WO2022190685A1

WO2022190685A1 - Clutch device and clutch outer used therein

Info

Publication number: WO2022190685A1
Application number: PCT/JP2022/002842
Authority: WO
Inventors: 紀彦横山; 真吾金原; 英紀永坂; 友太横道
Original assignee: 株式会社エフ・シー・シー
Priority date: 2021-03-10
Filing date: 2022-01-26
Publication date: 2022-09-15
Also published as: JP2024051103A; CN116867983A; JP2022138617A; JP7449255B2

Abstract

This clutch device is configured such that: a gear (13) having a plurality of through-holes (13d) and an outer (15) having a plurality of leg bosses (15d) in a quantity equal to that of the plurality of through-holes (13d) are disposed so as to oppose each other; and dampers (16) in a quantity less than that of the plurality of through-holes (13d) are provided to first through-holes (13d_-1) only. In a state where the first through-holes (13d_-1) have mounted therein the dampers (16) whereas a second through-hole (13d_-2) has mounted therein no dampers (16), by making a second leg boss (15d_-2) to be in a thickened-shape so as to balance the weight in the positions of the plurality of through-holes (13d) as a whole, it becomes possible to maintain a balanced-weight state as a whole, even if holes without the dampers (16) are provided.

Description

Clutch device and clutch outer used therefor

The present invention relates to a clutch device and a clutch outer used therein, and is particularly suitable for use in a clutch device provided with a damper for absorbing vibration between the clutch outer and the gear.

Generally, a damper made of an elastic material such as rubber is used in a clutch device that has the role of transmitting or blocking engine power to a transmission (see Patent Document 1, for example). A damper is installed between the clutch outer (housing) and the gear, which are two rotating members, and is a shock absorber that uses elastic deformation to absorb vibrations that occur when the engine crankshaft rotates and the clutch engages. be.

FIG. 7 is a diagram showing a partial configuration example of a conventional clutch device disclosed in Patent Document 1. FIG. In the configuration of FIG. 7, six bosses (columnar protrusions) 102a and 102b formed in the housing are inserted into six holes 101a and 101b provided in the gear 101, and the hole 101a is inserted. , 101b and

bosses

102a, 102b, respectively. In the configuration shown in FIG. 7,

bosses

102a and 102b having two different shapes are used.

By the way, there is a need to reduce the number of dampers used for the purpose of reducing costs. However, if the number of dampers used is reduced too much, there arises a problem that the damping performance as a whole deteriorates. Therefore, it is conceivable to reduce only one damper. If one damper is eliminated, the boss of the clutch outer corresponding to that location is also unnecessary. However, if a set of dampers and bosses are eliminated, the weight balance as a rotating member is deteriorated, and there is a possibility that abnormal vibrations and accompanying abnormal wear of each part may occur.

Japanese Utility Model Laid-Open No. 4-39450

The present invention has been made to solve such problems, and it is an object of the present invention to suppress the occurrence of abnormal vibration and abnormal wear even when some dampers are abolished. do.

In order to solve the above-described problems, in the present invention, a gear having a plurality of holes and an outer having a plurality of columnar protrusions of the same number as the plurality of holes are arranged so as to face each other in a power transmission path. In a clutch device in which dampers are provided in only some of the holes, the number of which is smaller than the number of holes provided in the gear, the dampers are interposed in some of the holes and are separated from the other holes. The plurality of holes and the plurality of columnar protrusions are configured so that the weights at the positions of the plurality of holes are balanced as a whole when dampers are not interposed in the holes.

According to the present invention configured as described above, even if holes without dampers are provided, it is possible to prevent deterioration of the overall weight balance of the rotating member. As a result, even if some dampers are abolished, it is possible to suppress the occurrence of abnormal vibration and accompanying abnormal wear in each part.

It is a figure which shows the whole structural example of the clutch apparatus by this embodiment. It is a perspective view showing a configuration example of a clutch outer according to the present embodiment. It is a figure showing an example of important section composition of a clutch device by this embodiment. FIG. 5 is a diagram showing a state in which the second foot boss contacts the through hole in the clutch device of the present embodiment; It is a figure which shows the other structural example of the clutch apparatus by this embodiment. It is a figure which shows the other structural example of the clutch apparatus by this embodiment. It is a figure which shows the example of a partial structure of the conventional clutch apparatus.

An embodiment of the present invention will be described below based on the drawings. FIG. 1 is a diagram showing an example of the overall configuration of a clutch device according to this embodiment. Here, as an example of a clutch device, a longitudinal sectional view of a wet multi-plate clutch provided on an input shaft 11 of a transmission of a motorcycle is shown. FIG. 2 is a perspective view showing a configuration example of the clutch outer 15 (hereinafter simply referred to as the outer) used in the clutch device of this embodiment. FIG. 3 is a diagram showing a configuration example of a main part of the clutch device according to the present embodiment, and shows a state in which the driven side gear 13 and the outer 15 are arranged to face each other.

As shown in FIG. 1, the clutch device of this embodiment is fixed to a driven side gear 13 and an outer 15, which are two rotating members arranged to face each other in a power transmission path, and an input shaft 11. It comprises a clutch center 14 , a plurality of dampers 16 provided between the driven side gear 13 and the outer 15 , a plurality of driving side discs 17 and a plurality of driven side discs 18 .

The driven side gear 13 corresponds to the gear in the claims, and is rotatable on the input shaft 11 so as to mesh with a driving side gear (not shown) fixed to the crankshaft of the engine. be supported. The outer 15 is formed by die-casting a light alloy (for example, an aluminum alloy), and is arranged between the clutch center 14 and the driven side gear 13 so as to surround the clutch center 14 . A plurality of drive-side discs 17 are engaged with the inner peripheral side of the outer 15 so as to be slidable in the axial direction. A plurality of driven side discs 18 are arranged so as to alternately overlap with a plurality of drive side discs 17, and are engaged with the outer peripheral side of the clutch center 14 so as to be slidable in the axial direction.

The clutch center 14 is integrally provided with a pressure-receiving plate 21 that faces the drive-side disk 17 located on the outermost side of the outer 15 on the open end side. A pressure plate 22 capable of pressing the drive-side disc 17 and the driven-side disc 18 toward the pressure-receiving plate 21 is arranged to face the drive-side disc 17 located on the innermost side of the outer 15 . When the pressure plate 22 is moved in the direction of arrow B, the clutch is turned off (power cutoff state), while when it is moved in the direction of arrow A, the clutch is turned on (power transmission state).

As shown in FIGS. 1 and 2, the outer 15 includes a cylindrical portion 15a coaxially surrounding the clutch center 14, and an end wall portion 15b connected to one end of the cylindrical portion 15a and facing the driven side gear 13. have as one. The end wall portion 15b is provided with a through-hole 15c in the central portion through which the support cylindrical portion 13e of the driven side gear 13 is inserted, and a plurality of foot bosses 15d _-1 , which are columnar projections, are provided around the through-hole 15c. , 15d _-2 (hereinafter collectively referred to as foot bosses 15d).

As shown in FIG. 3, the driven-side gear 13 includes a cylindrical portion 13a connected to a driving-side gear (not shown) and an end wall portion 13b connected to one end of the cylindrical portion 13a and facing the end wall portion 15b of the outer 15. and are integrated. A through-hole 13c through which the input shaft 11 is inserted is provided in the center of the end wall portion 13b, and a plurality of through-

holes

13d _-1 and 13d _-2 (hereinafter collectively referred to as through-holes 13d-1 and 13d-2) are provided around the through-hole 13c. 13d) is provided. 13 d of through-holes are equivalent to the hole of a claim.

In the present embodiment, the plurality of through holes 13d are cylindrical holes with a circular cross section and all have the same shape and size. The depth of the through hole 13 d is substantially the same as the height of the foot boss 15 d of the outer 15 and the height of the damper 16 . A plurality of foot bosses 15d of the outer 15 are inserted into the plurality of through-holes 13d, and a portion of the through-holes 13d _-1 and a portion of the foot bosses 15d inserted into the portion of the through-holes 13d _-1 are inserted. A damper 16 is interposed between _-1 .

In the present embodiment, there are six through-holes 13d, of which five through-holes 13d _-1 (hereinafter referred to as first through-holes 13d _-1 ) in which dampers 16 are interposed, There is one other through hole 13d _-2 (hereinafter referred to as a second through hole 13d _-2 ) in which the damper 16 is not interposed. The six through-holes 13d are provided at a plurality of symmetrical positions as a whole (point-symmetrical positions with respect to the center of the driven side gear 13). That is, the six through-holes 13 d are provided at positions such that the shape of the six through-holes 13 d connecting their respective center points is a regular hexagon, and the center of the regular hexagon coincides with the center of the driven side gear 13 . Among them, the five second through-holes 13d _-2 in which the dampers 16 are not interposed are located at non-symmetrical positions.

The leg bosses 15d of the outer 15 to be inserted into these through holes 13d are provided in six, the same number as the through holes 13d. Like the six through holes 13d, the six foot bosses 15d are also provided at a plurality of symmetrical positions as a whole. Of the six leg bosses 15d, five leg bosses 15d _-1 (hereinafter referred to as first leg bosses 15d _-1 ) are inserted into the first through holes 13d _-1 , and one leg boss 15d _- 1 is inserted into the first through hole 13d-1. ₂ (hereinafter referred to as the second foot boss 15d _-2 ) is inserted into the second through hole 13d _-2 . The first foot boss 15d _-1 corresponds to the first columnar protrusion in the claims, and the second foot boss 15d _-2 corresponds to the second columnar protrusion in the claims. As shown in Figures 2 and 3, the first foot boss 15d _-1 and the second foot boss 15d _-2 have different shapes (more on this later).

The damper 16 is made of an elastic material such as rubber, and has a through-hole 16a formed in its central portion with a cross-sectional shape similar to that of the first foot boss 15d _-1 . The first foot boss 15d _-1 passes through a through hole 16a in the central portion of the damper 16. As shown in FIG. As shown in FIG. 1, a retainer plate 19 is arranged at the upper end of the damper 16, and the retainer plate 19 is fixed to the tip surface of the first foot boss 15d _- 1 by rivets 20. As shown in FIG. As a result, the damper 16 is held between the retainer plate 19 and the end wall portion 15b.

By inserting the dampers 16 only in the five first through-holes 13d _-1 and not inserting them in the second through-holes 13d _-2 , the arrangement positions of the five dampers 16 lose their symmetry. If this is left as it is, the weight balance as a rotating member will be lost. On the other hand, in this embodiment, the second leg boss 15d- ₂ inserted into the second through hole 13d-2 in which no damper 16 is interposed is replaced by the first foot boss 15d _-2 in which five dampers 16 are interposed. It is made different from the shape of the first leg boss 15d _-1 inserted into the through hole 13d _-1 . As a result, in a state where the damper 16 is inserted in the first through-hole 13d _-1 and the damper 16 is not inserted in the second through-hole 13d _-2 , the weight at the position of the plurality of through-holes 13d is as a whole trying to balance.

Specifically, the second foot boss 15d _-2 is made larger than the first foot boss 15d _- 1, and one first foot boss 15d _-1 and one damper are provided. 16 and the weight of the second foot boss 15d _-2 are made substantially equal. That is, while the second foot boss 15d _-2 has the same height as the first foot boss 15d _- 1, the cross-sectional area of the second foot boss 15d _-2 is larger than the cross-sectional area of the first foot boss 15d _-1 . The second foot boss 15d _-2 is formed thicker than the first foot boss 15d _-1 so as to be larger. In the example of FIG. 3, the thickness of the second foot boss 15d _-2 is increased in comparison with the thickness of the first foot boss 15d _-1 in the circumferential direction of the outer 15 and in the radial direction outward from the center of the outer 15. ing.

As a result, even if the damper 16 arranged in the second through hole 13d _-2 of the six through holes 13d is omitted for the purpose of cost reduction or the like, the overall weight balance of the rotating member deteriorates. can be prevented. As a result, even if some of the dampers 16 are eliminated, it is possible to suppress the occurrence of abnormal vibration and accompanying abnormal wear in each part of the clutch device.

In the clutch device of the present embodiment configured as described above, the damper 16 vibrates due to fluctuations in rotation of the crankshaft of the engine, engagement of the clutch, etc. during running of the motorcycle equipped with the clutch device. vibration is absorbed by elastic deformation. At this time, if the torsion angle of the driven side gear 13 with respect to the outer 15 becomes too large, the damper 16 is greatly deformed, which may accelerate the elastic fatigue of the damper 16 or cause damage.

In contrast, according to the clutch device of the present embodiment, the damper 16 is not arranged in the second through-hole 13d _-2 , and the thickness of the outer 15 is increased in the circumferential direction. A foot boss 15d _-2 is inserted into the second through hole 13d _-2 . As a result, the gap distance between the second foot boss 15d _-2 and the wall surface of the second through hole 13d _-2 is the gap between the first foot boss 15d _-1 and the wall surface of the first through hole 13d _-1 shorter than the distance.

Therefore, as shown in FIG. 4, before the elastic deformation of the damper 16 in the first through-hole 13d _-1 becomes too large, the second foot boss 15d _-2 is pushed into the second through- hole 13d _- 1. ₂ , and the second foot boss 15d _-2 functions as a stopper that restrains the rotation of the driven side gear 13. As shown in FIG. As a result, excessive elastic deformation of the damper 16 can be suppressed without configuring the stopper as a separate part from the second foot boss 15d _-2 .

Here, the second foot boss 15d _-2 has a shape in which at least a portion of the side surface of the outer 15 located in the circumferential direction is in surface contact with at least a portion of the wall surface of the second through-hole 13d _-2 . It is configured. That is, in the cross-sectional shape of the second foot boss 15d _-2 , the shape of the side located in the circumferential direction of the outer 15 has the same diameter as the diameter of the circle that is the cross-sectional shape of the second through hole 13d _-2 . , and the side surface of the second foot boss 15d _-2 in the arc-shaped portion is in surface contact with the wall surface of the second through hole 13d _-2 . As a result, the surface pressure when the second foot boss 15d- ₂ comes into contact with the wall surface of the second through hole 13d _-2 can be reduced, and damage to the second foot boss 15d _-2 can be suppressed.

In the above-described embodiment, an example is described in which there are six through-holes 13d, of which the second through-hole 13d _-2 in which the damper 16 is not interposed is one, but the present invention is not limited to this. . That is, while the driven side gear 13 is provided with a plurality of through holes 13d, any clutch device in which the damper 16 is arranged only in a part of the first through holes 13d _- 1 among them is the present invention. It is possible to implement the invention. Here, among the plurality of through-holes 13d arranged at a plurality of positions having symmetry as a whole, the first through-hole 13d _-1 in which the damper 16 is interposed is located at a position without symmetry. The present invention can of course be applied to a clutch device in which the first through-holes 13d _-1 are located at symmetrical positions. The present invention can also be applied to a clutch device having a driven side gear 13 in which a plurality of through holes 13d are arranged at a plurality of positions that do not have symmetry as a whole.

For example, the present invention can be applied to a clutch device having eight through holes 13d and eight foot bosses 15d and six dampers 16. FIG. In this case, six of the eight are the first foot bosses 15d _-1 , two are the second foot bosses 15d _-2 , and six first foot bosses are provided for the six through-holes 13d. The foot boss 15d _-1 is inserted to interpose the damper 16, and the two second foot bosses 15d _-2 are inserted into the two second through-holes 13d _-2 . A plurality of foot bosses 15d are configured to be balanced as a whole. The present invention can also be applied to a clutch device having five or seven through-holes 13d and foot bosses 15d and a smaller number of dampers 16, for example.

In the above embodiment, the second foot boss 15d _-2 has a shape different from that of the first foot boss 15d _-1 to balance the overall weight. Not limited. For example, as shown in FIG. 5, all the foot bosses 15d are the same first foot boss 15d _-1 , and the damper 16 is inserted in the second through hole 13d _-2 ' in which the damper 16 is not inserted. It may be configured to be smaller than the first through hole 13d _-1 .

That is, as shown in FIG. 5, the diameter of the circle that is the cross-sectional shape of the second through hole 13d _-2 ′ is made smaller than the diameter of the circle that is the cross-sectional shape of the first through hole 13d _-1 . . As a result, the thickness of the end wall portion 13b at the portion where the second through hole 13d _-2 ′ is formed is greater than the thickness of the end wall portion 13b at the portion where the first through hole 13d _-1 is formed. growing. By adjusting the diameter of the second through-hole 13d _-2 ' so that the weight difference due to the difference in wall thickness of the end wall portion 13b is approximately the same as the weight of one damper 16, the first through-hole In a state where the damper 16 is inserted in the hole 13d _-1 and the damper 16 is not inserted in the second through-hole 13d _-2 ', the weight at the position of the plurality of through-holes 13d is balanced as a whole. is possible.

As another example, as shown in FIG. 6, the second foot boss 15d _-2 ' has the same shape and size as the first foot boss 15d _-1 , and all of the plurality of through holes 13d have the same shape and size. Above, by constructing the second foot boss 15d _-2 ' from a material heavier than the first foot boss 15d _-1 , the damper 16 is interposed in the first through hole 13d _-1 and the second foot boss 15d -1 is inserted. In a state where the damper 16 is not interposed in the through-holes 13d _-2 ′, the weight at the positions of the through-holes 13d may be balanced as a whole.

Further, in the above embodiment, the second leg boss 15d _-2 is thickened in the circumferential and radial directions of the outer 15, but it may be thickened only in the circumferential direction. However, it is possible to increase the contact area between the side surface of the second foot boss 15d _-2 and the wall surface of the second through hole 13d _-2 by making the structure thicker in the radial direction as well. It is preferable in that the surface pressure of can be made smaller.

Also, in the above embodiment, the case where the present invention is applied to a wet multi-plate clutch for a motorcycle has been described, but it is also possible to apply the present invention to a clutch in an automatic transmission of a four-wheeled vehicle.

In addition, each of the above-described embodiments merely shows an example of specific implementation of the present invention, and the technical scope of the present invention should not be construed as being limited by this. Thus, the invention may be embodied in various forms without departing from its spirit or essential characteristics.

13 Driven side gear (gear)
13d through hole (hole)
13d _-1 first through hole (partial hole)
13d _-2 , 13d _-2 ' second through hole (another hole)
15 Clutch outer (outer)
15d Foot boss (columnar protrusion)
15d _-1 First leg boss (first columnar protrusion)
15d _-2 , 15d _-2 ' Second leg boss (second columnar protrusion)
16 Damper

Claims

a gear and an outer, which are two rotating members arranged to face each other in the power transmission path;
A plurality of dampers provided between the gear and the outer,
The gear has a plurality of holes,
The outer has a plurality of columnar protrusions inserted into the plurality of holes of the gear, the same number as the plurality of holes,
The plurality of dampers are provided in a number smaller than the number of the plurality of holes, and are interposed between some of the plurality of holes and the columnar projections inserted into the part of the holes. dressed,
In a state in which the dampers are inserted in some of the holes and the dampers are not inserted in holes other than the one of the holes, the weights at the positions of the plurality of holes are balanced as a whole. A clutch device comprising a plurality of holes and the plurality of columnar projections.
All of the plurality of holes have the same shape and size,
The plurality of columnar protrusions include a first columnar protrusion inserted into the part of the hole in which the damper is interposed, and a second columnar protrusion inserted into the other hole in which the damper is not interposed. and a protrusion;
The second columnar projection is made different from the first columnar projection so that the weight at the positions of the plurality of holes is balanced as a whole when the dampers are interposed in some of the holes. 2. A clutch device according to claim 1, characterized in that there is a
The clutch device according to claim 2, characterized in that the second columnar protrusion is thicker at least in the circumferential direction of the outer than the first columnar protrusion.
The second columnar projection is configured such that at least a portion of a side surface of the outer circumferentially located surface contacts at least a portion of the wall surface of the separate hole. The clutch device according to claim 3.
3. The method according to claim 2, wherein the second columnar protrusion has the same shape and size as the first columnar protrusion and is made of a material heavier than the first columnar protrusion. clutch device.
all of the plurality of columnar projections have the same shape and size,
2. A clutch device according to claim 1, wherein said another hole in which said damper is not interposed is configured to be smaller than said part of said hole in which said damper is interposed.
The clutch device according to any one of claims 1 to 6, wherein the plurality of holes provided in the gear are provided at a plurality of positions having symmetry as a whole.
The clutch device according to claim 7, characterized in that the part of the holes are present at non-symmetrical positions among the plurality of holes.
The clutch device according to claim 8, characterized in that the number of said plurality of holes is six, and said separate hole in which said damper is not interposed is one.
A clutch outer arranged to face a gear having a plurality of holes in a power transmission path,
a plurality of columnar projections inserted into the plurality of holes of the gear, the same number of columnar projections as the plurality of holes, wherein the plurality of columnar projections are:
a first columnar protrusion inserted into a part of the plurality of holes in which a buffer damper is interposed between the columnar protrusion;
and a second columnar projection inserted into the hole other than the part of the plurality of holes and having no damper interposed between the columnar projection and the second columnar projection. has
In a state where the dampers are inserted in some of the holes and the dampers are not inserted in the other holes, the weight including the dampers at the positions of the plurality of holes is balanced as a whole. A clutch outer, wherein the second columnar projection is different from the first columnar projection.
The second columnar projection is configured such that at least a portion of a side surface of the clutch outer located in the circumferential direction is in surface contact with at least a portion of the wall surface of the separate hole. The clutch outer according to claim 10.