JP2002303336A - Switching clutch - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent a large shocking torque from being transmitted to a gear transmission when engaging a switching clutch in the switching clutch which is interposed between an output shaft of an internal combustion engine and an input shaft of the gear transmission whose gear ratio can be switched by transmission manipulation and is engaged/disengaged through the switching manipulation. SOLUTION: A damper is interposed between an output member of a switching clutch and a driven member connected to the input shaft of the gear transmission.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a switching clutch having an excellent damper function provided between an output shaft of an internal combustion engine and an input shaft of a gear transmission.

[0002]

2. Description of the Related Art A conventional switching clutch in which the clutch is switched on and off by operating the clutch is disclosed in Japanese Utility Model Publication No. 57-29.
No. 070 and Japanese Patent Application Laid-Open No. 9-264337, a damper is interposed between an input gear meshing with an output gear integrated with a crankshaft of an internal combustion engine and a clutch housing of a switching clutch. The clutch inner connected to the gear transmission via a plurality of clutch plates is integrally connected to the input shaft of the gear transmission by spline fitting.

[0003]

When the output member of the switching clutch is integrally connected to the input shaft of the gear transmission as described above, a large impulsive large torque generated when the switching clutch is connected is generated. It is easy to be transmitted to the transmission.

[0004]

SUMMARY OF THE INVENTION The present invention relates to an improvement of a switching clutch which overcomes the above-mentioned disadvantages. The first aspect of the present invention relates to an output shaft of an internal combustion engine and a speed change ratio by a speed change operation. In a switching clutch in which a clutch is engaged / disengaged by a switching operation interposed between an input shaft of a gear transmission to be switched, an output member of the switching clutch and a driven member connected to an input shaft of the gear transmission. , And a damper is interposed.

[0005] In the first aspect of the present invention, since the damper is interposed between the output member of the switching clutch and the driven member connected to the input shaft of the gear transmission, a large amount of power is generated due to intermittent switching of the switching clutch. Impulsive torque fluctuations are absorbed by the damper, and large impulsive torque is prevented from being applied to the gear transmission on the power transmission side, so that generation of noise, impact, and vibration can be avoided. .

[0006]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS One embodiment of the present invention shown in FIGS. 1 to 7 will be described below.

As shown in FIGS. 1 and 2, a main body of a single-cylinder OHC four-stroke cycle internal combustion engine 0 mounted on a motorcycle (not shown) has a cylinder hole 5 substantially in front (in FIG. A cylinder block 1 oriented in the horizontal direction, a cylinder head 2 arranged at the front end of the cylinder block 1, and the cylinder block 1
The right and left split crankcases 3 and 4 are arranged at the rear end of the right and left split crankcases. The right and left split crankcases 3 and 4 are connected to each other by bolts (not shown). At the same time, the right crankcase 3 and the left crankcase 4 pass through the cylinder head 2 and the cylinder block 1 from the front of the vehicle body.
The cylinder block 1, the cylinder head 2, the right crankcase 3, and the left crankcase 4 are integrally connected to each other by bolts 6 screwed to the cylinder block 1.

As shown in FIG. 2, a piston 7 is slidably fitted in a cylinder hole 5 of the cylinder block 1, and a right crankcase 3 and a left crankcase 4 have a vehicle width. Crankshaft 8 oriented in the direction
Is rotatably supported via a ball bearing 9, and the piston 7 and the crank shaft 8 are connected to each other by a connecting rod.
The crankshaft 8 is rotated clockwise in FIG. 1 in conjunction with the reciprocation of the piston 7.

A main shaft 11 and an output shaft 12 are rotatably supported by the right crankcase 3 and the left crankcase 4 in parallel with the crankshaft 8 (FIG. 1). The automatic centrifugal clutch 13 for starting shown in FIG. 3 is disposed, and a switching clutch 36 shown in FIG. 3 is disposed at the right end of the main shaft 11, and a gear (not shown) is mounted on the main shaft 11 and the output shaft 12. A drive sprocket (not shown) is integrally attached to a left end of the output shaft 12 protruding leftward from the left crankcase 4, and a driven sprocket (not shown) is integrally attached to a rear axle integral with a rear wheel (not shown). And an endless chain (not shown) is bridged between the drive sprocket and the driven sprocket.
And when the switching clutch 36 is connected,
By selective engagement of the gears of the main shaft 11 and the output shaft 12, a rear wheel (not shown) is rotationally driven at a predetermined gear ratio.

In the automatic centrifugal clutch 13 for starting, FIG.
As shown in FIG. 4, a centrifugal clutch inner 14 is rotatably fitted to the right side of the crankshaft 8, and is located near the outer end of the centrifugal clutch inner 14 and has a clutch center at the right end of the crankshaft 8. 15 is splined,
A clutch center 15 is integrally connected to the crankshaft 8 by a nut 16 screwed to the right end of the crankshaft 8.
The inner peripheral surface 14b of the circular concave portion of the outer disk portion 14a of the centrifugal clutch inner 14, and the outer peripheral surface 15 of the clutch center 15
As shown in FIGS. 3 and 6, a retainer 18 of a one-way clutch 17 is interposed between the
As shown in FIG. 6, the roller holding holes 18a are formed at regular intervals in the circumferential direction.
The roller 19 is loosely fitted to the roller 8a, and a clutch cam concave surface 15b is formed on the outer peripheral surface 15a of the clutch center 15, as shown in FIGS.

As shown in detail in FIG. 7, the clutch cam concave surface 15b is gently inclined radially from the bottom in a clockwise direction, and is inclined in a counterclockwise direction from the bottom. When the clutch center 15, that is, the crankshaft 8 rotates clockwise in FIG. 6 (the single-cylinder OHC four-stroke cycle internal combustion engine 0 rotates forward), the rotational torque of the clutch center 15 decreases. When the clutch center 15 rotates counterclockwise in FIG. 6 (the single-cylinder OHC four-stroke cycle internal combustion engine 0 reverses) without being transmitted to the centrifugal clutch inner 14, the rotational torque of the clutch center 15 is applied to the centrifugal clutch inner 14. When transmitted or when the centrifugal clutch inner 14 rotates clockwise in FIG. Torque clutch center
15 to be transmitted.

Further, the clutch center 15 and the retainer
A positioning ring-shaped spring 20 is interposed between the clutch center 18 and the spring force of the spring 20 so that the roller holding hole 18a of the retainer 18 can return to a position facing the bottom of the clutch cam concave surface 15b of the clutch center 15. It has become.

Further, a steel bowl-shaped clutch housing 21 is integrally joined to the outer peripheral surface of the right side of the clutch center 15 by welding, and the clutch housing 21 is a press-formed product.

The outer peripheral portion 21b of the disc-shaped portion 21a of the clutch housing 21 formed by the press forming is bent leftward at a substantially right angle in cross section with respect to the disc-shaped portion 21a. As shown in the drawing, overhangs 21c are formed at regular intervals in the circumferential direction, and among the overhangs 21c, openings 21d are formed at positions near the centers of every other overhangs 21c, and adjacent openings 21d are formed. An engaging claw 21 e for holding the support ring 25 is cut and raised in the middle of the opening 21 d to be opened, and the disk-shaped portion 21
a, the outer peripheral portion 21b, the overhang portion 21c, the opening 21d, and the locking claw 21e are formed at the same time when the clutch housing 21 is pressed.

The disk-shaped portion 2 of the clutch housing 21
Clutch center 15 and nut located at the center of 1a
A cover 22 for covering the clutch housing 21 is integrally attached to the disc-shaped portion 21a of the clutch housing 21 with bolts 23, and a weight cam 24 is loosely fitted into an opening 21d of the clutch housing 21. The weight cam 24 is pivotally supported by a support ring 25 sandwiched between the portion 21a and the locking claw 21e.

Further, as shown in FIG. 6, a large number of engagement recesses 14c are formed at equal intervals in the circumferential direction on the outer peripheral portion 14a of the centrifugal clutch inner 14, so that the engagement of the inner Clutch plate in mating recess 14c
26 are fitted with the inner peripheral projections 26a. Friction plates 27 are integrally attached to both side surfaces of the clutch plate 26.

Further, as shown in FIG. 3, outer projections 28a of two pressure plates 28 are provided on the overhanging portions 21c of the clutch housing 21.
And the two pressure plates 28
Among them, a guide pin 29 is integrally caulked in several places in the circumferential direction on the right pressure plate 28 toward the left, and the tip of the guide pin 29 is loosely fitted to the left pressure plate 28. And a coil spring is attached to the guide pin 29.
The spacer 30 is integrally crimped to the left side surface of the right pressure plate 28 at several places in the circumferential direction. The inner surface of the overhang portion 21c of the clutch housing 21 functions as a stopper, and the pressure plate 28 rotates integrally with the clutch housing 21.

When the crankshaft 8 and the clutch center 15 are stopped or rotating at a predetermined rotational speed or less, a large centrifugal force does not act on the weight cam 24, and the clutch plate 26 and the pressure plate 28 As shown in FIG. 3, the clutches are separated from each other and the clutch is disconnected.

Further, when the crankshaft 8 and the clutch center 15 rotate clockwise in FIG. 5 and FIG. 6 at a predetermined rotational speed or more, the weight cam 24 shown in FIG. 4 swings in the clockwise direction and tilts as shown in FIG. 4. The right pressure plate 28 is pushed leftward by the tilt of the weight cam 24, and the clutch plate 26 and the pressure plate
28 is pressed against each other via a friction plate 27, and the rotational torque of the crankshaft 8, that is, the clutch center 15 is transmitted to the centrifugal clutch inner 14 by the frictional force of the pressing.

Further, an output gear 33 is integrally formed on the left end of the centrifugal clutch inner 14, and a serration gear 34 is disposed adjacent to the output gear 33, and corresponds to a clutch housing of a switching clutch 36. A gear 38 is formed on the clutch outer 37 which is engaged with the output gear 33 and the serration gear 34, and the serration gear 34 is switched by the spring force of the spring 35 to the gear of the clutch 36.
It is constantly pressed against the 38 power non-transmission side gears to eliminate backlash.

In addition, a kick starter gear (not shown) or an output gear of a starter motor (not shown) is meshed with the output gear 33 integrated with the centrifugal clutch inner 14, and a kick pedal (not shown) is depressed or the starter motor is started. 5, a clockwise torque is applied to the output gear 33, the one-way clutch 17 is connected, and the crankshaft 8 is driven to rotate clockwise in FIG.
The single cylinder OHC 4-stroke cycle internal combustion engine 0 is started.

A flanged tubular body 40 is spline-fitted to the main shaft 39, which is an output shaft of the switching clutch 36, and is fixed so as not to be pulled out by a nut 41. The tubular portion 40a of the flanged tubular body 40 A thick disk-shaped torque receiving member 42 is relatively rotatably fitted to the thick disk-shaped torque receiving member 42, and is fixed immovably in the axial direction by a circlip 43 in contact with the right end surface. A clutch outer 37 is rotatably fitted on the outer peripheral surface of the member 42, and is fixed immovably in the axial direction by a circlip 44 that is in contact with the left end surface of the torque receiving member 42.

Further, on the inner peripheral surface of the clutch outer 37, a plurality of axially extending ridges 37a are formed in the circumferential direction, and recesses (which can be engaged with the ridges 37a of the clutch outer 37). (Not shown) is formed on the outer peripheral portion 45a of the clutch plate 45, and the clutch inner 46 is located on the center side of the clutch outer 37 and the tubular portion 40 of the flanged tubular body 40 is formed.
a.

Further, on the outer peripheral surface of the clutch inner 46, a plurality of protruding ridges 46a extending in the circumferential direction are formed in the circumferential direction, and the recesses can be engaged with the protruding ridges 46a of the clutch inner 46. (Not shown) are formed on the inner peripheral portion 47a of the pressure plate 47, and the clutch plates 45 and the pressure plates 47 are alternately overlapped with each other, and are formed on the torque receiving member 42 and the right side plate portion 46b of the clutch inner 46. They can be sandwiched and come into contact with each other.

The left side plate portion 4 of the clutch inner 46
A projection 46d projecting leftward is formed on 6c, and a recess 42a is formed on the right side surface of the torque receiving member 42, so that the torque receiving member 42 and the clutch inner 46 can rotate integrally. I have.

The left side plate portion 46 of the clutch inner 46
A cone disc spring 48 is loosely fitted to the tubular portion 40a of the flanged tubular body 40 at a position on the right side of FIG. In addition, a spring receiving portion 50 is disposed near an end of the tubular portion 40a of the flanged tubular body 40, and a circlip 51 for locking the spring receiving portion 50 is provided.
Is fitted into the tubular portion 40a of the flanged tubular body 40, and the clutch inner 46 is urged toward the torque receiving member 42 by the spring force of the cone disk spring 48. In a normal state, the clutch plate 45 and the pressure Plate 47
Are pressed against each other so that the switching clutch 36 is connected.

Further, three or more holes 48a are formed at equal intervals in the circumferential direction in the cone disk spring 48, and the clutch inner 46 has a cylindrical shape at a position corresponding to the hole 48a of the cone disk spring 48. A portion 46e is formed, and the clutch inner 46 and the pull-out member 52 are integrally connected by a bolt 53 that penetrates the disk portion 52a of the pull-out member 52 and is screwed to the cylindrical portion 46e of the clutch inner 46. I have.

Further, the cylindrical portion 52 of the drawer member 52
b, a drawer shaft 55 is rotatably fitted through a bearing 54, and an operating member 56 is connected to the right end of the drawer shaft 55. The operating member 56 overcomes the spring force of the cone disk spring 48 to move the operating member 56 to the right. To the drawer 52
The clutch inner 46 also moves to the right in conjunction with this, the mutual pressure contact between the clutch plate 45 and the pressure plate 47 is released, and the switching clutch 36 is cut off.

The main shaft 39 and a counter shaft (not shown) parallel to the main shaft 39 are provided with a plurality of gears, respectively, to form a gear transmission.

Further, the disk portion 40 of the flanged tubular body 40
b and a portion adjacent to the torque receiving member 42, semi-cylindrical recesses 40c and 42b are formed.
A coil spring damper 57 is interposed in 2b.

Since the embodiment shown in FIGS. 1 to 7 is configured as described above, when the crankshaft 8 is stopped or is rotating at a predetermined rotational speed or less, as shown in FIG. Meanwhile, a large centrifugal force does not act on the weight cam 24, and the automatic centrifugal clutch 13 for starting is in a disconnected state.

When the rotation speed of the crankshaft 8 exceeds a predetermined rotation speed, the pressure plate 28 is pressed against the clutch plate 26 by the centrifugal force acting on the weight cam 24 as shown in FIG. The automatic centrifugal clutch 13 is connected, and the torque of the crankshaft 8 is transmitted to the clutch outer 37 of the switching clutch 36.

The clutch housing 21 of the starting automatic centrifugal clutch 13 is formed by stamping and pressing a steel plate.
A disk-shaped portion 21a, an outer peripheral portion 21b of the clutch housing 21,
Since the overhang portion 21c, the opening 21d, and the locking claw 21e are simultaneously and integrally formed, a large number of complicated molds are not required, the number of parts and the number of processing steps can be reduced, and the clutch housing 21 is formed of a thin copper plate. As a result, the productivity that can be configured can be increased, so that the weight can be reduced and the cost can be significantly reduced.

Further, in the normal state in which the operating force to the right does not act on the operating member 56, the switching clutch 36 is in the connected state, so that when the rotation speed of the crankshaft 8 exceeds a predetermined rotation speed, the starting Since the automatic centrifugal clutch 13 is also in the connected state, the main shaft 39 is also driven to rotate.

Further, when the starting automatic centrifugal clutch 13 and the switching clutch 36 are in the connected state (FIG. 4), when the operating member 56 is operated rightward,
The switching clutch 36 is disengaged, the rotational torque is not transmitted to the main shaft 39, and the main shaft 39
It is also possible to selectively switch the meshing of the gears provided respectively on the countershafts arranged adjacently and in parallel. By performing the on / off operation of the switching clutch 36 and the speed change operation of the gear transmission, the motorcycle (not shown) can run at a required speed ratio.

Further, since the gear 38 is formed integrally with the clutch outer 37 of the switching clutch 36,
The axial dimension of the entire switching clutch 36 is reduced, so that the number of parts of the switching clutch 36 can be reduced, the structure can be simplified, the size and weight can be reduced, and the cost can be reduced.

Further, the fluctuation of the torque applied to the clutch outer 37 of the switching clutch 36 by the starting automatic centrifugal clutch 13 is absorbed by the mutual slip between the clutch plate 45 and the pressure plate 47, and then the flanged tubular body 40 The torque is further absorbed by the coil spring damper 57 interposed between the gear shaft and the torque receiving member 42, so that a large torque fluctuation is not applied to the gear teeth provided on the main shaft 39 and the counter shaft (not shown), Durability is improved.

Since the large driving torque generated when the switching clutch 36 is connected is absorbed by the coil spring damper 57, the power transmission side gear transmission input from the switching clutch 36 The impact force due to the switching operation of the clutch 36 is not easily transmitted.

In the above embodiment, the case where the configuration of the present invention is applied to a multiple disc switching clutch has been described. However, the configuration of the present invention is not limited to the multiple disc switching clutch,
It can be applied to other types of switching clutches. Further, in the above-described embodiment, an example in which a spring is used as the damper has been described, but the damper is not a spring,
A damper using hydraulic pressure may be used.

[Brief description of the drawings]

FIG. 1 is an external view of a single-cylinder OHC four-stroke cycle internal combustion engine including a multi-plate clutch according to an embodiment of the present invention.

FIG. 2 is a vertical sectional view of a main part of the internal combustion engine.

FIG. 3 is a longitudinal sectional view of a multiple disc clutch according to one embodiment of the present invention.

FIG. 4 is a diagram illustrating the operation of the multi-plate clutch.

FIG. 5 is a front view of a housing of the automatic centrifugal clutch for starting in the embodiment.

FIG. 6 is a cross-sectional view of a housing of the automatic centrifugal clutch for starting.

FIG. 7 is a partially enlarged sectional view of a one-way clutch of the automatic centrifugal clutch for starting.

[Explanation of symbols]

0 ... single cylinder OHC 4-stroke cycle internal combustion engine, 1 ...
Cylinder block, 2 ... cylinder head, 3 ... right crankcase, 4 ... left crankcase, 5 ... cylinder bore, 6 ... bolt, 7 ... piston, 8 ... crankshaft, 9 ...
Ball bearing, 10 connecting rod, 11 main shaft, 12 output shaft, 13 automatic centrifugal clutch for starting, 14 centrifugal clutch inner, 14a outer disk portion, 14b inner circumferential surface of circular recess, 14c engagement Recessed part, 15: clutch center, 15a: outer peripheral surface, 15b: concave surface of clutch cam, 16: nut, 17: one-way clutch, 18: retainer, 18a: roller holding hole, 19: roller, 20: spring, 21: clutch housing, 21a: disk-shaped part, 21b: outer peripheral part, 21c ...
Overhang, 21d ... opening, 21e ... locking claw, 22 ... cover,
23… bolt, 24… weight cam, 25… support ring, 26…
Clutch plate, 26a ... circumferential projection, 27 ... friction plate, 28 ...
Pressure plate, 28a: outer peripheral projection, 29: guide pin, 30: coil spring, 31: spacer, 33: output gear, 34: serration gear, 35: spring, 36: switching clutch, 37: clutch outer, 37a: projection Strip, 38 ... gear, 39 ... main shaft, 40 ... flanged tubular body, 40a ...
Tubular part, 40b disk part, 40c semi-cylindrical concave part, 41 nut, 42 torque receiving member, 42a concave part, 42b semi-cylindrical concave part, 43 circlip, 44 circlip, 45 clutch Plate, 45a: outer periphery, 46: clutch inner,
46a: ridge, 46b: right side plate, 46c: left side plate, 46d
... Projection, 46e ... Cylindrical part, 47 ... Pressure plate, 47a
... inner peripheral part, 48 ... cone disk spring, 48a ... hole,
49 ... spring receiving part, 50 ... spring receiving part, 51 ... circlip, 52 ... drawer member, 53 ... bolt, 54 ... bearing, 55 ... drawer shaft, 56 ... operating member, 57 ... coil spring damper.

Continuing from the front page (72) Inventor Takashi Kaneshiro 1-4-1 Chuo, Wako-shi, Saitama Pref. Inside of Honda R & D Co., Ltd. (72) Inventor Masashi Rikui 1-4-1 Chuo, Wako-shi, Saitama Co., Ltd. F-term in Honda R & D Co., Ltd. (reference) 3J056 AA60 AA63 BA03 BB16 BE27 CB14 CX12 CX23 CX74 CX82 DA02 GA02 GA13

Claims (1)

[Claims] An output shaft of an output shaft of an internal combustion engine and an input shaft of a gear transmission in which a gear ratio is switched by a shift operation, wherein the clutch is switched on and off by a switching operation. A switching clutch, wherein a damper is interposed between a member and a driven member connected to an input shaft of the gear transmission.