of the clutch spring (27) to disconnect the torque transmission by the friction clutch (18), and a clutch operation assistance device (50) that includes an assist mechanism (52) that includes an auxiliary elastic element (59) which, when the operating element (9) is operated in a direction of disengaging the friction clutch (18), pushes the transmission components (43a, 43b) in the direction of disengaging the friction clutch (18), while the operative element (9) is displaced from a starting position of disengagement, where the operative element (9) receives the reaction force of the clutch spring (27), to a disengaging position where it is compiled The friction clutch release (18), characterized in that the pushing force of an auxiliary elastic element (59), applied to the transmission component (43a, 43b) by means of a rotating element (57), is kept within a range fixed while the operating element (9) is displaced from an intermediate position between the starting position of disengagement and the position of disengagement to the position of disengagement, where the assist mechanism is arranged so that an increase in the pushing force of the Elastic auxiliary element (59) applied to the transmission components (43a, 43b) is canceled when the operating element (9) approaches the disengagement position.

Description

Clutch and vehicle operating device equipped with it

The present invention relates to a clutch operating device, which can reduce the force necessary to operate a friction clutch to disconnect the torque transmission by the friction clutch, and a vehicle equipped with the clutch operating device.

A motorcycle engine, for example, is equipped with a friction clutch that can connect and disconnect the transmission from the crankshaft torque to the transmission. The friction clutch has friction plates and clutch plates alternately placed one above the other. The friction plates are constantly pushed against the clutch plates by a clutch spring and maintained in a state capable of transmitting torque.

The friction clutch has a clutch release mechanism. The clutch release mechanism, which is used to relieve pressure against the friction plates produced by the clutch spring, is connected to a clutch lever by means of a clutch cable. When the rider squeezes the clutch lever, the friction plates are separated from the clutch plates against the thrust force of the clutch spring to disconnect the torque transmission from the friction plates to the clutch plates.

In a friction clutch used in a high revolution, high power engine, it is desirable that the clutch spring mounting load be set to a high value to increase torque capacity. However, since the clutch lever is operated by a human hand, when the mounting load of the clutch spring is increased, the load increases when operating the clutch lever.

As means for solving the above problem, a clutch operating device is known, in which an assist mechanism that can reduce the force necessary to operate the clutch lever is incorporated into a clutch release mechanism to which the clutch cable is connected. (JP-A-Hei 7-132872).

The conventional assistance mechanism has a rotating arm together with a push lever of the clutch release mechanism and a spring unit disposed between one end of the arm and the engine. The spring unit has a spring support that can expand and contract in its axial direction and a helical compression spring to push the spring support in the direction in which the spring support expands. The spring support has a first end rotatably connected to the end of the arm and a second end rotatably connected to a support extending from the motor.

In the conventional assistance mechanism, the center of rotation of the arm and the first and second ends of the spring support are aligned in a straight line when the clutch lever is operated a distance corresponding to its free play. Therefore, the thrust force of the compression coil spring acts in a direction such that it compresses the arm and does not act as a force (momentum) to rotate the arm.

However, when the clutch lever turns the free play, the joint between the end of the arm and the first end of the spring support deviates from the straight line connecting the center of rotation of the arm and the second end of the support dock. Therefore, the thrust force of the helical compression spring acts in a direction such that the arm rotates, and the arm is forcedly rotated in a direction such that it disengages the friction clutch. As a result, the thrust force of the compression coil spring is added to the force applied to operate the clutch lever and the force necessary to operate the clutch lever to disengage the friction clutch is reduced.

According to the clutch operating device described in JP-A-Hei 7-132872, when the clutch lever is turned to a starting position of disengagement at the end of the free clearance, the thrust force of the clutch spring is applied to the clutch lever The helical compression spring of the assist mechanism is expanded to cancel the thrust force of the clutch spring in synchronism with the operation of the clutch lever in a direction such that it disengages the friction clutch after the clutch lever has passed by the starting position of disengagement.

However, in the clutch operating device, the helical compression spring of the assist mechanism can be freely expanded after the clutch lever has passed through the starting position of disengagement. Therefore, the thrust force of the compression coil spring applied from the arm to the thrust lever is not controlled in any way. That is, since one end of the spring support is connected directly to one end of the arm and the spring unit rotates in the same manner as the arm, the magnitude of the pushing force applied to the pushing lever remains uncontrolled.

Thus, it is impossible to prevent the clutch lever from suddenly loosening when it is near a disengagement position where the friction clutch is disengaged while the clutch lever is moved in a direction such that it disengages the friction clutch. Therefore, the feeling of operation of the clutch lever is not natural, and there is still room for improvement in terms of the operability of the clutch lever.

When the clutch lever moves in a direction such that it disengages the friction clutch, the force necessary to operate the clutch lever is preferably small especially in the first half between the start position of disengagement and the position of disengagement (half on the side of the starting position of disengagement). That is, it is preferable to reduce the force necessary to operate the clutch lever in the initial stage of what is called half-clutch operation. However, with the conventional clutch operation device, a large force is needed in the first stage of the half-clutch operation. Therefore, there is also room for improvement in terms of the operability of the clutch lever in this regard.

The prior art document EP 1498346 A2, which constitutes prior art according to article 54 (3) EPC, describes a clutch operating device with friction clutch and a clutch spring, where an operating element is connected to the friction clutch, by transmission components, and being manually operable against the pushing force of the clutch spring to disconnect the torque transmission by the friction clutch. Said device includes a rotating element, directly connected to the spring means, which is adapted to the operation of the clutch.

An object of the present invention is to provide a clutch operating device with a clutch operating assistance device, with which the operation of the operating element when disengaging the friction clutch does not cause any discomfort and can improve the operability of the clutch. operating element, and a vehicle equipped with the clutch operation assistance device.

This objective is achieved in a novel way by a clutch operating device having the characteristics of independent claim 1. Preferred embodiments are set forth in the dependent claims.

Preferably, the auxiliary elastic element pushes the transmission component in a direction of engaging the friction clutch when the operating element is in a return position on the return side of the starting position of disengagement, and the direction of the force of The thrust applied to the transmission component is changed from the direction of engaging the friction clutch to the direction of disengaging the friction clutch when the operating element is moved from the return position to the disengagement position over the initial disengagement position, and where an elastic cancellation element is provided that applies a pushing force to cancel the pushing force of the auxiliary elastic element applied to the transmission component when the operating element is in the return position.

Also, preferably the friction clutch has a clutch release mechanism, and where the transmission component has a first clutch cable connected to the operating element and a second clutch cable connected to the clutch release mechanism and is interposed between the first clutch cable and the second clutch cable.

In addition, preferably the displacement of the first clutch cable and the displacement of the second clutch cable while the operating element is operated are equal to each other.

In addition, the clutch operating device also preferably includes a mobile element that can be moved in synchronism with the transmission component, where the auxiliary elastic element, when the operating element is operated in a direction such that it disengages the friction clutch, applies a pushing force to move the moving element in a direction such that it disengages the friction clutch while the operating element moves from a starting position of disengagement where the operating element receives the reaction force of the clutch spring to a disengaging position where the friction clutch release is completed, a rotating element for transmitting the pushing force of the auxiliary elastic element to the mobile element, and an eccentric mechanism that is interposed between the mobile element and the rotating element and that maintains the applied thrust force from the rotating element to the mobile element within a ran go fixed while the operating element moves from an intermediate position between the start position of disengagement and the position of disengagement to the position of disengagement.

Advantageously, the eccentric mechanism has an eccentric groove formed through one of the movable element and the rotary element, and an eccentric follower that is in contact with the eccentric groove and supported by the other of the movable element and the rotary element.

In addition, the transmission component advantageously has the first clutch cable connected to the operating element and the second clutch cable connected to a friction clutch release mechanism, and where the first and second clutch cables are connected to the mobile element .

Furthermore, advantageously, the eccentric groove prevents the auxiliary elastic element from expanding or contracting freely in conjunction with the eccentric follower while the operating element moves from the intermediate position to the disengagement position.

According to a preferred embodiment, the auxiliary elastic element pushes the transmission component in a direction of engaging the friction clutch when the operating element is in a return position on the return side from the starting position of disengagement, and the direction of The thrust force applied to the transmission component is changed from a direction of engaging the friction clutch to a direction of disengaging the friction clutch when the operating element is moved from the return position to the disengagement position on the starting position. of disengagement, and where the elastic cancellation element that pushes the rotating element in a direction of canceling the pushing force of the auxiliary elastic element is provided when the operating element is in the return position.

Preferably, the thrust force of the clutch spring applied to the movable element is zero and the rotary element receives the thrust force of the elastic cancellation element while the operating element moves from the return position to the starting position of disengagement.

Preferably, the clutch operating device further includes a stop to receive the rotating element when the operating element is in the return position, where the stop is pushed by the elastic cancellation element.

Also provided is a clutch operating device incorporated in a clutch operating assistance device and having a friction clutch with a clutch spring, a transmission component connected to the friction clutch, and an operating element that is connected to the component of transmission and that changes the engagement state of the friction clutch when it is operated against the thrust force of the clutch spring, including the clutch operating assistance device a moving element that can be moved in synchronism with the operating element, a rotating element, an oscillating auxiliary elastic element for applying a pushing force to rotate the rotating element, and a pushing force transmission component, in particular an eccentric mechanism interposed between the moving element and the rotating element for transmitting the force of thrust applied to the rotating element to the mobile element, where, when the e The operating element is operated in a direction such that it disengages the friction clutch, the auxiliary elastic element applies a pushing force to move the moving element in a direction such that it disengages the friction clutch while the operating element moves from a starting position. of disengagement where the operating element receives the reaction force of the clutch spring to a disengaged position where the friction clutch disengagement is completed.

Preferably, the thrust force transmission component, in particular the eccentric mechanism changes a speed ratio, which is the ratio of the rotational speed of the rotating element to the advancing speed of the moving element, while the operating element moves from the start position of disengagement to the position of disengagement.

In addition, preferably, the speed ratio at the time that the operating element is in the starting position of disengagement is larger than at the time the operating element is in the disengaging position.

In addition, preferably, the average speed ratio while the operating element is shifted from the starting position of disengagement to an intermediate position between the starting position of disengagement and the disengagement position is greater than the average of the relationship of speed while the operating element is moved from the intermediate position to the disengagement position.

Furthermore, preferably the eccentric mechanism gradually decreases the speed ratio while the operating element moves from the starting position of disengagement to the disengaging position.

Advantageously, the eccentric mechanism maintains the relationship between the reaction force of the clutch spring and the load applied to the operating element within a fixed range while the operating element moves from the starting position of disengagement to an intermediate position between the position. Start of disengagement and disengagement position.

Furthermore, advantageously, the mobile element is a rotating element.

Furthermore, advantageously, the eccentric mechanism has an eccentric groove formed through one of the mobile element and the rotating element, and an eccentric follower that is in contact with the eccentric groove and supported by the other of the mobile element and the rotating element. .

Furthermore, advantageously, the auxiliary elastic element is a spring.

The above objective is also achieved with a vehicle equipped with the friction clutch, the transmission component, the operating element and a clutch operation assistance device according to any of the previous embodiments.

The present invention is explained in more detail below with respect to its various embodiments in conjunction with the accompanying drawings, where:

Figure 1 is a side view of a motorcycle according to an embodiment.

Figure 2 is a cross-sectional view of a friction clutch for use in the embodiments.

Fig. 3 is a side view of an operating assistance device according to a first embodiment.

Fig. 4 is a side view of the operating assistance device of the first embodiment, illustrating the state of an assistive mechanism while a clutch lever is in a return position.

Figure 5 is a side view, partially in cross-section, illustrating the positional relationship between an articulation plate, a spring unit and a pressure pin while the clutch lever is in a return position in the first embodiment. .

Figure 6 is a cross-sectional view of the operating assistance device according to the first embodiment.

Fig. 7 is a perspective view of the operation assistance device according to the first embodiment.

Figure 8 is a perspective view of a case body in which the assist mechanism has been incorporated in the first embodiment.

Figure 9 is a perspective view of a box body in which the assist mechanism has been incorporated in the first embodiment.

Fig. 10 is a side view of the operating assistance device of the first embodiment, illustrating the state of the assistive mechanism while the clutch lever is in a starting position of disengagement.

Figure 11 is a side view, partially in cross-section, illustrating the positional relationship between the articulation plate, the spring unit and the pressure pin while the clutch lever is in the starting position of disengagement in the First realization

Fig. 12 is a side view of the operating assistance device of the first embodiment, illustrating the state of the assistive mechanism while the clutch lever is in a disengaged position.

Figure 13 is a side view, partially in cross-section, illustrating the positional relationship between the articulation plate, the spring unit and the pressure pin while the clutch lever is in the disengaged position in the first embodiment. .

Figure 14 is a cross-sectional view illustrating the positional relationship between a cancellation spring unit and a locking pin of the articulation plate in the first embodiment.

Figure 15 is a characteristic view depicting changes in loads applied to a thrust lever and a clutch lever when the clutch lever is moved in a direction such that it disengages the friction clutch in one embodiment.

Figure 16 is a side view of an operating assistance device according to a second embodiment.

Figure 17 is a side view illustrating the state in which a cover of the operating assistance device according to the second embodiment has been removed.

Fig. 18 is a side view of the operating assistance device of the second embodiment, illustrating the state of the assistive mechanism while the clutch lever is in a starting position of disengagement.

Fig. 19 is a side view of the operating assistance device of the second embodiment, illustrating the state of a part of the assistive mechanism while the clutch lever is in a starting position of disengagement.

Fig. 20 is a side view of the operating assistance device of the second embodiment, illustrating the state of an assistive mechanism while a clutch lever is in a return position.

Figure 21 is a side view of the operating assistance device of the second embodiment, illustrating the state of a part of the assistive mechanism while the clutch lever is in the return position.

Fig. 22 is a side view of the operating assistance device of the second first embodiment, illustrating the state of the assistive mechanism while the clutch lever is in a disengaged position.

Fig. 23 is a side view of the operating assistance device of the second embodiment, illustrating the state of a part of the assistive mechanism while the clutch lever is in the disengaged position.

Fig. 24 is a cross-sectional view of the operating assistance device according to the second embodiment.

Figure 25 is a perspective view of the operation assistance device according to the second embodiment.

Fig. 26 is a reverse side view of a case body of the second embodiment.

Figure 27 is a side view illustrating the installation status of a first support.

Figure 28 is a side view illustrating the installation status of a second support.

Figure 29 is a side view illustrating the installation status of a third support.

Figure 30 is a side view illustrating the installation status of a mounting plate.

Figure 31 is a side view illustrating the installation status of the operating assistance device.

Figure 32 is a plan view illustrating the installation status of the operating assistance device.

Figure 33 is a cross-sectional view illustrating the connection structure between the operating assistance device and a second clutch cable.

Figure 34 is a characteristic view depicting changes in loads applied to a thrust lever and a clutch lever when the clutch lever is moved in a direction such that it disengages the friction clutch in one embodiment.

Figure 35 is a side view of a motorcycle according to a modification.

Figure 36 is a cross-sectional view illustrating the connection structure between the operating assistance device and the friction clutch in another modification.

And Figure 37 is a view seen in the direction of arrow A of Figure 36.

The embodiments are described below with reference to the drawings. In the following embodiments, a clutch operating device and an operating assistance device have been applied to a motorcycle. However, the clutch operating device and the operating assistance device can be applied to vehicles of the astride type other than motorcycles and to vehicles other than the astride type vehicles.

(First realization)

A motorcycle 1 shown in Figure 1 has a frame 2. The frame 2 has a front steering tube 3, a main frame element 4 and a down tube 5. The front steering tube 3 supports a front fork 6. At the end In the upper part of the front fork 6 a handlebar 8 is fixed to drive a front wheel 7. A clutch lever 9 as an example of an operating element is mounted on the left end of the handlebar 8.

The main frame element 4 extends backwards from the front steering tube 3. The main frame element 4 supports a fuel tank 10 and a seat 11. The down tube 5 has a first portion 5a which extends down the end front of the main frame element 4 and a second portion 5b extending backward from the lower end of the first portion 5a.

The frame 2 supports a two-cylinder V-motor 13. The engine 13 has a crankcase 14, a front cylinder 15 and a rear cylinder 16. The front cylinder 15 and the rear cylinder 16 protrude from an upper surface of the crankcase 14 towards the fuel tank 10 above the crankcase 14.

The descending tube 5 of the frame 2 holds the motor 13. The first portion 5a of the descending tube 5 extends vertically straight in front of the motor 13, and the second portion 5b of the descending tube 5 extends longitudinally below the crankcase 14.

As shown in Fig. 1 and Fig. 2, the crankcase 14 houses a crankshaft 17 and a wet friction clutch of multiple plates 18. The crankshaft 17 is arranged horizontally in the vehicle width direction, and a small gear speed reduction 19 is fixed to the left end of the crankshaft 17. The friction clutch 18 is located behind the small speed reduction gear 19 and at the left end in the crankcase 14. The friction clutch 18 is covered with a cover of clutch 20 mounted on the left side of the crankcase 14.

The friction clutch 18 is used to connect or disconnect the transmission of the crankshaft torque 17 to an input shaft 21 of a transmission and is operated manually when the motorist squeezes the clutch lever 9 with one hand. As shown in FIG. 2, the friction clutch 18 has a clutch housing 23, a clutch boss 24, a plurality of friction plates 25, a plurality of clutch plates 26, a clutch spring 27 and a mechanism clutch release 28.

The clutch housing 23 is rotatably supported on the left end of the input shaft 21 by means of a support 30. A large speed reduction gear 31 is coaxially connected to one end of the clutch housing 23. The large speed reduction gear 31 It is in a gear hitch with the small speed reduction gear 19. This hitch allows the crankshaft torque 17 to be transmitted to the clutch housing 23.

The clutch boss 24 is fixed to the left end of the input shaft 21 so that it is rotatable in conjunction with the input shaft 21. The clutch boss 24 is surrounded by the clutch housing 23 and has a plurality of protruding portions 32 ( of which only one is shown in figure 2) that protrude towards the clutch cover 20.

The friction plates 25 are supported on the outer periphery of the clutch housing 23. The friction plates 25 are rotatable together with the clutch housing 23 and are coaxially arranged in the axial direction of the input shaft 21 with intervals between.

The clutch plates 26 are supported on the outer periphery of the clutch boss 24. The clutch plates 26 are rotatable together with the clutch boss 24, and each of the clutch plates 26 extends between adjacent friction plates 25. Therefore, the friction plates 25 and the clutch plates 26 are alternately arranged in the clutch housing 23.

In this embodiment, a diaphragm spring is used as the clutch spring 27. The clutch spring 27 is located on the left side of the clutch housing 23 and the clutch boss 24 and is supported at the ends of the protruding portions 32. The clutch spring 27 constantly pushes the friction plates 25 against the clutch plates 26 by means of a pressure plate 33. Thus, a frictional force is generated between the friction plates 25 and the clutch plates 26 and maintains the clutch of friction 18 in clutch condition capable of transmitting torque.

The clutch release mechanism 28 is used to relieve the pressure on the friction plates 25 produced by the clutch spring 27. In this embodiment, the clutch release mechanism 28 is of the rack and pinion type. The clutch release mechanism 28 has a push rod 37 that has a rack 36, and a push lever shaft 39 that has a pinion 38.

The push rod 37 is rotatably supported in the center of the pressure plate 33 by a support 35 and is coaxially located with the input shaft 21. The push rod 37 is also supported by a clutch cover 20 for sliding movement in directions of approach and distance of the input shaft 21.

The push lever shaft 39 is rotatably supported by the clutch cover 20. The push lever shaft 39 extends in a vertical direction and perpendicular to the push rod 37, and the pinion 38 of the push lever shaft 39 it is engaged in engagement with the zipper 36 of the push rod 37. The upper end of the push lever shaft 39 protrudes upward from the clutch cover 20. One end of a push lever 40 is fixed to the upper end of the thrust lever shaft 39. The thrust lever 40 extends horizontally from the upper end of the thrust lever shaft 39 and has a cable connection portion 41 at its other end.

The cable connection portion 41 of the thrust lever 40 is connected to the clutch lever 9 via a clutch cable 43 (see Figure 1). When the rider squeezes the clutch lever 9 with one hand, the other end of the push lever 40 is pushed by the clutch cable 43 to rotate the push lever shaft 39. The rotation of the push lever shaft 39 is converted to linear motion through the pinion gear 38 with the rack 36. Therefore, the pressure plate 33 slides in a direction away from the friction plates 25 against the pushing force of the clutch spring 27 to release the Pressure contact between the friction plates 25 and the clutch plates 26. As a result, the friction clutch 18 moves to the disengagement condition in which the torque transmission is disconnected. The push lever shaft 39, the push lever 40, the clutch cable 43, etc., constitute a transmission component for transmitting the operating force applied to the clutch lever 9 to the friction clutch 18.

Therefore, the clutch lever 9 is rotatable between a return position where the friction clutch 18 is maintained in the clutch condition and a disengagement position where the friction clutch 18 is in the disengagement condition. Since the clutch lever 9 has a free clearance, for example, 10 to 15 mm from the return position measured at the end of the clutch lever 9, the disengagement condition is maintained even when the clutch lever 9 is compressed within this range. The clutch cable 43 is pushed only slightly and the thrust force of the clutch spring 27 is not transmitted to the clutch lever 9 when the clutch lever 9 is operated within this free play range. The position where the free play of the clutch lever 9 ends is a starting position of disengagement (see Figure 15). When the clutch lever 9 is in the starting position of disengagement, the thrust force of the clutch spring 27 acts on the clutch lever 9 via the clutch cable

43

Figure 15 represents the relationship between the amount of stroke of the clutch cable 43 and the cable load while the clutch lever 9 is rotated from the return position to the disengagement position. In figure 15, the characteristic curve X represents the change of the load applied to the thrust lever 40 by the clutch spring 27.

As can be understood by the characteristic curve X, when the clutch lever 9 reaches the starting position of disengagement from the return position, a load (reaction force) is applied to the thrust lever 40 by the clutch spring 27. The load increases rapidly with the increase in the amount of stroke of the clutch cable 43, and maintains a generally constant value after the clutch lever 9 has passed through the midpoint between the starting position of disengagement and the position of disengagement In this embodiment, the point where the load applied to the thrust lever 40 is generally constant is the midpoint between the starting position of disengagement and the position of disengagement. However, the point where the load is generally constant may be a point between the starting position of disengagement and the disengagement position other than the midpoint depending on the regulation conditions of the thrust lever 40, the type of the friction clutch 18, etc. The point where the load is generally constant is not limited to the midpoint. The load applied to the thrust lever 40 is transmitted to the clutch lever 9 via the clutch cable 43. Therefore, when the mounting load of the clutch spring 27 is set to a high value to increase the torque capacity of the friction clutch 18, the clutch lever 9 will be hard to operate.

In this embodiment, an operation assist device 50 is installed at an intermediate point of the clutch cable 43 to reduce the load when operating the clutch lever 9. In other words, the clutch cable 43 has a first clutch cable 43a connected to the clutch lever 9 and a second clutch cable 43b connected to the thrust lever 40, and the first clutch cable 43a and the second clutch cable 43b are connected to each other by the operating assistance device 50.

As shown in Figure 4, each of the first clutch cable 43a and the second clutch cable 43b has an inner metal cable 44 and an outer synthetic resin tube 45 surrounding the inner cable 44. The inner cables 44 are in contact sliding with the outer tubes 45, and both ends of the inner cables 44 protrude from both ends of the outer tubes 45.

As shown in Figure 3 to Figure 7, the operating assistance device 50 has an outer box 51 and an assist mechanism 52 housed in the outer box 51. The outer box 51 is made of a metallic material such as a aluminium alloy. The outer surfaces of the outer box 51 are plated to improve the appearance of the outer box 51. The outer surfaces of the outer box 51 may be painted.

The outer box 51 has a box body 53 and a box cover 54. The box body 53 has a plate shape that opens to the left of the motor 13 and is supported in the first portion 5a of the down tube 5 by a support (not shown). The case cover 54 is fixed to the case body 53 by a plurality of bolts 55 and covers the open end of the case body 53. The outer case 51 is generally placed at the same height as the push lever 40 when the motorcycle 1 It is seen from its left side.

As shown in Figure 4 to Figure 9, the assist mechanism 52 has a first rotating element 57, a second rotating element 58 and a spring unit 59. The first rotating element 57 is formed by stamping a metal plate, for example . The first rotating element 57 has a pivot part 60, a cable connection part 61 and a lever part 62.

The pivot part 60 is located between the cable connection part 61 and the lever part 62, and is rotatably supported by a projecting part 64 of the housing body 53 by a first pivot axis 63 (see Figure 6 and the figure 9). The end of the first pivot shaft 63 in front of the projecting part 64 is supported by a support part 65 of the case cover 54.

As shown in Figure 4, the cable connection part 61 of the first rotating element 57 is located in the space of the front half (in the left half in Figure 4) in the housing body 53. The connection part of cable 61 has a lower edge 67. The lower edge 67 is curved in an arc around the first pivot axis

63. The lower edge 67 of the cable connection part 61 has a hook groove 68 (see Figure 8) and a hook hole 69. The hook groove 68 receives the inner cable 44 of the first clutch cable 43a and the inner cable 44 of the second clutch cable 43b and opens on the outer peripheral surface of the edge 67. The hitch hole 69 is an elongated groove along the circumferential direction of the lower edge 67. The hitch hole 69 opens on the outer peripheral surface of the bottom edge 67 and in the engagement groove

68. Hook elements 70 having a cylindrical column shape and fixed to ends of the inner cables 44 are hooked with the opening edge of the hitch hole 69.

Therefore, the inner cable 44 of the first clutch cable 43a and the inner cable 44 of the second clutch cable 43b are integrally connected to each other by the first rotating element 57. This connection allows the inner cable 44 of the first cable of Clutch 43a and the inner cable 44 of the second clutch cable 43b move together the same distance.

The lever part 62 is located on the rear side in the space of the rear half in the case body 53. The lever part 62 has an eccentric groove 71. As shown in Figure 4, the eccentric groove 71 is a arched and curved groove in a direction opposite to that of the bottom edge 67 of the cable connection part

61.

The second rotating element 58 has an articulation plate 72 and an articulation lever 73. The articulation plate 72 and the articulation lever 73 are each formed by stamping a metal plate, for example, and are arranged parallel to each other. with the lever part 62 of the first rotating element 57 interposed therebetween. The articulation plate 72 is rotatably supported by a projecting part 75 of the housing body 53 (see Figure 6) by a second pivot axis 74. The articulation lever 73 is rotatably supported by a support part 77 of the cover housing 54 by a third pivot axis 76. The second pivot axis 74 and the third pivot axis 76 are arranged coaxially with each other. The articulation plate 72 and the articulation lever 73 are integrally joined to each other by first and second pins 78a and 78b. The first pin 78a extends through the eccentric groove 71 of the first rotating element 57. An eccentric follower 79, such as a roller, is rotatably supported by the first pin 78a. The eccentric follower 79 is located in the eccentric groove 71 and in contact with the inner surface of the eccentric groove 71.

Therefore, the eccentric groove 71 and the eccentric follower 79 can transmit the movement of the first rotating element 57 to the second rotating element 58 and vice versa. The eccentric groove 71 and the eccentric follower 79 constitute an eccentric mechanism.

As shown in Figure 5, the spring unit 59 has a spring support 81 and an auxiliary spring 82. The spring support 81 has an inner cylinder 83 and an outer cylinder 84. The inner cylinder 83 is axially mounted sliding on the outer cylinder 84, allowing the spring support 81 to expand and contract.

The inner cylinder 83 has a spring receiver 85 and a pivot end 86. The spring receiver 85 extends as a flange from an outer peripheral surface at one end of the inner cylinder 83. The pivot end 86 is located at a end of the inner cylinder 83 and is rotatably supported in a mounting seat 87 formed at a front end within the case body 53.

The outer cylinder 84 has a spring receiver 88 and a connection end 89. The spring receiver 88 extends as a flange from an outer peripheral surface at one end of the outer cylinder 84. The connection end 89 is located at a end of the outer cylinder 84 and rotatably connected to the articulation plate 72 of the second rotating element 58 by means of a pin 90. Therefore, the spring support 81 connects a front end of the case body 53 and the articulation plate 72 and is extends in the longitudinal direction of the case body 53.

The auxiliary spring 82 is a helical compression spring and is interposed between the spring receiver 85 of the inner cylinder 83 and the spring receiver 88 of the outer cylinder 84 in a compressed state. Therefore, the spring support 81 is constantly pushed in the direction in which it expands. When the clutch lever 9 is in the disengagement start position, the pivot end 86 and the connecting end 89 of the spring support 81, and the second and third pivot axes 74 and 76 as the center of rotation of the second Rotating element 58 are placed in a straight line S1, as shown in Figure 11.

As shown in Figure 3 and Figure 7, the housing cover 54 has a pair of a first cable entry hole 95a and 95b and a second cable introduction hole 96. The first and second input holes 95a, 95b and 96 open to the outer case 51. The first cable entry hole 95a protrudes upwardly from an upper part of the front end of the box cover 54. The other first cable introduction hole 95b protrudes obliquely upwards from an intermediate part of the front end of the case cover 54. The second cable insertion hole 96 protrudes backward from a lower part of the rear end of the case cover 54.

In this embodiment, the first clutch cable 43a is inserted into the first cable insertion hole 95a. The inner cable 44 of the first clutch cable 43a extends to the outer case 51 and is connected to the first rotating element 57. The first clutch cable 43a extends upwardly along the first portion 5a of the down tube 5 from a front end of outer box 51 (see figure 1).

The first cable introduction hole 95b is used to change the direction in which the clutch cable 43a extends from the outer case 51. The first cable introduction hole 95b is preferably closed by a dust cap (not shown) for avoid the entry of dust or foreign objects into the outer box 51 when not in use.

The second clutch cable 43b is inserted into the second cable insertion hole 96. The inner cable 44 of the second clutch cable 43b extends to the outer case 51 and is connected to the first rotating element

57. The second clutch cable 43b extends backwards from a rear end of the outer case 51 along the left side of the motor 13 and linearly connects the first rotating element 57 of the assist mechanism 52 and the thrust lever 40 ( see figure 1).

Figure 4 and Figure 5 show the status of the assist mechanism 52 while the clutch lever 9 is in the return position. When the clutch lever 9 is in the return position, the second pivot axis 74 of the articulation plate 72 and the third pivot axis 76 of the articulation lever 73 are positioned below the straight line S1 connecting the end pivot 86 and connection end 89 of the spring support

81. In addition, the spring unit 59 is inclined such that the connecting end 89 of the spring support 81 is positioned higher than the pivot end 86. In addition, the eccentric groove 71 of the articulation plate 72 extends in the longitudinal direction of the case body 53 and is maintained in a position such that it is convex upwards.

When the motorist moves the clutch lever 9 from the return position to the starting position of disengagement, the first rotating element 57 is pushed up by the first clutch cable 43a and is turned in the right direction as indicated by the arrows in figure 10 and figure 11. The rotation of the rotating element 57 causes the lever portion 62 having the eccentric groove 71 to move downward. Therefore, the eccentric follower 79 in contact with the eccentric groove 71 receives a force that pushes it towards the front of the case body 53 and the articulation plate 72 and the articulation lever 73 are turned in the direction towards the left. As a result, the spring unit 59 is rotated downwardly around the pivot end 86.

When the clutch lever 9 reaches the starting position of disengagement, the second and third pivot axes 74 and 76 are placed in the straight line S1 connecting the pivot end 86 and the connecting end 89 of the spring support 81 as shown in Figure 11. Therefore, although the thrust force of the auxiliary spring 82 is being applied to the articulation plate 72 and the articulation lever 73, the articulation plate 72 and the articulation lever 73 are not they spin by pushing force.

When the clutch lever 9 moves from the starting position of disengagement to the disengaging position, the first rotating element 57 is further rotated in the right direction. The rotation of the first rotating element 57 causes the lever portion 62 having the eccentric groove 71 to move downward, and the eccentric groove 71 is placed in an upright position. Therefore, the eccentric follower 79 in contact with the eccentric groove 71 receives a force that pushes it obliquely down towards the front of the case body 53 and the articulation plate 72 and the articulation lever 73 are rotated in the direction to the left.

In this embodiment, when the clutch lever 9 is moved from the starting position of disengagement to the disengaging position, the spring unit 59 is turned downwardly around the pivot end 86 and the straight line S1 connecting the end of pivot 86 and the connecting end 89 of the spring unit 59 deviates to a position below the center of rotation of the articulation plate 72 and the articulation lever 73.

Therefore, the spring support 81 that receives the pushing force of the auxiliary spring 82 expands, and the pushing force of the auxiliary spring 82 acts as a force to rotate the articulation plate 72 and the articulation lever 73. Thus , when the clutch lever 9 is moved towards the disengagement position on the starting position of disengagement, the articulation plate 72 and the articulation lever 73 are rotated in the left direction by the auxiliary spring 82. therefore, the thrust force of the auxiliary spring 82 is added to the operating force that the rider applies to tighten the clutch lever 9. Thus, the load imposed on the rider can be reduced by operating the clutch lever 9.

According to this embodiment, the eccentric groove 71 determines the time in which the articulation plate 72 and the articulation lever 73 receive a pushing force from the spring unit 59 and begin to move in the left direction. More specifically, the eccentric groove 71 is such that it maintains the thrust force of the auxiliary spring 82 applied from the articulation plate 72 and the articulation lever 73 to the first rotating element 57 within a fixed range when the clutch lever 9 be moved from the midpoint between the starting position of disengagement and the position of disengagement towards the position of disengagement.

In other words, the eccentric groove 71 is such that it allows the movement of the articulation plate 72 and the articulation lever 73 while the clutch lever 9 moves from the starting position of disengagement to the midpoint and restricts the movement of the articulation plate 72 and the articulation lever 73 to prevent the auxiliary spring 82 from expanding freely while the clutch lever 9 moves from the midpoint to the disengagement position. Therefore, in this embodiment, the eccentric mechanism constituted by the eccentric groove 71 and the eccentric follower 79 controls the thrust force of the auxiliary spring 82 applied to the first rotating element 57.

In Figure 15, the characteristic curve designated Y represents the change in the load applied to the clutch lever 9 when the clutch lever 9 moves in a direction such that it disengages the friction clutch 18. As can be understood from of the characteristic curve Y, the load applied to the clutch lever 9 is always less than the load of the clutch spring 27 applied to the thrust lever 40 while the clutch lever 9 is moved to the disengaged position on the position of start of disengagement This is because, when the articulation plate 72 is turned in the left direction by the force transmitted through the first clutch cable 43a, the thrust force of the auxiliary spring 82 that pushes the plate forcibly is added of articulation 72 so that it turns in the direction to the left.

Furthermore, in this embodiment, since the shape of the eccentric groove 71 is determined as described above, the load applied to the clutch lever 9 can generally be kept constant while the clutch lever 9 is displaced from the midpoint between the start position of disengagement and the position of disengagement to the position of disengagement. As a result, the load applied to the thrust lever 40 and the load applied to the clutch lever 9 change with similar characteristics with respect to the amount of cable run, as shown in Figure 15.

As described above, when the clutch lever 9 is in the return position, the second pivot axis 74 of the articulation plate 72 and the third pivot axis 76 of the articulation lever 73 are positioned below the line line S1 connecting the pivot end 86 and the connecting end 89 of the spring support 81 as shown in Figure 4 and Figure 5. Therefore, the articulation plate 72 and the articulation lever 73 are pushed in the direction to the right, that is, in a direction opposite to the direction when disconnecting the friction clutch 18, by the pushing force of the auxiliary spring 82.

The force that pushes the articulation plate 72 in the right direction serves as a counter-assistance force against the force to rotate the clutch lever 9 from the return position to the start-off position. As a result, if nothing is changed, the initial input load necessary to tighten the clutch lever 9 is increased first and the operability of the clutch lever 9 is adversely affected.

Therefore, in the operation assistance device 50 of this embodiment a cancellation spring unit 100 is incorporated into the case body 53 of the outer case 51. As shown in Figure 4 and Figure 14, the body of box 53 has a housing part 101 to accommodate the cancellation spring unit 100. The housing part 101 is placed in a lower part of the rear end of the box body 53 and is located on one side of the second cable insertion hole 96.

As shown in Figure 14, the housing part 101 has a cylinder 102 that extends vertically. At the upper end of the cylinder 102 a hole 102a has been formed which opens to the outer case 51. The hole 102a is in front of a locking pin 103 fixed to the articulation plate 72. The locking pin 103 is located in a position opposite the connecting end 89 where the articulation plate 72 is connected to the spring unit 59 with respect to the second pivot axis 74.

As shown in Figure 14, the cancellation spring unit 100 has a pressure pin 104 and a cancellation spring 105. The pressure pin 104 has a hollow shape with a closed upper end, and a flange-shaped stop. 106 is formed at the lower end of the pressure pin 104. The pressure pin 104 is slidably inserted into the cylinder 102 below the housing part 101.

A spring receiver 108 is fixed to the lower end of the housing part 101 by a circular clip

107. Spring receiver 108 is located under cylinder 102.

The cancellation spring 105 is a helical compression spring and is interposed between the upper inner surface of the pressure pin 104 and the spring receiver 108 in a compressed state. Cancellation spring 105 constantly pushes pressure pin 104 up. The pushing force of the cancellation spring 105 is set slightly below that of the counter-assistance force produced by the auxiliary spring 82.

The pressure pin 104 can be moved elastically between a first position where its upper end protrudes largely from the hole 102a of the cylinder 102, and a second position where its upper end slightly protrudes from the hole 102a of the cylinder 102. When the pressure pin 104 is in the first position, the stop 106 of the pressure pin 104 rests against the lower end of the cylinder 102 to restrict the position of the pressure pin 104. When the pressure pin 104 is in the second position, the stop 106 of the pin Pressure 104 rests against spring receiver 108 to restrict the position of the pressure pin

104. While the clutch lever 9 is moved from the return position to the start-off position, the upper end of the pressure pin 104 rests against the locking pin 103 of the articulation plate 72 below, as shown in Fig. 5 and Fig. 11. Therefore, the articulation plate 72 receives the pushing force of the cancellation spring 105 by the locking pin 103. As a result, all the pushing force of the auxiliary spring 82 and the force The thrust of the cancellation spring 105 applied to the articulation plate 72 is almost zero and the articulation plate 72 is prevented from turning in the right direction when the clutch lever 9 is in the free play range.

When the clutch lever 9 approaches the disengagement position on the initial disengagement position, the locking pin 103 of the articulation plate 72 is separated from the upper end of the pressure pin 104 as shown in Figure 13. As a result, the pressure pin 104 is held in the first position by the pushing force of the cancellation spring 105, and the articulation plate 72 and the articulation lever 73 are rotated in the left direction by the force of auxiliary spring thrust 82.

As shown in Fig. 3, Fig. 6 and Fig. 7, the box cover 54 of the outer box 51 has a circular hole 110. The hole 110 is in front of the cable connection portion 61 of the first rotating element 57 , and the engagement groove 68 and the engaging hole 69 of the cable connection portion 61 are exposed to the outside of the outer case 51 through the hole 110. In other words, the fingers or a tool can be inserted through of the hole 110 for engaging the inner cables 44 to the engagement groove 68 of the cable connection part 61 or for engaging the engagement elements 70 at the ends of the interior cables 44 to the engagement hole 69. Therefore, the Inner cables 44 can be connected to the first rotating element 57 with the case cover 54 fixed to the case body 53.

The box cover 54 has a support wall 111 extending from the opening edge of the hole 110 to the center of the hole 110. The support wall 111 is located in a position that does not interfere with the cable connection part 61 of the first rotating element 57 and has a protruding part 113 with a screw hole 112 at its end. The position of the threaded hole 112 coincides with the center of the hole 110.

The hole 110 is covered with a disk-shaped lid 114 (see Figure 1). The cover 114 is removably mounted in the hole 110 and fixed to the support wall 111 with a bolt 115 (see Figure 6). The bolt 115 extends through the center of the cover 114 and is screwed into the threaded hole 112 of the projecting portion 113.

As shown in Figure 3 and Figure 9, the cable connection portion 61 of the first rotating element 57 has an insertion hexagonal hole 118. The introduction hole 118 is located in the area of the hole 110, and is in a position corresponding to a positioning recess 119 of the case body 53 when the clutch lever 9 is in the correct starting position. Therefore, by inserting a tool, such as a hexagonal wrench, into the insertion hole 118 through the hole 110 and by hooking the tool tip into the recess 119, the first rotating element 57 can be held in the position represented in Figure 10

Thus, the position of the first rotating element 57 can be determined while the clutch lever 9 is in the correct starting position, and in this state the free play of the clutch cable 43 can be adjusted.

According to this embodiment, the assist mechanism 52 installed at an intermediate point of the clutch cable 43 maintains the pushing force of the auxiliary spring 82 applied to the clutch cable 43 by the first rotating element 57 within a fixed range while the clutch lever 9 is moved from the midpoint between the starting position of disengagement and the position of disengagement to the position of disengagement. In other words, the assist mechanism 52 cancels the increase in the thrust force of the auxiliary spring 82 applied to the clutch cable 43 when the clutch lever 9 approaches the disengagement position.

Therefore, the load applied from the clutch spring 27 to the thrust lever 40 of the clutch release mechanism 28 and the actual load applied to the clutch lever 9 through the assist mechanism 52 changes with similar characteristics with respect to to the amount of cable run.

As a result, the clutch lever 9 can suddenly be loosened when it approaches the disengagement position when the friction clutch 18 is disconnected even if the thrust force of the auxiliary spring 82 is applied to the clutch cable 43. Thus, the force necessary to operate the clutch lever 9 can be reduced, and the clutch lever 9 can be operated with the same operating sensation as when operating a conventional clutch lever. Therefore, the operation of the clutch lever 9 does not cause any discomfort. Furthermore, according to this embodiment, the first clutch cable 43a and the second clutch cable 43b are moved at the same time as they maintain the one-to-one relationship. Therefore, the assist mechanism 52 can be installed in the path through which the movement of the clutch lever 9 is transmitted to the thrust lever 40 without changing the constitution of the friction clutch 18.

In addition, the assist mechanism 52 of this embodiment has the cancellation spring unit 100, which rests against the locking pin 103 of the articulation plate 72 below when the clutch lever 9 is in the return position. The cancellation spring 105 of the cancellation spring unit 100 acts to cancel the counter-assistance force produced by the auxiliary spring 82 and prevents rotation of the articulation plate 72 in a direction such that it engages the friction clutch 18 in base to the force of counter-assistance.

Therefore, the initial input load necessary to tighten the clutch lever 9 is not increased first, and it has the advantage that the operability of the clutch lever 9 can be improved.

(Second embodiment)

In the second embodiment, the operation assistance device 50 according to the first embodiment has been modified as shown in Figure 16 to Figure 25. The operation assistance device 50 of the first embodiment is reduced in size. In the following description, the parts corresponding to the components of the first embodiments are identified with the same reference numbers.

As shown in Figure 16 to Figure 18, the operating assistance device 50 has an outer case 51 and an assist mechanism 52 also in the second embodiment. The outer box 51 has a box body 53 and a box cover 54. In the second embodiment, the areas of the box body 53 and the box cover 54 as seen from one side are smaller than those of the first embodiment.

As shown in Fig. 16 and Fig. 18, each of the case body 53 and the case cover 54 has first, second and third fastener portions 151, 152 and 153 each having a bolt hole. The case body 53 and the case cover 54 are fixed to each other in the clamping portions 151, 152 and 153 with bolts 115.

As shown in Figure 18, the assist mechanism 52 has a first rotating element 57, a second rotating element 58, a spring unit 59, and a cancellation spring unit 100.

The first rotating element 57 has a pivot part 60 and a cable connection part 61. As shown in Figure 4, the first rotating element 57 of the first embodiment has a lever part 62 which has the eccentric groove 71 in addition of the cable connection part 61. On the contrary, the rotating element 57 of the second embodiment does not have the lever part 62, and the cable connection part 61 has an eccentric groove 71 as shown in Figure 18. In this embodiment, since the lever part 62 is omitted, the area of the first rotating element 57 is small. The first rotating element 57 is generally in the form of a sector with a central angle of less than 120 ° as seen along the axial direction of the first pivot axis 63.

As shown in Figure 24, the pivot part 60 is rotatably supported by a projecting part 64 of the case body 53 by the first pivot axis 63. The end of the first pivot axis 63 in front of the projection part 64 is supported. by a support part 65 of the case cover 54.

As shown in Figure 18 and Figure 25, the cable connection part 61 has a first engagement groove 68a and a first engagement hole 69a at one end of its lower edge. The cable connection portion 61 has a second engagement slot 68b and a second engagement hole 69b at the other end of its lower edge.

The inner cable 44 of the first clutch cable 43a is received in the first engagement groove 68a. The first engagement groove 68a opens on the outer peripheral surface of the lower edge. The first hook hole 69a is circular in shape. The first hitch hole 69a opens in the outer peripheral surface of the lower edge and in the first hitch groove 68a. A coupling element 70a with a cylindrical column shape is mounted at one end of the inner cable 44 of the first clutch cable 43a. The hooking element 70a engages with the opening edge of the first hook hole 69a. The inner cable 44 of the first clutch cable 43a is thereby engaged with the cable connection part 61.

The inner cable 44 of the second clutch cable 43b is received in the second latch groove 68b. The second latch groove 68b opens on the outer peripheral surface of the lower edge. The second hitch hole 69b is also circular in shape. The second hitch hole 69b opens in the outer peripheral surface of the lower edge and in the second hitch groove 68b. A coupling element 70b with a cylindrical column shape fixed to one end of the inner cable 44 of the second clutch cable 43b is engaged with the opening edge of the second coupling hole 69b. The inner cable 44 of the second clutch cable 43b is thereby engaged with the cable connection part 61.

The first hitch slot 68a and the second hitch slot 68b are curved in an arc around the first pivot shaft 63. The inner cable 44 of the first clutch cable 43a and the inner cable 44 of the second clutch cable 43b are integrally connected. to each other by the first rotating element 57. Therefore, the inner cable 44 of the first clutch cable 43a and the inner cable 44 of the second clutch cable 43b can be moved together at the same travel rate. Since the distance from the first pivot axis 63 to the coupling element 70a and the distance from the first pivot axis 63 to the coupling element 70b are the same, the inner cables 44 can move the same distance.

The eccentric groove 71 is located between the first engagement hole 69a and the second engagement hole 69b. The eccentric groove 71 is a curved groove that is concave toward the first engagement hole 69a.

The second rotating element 58 of the first embodiment has an articulation plate 72 and an articulation lever 73 (see Figure 4). On the contrary, the second rotating element 58 of this embodiment consists only of an articulation plate 72 as shown in Figure 19. The articulation plate 72 is located on the reverse side of the first rotary element 57. The articulation plate 72 is rotatably supported by a projecting portion 75 (see Figure 24) of the case body 53 by a second pivot shaft

74.

A first pin 78a, which extends to the front side of the first rotating element 57, is attached to the articulation plate 72. An eccentric follower 79, such as a roller, is rotatably supported by the first pin 78a. The eccentric follower 79 is located in the eccentric groove 71 and in contact with the inner surface of the eccentric groove 71.

Therefore, the eccentric groove 71 and the eccentric follower 79 can transmit a force from the first rotating element 57 to the second rotating element 58 or from the second rotating element 58 to the first rotating element 57 when the first rotating element 57 or the second rotating element 58 rotate. The eccentric groove 71 and the eccentric follower 79 constitute an eccentric mechanism.

The constitution of the spring unit 59 is the same as that of the first embodiment. However, the spring unit 59 is mounted in a different position and in a different position in this embodiment. As shown in Figure 21, the mounting seat 87 for supporting the pivot end 86 of the spring unit 59 is disposed at a rear end (at a right end in Figure 21) in the case body 53 in this realization. The spring unit 59 extends forward or obliquely forward from a rear end in the case body 53 (see Figure 23).

As shown in Figure 19, the connecting end 89 of the spring unit 59 is rotatably connected to the articulation plate 72 of the second rotating element 58 by means of a pin 90. When the clutch lever 9 is in the starting position of disengagement (in the state shown in Figure 19), the pivot end 86 and the connecting end 89 of the spring support 81 and the second pivot axis 74 as the center of rotation of the second rotating element 58 are placed in a straight line S1.

Figure 20 and Figure 21 represent the state of the assist mechanism 52 while the clutch lever 9 is in the return position. When the clutch lever 9 is in the return position, the second pivot axis 74 of the articulation plate 72 is positioned above the straight line S1 connecting the pivot end 86 and the connecting end 89 of the spring support 81 as shown in Figure 21. The eccentric follower 79 is placed at the left end of the eccentric groove 71.

When the rider moves the clutch lever 9 from the return position to the starting position of disengagement, the first rotating element 57 is pushed up by the first clutch cable 43a and is rotated in the right direction around the first pivot shaft 63. The rotation of the first rotating element 57 causes the eccentric groove 71 also to rotate in the direction to the right around the pivot axis 63 and move upwards. Therefore, the eccentric follower 79 in contact with the eccentric groove 71 receives a force that pushes it up, and the articulation plate 72 is rotated in the opposite direction to the right around the second pivot axis 74. As a result , the spring unit 59 is rotated in the right direction around the pivot end 86.

When the clutch lever 9 reaches the starting position of disengagement, the second pivot shaft 74 is placed in the straight line S1 connecting the pivot end 86 and the connecting end 89 of the spring support 81 as shown in Figure 19. Therefore, the pushing force of the auxiliary spring 82 does not act to rotate the articulation plate 72.

When the clutch lever 9 is moved from the starting position of disengagement to the disengaging position, the first rotating element 57 is further rotated in the right direction. The rotation of the first rotating element 57 causes the eccentric groove 71 to rotate more around the pivot axis 63 and move upwards. Then, the eccentric groove 71 is placed in a horizontal position as a whole. As a result, the eccentric follower 79 in contact with the eccentric groove 71 receives a force that pushes it towards the top or the front of the case body 53, and the articulation plate 72 is further rotated in the left direction.

When the clutch lever 9 is moved from the starting position of disengagement to the disengaging position, the spring unit 59 is further rotated in the right direction around the pivot end

86. Then, the straight line S1 connecting the pivot end 86 and the connecting end 89 of the spring unit 59 is deflected upward from the center of rotation of the articulation plate 72 (pivot axis 74).

Therefore, the spring support 81 that receives the pushing force of the auxiliary spring 82 expands, and the pushing force of the auxiliary spring 82 is transmitted to the articulation plate 72 and acts as a force to rotate the articulation plate 72 in the left direction. Thus, when the clutch lever 9 is moved towards the disengagement position on the starting position of disengagement, the articulation plate 72 is rotated in the direction to the left by the auxiliary spring 82. Therefore, the force of Auxiliary spring 82 thrust is added to the operating force that the rider applies to squeeze the clutch lever 9, and the load imposed on the rider can be reduced by operating the clutch lever 9.

Also in this embodiment, the eccentric groove 71 determines the time in which the articulation plate 72 receives a pushing force from the spring unit 59 and begins to move in the left direction. The eccentric groove 71 is such that the angular velocity ratio changes, which is the ratio of the angular velocity of the second rotating element 58 to the angular velocity of the first rotating element 57, while the clutch lever 9 is moved from the position from start of disengagement to the position of disengagement. The eccentric groove 71 is such that the thrust force of the auxiliary spring 82 transmitted to the first rotating element 57 by the articulation plate 72 (more specifically, the moment the first rotating element 57 rotates in the right direction) can increase more rapidly than in a conventional device in the initial stage of the process where the clutch lever 9 is moved from the starting position of disengagement to the midpoint.

Figure 34 represents in contrast the variation characteristics of the pushing force Z of the auxiliary spring 82 and the variation characteristics of the pushing force Z0 in a conventional device. The gradient in the ascending section of the characteristic curve of the pushing force Z in this assist mechanism 52 is larger than that of a conventional device.

Here, the conventional device is a device in which a rotating element connected to a clutch release mechanism is connected directly to an auxiliary spring and in which the rotating element and auxiliary spring rotate at the same speed and the auxiliary spring is It can expand freely when the rotating element rotates (for example, the device described in JP-A-Hei 7-132872).

In this assistance mechanism 52, the ratio of the angular speed of the second rotating element 58 to the angular speed of the first rotating element 57 is larger when the clutch lever 9 is in the starting position of disengagement than when the clutch lever 9 is in the release position. In addition, the average angular velocity ratio while the clutch lever 9 is shifted from the starting position of disengagement to the midpoint is larger than the average angular velocity ratio at the time the clutch lever 9 is moved from the midpoint to the disengagement position. The angular velocity ratio may be gradually lower while the clutch lever 9 is moved from the start disconnection position to the disengagement position. By properly regulating the angular velocity ratio, the variation characteristics of the thrust force Z of the auxiliary spring 82 transmitted to the first rotational element 57, that is, the variation characteristics of the assistive force that the clutch lever 9 receives, is They can put arbitrarily.

As described above, by properly establishing the shape of the eccentric groove 71, the variation characteristics of the assistance force can be freely regulated. As shown in Fig. 34, the load X applied to the thrust lever 40 of the friction clutch 18 varies greatly immediately after the clutch lever 9 has passed through the starting position of disengagement, and the degree of Change is minor after that. With this assistance mechanism 52, the gradient of the ascending section of the characteristic curve of the thrust force Z can be large so that the load Y applied to the clutch lever 9 can be changed with characteristics almost identical to those of the load X applied to the thrust lever 40 of the friction clutch 18 while the clutch lever 9 is moved from the start position of disconnection to the midpoint. That is, the relationship between the load Y applied to the clutch lever 9 and the load X applied to the thrust lever 40 may be within a fixed range. Therefore, it is possible to reduce the load necessary to operate the clutch lever 9 and provide the same operating sensation as a conventional clutch lever in half-clutch operation.

As described in the description of the first embodiment, the assistance force applied to the first rotating element 57 is maintained within a fixed range when the clutch lever 9 is moved from the midpoint to the disengaged position. That is, the eccentric groove 71 is such that it maintains the thrust force of the auxiliary spring 82 applied to the first rotating element 57 by the articulation plate 72 within a fixed range when the clutch lever 9 is moved from the midpoint. towards the release position.

In this embodiment, the housing part 101 housing the cancellation spring unit 100 is disposed at a front upper end of the case body 53 of the outer case 51 as shown in Figure 19. The housing part 101 is aligned with the first cable entry hole 95a in the transverse direction (in a direction perpendicular to the plane of Figure 19). The internal structure of the cancellation spring unit 100 is the same as that of the cancellation spring unit 100 of the first embodiment.

As shown in Figure 23, the hole 102a of the cylinder 102 of the cancellation spring unit 100 opens downward. The pressure pin 104 is elastically mobile between a first position where its lower end protrudes largely from the hole 102a of the cylinder 102, and a second position where its lower end slightly protrudes from the hole 102a of the cylinder 102. When the pressure pin 104 is in the first position, the stop 106 of the pressure pin 104 rests against the upper end of the cylinder 102 to restrict the position of the pressure pin 104. When the pressure pin 104 is in the second position, the stop 106 of the pin Pressure 104 rests against the spring receiver (not shown) to restrict the position of the pressure pin 104.

While the clutch lever 9 is moved from the return position (see Figure 21) to the starting position of disengagement (see Figure 19), the pressure pin 104 rests against the locking pin 103 of the articulation plate 72 above. Thus, the articulation plate 72 receives the pushing force of the cancellation spring 105 (not shown in Figure 21, etc., see Figure 14) by the locking pin 103. As a result, when the clutch lever 9 is in the free play range, the pushing force of the auxiliary spring 82 applied to the articulation plate 72 is canceled by the pushing force of the cancellation spring

105. Therefore, the force applied to the articulation plate 72 is substantially zero and the rotation of the articulation plate 72 in the right direction produced by the auxiliary spring 82 (and thus the return of the clutch lever 9).

When the clutch lever 9 approaches the disengagement position on the starting disengagement position, the locking pin 103 of the articulation plate 72 is separated from the lower end of the pressure pin 104 as shown in Figure 23. As a result, the pressure pin 104 is held in the first position by the pushing force of the cancellation spring 105, and the articulation plate 72 receives a force that pushes it to rotate in the left direction of the auxiliary spring 82 .

As shown in Fig. 17, the box cover 54 of the outer box 51 has a circular hole 110. The hole 110 is in front of the cable connection part 61 of the first rotating element 57, and the engagement slots 68a and 68b and the hook holes 69a and 69b of the cable connection part 61 are exposed to the outside of the outer case 51 through the hole 110. In other words, the fingers or a tool can be inserted through the hole 110 to hook the inner cables 44 to the hook grooves 68a and 68b of the cable connection part 61 or to hook the hook elements 70a and 70b at the ends of the inner cables 44 to the hook holes 69a and 69b. Therefore, the inner cables 44 can be connected to the first rotating element 57 with the case cover 54 fixed to the case body 53.

The box cover 54 has first and second support walls 111a and 111b extending from the edge of the hole 110 towards the center of the hole 110. The first support wall 111a and the second support wall 111 b are located in opposite positions with respect to the center of the hole 110. Each of the first and second support walls 111a and 111b has a projecting portion 113 with a screw hole 112 at its end.

As shown in Fig. 16, the hole 110 is covered with a disk-shaped cover 114. The cover 114 is removably mounted in the hole 110 and fixed to the support walls 111a and 111b with bolts 115. The bolts 115 are threaded into the threaded holes 112 of the projecting portions 113 of the support walls 111a and 111b.

As shown in Fig. 17, the cable connection portion 61 of the first rotating element 57 has a hexagonal insertion hole 118. The insertion hole 118 is located in the area of the hole 110. Therefore, when a tool, such as a hexagonal wrench, through hole 110 to the insertion hole 118, the position of the first rotating element 57 can be adjusted. The cable connection part 61 of the first rotating element 57 has a positioning recess 119a. The second support wall 111b of the box cover 54 has a positioning projection 119b. The protrusion 119b and the recess 119a align with each other when the clutch lever 9 is in the correct starting position. Therefore, by regulating the amount of free play of the clutch lever 9 so that the projection 119a and the recess 119b can be aligned with each other, the starting position of disengagement can be easily set.

The method of mounting the operating assistance device 50 to the frame 2 of the motorcycle 1 and an example of its mounting structure are described below. The operation assistance device 50 described below is the same as the operation assistance device 50 described above except that the position of the third clamping part 153 is changed from on an upper part of the box body 53 to on a lower part of the case body 53 (see Figure 26). The rest of the constitution is the same as described above.

As shown in FIG. 32, the operating assistance device 50 is mounted on the down tube 5 of the frame 2 by a first support 161, a second support 162, a third support 163 and a mounting plate 164.

As shown in Figure 27, the first support 161 is fixed to the down tube 5. The method of fixing the first support 161 is not specifically limited. Here, the first support 161 is attached to the descending tube 5 by welding. The first support 161 is originally connected, as in the case with the second support 162, to the down tube 5 to support a part of the engine 13. That is, the operating assistance device 50 is mounted using the existing supports 161 and 162. The first support 161 extends along the longitudinal direction of the descending tube 5. The first support 161 has bolt holes 171 at its longitudinal ends.

As shown in Figure 28, the second support 162 is placed on the front side of the first support 161. The second support 162 is a curved sheet element with a generally triangular shape as seen from one side. The second support 162 has a front half 162a extending in an inclined direction from the longitudinal direction of the vehicle along the first support 161 and a rear half 162b located behind the front half 162a and curved inward (see Figure 32 ). The front half 162a of the second support 162 has bolt holes 172 in positions corresponding to the bolt holes 171 of the first support 161. The rear half of the second support 162 also has a bolt hole 173. As shown in Figure 32, A bolt 174 for fixing a part of the motor 13 is mounted in the bolt hole 173. The part of the motor 13 is supported by the descending tube 5 by the first support 161 and the second support 162.

As shown in Fig. 29, the third support 163 is placed on the front side of the second support 162. The third support 163 is a curved sheet in three sections from front to back, and has a front part 163a that extends along of the front half 162a of the second support 162, an intermediate part 162b extending outwardly from the front part 163a, and a rear part 163c extending into the intermediate part 162b (see Figure 32). The front part 163a has bolt holes 175 in positions corresponding to the bolt holes 172 of the front half 162a of the second support 162. The rear part 163c also has bolt holes 176 at its upper and lower end.

As shown in Fig. 32, bolts 177 are introduced through bolt holes 171 of first support 161, bolt holes 172 of second support 162 and bolt holes 175 of third support 163. Second support 162 and the third support 163 are fixed together with the first support 161.

As shown in Figure 30, the mounting plate 164 is placed on the front side of the rear portion 163c of the third support 163. The mounting plate 164 is in the form of a flat plate (see Figure 32). The mounting plate 164 has grooves 178 that extend in the longitudinal direction at its upper and lower rear ends. The mounting plate 164 has a hole 179 that is shaped like a running track in its center. The mounting plate 164 also has three bolt holes 181 through which bolts (not shown) are introduced to join the housing body 53 of the operating assistance device 50.

Bolts 180 (see Fig. 32) are inserted through the bolt holes 176 of the third support 163 and the slots 178 of the mounting plate 164. The bolts 180 can be fixed in arbitrary positions in the slots 178. By therefore, by sliding the mounting plate 164 from one side to the other with the bolts 180 inserted through the slots 178, the longitudinal position of the mounting plate 164 with respect to the third support 163 can be easily finely regulated.

As shown in Figure 26, three bolt holes 182 corresponding to bolt holes 181 of the mounting plate 164 are formed on the reverse side of the housing body 53 of the operating assistance device 50. The housing body 53 it is thus positioned so that the bolt holes 182 overlap the bolt holes 181 of the mounting plate 164 and are placed on the front side of the mounting plate 164 (see Figure 32). Then, bolts (not shown) are screwed into the bolt holes 181 of the mounting plate 164 and the bolt holes 182 of the housing body 53 to secure the housing body 53 to the mounting plate 164. As described above. Previously, since the longitudinal position of the mounting plate 164 can be adjusted easily with ease, the longitudinal position of the housing body 53 fixed to the mounting plate 164 can be adjusted easily with ease. Therefore, the position of the box body 53 can be adjusted so that the box body 53 can be placed in a desired position if necessary after mounting the box body 53 on the mounting plate 164.

After the mounting plate 164 has been mounted in the case body 53, the case cover 54 is placed in the case body 53 and bolts are screwed into the bolt holes of the first, second and third fastening parts 151, 152 and 153 to secure the case cover 54 to the case body 53. Then, the first clutch cable 43a and the second clutch cable 43b are mounted on the first rotating element 57 through the hole 110 of the cover box 54.

As shown in Figure 33, a hitching element 200 with a cylindrical column shape (not shown in Figure 31, etc.) is fixed to one end of the outer tube 45 of the second clutch cable 43b. The coupling element 200 can be attached to the outer tube 45 or snapped onto the outer tube 45. A block 204 with a screw hole is fixed in a cable insertion hole of the case cover 54. A screw 201 which extending in the longitudinal direction (lateral direction of figure 33) is screwed into the threaded hole of block 204.

The screw 201 has a threaded part 201a and a large diameter part 201b formed on the rear side of the threaded part 201a. The coupling element 200 is rotatably inserted in the large diameter part 201b. The large diameter part 201b has a passage at its distal end so that the rear end of the coupling element 200 can be caught in the passage and is prevented from leaving the large diameter part 201b. Therefore, when the screw 201 is moved from one side to the other by turning it, the outer tube 45 moves from one side to the other together with the screw 201.

The screw 201 and the hitch element 200 have through holes through which the inner tube 44 can extend. The inner tube 44 of the second clutch cable 43b extends through the through holes of the hitch element 200 and the screw 201 and connects to the first rotating element 57. A plug 203 is mounted on the outer periphery of the large diameter part 201b of the screw 201. The reference number 202 designates a nut to fix the position of the screw 201.

The screw 201 is used to regulate the installation positions of the second clutch cable 43b and the operating assistance device 50. That is, after the outer tube 45 of the second clutch cable 43b has been mounted in a predetermined position in the friction clutch side 18, the bolts 180 are inserted into the bolt holes 176 of the third support 163 and the grooves 178 of the mounting plate 164 and are fixed to the extent that the operating assistance device 50 can slide from side to side as described above. Then, the length of the outer tube 45 of the second clutch cable 43b is regulated so that the positioning recess 119a of the first rotating element 57 and the projection 119b of the case cover 54 align with each other by turning the screw 201. When the recess 119a and the projection 119b are aligned with each other, the nut 202 is tightened to fix the position of the screw 201. The outer tube 45 of the second clutch cable 43b can therefore be set to an appropriate length. After that, the bolts 180 are tightened to securely fix the mounting plate 164. Then, the cover 114 is placed over the hole 110 of the case cover 54 and fixed to the support walls 111a and 111b of the cover box 54 with bolts 115.

As previously described, an eccentric mechanism having the eccentric groove 71 and the eccentric follower 79 is interposed between the first rotating element 57 and the second rotating element 58 also in this embodiment. Therefore, by properly determining the curve of the eccentric groove 71, the relationship between the oscillation of the spring unit 59 and the rotation of the first rotating element 57 can be freely set and the desired operability can be achieved.

When the clutch lever 9 moves from the starting position of disengagement to the midpoint, the increasing rate of the thrust force of the auxiliary spring 82 applied to the first rotating element 57 can be high in the initial stage immediately after the position of start of disengagement and then lower. Therefore, since the assistance force can be significantly large at the initial stage of the half-clutch operation, operability can be improved.

In addition, when the clutch lever 9 moves from the starting position of disengagement to the midpoint, the ratio between the clutch spring load 27 applied to the thrust lever 40 of the clutch release mechanism 28 and the actual load applied The clutch lever 9 can be kept within a fixed range. Therefore, the load applied to the clutch lever 9 when the clutch lever 9 is operated, is less than the load applied to the thrust lever 40 and varies with a trend similar to that of the clutch spring load 27 Therefore, the load can be reduced by operating the clutch lever 9, and a natural and comfortable operating sensation can be obtained.

The spring unit 59 having the auxiliary spring 82 can oscillate around the pivot end 86. Thus, since the direction in which the pushing force of the spring 82 acts can be freely changed, the pushing force can always be applied. in the appropriate direction. Therefore, even if an eccentric mechanism is interposed between the spring unit 59 and the first rotating element 57, the loss of the pushing force of the auxiliary spring 82 applied to the first rotating element 57 can be reduced. Furthermore, the wear of the assist mechanism 52 can be reduced, and the service life and reliability of the operation assist device 50 can be improved.

The present invention is not limited to the embodiments described above, and various modifications can be made in the present invention without departing from its scope.

For example, the operative element for operating the friction clutch is not limited to a clutch lever to be operated with one hand and may be a clutch pedal to be operated with one foot.

In the embodiments described above, the clutch cable 43 consists of two cables: the first and second clutch cables 43a and 43b. However, the clutch cable 43 may be constituted by a cable provided that it can be connected to a mobile element (rotating element 57). The first clutch cable 43a and the second clutch cable 43b (more specifically, its inner cables 44) may be formed by a cable. That is, a side portion and another side portion of a cable (linear element) connected to the first rotating element 57 can be considered as the first clutch cable 43a and the second clutch cable 43b, respectively. In this case, although the joint between the first clutch cable 43a and the first rotating element 57 and the joint between the second clutch cable 43b and the first rotating element 57 may be located in different positions, the linear element may be connected to the First rotating element 57 at a point so that the first and second clutch cables 43a and 43b are connected to the rotating element 57 in a common joint.

The auxiliary elastic element for applying a pushing force to the first rotating element 57 is not limited to the spring unit 59 which has the auxiliary spring 82. The auxiliary spring 82 is not limited to a compression spring that can apply a pushing force in the direction in which it expands and can be a tension spring that can apply a pushing force in the direction in which it contracts. The elastic cancellation element for applying a cancellation force to cancel the thrust force of the auxiliary spring 82 when the clutch lever 9 is between the return position and the start disengagement position is not limited to the cancellation spring unit 100 having the cancellation spring 105. A different type of elastic element, such as a pneumatic spring, can be used for the auxiliary elastic element or the elastic cancellation element.

In the embodiments described above, the moving element that moves in synchronism with the clutch lever 9 is the rotating element 57 that can rotate about a specific axis of rotation (pivot axis 63). Therefore, the operation assistance device 50 can be of simplified structure and have high strength. However, the moving element that moves in synchronism with the clutch lever 9 is not limited to said rotating element. For example, the movable element may be a sliding element that can be alternated along one direction (linearly or in a curve) or the like. When the mobile element is an element that can be alternated along one direction, the forward speed of the mobile element can be specified, for example, as a speed in the direction. Therefore, the speed ratio, which is the ratio of the rotational speed of the rotating element to the moving speed of the moving element, can be specified, for example, as the ratio between the speed of the moving element in the previous direction and the angular speed of the rotating element.

In addition, the friction clutch is not limited to a wet multi-plate clutch and may be a dry single-plate clutch. In addition, the clutch release mechanism is not limited to rack and pinion type. The present invention can be implemented when the clutch release mechanism is of the ball screw type or of the eccentric type.

In the embodiments described above, the operating assistance device 50 is supported by the descending tube 5 of the frame 2. However, the installation position of the operating assistance device 50 is not specifically limited. For example, the operating assistance device 50 may be located under the fuel tank 10 or the seat 11 with the first clutch cable 43a extending in the longitudinal direction as shown in Figure 35.

Although not shown, the operating assistance device 50 may be located near the friction clutch 18. When the outer case 51 of the operating assistance device 50 is mounted on the clutch cover 20, the second clutch cable 43b is can skip.

As shown in Figure 36 and Figure 37, the second clutch cable 43b can be omitted and an axis that extends coaxially from the thrust lever axis 39 can be used as a pivot axis 63 as the rotary axis for the first rotating element 57. This configuration can create an effect almost the same as those of the embodiments described above.

The above description describes (among others) an embodiment of a clutch operation assistance device incorporated in a clutch operating device having a friction clutch with a clutch spring, and an operating element connected to the friction clutch by means of a component of transmission and being manually operable against the thrust force of the clutch spring to disconnect the torque transmission by the friction clutch, including the clutch operation assistance device: an auxiliary elastic element which, when the operating element is operated in such a direction that disengages the friction clutch, pushes the transmission component in a direction such that it disengages the friction clutch while the operating element moves from a starting position of disengagement where the operating element receives the reaction force from the spring of clutch to a disengagement position don the friction clutch release is completed, where the thrust force of the auxiliary spring applied to the transmission component is maintained within a fixed range while the operating element moves from an intermediate position between the start position of disengagement and the position from disengagement to the disengaged position.

According to this clutch operation assistance device, when the operating element is operated in a direction such that it disengages the friction clutch, the pushing force of the auxiliary elastic element is applied to the operating element. Therefore, the operating element can be easily operated with a small force.

In addition, the pushing force of the auxiliary elastic element applied to the transmission component does not increase in a fixed range even when the operating element approaches the disengagement position, and it is possible to prevent the operating element from suddenly loosening in one position. near the disengagement position. Therefore, the operation of the operative element does not produce any sensation of discomfort and a better operability can be achieved.

According to the description, it is preferred that the auxiliary elastic element pushes the transmission component in a direction such that it engages the friction clutch when the operating element is in a return position on the return side of the start-off start position, and The direction of the thrust force applied to the transmission component is changed from a direction such that it engages the friction clutch in a direction such that it disengages the friction clutch when the operating element moves from the return position to the disengagement position. on the starting position of disengagement, and where an elastic cancellation element is provided, which applies a pushing force to cancel the pushing force of the auxiliary elastic element applied to the transmission component when the operating element is in the return position.

It is also preferred that the friction clutch has a clutch release mechanism, and where the transmission component has a first clutch cable connected to the operating element and a second clutch cable connected to the clutch release mechanism and is interposed between the first clutch cable and the second clutch cable.

It is also preferred that the displacement of the first clutch cable and the displacement of the second clutch cable while the operating element is operated are equal to each other.

The description also describes an embodiment of a clutch operation assist device for a clutch operating device that has a friction clutch with a clutch spring and an operating element that is connected to the friction clutch by a transmission component and manually operable against the pushing force of the clutch spring to disconnect the torque transmission by the friction clutch, the clutch operating assistance device being interposed between the operating element and the friction clutch to reduce the force necessary to operate the element operating to disengage the friction clutch and including: a movable element that can be moved in synchronism with the transmission component, an auxiliary elastic element that, when the operating element is operated in a direction such that it disengages the friction clutch, applies a pushing force to move the element or mobile in a direction such that it disengages the friction clutch while the operating element moves from a starting position of disengagement where the operating element receives the reaction force of the clutch spring to a disengagement position where clutch disengagement is completed of friction; a rotating element for transmitting the pushing force of the auxiliary elastic element to the mobile element; and an eccentric mechanism that is interposed between the mobile element and the rotating element and that maintains the thrust force applied from the rotating element to the mobile element within a fixed range while the operating element moves from an intermediate position between the position of start of disengagement and the position of disengagement to the position of disengagement.

The description describes that it is preferable that the eccentric mechanism has an eccentric groove formed through one of the movable element and the rotating element, and an eccentric follower in contact with the eccentric groove and supported by the other of the movable element and the element rotary.

It is preferred that the transmission component has a first clutch cable connected to the operating element and a second clutch cable connected to a friction clutch release mechanism, and where the first and second clutch cables are connected to the moving element .

In addition, it is preferred that the eccentric groove prevents the auxiliary elastic element from expanding or contracting freely in conjunction with the eccentric follower while the operating element moves from the intermediate position to the disengagement position.

Furthermore, it is preferred that the auxiliary elastic element pushes the transmission component in a direction such that it engages the friction clutch when the operating element is in a return position on the return side of the start-off position, and the direction of the thrust force applied to the transmission component is changed from a direction such that it engages the friction clutch to a direction such that it disengages the friction clutch when the operating element is moved from the return position to the disengagement position on the starting position of disengagement, and where an elastic cancellation element is provided, which pushes the rotating element in a direction such that it cancels the pushing force of the auxiliary elastic element when the operating element is in the return position.

It is also preferred that the thrust force of the clutch spring applied to the mobile element is zero and that the rotating element receives the thrust force of the elastic cancellation element while the operating element moves from the return position to the starting position of disengagement

In addition, the clutch operation assist device could also include a stop to receive the rotating element when the operating element is in the return position, where the stop is pushed by the elastic cancellation element.

The above description also describes another embodiment of a clutch operation assist device incorporated in a clutch operating device having a friction clutch with a clutch spring, a transmission component connected to the friction clutch, and an operating element that It is connected to the transmission component and it changes the friction clutch engagement state when it is operated against the thrust force of the clutch spring, including the clutch operation assist device: a movable element that can be moved in synchronism with the operative element; a rotating element; an oscillating auxiliary elastic element for applying a pushing force to rotate the rotating element; and an eccentric mechanism interposed between the mobile element and the rotating element to transmit the thrust force applied to the rotating element to the mobile element, where, when the operating element is operated in a direction such that it disengages the friction clutch, the elastic element The auxiliary applies a pushing force to move the moving element in a direction such that it disengages the friction clutch while the operating element moves from a starting position of disengagement where the operating element receives the reaction force from the clutch spring to a position release where the friction clutch release is complete.

According to this clutch operation assistance device, a rotating element and an eccentric mechanism are interposed between the oscillating auxiliary elastic element and the mobile element. Since the auxiliary elastic element can oscillate, the direction of the pushing force can be freely changed. Therefore, the thrust force can always be applied in an appropriate direction, and the loss of the thrust force applied to the movable element can be reduced even if an eccentric mechanism is interposed between the auxiliary elastic element and the movable element. In addition, wear of the components in the clutch operation assistance device can be reduced, and the service life and reliability of the clutch operation assistance device can be improved.

Furthermore, since the eccentric mechanism is interposed between the auxiliary elastic element and the mobile element, the relationship between the oscillation of the auxiliary elastic element and the movement of the mobile element can be freely established. Therefore, the variation characteristics of the thrust force applied to the mobile element (in other words, the variation characteristics of the thrust force while the operating element is operated) can be set arbitrarily. Therefore, the operability of the clutch lever can be further improved, for example, by reducing the force necessary to operate the clutch lever immediately after the friction clutch release has begun.

The description describes that it is preferable for the eccentric mechanism to change a speed ratio, which is the ratio of the rotational speed of the rotating element to the advancing speed of the moving element, while the operating element moves from the starting position of disengagement. to the release position.

It is also preferable that the speed ratio at the time that the operating element is in the starting position of disengagement is greater than the time in which the operating element is in the disengaging position.

It is also preferable that the average of the speed ratio while the operating element is shifted from the start position of disengagement to an intermediate position between the start position of disengagement and the position of disengagement is larger than the average of the speed ratio while the operating element is moved from the intermediate position to the disengagement position.

It is also preferable that the eccentric mechanism gradually decreases the speed ratio while the operating element moves from the starting position of disengagement to the disengaging position.

It is also preferable that the eccentric mechanism maintains the relationship between the reaction force of the clutch spring and the load applied to the operating element within a fixed range while the operating element moves from the starting position of disengagement to an intermediate position between the start position of disengagement and the position of disengagement.

In addition, the mobile element can be a rotating element.

In addition, the eccentric mechanism may have an eccentric groove formed through one of the movable element and the rotating element, and an eccentric follower may be in contact with the eccentric groove and supported by the other of the movable element and the rotary element.

Similarly, the auxiliary elastic element may be a spring.

The above description also describes an embodiment of a clutch operation assist device incorporated in a clutch operating device having a friction clutch with a clutch spring, a transmission component connected to the friction clutch, and an operating element that It is connected to the transmission component and changes the friction clutch engagement state when it is operated against the thrust force of the clutch spring, including the clutch operation assist device: a movable element that can be moved in synchronism with the operative element; a rotating element; an oscillating auxiliary elastic element for applying a pushing force to rotate the rotating element; and a thrust force transmission component interposed between the movable element and the rotary element to transmit to the movable element the thrust force produced by the auxiliary elastic element that the rotary element receives, where, when the operating element is operated in one direction such that it disengages the friction clutch, the auxiliary elastic element applies a pushing force to move the movable element in a direction such that it disengages the friction clutch while the operating element moves from a starting position of disengagement where the operating element receives the reaction force of the clutch spring to a disengagement position where the friction clutch disengagement is completed, and where the thrust force transmission component changes a speed ratio, which is the ratio of the rotational speed of the rotating element at the feed rate of the moving element, while the element operating moves from the start position of disengagement to the position of disengagement.

The description also describes an embodiment of a vehicle equipped with the friction clutch, the transmission component, the operating element and a clutch operation assistance device according to any of the previous embodiments.

According to the present embodiments, the force necessary to operate the operative element to disengage the friction clutch can be reduced, and a natural and comfortable operating sensation can be obtained.

The above description describes, as an especially preferred embodiment, in order to provide a clutch operation assistance device with which the operation of the operating element does not produce any sensation of discomfort and which can improve the operability of the operating element, a device operating clutch that has a friction clutch with a clutch spring, a clutch lever connected to the friction clutch by means of clutch cables 43a and 43b and that is manually operable against the thrust force of the clutch spring, and a operation assistance The operating assistance device has an assist mechanism 52 having an auxiliary spring 82 that pushes the clutch cables 43a and 43b in a direction such that it disengages the friction clutch while the clutch lever moves from a starting position. of disengagement where the clutch lever receives the reaction force of the clutch spring to a disengaged position where the friction clutch disengagement is completed. The assist mechanism 52 maintains the thrust force of the auxiliary spring 82 applied to the clutch cables 43a and 43b within a fixed range while the clutch lever moves from the midpoint between the starting position of disengagement and the position from disengagement to the disengaged position.

Claims (20)

1. Clutch operating device having a friction clutch (18) with a clutch spring (27), and an operating element (9) connected to the friction clutch (18) by transmission components (43a, 43b) and being manually operable against the thrust force of the clutch spring (27) to disconnect the torque transmission by the friction clutch (18), and a clutch operation assist device

(fifty)

 which includes an assist mechanism (52) that includes an auxiliary elastic element (59) which, when the operating element (9) is operated in a direction of disengaging the friction clutch (18), pushes the transmission components (43a, 43b) in the direction of disengaging the friction clutch (18), while the operating element (9) is displaced from a starting position of disengagement, where the operating element

(9)

 receives the reaction force of the clutch spring (27), to a disengagement position where the friction clutch disengagement (18) is completed, characterized in that

The pushing force of an auxiliary elastic element (59), applied to the transmission component (43a, 43b) by means of a rotating element (57), is maintained within a fixed range while the operating element (9) is displaced from a position intermediate between the start position of disengagement and the position of disengagement to the position of disengagement, where the assist mechanism is arranged so that an increase in the pushing force of the auxiliary elastic element (59) applied to the transmission components ( 43a, 43b) is canceled when the operating element (9) approaches the disengagement position.

2.

 Clutch operating device according to claim 1, wherein the auxiliary elastic element (59) pushes the transmission component (43a, 43b) in a direction of engaging the friction clutch (18) when the operating element (9) is in a position of return on the return side of the starting position of disengagement, and the direction of the thrust force applied to the transmission component (43a, 43b) is changed from the direction of engaging the friction clutch (18) to the direction of disengaging the friction clutch (18) when the operating element (9) is moved from the return position to the disengagement position on the starting position of disengagement, and where an elastic cancellation element (100) is provided that applies a pushing force to cancel the pushing force of the auxiliary elastic element applied to the transmission component (43a, 43b) when the operating element (9) is in the return position no.

3.

 Clutch operating device according to claim 1 or 2, wherein the friction clutch (18) has a clutch release mechanism, and where the transmission component (43a, 43b) has a first clutch cable (43a) connected to the element operating (9) and a second clutch cable (43b) connected to the clutch release mechanism that is interposed between the first clutch cable (43a) and the second clutch cable (43b).

Four.

 Clutch operating device according to claim 3, wherein the displacement of the first clutch cable (43a) and the displacement of the second clutch cable (43b) while the operating element (9) is operated are equal to each other.

5.

 Clutch operating device according to claim 3 or 4, wherein the first and second clutch cables (43a, 43b) are connected to the rotating element (57).

6.

 Clutch operating device according to one of claims 1 to 5, further including:

a mobile element (58) that can be moved in synchronism with the transmission component (43a, 43b), where the auxiliary elastic element, when the operating element (9) is operated in a direction such that it disengages the friction clutch (18), applies a pushing force to move the mobile element (58) in a direction such that it disengages the clutch of friction (18) while the operating element (9) is displaced from a starting position of disengagement where the operating element (9) receives the reaction force of the clutch spring (27) to a disengaging position where the disengagement is completed the friction clutch (18); said rotating element (57) is provided to transmit the pushing force of the auxiliary elastic element to the mobile element (58).

7.

 Clutch operating device according to claim 6, further including an eccentric mechanism (71, 79) that is interposed between the movable element (58) and the rotary element (57) and that maintains the thrust force applied from the rotary element ( 57) to the mobile element (58) within a fixed range while the operative element (9) is moved from an intermediate position between the starting position of disengagement and the position of disengagement to the position of disengagement.

8.

 Clutch operating device according to claim 7, wherein the eccentric mechanism (71, 79) has an eccentric groove (71) formed through one of the movable element (58) and the rotary element (57), and an eccentric follower (79) in contact with the eccentric groove (71) and supported by the other of the movable element (58) and the

rotating element (57).

9.

 Clutch operating device according to claim 8, wherein the eccentric groove (71) prevents the auxiliary elastic element from expanding or contracting freely in conjunction with the eccentric follower (79) while the operating element (9) is displaced from the intermediate position to the release position.

10.

 Clutch operating device according to one of claims 2 to 9, wherein the auxiliary elastic element pushes the transmission component (43a, 43b) in a direction of engaging the friction clutch (18) when the operating element (9) is in a return position on the return side of the start release position, and the direction of the thrust force applied to the transmission component (43a, 43b) is changed from one direction of engaging the friction clutch (18) to a direction of disengaging the friction clutch (18) when the operating element (9) is moved from the return position to the disengagement position on the starting position of disengagement, and where the elastic cancellation element (100) is provided which pushes the rotating element (57) in a direction to cancel the pushing force of the auxiliary elastic element when the operating element (9) is in the return position.

eleven.

 Clutch operating device according to one of claims 6 to 10, wherein the thrust force of the clutch spring (27) applied to the movable element (58) is zero and the rotating element (57) receives the thrust force of the elastic element of cancellation (100) while the operating element (9) is moved from the return position to the starting position of disengagement.

12.

 Clutch operating device according to claim 11, further including a stop (103) for receiving the rotating element (57) when the operating element (9) is in the return position, where the stop (103) is pushed by the elastic element cancellation (100).

13.

 Clutch operating device according to one of claims 1 to 12, wherein the thrust force transmission components (43a, 43b), in particular the eccentric mechanism (71, 79) changes a speed ratio, which is the ratio of the rotational speed of the rotating element (57) at the forward speed of the mobile element (58), while the operating element (9) is moved from the starting position of disengagement to the disengaging position.

14.

 Clutch operating device according to claim 13, wherein the speed ratio at the time that the operating element (9) is in the starting position of disengagement is larger than at the time in which the operating element (9) is in the position of disengagement

fifteen.

 Clutch operating device according to claim 13 or 14, wherein the average speed ratio while the operating element (9) is shifted from the starting position of disengagement to an intermediate position between the starting position of disengagement and the disengagement position is larger than the average speed ratio while the operating element (9) is moved from the intermediate position to the disengagement position.

16.

 Clutch operating device according to one of claims 13 to 15, wherein the eccentric mechanism (71, 79) gradually decreases the speed ratio while the operating element (9) is shifted from the starting position of disengagement to the disengaging position. .

17.

 Clutch operating device according to one of claims 7 to 16, wherein the eccentric mechanism (71, 79) maintains the relationship between the reaction force of the clutch spring and the load applied to the operating element (9) within a fixed range while the operative element (9) is moved from the starting position of disengagement to an intermediate position between the starting position of disengagement and the position of disengagement.

18.

 Clutch operating device according to one of claims 6 to 17, wherein the mobile element is a second rotating element (58).

19.

 Clutch operating device according to one of claims 1 to 18, wherein the auxiliary elastic element

(59) is a dock. 20. A vehicle equipped with the clutch operating device according to one of claims 1 to 19.