JP2007231989A - Release mechanism of clutch - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a release mechanism of a clutch capable of reducing components and capable of contributing to reduction of the cost. <P>SOLUTION: The release mechanism of the clutch is provided with a fixed cam member 46 supported by a supporting shaft 45, a locking means 53 arranged between the fixed cam member 46 and a crankcase 15 and suppressing turning of the fixed cam member 46 around the supporting shaft 45, and a movable cam member 47 confronting the fixed cam member 46 and arranged coaxially with the supporting shaft 45 so as to be turnable. The locking means 53 is constituted by a locking shaft part 54 integrally formed on an arm 51a extending in a radial direction outer side of the fixed cam member 46 by bending a part thereof to be parallel to the supporting shaft 45, and a locking hole 55a formed on an inner side surface of the crankcase 15 so that a locking shaft part 54 is fitted thereto. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a fixed cam member supported by a support shaft provided in an engine crankcase, and a rotation stopper provided between the fixed cam member and the crankcase to prevent the rotation of the fixed cam member around the support shaft. And a movable cam member arranged to be coaxially rotatable with the support shaft so as to face the fixed cam member, and the fixed cam member and the movable cam member are configured to reciprocally rotate the movable cam member. Improvement of the release mechanism of the clutch, which is configured to reciprocate the movable cam member in the axial direction with respect to the fixed cam member, and the movable cam member provides the disconnection operation to the clutch by one axial movement. About.

Such a clutch release mechanism is already known, as disclosed in Japanese Patent Application Laid-Open No. H10-228707.
Japanese Patent Laid-Open No. 1-145427

  Conventionally, the detent means of the fixed cam member in such a clutch release mechanism includes a detent pin fixed by caulking or welding to the tip of the arm extending radially outward of the fixed cam member, and the inner surface of the crankcase. Since the fixed cam member and the non-rotating pin are separated from each other, there are many components and there is a limit to cost reduction. It was.

  The present invention has been made in view of such circumstances, and an object of the present invention is to provide a release mechanism for the clutch that has fewer components and can contribute to cost reduction.

  In order to achieve the above object, the present invention provides a fixed cam member supported by a support shaft provided in an engine crankcase, and a portion around the support shaft of the fixed cam member provided between the fixed cam member and the crankcase. A rotation-preventing means for preventing the rotation of the movable cam member, and a movable cam member disposed so as to be rotatable coaxially with the support shaft so as to face the fixed cam member. The movable cam member is configured to reciprocate in the axial direction with respect to the fixed cam member as the movable cam member reciprocates, and the movable cam member is configured to provide a shut-off operation to the clutch by one axial movement. In the clutch release mechanism, the rotation-preventing means is integrally formed by bending an arm extending outward in the radial direction of the fixed cam member and bending a part thereof in parallel with the support shaft. And because shaft portion, said detent shaft portion is formed on the inner surface of the crankcase to the first, characterized in that is constituted by a detent hole to be fitted.

  According to the present invention, in addition to the first feature, the rotation-preventing shaft portion is configured by a pair of projecting pieces having an arcuate cross section that bend from both side edges of the tip end portion of the arm and face the concave surfaces. The second feature.

  Furthermore, in addition to the first or second feature, the present invention defines the rotation-preventing hole by an inner peripheral surface of a cylindrical wall projecting from the inner surface of the crankcase. A third feature is that a notch for receiving a part is provided.

  According to the first feature of the present invention, the anti-rotation shaft portion is integrally formed at the tip end portion of the arm of the fixed cam member by a part thereof, so that the anti-rotation shaft is simultaneously produced by the press working of the fixed cam member. The shaft portion can be molded, and the number of components of the fixed cam member can be reduced, and the cost can be reduced.

  According to the second feature of the present invention, the anti-rotation shaft portion is composed of a pair of projecting pieces having an arc-shaped cross section that bends at right angles from the both side edges of the arm toward the side cover and faces the concave surfaces. In addition, it is possible to easily press-form the protruding piece, that is, the non-rotating shaft portion, and to sufficiently secure a fitting area with the non-rotating hole of the non-rotating shaft portion, thereby improving durability.

  According to the third feature of the present invention, it is possible to fit the pair of projecting pieces, that is, the entire rotation shaft portion into the rotation prevention hole while avoiding interference between the arm of the fixed cam member and the cylindrical wall. Therefore, it is possible to secure a large fitting area with the rotation prevention hole of the rotation prevention shaft portion.

  Hereinafter, embodiments of the present invention will be described based on preferred examples shown in the accompanying drawings.

  FIG. 1 is a side view of a motorcycle according to a first embodiment of the present invention, FIG. 2 is an enlarged sectional view of a periphery of a clutch in the engine of the motorcycle, FIG. 3 is an enlarged view of a release mechanism portion of FIG. Is a sectional view taken along line 4-4 in FIG. 3, FIG. 5 is a sectional view taken along line 5-5 in FIG. 4, FIG. 6 is a sectional view taken along line 6-6 in FIG. Indicates the state of the hour. FIG. 7 is a view corresponding to FIG. 3, showing a second embodiment of the present invention, and FIG. 8 is a sectional view taken along line 8-8 of FIG.

  First, the first embodiment of the present invention shown in FIGS. 1 to 6 will be described.

  In FIG. 1, a body frame F of a motorcycle M extends downward from a pipe-shaped main frame portion 2 inclined downward from the head pipe 1 and a rear end portion of the main frame portion 2. The head pipe 1 is composed of a pivot support frame portion 3 and a pair of left and right seat rail portions 4 and 4 which are coupled to the rear end portions of the pivot support frame portion 3 and the main frame portion 2 and extend rearward and upward. Thus, the steering stem 6a of the front fork 6 that supports the front wheel 5f is supported, and the steering handle 7 is connected to the upper end of the steering stem 6a. A pivot shaft 9 is fixed to the pivot support frame portion 3, whereby the rear fork 8 that pivotally supports the rear wheel 5 r is supported so as to be swingable up and down. A rear cushion 12 is interposed between the rear fork 8 and the seat rail portions 4 and 4.

  The engine E located between the front wheel 5f and the rear wheel 5r is attached to the main frame part 2 and the pivot support frame part 3. The power of the engine E is transmitted to the rear wheel 5r via the chain transmission device 11.

  A body cover 16 is attached to the body frame F and covers a cylinder portion of the engine E, and a pair of left and right leg shields 17 are connected to the front end of the body frame.

  A change spindle 20 for switching the gear transmission inside the engine E is supported on the crankcase 15 of the engine E, and a change pedal 21 is provided at an outer end portion of the change spindle 20 protruding from the left side surface of the crankcase 15. It is attached.

  As shown in FIG. 2, the crankcase 15 includes an engine crankshaft (not shown), a case main body 15a that rotatably supports an input shaft 19 and an output shaft (not shown) of the gear transmission, A side cover 15b that is detachably bolted to the right end surface of the case body 15a and defines the clutch chamber 22 between the case body 15a and the clutch chamber 22 includes a space between the crankshaft and the input shaft 19. A primary reduction gear train 23 disposed in the motor and a clutch 24 for controlling power transmission from the primary reduction gear train 23 to the input shaft 19 are housed. The change spindle 20 is rotatably supported by the case body 15a and the side cover 15b.

  The driven gear 23a of the primary reduction gear train 23 is rotatably supported on the input shaft 19 via a needle bearing 25, and the clutch 24 is connected to one side of the driven gear 23a via a rubber damper 26. The bottomed cylindrical clutch outer 30, the clutch inner 33 disposed in the clutch outer 30 and splined to the input shaft 19 and fixed by the nut 41, and the inner peripheral wall of the clutch outer 30 A plurality of drive friction plates 31 that are slidably fitted to each other, and one drive friction plate 31 that is alternately overlapped with these drive friction plates 31 and that is slidably fitted to the outer periphery of the clutch inner 33 or A plurality of driven friction plates 32 and a clutch inner 33 are integrally connected to the outermost drive friction plates 31. 3 pressure receiving plate 34 which is axially slidably splined to, and a pressure plate 35 disposed adjacent to the drive friction plates 31 ... of the innermost position. The pressure plate 35 has a plurality of connecting bosses 37 (one of which is shown in the figure) penetrating through a plurality of through holes 36 (one of which is shown in the figure) provided in the clutch inner 33. Are integrally formed. A release plate 38 is fixed to the end surfaces of the connecting bosses 37 by bolts 39. A clutch spring 40 is contracted between the release plate 38 and the clutch inner 33. An elastic force is exerted to urge the pressure plate 35 toward the pressure receiving plate 34 via the release plate 38.

  Thus, in the free state of the release plate 38, the pressure plate 35 presses the drive friction plates 31 ... and the driven friction plates 32 against the pressure receiving plate 34 by the urging force of the clutch spring 40. The plates 31 ... and the driven friction plates 32 are pressed against each other to connect the clutch outer 30 and the clutch inner 33, the clutch 24 is in a connected state, and the power of the crankshaft is supplied to the input shaft 19 via the primary reduction gear train 23. Can be communicated to. Further, when the release plate 38 is moved back from the driving friction plates 31 and the driven friction plates 32 against the urging force of the clutch spring 40, the driving friction plates 31 and the driven friction plates 32 are free to mutually. Thus, since the connection between the clutch outer 30 and the clutch inner 33 is released, the clutch 24 is in a disconnected state, and the power transmission from the primary reduction gear train 23 to the input shaft 19 can be cut off.

  In FIG. 3, the release plate 38 is connected to a release mechanism 44 that can operate the release plate 38 in the direction of disengagement of the clutch 24 by a predetermined rotation of the change spindle 20. The release mechanism 44 includes a support shaft 45 coaxially supported with the input shaft 19 and rotatably supported by the side cover 15b, a fixed cam member 46 supported by the support shaft 45 in the clutch chamber 22, and the fixed cam member. 46 includes a movable cam member 47 that is disposed so as to be relatively rotatable, and a clutch lever 48 that is serrated to the change spindle 20 to rotate the movable cam member 47.

  The support shaft 45 includes an adjustment screw shaft portion 45a that is screwed into a hub 50, which will be described later, of the movable cam member 47, and a flange portion 45b that contacts the inner surface of the side cover 15b. The lock nut 49 is usually screwed and tightened to the outer end protruding outside the side cover 15b, so that it is normally fixed to the side cover 15b.

  The fixed cam member 46 includes a hub 50 that is screwed and supported by the adjusting screw shaft portion 45a, and a fixed cam plate 51 that is fixed to the outer periphery of the hub 50 by caulking or welding. The fixed cam plate 51 integrally has an arm 51a extending in the radial direction from the outer periphery of the fixed cam plate 51, and a detent means 53 for preventing rotation of the fixed cam member 46 around the support shaft 45 between the arm 51a and the side cover 15b. Is provided. The anti-rotation means 53 is integrally formed by a part of the tip of the arm 51a, and the anti-rotation shaft portion 54 that protrudes in parallel to the support shaft 45 toward the side cover 15b and the anti-rotation shaft portion 54 is slid. It is comprised with the bottomed anti-rotation hole 55a formed in the inner wall of the side cover 15b so that it may movably fit.

  As shown in FIGS. 3 to 5, the anti-rotation hole 55 a is defined by an inner surface of a cylindrical wall 55 that projects integrally with the inner wall of the side cover 15 b. On the other hand, the anti-rotation shaft portion 54 is formed integrally with the tip portion of the arm 51a, and particularly preferably, the anti-rotation shaft portion 54 is bent at right angles from both side edges of the arm 51a toward the side cover 15b so that the concave surfaces face each other. It comprises a pair of projecting pieces 54a, 54a having a circular arc cross section. At that time, the projecting pieces 54a and 54a are formed at the same time when the fixed cam plate 51 is manufactured from one steel plate by press working.

  The movable cam member 47 includes a hub 52h that is rotatably supported on the outer peripheral surface of the hub 50, and a movable cam plate 52 that is integrally connected to one end of the hub 52h. It is connected to the release plate 38 via a release bearing 61.

  The fixed cam plate 51 and the movable cam plate 52 have a plurality of cam recesses 51b ...; 52b ... arranged at equal intervals in the circumferential direction on their opposing surfaces, and between the opposing cam recesses 51b, 51b, Balls 56 held by the retainer 57 are arranged, and a spring 58 is contracted between the retainer 57 and the fixed cam plate 51 so as to urge these balls 56 toward the movable cam plate 52 side.

  The movable cam plate 52 is integrally provided with an arm 52a extending radially from the outer periphery of the movable cam plate 52, and a roller 48a that is pivotally supported by the distal end portion of the clutch lever 48 in a long hole 60 formed in the arm 52a. Are engaged.

  A known neutral return mechanism 42 that biases the change spindle 20 to the neutral position is provided between the change spindle 20 and the case main body 15a. The change spindle 20 is connected to a known change mechanism (not shown) for shifting the gear transmission.

  Next, the operation of the first embodiment will be described.

  In the state where the change spindle 20 is held at the neutral position, the movable cam member 47 has its own cam recess 51b facing the cam recess 52b of the fixed cam member 46 as shown in FIG. Thus, the corresponding ball 56 is deeply received in the cam recesses 51b and 51b, thereby occupying a position close to the fixed cam member 46 side and releasing the release plate 38. As a result, the pressure plate 35 presses the driving friction plates 31 and the driven friction plates 32 to the pressure receiving plate 34 side by the urging force of the clutch spring 40, so that the clutch 24 is in a connected state.

  In this state, if the lock nut 49 is loosened and the support shaft 45 is rotated, the adjusting screw shaft portion 45a advances and retracts the movable cam member 47 in the axial direction in accordance with the rotation direction, and the cam recesses of both cam members 46 and 47 are moved. The gap between the balls 51b and 51b can be adjusted appropriately. At this time, the detent shaft portion 54 of the fixed cam member 46 slides in the detent hole 55a of the side cover 15b, so that the axial movement of the fixed cam member 46 is not hindered.

  When the change pedal 21 is rotated by one stroke from the neutral position to shift the gear transmission by one step, first, the clutch lever 48 moves the movable cam member 47 in FIG. ), As shown by the arrow, and the ball 56 climbs the slopes of the cam recesses 51b and 51b of the cam members 46 and 47, thereby moving the movable cam member 47 away from the fixed cam member 46. Since the release plate 38 is pushed toward the release plate 38, the push is transmitted to the pressure plate 35 via the release bearing 61 and the release plate 38, and the pressure plate 35 is driven against the urging force of the clutch spring 40. .. And the driven friction plates 32 are retracted, and the clutch 24 is disengaged.

  When the rotation of the change spindle 20 proceeds to the second half, the change mechanism is operated and the gear transmission is shifted one step while the clutch 24 is maintained in the disengaged state.

  Thereafter, when the change spindle 20 is returned to the neutral position by the neutral return mechanism 42, the movable cam member 47 returns to the original state, and the release plate 38 and the pressure plate 35 are also returned to the original state due to the repulsive force of the clutch spring 40. At the same time, the pressure plate 35 again presses the driving friction plates 31 and the driven friction plates 32 toward the pressure receiving plate 34, so that the clutch 24 is brought into a connected state.

  During this time, the detent shaft portion 54 of the fixed cam member 46 is fitted in the detent hole 55a of the side cover 15b and prevents rotation of the movable cam member 47 around the support shaft 45. 47 can be reliably rotated and the release mechanism 44 can be reliably disconnected and connected to the clutch 24.

  By the way, as described above, the detent shaft portion 54 is formed integrally with the tip portion of the arm 51a as a part thereof, so that the detent shaft portion 54 is simultaneously formed by pressing the fixed cam plate 51. Therefore, it is possible to reduce the number of constituent parts of the fixed cam member 46 and to reduce the cost.

  In that case, in particular, it is desirable that the rotation-preventing shaft portion 54 is composed of a pair of projecting pieces 54a, 54a having an arcuate cross section that bends at right angles from both side edges of the arm 51a toward the side cover 15b and faces the concave surfaces. In this way, the pair of projecting pieces 54a, 54a, that is, the non-rotating shaft portion 54 can be easily press-formed, and a sufficient engagement area with the non-rotating hole 55a of the non-rotating shaft portion 54 can be secured. Thus, durability can be improved.

  Next, a second embodiment of the present invention shown in FIGS. 7 and 8 will be described.

  In the second embodiment, a notch 62 that opens one side of the rotation stop hole 55a is formed in a part of the cylindrical wall 55 of the inner wall of the side cover 15b, and the arm 51a of the fixed cam plate 51 is formed in the notch 62. Part of is accepted. Since the other configuration is the same as that of the previous embodiment, the same reference numerals are given to the portions corresponding to those of the previous embodiment in FIGS.

  According to the second embodiment, while avoiding interference between the arm 51a of the fixed cam plate 51 and the cylindrical wall 55, the pair of projecting pieces 54a, 54a, that is, the entire rotation-preventing shaft portion 54 is fitted into the rotation-preventing hole 55a. This makes it possible to secure a large fitting area with the detent hole 55a of the detent shaft portion 54.

  As mentioned above, although the Example of this invention was described, this invention is not limited to the said Example, A various design change can be performed in the range which does not deviate from the summary of this invention.

1 is a side view of a motorcycle according to a first embodiment of the present invention. The expanded sectional view of the clutch peripheral part in the engine of the same motorcycle. The enlarged view of the release mechanism part of FIG. FIG. 4 is a sectional view taken along line 4-4 of FIG. FIG. 5 is a sectional view taken along line 5-5 of FIG. 3A is a cross-sectional view taken along the line 6-6 in FIG. 3, and FIG. FIG. 4 is a diagram corresponding to FIG. 3 showing a second embodiment of the present invention. FIG. 8 is a cross-sectional view taken along line 8-8 in FIG.

Explanation of symbols

E ... Engine 15 ... Crankcase 24 ... Clutch 44 ... Release mechanism 45 ... Support shaft 46 ... Fixed cam member 47 ··· movable cam member 53 ··· anti-rotation means 54 ··· anti-rotation shaft portion 54a ··· projection 55 ··· cylindrical wall 55a ··· anti-rotation hole 62 ... notches

Claims (3)

A fixed cam member (46) supported by a support shaft (45) provided in a crankcase (15) of the engine (E), and a fixed cam provided between the fixed cam member (46) and the crankcase (15). A rotation preventing means (53) for preventing the rotation of the member (46) around the support shaft (45), and a rotation of the support shaft (45) coaxially with the fixed cam member (46). A movable cam member (47) disposed, and the fixed cam member (46) and the movable cam member (47) are provided with the movable cam member (47) as the movable cam member (47) reciprocally rotates. The release of the clutch is configured to reciprocate in the axial direction with respect to the fixed cam member (46), and the movable cam member (47) is configured to provide a shut-off operation to the clutch (24) by one axial movement. In the mechanism,
The anti-rotation means (53) is an anti-rotation formed integrally with an arm (51a) extending radially outward of the fixed cam member (46) by bending a part thereof in parallel with the support shaft (45). A clutch release comprising a shaft portion (54) and a non-rotating hole (55a) formed on an inner surface of the crankcase (15) and into which the non-rotating shaft portion (54) is fitted. mechanism. The release mechanism for a clutch according to claim 1,
The anti-rotation shaft portion (54) is constituted by a pair of projecting pieces (54a, 54a) having an arcuate cross section bent from both side edges of the tip end portion of the arm (51a) and facing the concave surfaces. The release mechanism of the clutch. The clutch release mechanism according to claim 1 or 2,
The anti-rotation hole (55a) is defined by an inner peripheral surface of a cylindrical wall (55) projecting from the inner surface of the crankcase (15), and one of the arms (51a) is formed in the cylindrical wall (55). A release mechanism for the clutch, characterized in that a notch (62) for receiving the portion is provided.

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