JP2000081064A - Conical spring washer - Google Patents

Abstract

PROBLEM TO BE SOLVED: To hard to generate the stick without increasing the machining cost of each member extremely in a conical spring washer used in a friction mechanism. SOLUTION: A second conical spring washer 101 is a member for giving a repulsion force to both members by being arranged in a compressed state between flanges 64, 65 and bush 19 arranged side by side in the axial direction. The second conical spring washer 101 is provided with a ring shape plate main body and a fulcrum 105. The ring shape plate main body has a prescribed width in a radius direction. The fulcrum 105 is formed on the inner periphery part of the plate main body and supported to the flange 64 while projecting from the other part.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a disc spring and, more particularly, to a disc spring for pressing relatively rotating members of a friction mechanism.

[0002]

2. Description of the Related Art A clutch disk assembly used for a vehicle clutch has a clutch function for connecting and disconnecting to and from a flywheel, and a damper function for absorbing and attenuating torsional vibration transmitted from the flywheel. Have. The clutch disk assembly includes a clutch disk, a pair of input plates fixed to the clutch disk, a hub disposed on an inner peripheral side of the input plate, and elastically connects the hub and the input plate in a rotational direction. An elastic member. The elastic member is disposed between the input plate and the hub, and is compressed in the rotational direction when the two rotate relatively. When the clutch disc is connected to the flywheel, torque is input from the flywheel to the input plate of the clutch disc assembly. The torque is transmitted to the hub via the elastic member, and is output to a shaft extending from the transmission. When torque fluctuations from the engine are input to the clutch disk assembly, relative rotation occurs between the pair of input plates and the hub, and the elastic member is repeatedly compressed in the circumferential direction.

[0003] The clutch disk assembly further includes a friction mechanism. The friction mechanism is disposed between the input plate and the hub, and generates frictional resistance when the two members rotate relative to each other. The friction mechanism is composed of a plurality of washers and urging members. The separation hub type clutch disk assembly
A conventional flange of a hub is separated from a boss to form a hub flange, and the boss and the hub flange are connected in a rotational direction by a low-rigidity elastic member. In this clutch disk assembly, the torsion angle between the input plate and the hub is widened, and two-stage rigidity (low rigidity and high rigidity) can be obtained.

In the above-mentioned conventional separated hub type clutch disk assembly, for example, a small friction mechanism is provided between a retaining plate (one of a pair of input plates) and a hub boss, and the retaining plate and the hub flange are provided. Is provided with a large friction mechanism. A first friction member that contacts the hub flange and further engages with the retaining plate so as to be relatively non-rotatable and movable in the axial direction;
A first cone spring (disc spring) is disposed between the first friction member and the retaining plate and biases the first friction member toward the hub flange. The second friction mechanism is configured to abut the flange of the hub and engage the retaining plate relatively non-rotatably and axially movably.
A second friction member disposed between the friction member and the second friction member and the retaining plate for urging the second friction member toward the flange side;
And a cone spring (disc spring). Generally, the first friction member has a higher friction coefficient than the second friction member, and the first cone spring is set to have a larger urging force than the second cone spring. For this reason, the large friction mechanism has larger friction (high hysteresis torque) than the small friction mechanism
Occurs.

In the first-stage torsional angle range in which the hub flange and the hub rotate relative to each other, the low-rigidity elastic member is compressed,
In the small friction mechanism, the second friction member slides on the flange of the boss. Here, characteristics of low rigidity and low hysteresis torque are obtained. When the hub flange starts to rotate integrally with the boss, a relative rotation thereafter occurs between the hub flange and the pair of input plates. In the second stage range, the highly rigid elastic member is compressed between the hub flange and the pair of input plates, and the second friction member slides on the hub flange in the large friction mechanism. Therefore, characteristics of high rigidity and high hysteresis torque can be obtained.

[0006]

The cone spring (disc spring) in the friction mechanism of the conventional clutch cover assembly is disposed, for example, in an axially compressed state between a retaining plate and a friction member. A repulsive force is given to the member. As a result, the friction plate is pressed against, for example, the hub or the flange in the axial direction.

As a general characteristic, when a cone spring (disc spring) is sandwiched between flat plates and pressed, the load rapidly increases near the close contact. In order to avoid this, relief is provided in the pressurizing section so that the cone spring does not come into close contact even when it becomes flat, for example. Even in the conventional clutch disk assembly, when the cone spring comes into close contact with the flat plate, a large load is generated, and the hysteresis torque in the friction generating portion increases. As means for avoiding the close contact state, in the clutch disk assembly, a step is provided on a member supporting the cone spring so that the member does not adhere to both members even when the cone spring becomes flat. Specifically, a concave portion having a step is formed at a portion corresponding to the inner peripheral side portion of the cone spring in the supporting member where the outer peripheral portion of the cone spring is supported, so as to be further away from the cone spring than the supporting portion. .

On the other hand, providing steps on both sides of the cone spring has the problem of increasing the processing cost of each member. SUMMARY OF THE INVENTION It is an object of the present invention to provide a disc spring used in a friction mechanism, which does not significantly increase the processing cost of each member and makes it difficult to cause close contact. Another object of the present invention is to make a coned disc spring used in a friction mechanism more flexible than a flat one with a simple structure.

[0009]

According to a first aspect of the present invention, there is provided a disc spring for press-contacting relatively rotating members in a friction mechanism that generates friction to attenuate torsional vibration. The disc spring has an annular plate body and a fulcrum. The annular plate body has a predetermined width in the radial direction.
The fulcrum is formed on at least one of the inner and outer peripheral portions of the plate body, protrudes from other portions, and is a structure for being supported by one of the two members.

According to the first aspect of the present invention, since the fulcrum protruding from the other portion is formed on the plate body, the end of the conical spring opposite to the fulcrum is on the side of the fulcrum in the direction of projection. Even if it is flattened in a state where it is pressed, no close contact occurs. In addition, the same effect as that of the related art can be obtained without providing a step in the supporting member that supports the fulcrum, and the processing cost of the supporting member is reduced.

Further, in the case of a member provided with a supporting member as in the conventional case, the amount of deflection of the disc spring is further increased by a combination of the fulcrum of the disc spring and the step.
In this case, for example, the area where the wear margin in the friction mechanism can be effectively used becomes large. According to a second aspect of the present invention, in the first aspect, a plurality of fulcrum portions are formed in the circumferential direction.

According to a third aspect of the present invention, in the second aspect, a plurality of lever portions are formed by a plurality of radially extending slits on one of the inner and outer peripheral portions of the plate body, and the fulcrum portion is formed on the lever portion. Is formed. According to a fourth aspect of the present invention, in the first aspect, the plate body has a conical shape in a free state.

According to the fifth aspect of the present invention, there is provided a disc spring.
In any one of 4, the fulcrum portion is curved such that the surface on the protruding side is convex.

[0014]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Basic Structure FIGS. 1 to 5 show a clutch disk assembly 1 as a basic structure in which a second cone spring (101, 110, 114, 120) as an embodiment of the present invention can be adopted. Is shown. The clutch disk assembly 1 is used for a vehicle clutch. An engine and a flywheel (not shown) are arranged on the left side of the clutch disk assembly in FIGS. 3 to 5, and a transmission (not shown) is arranged on the right side in FIGS. 3 to 5. Hereinafter, the left side in FIGS. 3 to 5 is referred to as a first axial direction side (engine side), and the right side in FIGS.
It is called the axial side (transmission side). O- in each figure
O is the rotation axis of the clutch disc assembly 1, that is, the center of rotation, and the arrow R1 shown in FIG. 1 is the rotation direction (positive side) of the flywheel and the clutch disc assembly 1,
R2 is the opposite rotation direction (negative side).

The schematic clutch disk assembly 1, as shown in the machine circuit diagram of FIG. 6, mainly, the input rotary member 2, a hub 3 (the output rotor)
And a damper mechanism 4 interposed therebetween. The damper mechanism 4 further includes a first damper mechanism 5 that provides a second-stage characteristic of the torsion angle, and a first
And a second damper mechanism 6 that provides the characteristics of the stage. The first damper mechanism 5 and the second damper mechanism 6 are arranged so as to act in series between the input rotary body 2 and the hub 3 via a hub flange 18 (intermediate plate) therebetween.

The first damper mechanism 5 includes a first elastic mechanism 7 including a first spring 16 and a spring 17, and a first friction mechanism 8 that generates friction when the hub flange 18 and the input rotary body 2 rotate relative to each other. And a mechanism for restricting the relative rotation angle between the hub flange 18 and the input rotary body 2, and the torsion angle θ
The first stopper 11 allows relative rotation between the input rotary member 2 and the hub flange 18 by 2 + θ3. The first elastic mechanism 7, the first friction mechanism 8, and the first stopper 11 are arranged between the hub flange 18 and the input rotary body 2 so as to act in parallel.

The second damper mechanism 6 mainly includes a second elastic mechanism 9, a second friction mechanism 10, and a second stopper 12. The second spring 21 of the second elastic mechanism 9 has a smaller spring constant than the first spring 16 of the first elastic mechanism 7. The second friction mechanism 10 is set to generate a smaller friction than the friction generated by the first friction mechanism 8. The second stopper 12 is a mechanism for regulating the relative rotation between the hub 3 and the hub flange 18, and has a torsion angle θ1.
Only the relative rotation between the hub 3 and the hub flange 18 is allowed. The second elastic mechanism 9, the second friction mechanism 10, and the second stopper 12 are arranged so as to act in parallel between the hub 3 and the hub flange 18.

[0018] Detailed description will now be described in detail each structure of the clutch disk assembly 1. The input rotator 2 includes a clutch plate 31
, Retaining plate 32 and clutch disc 3
And 3. The clutch plate 31 and the retaining plate 32 are disk-shaped or annular plate members, and are arranged at a predetermined distance from each other in the axial direction. The clutch plate 31 is arranged on the first axial direction side, and the retaining plate 32 is arranged on the second axial direction side. The outer peripheral portions of the clutch plate 31 and the retaining plate 32 are fixed to each other by a plurality of stop pins 40 arranged in a circumferential direction. As a result, the axial distance between the clutch plate 31 and the retaining plate 32 is determined, and the plates 31 and 32 rotate integrally. Clutch plate 31
The cushioning plate 41 of the clutch disk 33 is fixed to the outer peripheral portion of the vehicle by a plurality of rivets 43. An annular friction facing 42 is fixed to both sides of the cushioning plate 41.

The clutch plate 31 and the retaining plate 32 are formed with a plurality of first housing portions 34 at equal intervals in the circumferential direction. The first housing portion 34 is a portion slightly swelled in the axial direction, and the first support portions 35 are provided on both sides in the circumferential direction.
have. The first support portions 35 face each other in the circumferential direction. Furthermore, the clutch plate 31 and the retaining plate 32 are provided with a plurality of second
An accommodating portion 36 is formed. The second storage section 36 is
It is arranged adjacent to the accommodation section 34 on the R1 side. The second storage section 36 has second support sections 37 on both sides in the circumferential direction. Each second housing portion 36 is formed longer in the radial direction and the circumferential direction than the first housing portion 34. A plurality of bent portions 51 bent toward the second axial direction are formed on the outer peripheral edge of the retaining plate 32. Bending part 5
1 is formed corresponding to the stop pin 40. The bent portion 51 improves the strength of the periphery of the stop pin 40 and the strength of the stop pin 40. Therefore, stop pin 4
0 is the clutch plate 31 and the retaining plate 3
2 can be arranged most radially outward, so that the stopper torque can be increased. Furthermore, since the bent portion 51 does not lengthen the radial direction of the retaining plate 32,
The space in the radial direction can be reduced as compared with the conventional one having the same strength. If the radial space is to be kept as before, the stop pins can be arranged further radially outward than in the prior art. Since the bent portion 51 is formed only partially, the sheet metal material can be saved.

The hub flange 18 has a clutch plate 31
And between the retaining plate 32, that is, between the two members in the axial direction. The hub flange 18 functions as an intermediate member between the input rotating body 2 and the hub 3. The hub flange 18 is a disk-shaped or annular member that is thicker than the plates 31 and 32. A first window hole 57 is formed in the hub flange 18 so as to correspond to the first housing portion 34. The first window hole 57 is formed with respect to the first storage section 34.
The circumferential angle of the first window hole 57 is smaller than the circumferential angle between the first support portions 35 of the first housing portion 34. The center of the first window hole 57 in the rotation direction substantially coincides with the center of the first housing portion 34 in the rotation direction. For this reason, the first window hole 57
A gap having a twist angle θ2 is provided between both ends in the circumferential direction and the first support portion 35 of the first housing portion 34 on both sides in the circumferential direction. The spring 17 is arranged in the first window hole 57. The spring 17 is a coil spring, and both ends in the circumferential direction are in contact with both ends in the circumferential direction of the first window hole 57. In this state, both ends in the circumferential direction of the spring 17 are separated from each other by the torsion angle θ2 with respect to the first support portion 35 of the first housing portion 34.

A second window hole 56 is formed in the hub flange 18 at a position corresponding to the second accommodating portion 36. The length of the second window hole 56 in the radial direction and the circumferential direction is substantially equal to the second housing portion 36. The first spring 16 is arranged in the second window 56. The first spring 16 is an elastic member formed by combining two sets of coil springs, and both ends in the circumferential direction are in contact with both ends in the circumferential direction of the second window hole 56. The circumferential ends of the first spring 16 are in contact with the second support portion 37 of the second housing portion 36. A cylindrical portion 59 extending on both axial sides is formed on the inner peripheral portion of the hub flange 18.
The cylindrical portion 59 has a plurality of inner peripheral teeth 6 extending inward in the radial direction.
1 is formed.

The hub 3 is a cylindrical member arranged in the inner peripheral portions of the plates 31, 32 and the hub flange 18, that is, in the center holes of the respective members. The hub 3 mainly includes a cylindrical boss 62. A plurality of splines 63 are formed in the center hole of the boss 62. The engagement of the splines 63 with the splines of the shaft extending from the transmission enables output from the hub 3 to the shaft. The boss 62 has a flange 64 extending radially outward.
Are formed. In this embodiment, the radial width of the flange 64 is small. The flange 64 is further formed with a plurality of outer peripheral teeth 65 extending radially outward. The outer peripheral teeth 65 may be considered to form a part of a flange extending radially outward from the boss 62. Outer teeth 6
5 has a radial length corresponding to the cylindrical portion 59 of the hub flange 18. The outer teeth 65 extend between the inner teeth 61 in the circumferential direction, and have gaps on both sides in the circumferential direction by a predetermined torsion angle θ1. The torsional angle θ1 on the R2 side as viewed from the outer peripheral teeth 65 is the torsional angle θ1 on the R1 side.
It is set slightly larger than. Each of the inner peripheral teeth 61 and the outer peripheral teeth 65 has a shape in which the circumferential width decreases toward the radial end.

The inner peripheral teeth 61 and the outer peripheral teeth 65 are formed over the entire circumferential direction, so that the area in which they can come into contact is increased. That is, unlike the conventional case, a part of the teeth is omitted to form no notch for disposing the low-rigidity elastic member. As a result, the contact area between the inner peripheral teeth 61 and the outer peripheral teeth 65 is increased. That is, the surface pressure between the two members is reduced, and wear and breakage are less likely to occur. For this reason, high torque characteristics can be realized in a space-saving manner in a case where teeth are partially cut away.

Next, the second damper mechanism 6 will be described. The second damper mechanism 6 includes a hub 3 and a hub flange 18.
And transmit torsion and absorb torsional vibration.
It is for damping. The second of the second damper mechanism 6
The elastic mechanism 9 mainly includes a second spring 21. The second friction mechanism 10 of the second damper mechanism 6 includes a bush 19
And a fixing plate 20 and a second cone spring 78. That is, the second damper mechanism 6 is located at a position displaced in the axial direction from the inner peripheral teeth 61 and the outer peripheral teeth 65 which are the engagement portions between the hub 3 and the hub flange 18. More specifically, the second damper mechanism 6 is arranged to be shifted from the inner peripheral teeth 61 and the outer peripheral teeth 65 toward the transmission. Thereby, a sufficient contact area between the outer teeth 65 and the inner teeth 61 can be secured. Further, the second damper mechanism 6 is provided with the inner peripheral teeth 6.
Since it is not arranged between the first and outer peripheral teeth 65, unlike the related art, a sufficient allowance for the second spring 21 can be secured. As a result, the spring seat can be omitted, and the assemblability of the second spring 21 is improved.

The fixed plate 20 has a second damper mechanism 6
Functions as an input side member. That is, the fixing plate 20 is a member to which the torque from the hub flange 18 is input. The fixing plate 20 is a hub flange 1
8 is a thin plate member made of sheet metal disposed between an inner peripheral portion of the retaining plate 8 and an inner peripheral portion of the retaining plate 32. As shown in FIGS. 8 to 11, the fixing plate 20 includes a first disk-shaped portion 71, a cylindrical portion 72 extending from an inner peripheral edge of the first disk-shaped portion 71 in a second axial direction (transmission side), Cylindrical part 7
2 and a second disk-shaped portion 73 extending further inward in the radial direction.

A spacer 80 is arranged between the first disk-shaped portion 71 of the fixed plate 20 and the hub flange 18. The spacer 80 connects the fixing plate 20 to the hub flange 18 in the rotation direction, and
And has a role of receiving a force acting on the hub flange 18 from the side. The spacer 80 is a ring-shaped resin member, and has a large number of hollow portions for weight reduction. Spacer 8
0 has an annular portion 81 and a plurality of projecting portions 82 projecting radially outward from the annular portion 81. The projection 82 has two notches 83 formed on the outer peripheral edge. Further, a protrusion 84 extends from the protruding portion 82 in the first axial direction and is inserted into an engagement hole 58 formed in the hub flange 18. The projection 84 is engaged with the engagement hole 58 so as to be slightly movable in the radial direction and relatively immovable in the rotation direction.

The first disk-shaped portion 71 of the fixed plate 20 is formed with a plurality of projections 74 projecting radially outward at regular intervals in the circumferential direction. The protrusion 74 is formed corresponding to the protrusion 82 of the spacer 80. The protrusion 74 of the fixing plate 20 has a claw 75 that engages with a notch 83 formed in the protrusion 82 of the spacer 80. In the structure described above, the fixing plate 2
Numeral 0 indicates that the hub flange 18 cannot be rotated relative to the hub flange 18 via the spacer 80, that is, torque can be input from the hub flange 18. Further, the fixing plate 20 is supported on the first axial direction side by the hub flange 18 via the spacer 80. The fixing plate 20 is separated from the spacer 80 and the hub flange 18 by the second
It is movable in the axial direction.

Next, the first friction mechanism 8 formed between the fixed plate 20 and the retaining plate 32 will be described. The first friction mechanism 8 includes a first friction washer 48
And a first cone spring 49.
The first friction washer 48 is provided on the retaining plate 32.
Engages with the shaft so that it cannot rotate relative to
This is a friction member for generating friction by sliding with respect to the fixed plate 20. The first friction washer 48 is mainly made of an annular resin member. The first friction washer 48 has an annular portion 85 made of resin.

In the annular portion 85, a friction material 86 is molded or bonded to the fixed plate 20 side. Friction material 8
Reference numeral 6 denotes a member for increasing the coefficient of friction between the first friction washer 48 and the fixed plate 20, and extends in an annular or disk shape. A plurality of rotation direction engaging portions 87 extending toward the second axial direction are formed on the inner peripheral portion of the annular portion 85.
The rotation direction engaging portion 87 is inserted into a plurality of notches 53 formed in the center hole 52 (inner peripheral edge) of the retaining plate 32. Thereby, the first friction washer 48
Is engaged with the retaining plate 32 so as to be relatively non-rotatable and movably in the axial direction. Further, the annular portion 8
5 is formed with an engaging portion 88 extending radially outward from the outer peripheral edge and further extending therefrom toward the second axial direction. The engaging portion 88 has a relatively thin shape, and a claw portion is formed at the tip. The engaging portion 88 is inserted into the hole 54 formed in the retaining plate 32, and the claw portion is engaged with the retaining plate 32. The engaging portion 88 urges itself radially outward in the engaged state, and is in pressure contact with the hole 54. Therefore, the first friction washer 48 is unlikely to come off the retaining plate 32 even after the sub-assembly is assembled. As described above, the first friction washer 48 has an engaging portion (rotational direction engaging portion 87) for transmitting torque and an engaging portion (engaging portion 88) for temporarily fixing the member to the retaining plate 32. Are separately provided, and the engaging portion 88 is formed into a thin and bendable shape. Since the engaging portion 88 has low rigidity, it is not easily broken at the time of sub-assembly. For this reason, no force is applied to the rotation direction engaging portion 87 at the time of sub-assembly assembling, and the conventional resin friction washer has a radial engaging portion having a claw portion for engaging with the retaining plate. Hard to break even when compared. Further, a press-fitting machine is not required at the time of assembling the sub-assembly, so that equipment costs can be reduced.

The first cone spring 49 is arranged between the first friction washer 48 and the inner peripheral portion of the retaining plate 32, and is arranged to be axially compressed between both members. The first cone spring 49 has an outer peripheral end supported by the retaining plate 32 and an inner peripheral end
It is in contact with the annular portion 85 of the friction washer 48. First
A plurality of notches 49 are provided on the inner peripheral side of the cone spring 49.
a is formed. It may be considered that a plurality of protrusions are formed on the inner peripheral edge by the notch 49a. A projection formed on the outer peripheral side of the rotation direction engaging portion 87 of the first friction washer 48 is inserted into the notch 49a. Thus, the first cone spring 49 is engaged with the first friction washer 48 so as not to rotate relatively.

A plurality of cut-and-raised portions 76 are formed in the second disk-shaped portion 73 of the fixed plate 20 at equal intervals in the circumferential direction. The cut-and-raised portion 76 has a shape cut and raised in the axial direction from the inner peripheral side of the second disk-shaped portion 73, and is arranged on the second axial direction side as compared with other portions of the second disk-shaped portion 73. Have been. In the portion where the cut-and-raised portion 76 is formed, a cutout portion is formed in the second disk-shaped portion 73. Support portions 77 are formed at both ends in the circumferential direction of the cutout portion.

The bush 19 functions as a member on the output side in the second damper mechanism 6, and is engaged with the hub 3 so as not to rotate relatively. More specifically, the bush 1
9 is a cylindrical portion 72 of the fixed plate 20 on the second axial direction side of the inner peripheral teeth 61 of the hub flange 18 and the outer peripheral teeth 65 of the hub 3.
Is a ring-shaped resin member arranged in a space on the inner peripheral side of the boss 62 and on the outer peripheral side of the second axial direction portion of the boss 62. The bush 19 is mainly composed of an annular portion 89 as shown in FIGS. In the annular portion 89, a plurality of spring accommodating portions 90 are formed on the second axial side surface at equal intervals in the circumferential direction. The spring accommodating portion 90 is formed corresponding to the cut-and-raised portion 76 of the fixed plate 20, that is, the notched portion.
The spring accommodating portion 90 is a concave portion formed on the side surface of the bush 19 in the second axial direction. This recess is formed smoothly so as to form a part of a circle in cross section as shown in FIGS. A hole is formed in the center of each spring accommodating portion 90 in the radial and circumferential directions so as to penetrate in the axial direction. Further, a cylindrical inner peripheral support portion 91 extending toward the second axial direction is formed on the inner peripheral portion of the annular portion 89. The inner peripheral surface 91a of the bush 19 including the inner peripheral support portion 91 is
2 is in contact with or close to the outer peripheral surface. Further, a second axial side surface 89 a formed on the annular portion 89 of the bush 19 is in contact with the first axial side surface of the second disk-shaped portion 73 of the fixed plate 20. Here, the annular portion 89 of the bush 19
The second friction mechanism 10 is formed between the second friction member 10 and the second disk-shaped portion 73 of the fixed plate 20.

A second spring 21 is arranged in each spring accommodating portion 90. The second spring 21 includes the first spring 16 and the spring 1
7 is a small coil spring, and has a small spring constant. The second spring 21 is disposed in the spring housing portion 90, and both ends in the circumferential direction are in contact with or close to both ends in the circumferential direction of the spring housing portion 90. The second spring 21 includes a spring housing 90
Inside, the bush 19 supports the inner side in the axial direction (the first axial side) and the inner peripheral side.

At both ends of the second spring 21 in the circumferential direction, support portions 77 of the fixed plate 20 are engaged (contact) in the rotational direction. Thus, the torque from the fixed plate 20 is transmitted to the bush 19 via the second spring 21. The circumferential end surface of the second spring 21 is
The first axial direction side is entirely supported by the circumferential end portion 0. In addition, the support portion 77 supports the end face in the circumferential direction of the second spring 21 in the radial direction. As described above, the allowance of the second spring 21 at both ends in the circumferential direction is large. In other words, the area of the portion supported at both ends in the circumferential direction of the second spring 21 is increased. This is made possible by arranging the second spring at a position shifted in the axial direction from between the conventional hub and the hub flange. As a result, the spring seat can be eliminated and the number of parts is reduced.

The second spring cut-and-raised portion 76 is arranged to support the outside of the second spring 21 in the axial direction (the second axial direction side). In this manner, the second spring 21 is supported by the fixed plate 20 on the outer peripheral side and the outer side in the axial direction. The bush 19 has an engagement portion 99 extending from the annular portion 89 toward the first axial direction. The engaging portion 99 is a protrusion extending in the second axial direction, and is configured to transmit the torque of the bush 19 to the hub 3. The engaging portion 99 has a cross section that matches the gap between the outer teeth 65, and is inserted between the outer teeth 65 of the hub 3 to engage with the outer teeth 65 so as to be immovable in the circumferential direction. I have.

The second cone spring 92 is an urging member for urging the second disk-shaped portion 73 and the annular portion 89 in the second friction mechanism 10 in the axial direction. The second cone spring 92 is disposed between the outer peripheral teeth 65 of the hub 3 and the inner peripheral teeth 61 of the hub flange 18 and the bush 19 in the axial direction. The inner peripheral portion of the second cone spring 92 has the hub 3.
, And an outer peripheral portion thereof is in contact with an annular portion 89 of the bush 19. The second cone spring 92 is compressed in the axial direction, and urges the bush 19 toward the second axial direction. As a result, the second axial side surface 89a of the annular portion 89 of the bush 19 and the first axial side surface of the second disk-shaped portion 73 of the fixed plate 20 are urged in the axial direction by a predetermined force. The second cone spring 92 has smaller inner and outer diameters than the first cone spring 49,
The thickness is also significantly smaller. Thus, the urging force of the second cone spring 92 is much smaller than that of the first cone spring 49. A plurality of notches 92 a are formed on the inner peripheral edge of the second cone spring 92. It may be considered that a plurality of protrusions are formed on the inner peripheral edge by the notch 92a. The above-mentioned engaging portion 99 extends inside the notch 92a.

As described above, the fixing plate 20
Functions as a member on the input side that engages with the second spring 21 in the second damper mechanism 6 and a member that configures the second friction mechanism 10, and also functions as a member that configures the first friction mechanism 8. Hereinafter, advantages of using the fixing plate 20 will be described. As described above, the fixed plate 20 functions as a support member that supports the circumferential ends of the second spring 21 in the second damper mechanism 6 and a member that constitutes the second friction mechanism 10. Since two functions are realized by one member, the number of parts is reduced. Further, the fixing plate 20 also supports the second spring 21 outside in the axial direction. Further, the fixing plate 20
The two friction surfaces of the second friction mechanism 10 that generates friction by sliding at the first stage of the torsional characteristic and the first friction mechanism 8 that generates friction by sliding at the second stage of the torsional characteristic Make up. As described above, since both friction surfaces are formed by one member, it is easy to adjust and manage the friction characteristics of both friction surfaces. Specifically, it is no longer necessary to manage the sliding surfaces of both the boss flange and the hub flange as in the related art. In particular, since the fixing plate 20 has a small and simple configuration unlike a conventional hub or hub flange, it is easy to manage the friction surface. The fixing plate 20 described above is made of sheet metal, and can easily realize a desired shape by press working, and can be realized at low cost.

Next, advantages of the bush 19 will be described. The bush 19 is made of resin and can easily realize a desired shape. In particular, since it is made of resin, the engaging portion 99 can be integrally molded, and the manufacture is easy. Since the engaging portion 99 is engaged between the peripheral teeth 65 of the hub 3 in the circumferential direction, it is not necessary to form a special hole, a concave portion, or the like for engagement in the hub 3. Therefore, the number of processing steps of the hub 3 does not increase. The bush 19 functions as a member on the output side of the second damper mechanism 6, engages with both circumferential sides of the second spring 21, and constitutes a part of the second friction mechanism 10. Since the torque transmission and the friction generator are realized by a single member,
The total number of parts is reduced.

A second cone spring 78 as a member for urging the friction surfaces in the second friction mechanism 10 in the axial direction.
Are supported by the flange 64 of the hub 3. Since the second cone spring 78 is supported by another member instead of being supported by the retaining plate as in the related art, the hysteresis torque in the characteristics of the first stage is stabilized. Therefore, the adjustment of the first-stage hysteresis torque is easy. Conventionally, since both the first urging member and the second urging member are supported by the retaining plate, the retaining plate may be deformed by the urging force of the first elastic member, and therefore, the second urging member may be deformed. There is a problem that the posture of the member changes and the urging force of the second urging member is not stabilized. In this embodiment, the urging force of the first cone spring 49 and the urging force of the second cone spring 78 act on the fixed plate 20 in opposite directions in the axial direction. That is, the first cone spring 49 urges the fixed plate 20 to the first axial direction through the first friction washer 48, and the second cone spring 78 pushes the fixed plate 20 to the second axial direction through the bush 19. It is energizing.

The second stopper 12 has a structure in which torque is not applied to each member of the second damper mechanism 6 in a region where the torque is large. In the second range of torsion characteristics, bush 1
9. No torque acts on the second spring 21 and the fixed plate 20. Therefore, it is not necessary to extremely increase the strength of each member, and the design is easy. Next, the bush 93 provided on the inner peripheral side of the clutch plate will be described.
The bush 93 is provided on the inner peripheral portion of the clutch plate 31, and has an outer peripheral surface of the hub 3, an end surface of the flange 64, and outer peripheral teeth 6.
5, a member that comes into contact with the cylindrical portion 59 and the inner peripheral teeth 61 of the hub flange 18. The function of the bush 93 is to generate friction to attenuate vibration in the rotational direction, to position the clutch plate 31 in the radial direction with respect to the hub 3, to position the hub flange 18 in the radial direction with respect to the hub 3, and the like. There is. As shown in FIGS. 20 to 22, the bush 93 is mainly configured by an annular portion 94 made of resin. The annular portion 94 is a disk-shaped member having a predetermined width in the radial direction and a small thickness in the axial direction. The annular portion 94 is disposed between the inner peripheral portion of the clutch plate 31 and the inner peripheral portion of the hub flange 18 in the axial direction. An annular friction member 95 is molded, bonded, or simply arranged on the second axial direction side of the annular portion 94. The friction member 95 is an annular member having a predetermined width in the radial direction and a small thickness in the axial direction. The friction member 95 is made of, for example, a rubber-based or glass-based blended or impregnated molded product having a high friction coefficient, or a ceramic. The friction member 95 gives the bush 93 a characteristic of a high friction coefficient, and the magnitude of friction can be adjusted by selecting a material.

As shown in the plan view of FIG.
The friction member 95 has a circular inner and outer diameter. The friction member 95 may be considered to be disposed so as to abut on the second axial side surface of the annular portion 94, or is disposed in a groove formed on the second axial side surface of the annular portion 94. May be considered. That is, a cylindrical portion 96 extending in the second axial direction is formed on the inner peripheral edge of the annular portion 94, and the
A cylindrical portion 97 extending in the axial direction is formed. An annular space surrounded by the cylindrical portions 96 and 97 forms a groove of the annular portion 94. The groove has a circular inner and outer diameter, and the friction member 95 is disposed in the groove.

The cylindrical portion 96 is the first portion of the flange 64 of the hub 3.
It is in contact with the axial side surface. This portion slides in the first-stage torsion range. The friction member 95 is in contact with the cylindrical portion 59 of the hub flange 18 and the first axial side end surface of the inner peripheral teeth 61. This portion slides in the torsional range of the second stage. Friction member 95 and hub 3
A slight gap is secured between the outer peripheral tooth 65 and the first axial side surface. The first axial side end surfaces of the cylindrical portion 59 of the hub flange 18 and the inner peripheral teeth 61 are in contact with the friction member 95 only in the axial direction.

The friction member 95 is formed with a plurality of holes 95a arranged in the circumferential direction.
4, the projection 94a is inserted. Thereby, rotation prevention of the annular portion 94 and the friction member 95 is realized. In particular, since the friction member 95 is circular, such a detent plays an important role. Conventionally, when the friction member has a circular shape, there is a possibility that a problem regarding strength such as peeling may occur even if the friction member is adhered to a back plate made of SPCC. For this reason, the friction member is formed into a square shape to prevent rotation.
In the friction member 95 according to the present invention, problems such as peeling are solved while the friction member 95 is kept in a simple structure of a circle. In particular, the formation of the hole 95a of the friction member 95 and the formation of the projection 94a of the resin annular portion 94 are both easy, and cost reduction is realized.

In this embodiment, the friction member 95 is not fixed to the annular portion 94 and can be removed in the axial direction. Therefore, work such as bonding is not required. However,
Also in the configuration of the present invention, the friction member 95 and the annular portion 94 may be bonded or the like. Further, the annular portion 94 is formed with a plurality of holes 94b arranged in the circumferential direction. Hole 9
Reference numeral 4b extends in the axial direction, connects the first axial direction side and the second axial direction side of the annular portion 94, and exposes a part of the first axial side surface of the friction member 95. Also, clutch plate 3
A hole 13 is formed in the inner peripheral portion of the device 1 so as to correspond to the hole 94b. The hole 13 has a larger diameter than the hole 94b and further extends around the hole 94b. A part of the friction member 95 is exposed to the outside of the clutch disc assembly 1 by the holes 94b and the holes 13 formed at the same positions as described above. Therefore, the friction member 95 is sufficiently cooled, that is, the friction member 95 also radiates heat to the atmosphere to the clutch plate 31 side, and a change in friction characteristics due to frictional heat of the friction member 95 is suppressed. Furthermore, the durability of the friction member 95 is improved, and a decrease in the hardness of the hub 3 and the hub flange 18 is prevented. Further, a hole 94c extending in the axial direction and penetrating is formed in the projection 94a. The hole 94c penetrates the first axial direction side and the second axial direction side of the annular portion 94. The holes 94b and 94c reduce the overall volume of the bush 93, thereby reducing the amount of resin used and the cost.

At the inner peripheral edge of the annular portion 94, a cylindrical portion 98 extending toward the first axial direction is formed. Cylindrical parts 96, 98
Has an inner peripheral surface in contact with the outer peripheral surface of the boss 62. Thereby, the clutch plate 31 and the retaining plate 3
2 is positioned (centered) in the radial direction with respect to the hub 3. A groove 98a is formed on the outer peripheral surface of the cylindrical portion 98 to engage with a plurality of protrusions formed on the inner peripheral edge of the clutch plate 31. Thereby, the bush 9
3 is slidable on the flange 64 of the hub 3 and further on the cylindrical portion 59 of the hub flange 18 by rotating integrally with the clutch plate 31.

A plurality of notches 97a are formed in the cylindrical portion 97. The radially inner side surface of the cylindrical portion 97 is in contact with the outer peripheral surface of the cylindrical portion 59 of the hub flange 18 on the first axial direction side. That is, the hub flange 18 is connected to the bush 9.
3, the hub 3 and the clutch plate 3
1 and the retaining plate 32 are positioned in the radial direction.

A plurality of engaging portions 14 extending in the first axial direction are formed on the outer peripheral edge of the annular portion 94. The engaging portions 14 are formed at equal intervals in the circumferential direction. The engaging portion 14 has a claw shape, and is provided with a hole 1 formed in the clutch plate 31.
5 is engaged. Thus, the bush 93 is temporarily fixed to the clutch plate 31 in the axial direction. The bush 93 described above has a friction surface that abuts the outer peripheral surface of the boss 62 to position the clutch plate 31 in the radial direction with respect to the hub 3 and abuts the flange 64 and the cylindrical portion 59, respectively. Generates the first-stage and second-stage hysteresis torque. As described above, by providing a plurality of functions to one member, the number of components as a whole is reduced.

When the clutch disk 33 of the input rotating body 2 is pressed against a flywheel (not shown), torque is input to the clutch disk assembly 1. The torque is transmitted from the clutch plate 31 and the retaining plate 32 in the order of the first spring 16, the hub flange 18, the spacer 80, the fixed plate 20, the second spring 21, and the bush 19, and finally from the hub 3 to a shaft (not shown). Is output.

When torque fluctuations from the engine are input to the clutch disk assembly 1, torsional vibration, that is, relative rotation occurs between the input rotating body 2 and the hub 3, and the first spring 1
6, the spring 17 and the second spring 21 are compressed in the rotation direction. Next, the operation of the clutch disk assembly 1 as a damper mechanism will be described with reference to the mechanical circuit diagram of FIG. 6 and the torsional characteristic diagram of FIG. The mechanical circuit diagram shown in FIG. 6 schematically illustrates a damper mechanism 4 formed between the input rotary body 2 and the hub 3. It is a figure for explaining operation relation of each member at the time of twisting (for example, R2 direction).

When the hub 3 is twisted toward the R2 side with respect to the input rotary body 2, the second damper mechanism 6 mainly operates at angles up to the torsion angle θ1. That is, the second spring 21 is compressed in the rotation direction, and sliding occurs in the second friction mechanism 10. Here, since no sliding occurs in the first friction mechanism 8, the characteristic of high hysteresis torque does not occur. As a result,
The first-stage characteristics of low rigidity and low hysteresis torque can be obtained. When the torsion angle exceeds the torsion angle θ1, the second stopper 12 abuts and the relative rotation between the hub 3 and the hub flange 18 stops. That is, the second damper mechanism 6 does not operate when the torsion angle θ1 or more. Since the second spring 21 is not compressed at the torsion angle θ1 or more, the second spring 21
Hardly breaks. In addition, since the strength of the second spring 21 does not need to be concerned, the design becomes easy. In the second stage of the torsional characteristic, the first damper mechanism 5 operates. That is, the first
The spring 16 is compressed in the rotation direction between the hub flange 18 and the input rotating body 2, and sliding occurs in the first friction mechanism 8. As a result, a second-stage characteristic of high rigidity and high hysteresis torque is obtained. If the torsion angle exceeds θ1 + θ2, the spring 17
Is in contact with the second support portion 37 of the second housing portion 36. That is, in the second damper mechanism 6, the first spring 16 and the spring 17 are compressed in parallel. As a result, 3
At the stage, higher rigidity is obtained than at the second stage. Torsion angle θ
When 1 + θ2 + θ3, the first stopper 11 abuts,
The relative rotation between the input rotator 2 and the hub 3 stops.

Even at the negative side of the torsional characteristic, each torsion angle θ1
The same characteristics can be obtained although the magnitude of θ3 is different.
In the first stage of the torsional characteristic, friction occurs between the bush 93, the flange 64 of the hub 3, and the outer peripheral teeth 65. Further, friction occurs between the bush 93 and the inner peripheral portion of the hub flange 18 in the second and third stages.

When the abrasion of the bush 19 progresses on the friction surface formed by the annular portion 89 and the second disk-shaped portion 73 in the second damper mechanism 6, the bush 19 moves in the second axial direction with respect to other members. It is possible. In this case, the posture of the second cone spring 78 changes, and more specifically, the second cone spring 78 rises. Therefore, the second cone spring 78
The urging force (set load) changes, specifically, increases once and then decreases. Thus, the magnitude of the hysteresis torque in the second friction mechanism 10 changes and is not stable.

However, in the present invention, the first cone spring 49 urges the fixing plate 20 in the first axial direction, and the urging force acts on the hub flange 18 and the bush 93. Therefore, if the amount of wear on the second friction mechanism 10 and the amount of wear on the friction surface between the bush 93 and the hub flange 18 correspond or match, the following effects can be obtained. When the portion (friction member 95) of the bush 93 corresponding to the cylindrical portion 59 of the hub flange 18 is worn, the hub flange 18, the spacer 80,
The fixed plate 20 and the first friction washer 48 move in the first axial direction. Therefore, the second disk-shaped portion 73 also moves toward the first axial direction on the friction surface of the second friction mechanism 10. The axial position of the bush 19 relative to the hub 3 hardly changes, so that the flange 64 and the bush 19
And the attitude of the second cone spring 78 disposed between them also hardly changes. As described above, the posture of the second cone spring 78 is maintained constant by the wear following mechanism using the hub flange 18 and the first friction mechanism 8 irrespective of the wear on the friction surface of the second friction mechanism 10. 2 friction mechanism 1
Hysteresis torque at 0 can be stably generated. As a result, a hysteresis torque with little change over time is obtained, and the sound vibration performance is improved. In addition, since it is not necessary to consider the wear allowance of the second cone spring 78, the degree of freedom in designing the second cone spring 78 increases. Specifically, the second cone spring 78 can be designed to have a low stress and a high load.

The set load of the second cone spring 78 is set near the peak of the load characteristic of the cone spring. When the amount of wear on the bush 19 and the amount of wear on the bush 93 are maintained equal, the load on the second cone spring 78 is maintained near the maximum. Bush 19
When the abrasion amount of the bush 93 differs from the abrasion amount of the bush 93, the set load slightly deviates from both sides of the peak of the load characteristic.
Even in this case, the change amount of the set load is set to be minimized, and the change is predictable. [Other Embodiments] As shown in FIG. 23, the spacer of the above embodiment is eliminated, and the fixing plate 20 is connected to the hub flange 1.
8 may be directly engaged. The first disk-shaped portion 71 of the fixing plate 20 is directly supported by the cylindrical portion 59 of the hub flange 18. Also, from the outer peripheral edge of the first disc-shaped portion 71,
The engagement claws 28 extend into the engagement holes 58 of the hub flange 18. In this configuration, the spacer can be omitted, and the number of parts is reduced.

Further, another elastic member, that is, a spring may be arranged at the position of the spacer 80 in the mechanical circuit diagram of FIG. In this case, four-stage characteristics are obtained as a whole. In the description of this embodiment, "engaged so as to rotate integrally" or "engaged so as not to rotate relatively" means that both members are capable of transmitting torque in the circumferential direction. Means. That is, a case where a gap or the like is formed in the rotation direction between the two members and the two members do not transmit torque until a predetermined angle is included.

The second cone spring and the second cone spring according to the present invention
The structure of the second cone spring 101 and the members on both sides thereof will be described in detail with reference to FIGS. Second
The cone spring 101 is the second in the basic structure described above.
This is a member used in place of the cone spring 78. The second cone spring 101 is a disc spring. The disc spring is a circular disc-shaped spring in which a ring having a hole formed in the center of a disk is formed in a conical shape. Belleville springs generally apply a load to the outer and inner edges to deflect in the direction of decreasing the cone height, thereby obtaining a spring action. As a feature of the disc spring, a large load capacity can be obtained in a relatively small space in the load direction (axial direction of the clutch).

The second cone spring 101 is a conical disk spring in a free state. In this embodiment, the inner peripheral portion is located on the first axial side with respect to the outer peripheral portion. FIG.
In the assembled state shown in FIG.
The inner peripheral portion is supported by the flange 64 of the hub 3, and the outer peripheral portion is supported by the first axial side surface of the bush 19. In this state, the second cone spring 101 is in a state of being bent in the axial direction, and applies a force repelling in the axial direction to the flange 64 and the bush 19. As a result, the bush 19
Are urged toward the second axial direction and are pressed against the second disk-shaped portion 73 of the fixed plate 20. As a result, the bush 19
When the bush 19 and the fixed plate 20 rotate relatively,
A predetermined friction, that is, a hysteresis torque is generated between the motor and the fixing plate 20. The magnitude of the hysteresis torque generated here is determined by the friction coefficient of the friction surface and the load from the second cone spring 101.

The flange portion (flange 64 and outer teeth 65) supporting the inner peripheral portion of the second cone spring 101 forms a flat surface on the second axial direction side, that is, a plane perpendicular to the axial direction of the clutch. . Meanwhile, bush 1
A first axial side surface 9 includes a first surface A and a second surface B which is recessed in the axial direction therefrom. The first surface A is formed on the outer peripheral side of the second axial side surface of the bush 19, and the second surface B is formed from a radially intermediate portion of the bush 19 to a further inner peripheral portion. The first surface A and the second surface B are the second
On the axial side, a flat surface, that is, a plane perpendicular to the axial direction of the clutch is formed. The first surface A supports the outer peripheral edge of the second cone spring 101. The second surface B has a gap in the axial direction between the radially intermediate portion of the second cone spring 101 and the radially outer peripheral portion. The height difference between the first surface A and the second surface B in the axial direction is T1.

As shown in FIGS. 25 and 26, the second cone spring 101 includes an annular portion 102 and an annular portion 102.
And a plurality of lever portions 103 extending inward in the radial direction. A plurality of lever portions 103 are formed at equal intervals in the circumferential direction. Second cone spring 101
May be considered to be a disk-shaped member having a center hole formed therein and formed with a plurality of slits 104 extending radially outward from the inner peripheral edge. If you make a slit in the disc spring,
The deflection can be increased and the stress can be suppressed.
The inner peripheral edge of the second cone spring 101, that is, the tip of each lever portion 103, has a second axial side, that is, a flange 64.
And a fulcrum 105 extending toward the outer teeth 65. The fulcrum 105 has a rib shape in which the tip of each lever 103 is bent in the first axial direction. The fulcrum 105 is in contact with the second axial side surface of the flange 64. With such a configuration, in the assembled state in FIG.
A portion of the inner peripheral portion of the cone spring 101 further on the inner peripheral side than the fulcrum portion 105 and a flange portion of the hub 3 (the flange 6
A gap T2 is provided between the outer peripheral teeth 65) and the outer peripheral teeth 65) in the axial direction. A gap T2 is provided between the outer peripheral teeth 65 and the radially intermediate portion and the radially outer portion of the second cone spring 101.
The above gap is ensured.

FIG. 39 shows the load characteristics (load-deflection) of the second cone spring 101. A general description of load characteristics will be given. When wear occurs in the friction mechanism, the deflection of the second cone spring 101 decreases, and the set load (installation load) also changes. At this time, if the area where the amount of load change is small is large, the wear margin of the friction member can be used most effectively.

As can be seen from FIG. 39, when the deflection of the second cone spring 101 increases from 0, the load increases, and the second cone spring 101 shifts to a smooth flat region. In the region where the deflection is greatest, the load slightly increases from the flat state. The state shown in FIG. 24 is set to a normal set posture, and its deflection is set to a. Second cone spring 10
The flexure of 1 is a flat flexure and is b. Deflection b is greater than deflection a. Approximately the same load is obtained before and after the deflection a. The load in the flat state is almost the same as the set load. Also, there is a region where a load substantially equal to the set load can be obtained even in a reverse sled state in which the deflection is greater than that of the flat. This means that, when the second cone spring 101 is set in a reverse sled state, a large area can be secured as a margin for abrasion when the deflection of the second cone spring 101 is reduced due to wear of the friction mechanism. Means That is, if the deflection of the second cone spring 101 is made flat or more, the load can be stabilized for a long period of time. [Modified Example of Set State of Disc Spring] In the clutch disk assembly having the above-described structure, for example, as shown in FIG. 27, the second cone spring 101 may be arranged in a substantially flat state (flexure b in FIG. 39). is there. In this case, the second cone spring 101 is connected to the fulcrum 10.
5 abuts against the flange 64, and the other portions
And a gap T2 is secured between them. As described above, even when the second cone spring 101 is flat due to the fulcrum portion 105, the second cone spring 101 does not entirely adhere to the outer peripheral teeth 65. Here, since there is no need to provide a step on the flange 64 and the outer peripheral teeth 65 side,
Processing costs are decreasing.

As shown in FIG. 28, when the second cone spring 101 is further bent more than flat (when it exceeds the bending b in FIG. 39), the second cone spring 10
In some cases, a gap is provided between the outer peripheral portion 1 and the second axial side surface of the outer peripheral tooth 65. In the embodiment shown in FIG. 29, the step on the surface of the outer peripheral teeth 65 on the second axial direction side becomes lower in the axial direction from the surface on the second axial direction of the flange 64 that supports the fulcrum 105 of the second cone spring 101. A portion 65a is formed. This is the second cone spring 101
Means that a step portion similar to the conventional one is provided on the support member on the side where the fulcrum portion 105 is formed. As a result,
The second cone spring 101 can bend further in the first axial direction than the state shown in FIG. That is, even though the outer peripheral portion of the second cone spring 101 is further disposed on the first axial direction side than the axial position of the surface on the second axial direction of the flange 64 on which the fulcrum portion 105 is supported, the outer peripheral teeth 65 A gap is provided between the second axial direction surface and the second axial direction surface. Thus, the second cone spring 101
The following effects can be obtained by ensuring a large deflection of the magnetic field. When the bush 19 made of, for example, resin is worn due to frictional sliding between the bush 19 and the fixed plate 20, the bush 19 moves in the second axial direction with respect to the fixed plate 20. Due to the movement of the bush 19, the attitude of the second cone spring 101 gradually changes. At this time, since the initial deflection of the second cone spring 101 is larger than the deflection of the conventional cone spring in the normal set state and the flat state, a large area capable of generating a predetermined load is secured. As a result, even if the bush 19 is worn, stable friction performance can be maintained for a long period of time. [Modification of Type of Disc Spring] In the structure shown in FIG.
A fulcrum 109 is formed on the outer peripheral end of the cone spring 101. The fulcrum 109 is the second cone spring 10
1 is a portion obtained by bending the outer peripheral portion toward the second axial direction. The fulcrum 109 is supported on a surface of the bush 19 on the first axial direction side. Thereby, a step can be omitted on the first axial side surface of the bush 19. Further, by providing a step in the bush 19 as in the above-described embodiment, the amount of deflection of the second cone spring 101 can be increased.

The disc spring 110 shown in FIG. 31 and FIG.
This is the same disc spring as in the above embodiment. This disc spring 110
Does not have a lever portion formed by a plurality of slits. A fulcrum 111 projecting in the axial direction is formed on the inner periphery of the annular plate body of the disc spring 110. Fulcrum 111
Is formed in an annular shape and protrudes axially from other portions. The fulcrum 111 is curled and has a semicircular cross section. As shown in FIG. 32, the fulcrum 111 has a curved surface that is convex toward the protruding side. As described above, since the side of the fulcrum portion 111 that contacts the support member is curved, the second cone spring 101
The fulcrum 111 always stably abuts the support member even if the posture changes. Therefore, the second cone spring 10
The load of 1 is stable.

The disc spring 114 shown in FIG. 33 and FIG.
It comprises an annular portion 115 and a plurality of lever portions 116 extending radially inward from the annular portion 115. A fulcrum 117 is formed at the tip of each lever 116 so as to protrude axially from other portions. The fulcrum 117 is curved like a fulcrum 111 shown in FIGS. 31 and 32 and has a semicircular cross section, and has a convex surface smoothly curved to the side protruding in the axial direction. In this embodiment, since the fulcrum 117 is formed on each of the levers 116, it is easier to process than the fulcrum 111 shown in FIGS. 31 and 32.

In the disc spring 120 shown in FIGS. 35 and 36, a plurality of fulcrum portions 122 are formed on an annular plate body. The fulcrum part 122 has a structure formed so as to protrude in the axial direction at the inner peripheral portion of the plate body. Fulcrum 12
Reference numeral 2 is formed on the plate body by drawing. Each fulcrum 12
Numerals 2 are formed at equal intervals in the circumferential direction, and have a smoothly curved convex surface on the surface protruding in the axial direction.
Embodiments in which the fulcrum 122 is provided on the outer peripheral edge of the annular plate body are shown in FIGS. [Modification] The disc spring according to the present invention can be applied to a structure other than the clutch disk assembly described in this embodiment. For example, the present invention is also applicable to a cone spring disposed between a retaining plate and a flange of a hub. In particular, the present invention is effective when adopted in a disc spring disposed in a space limited in the axial direction.

The load characteristics of the disc spring are not limited to those shown in FIG. Further, supporting points may be provided on both the inner and outer peripheral portions of the disc spring.

[0067]

In the disk spring according to the present invention, the plate body has a fulcrum protruding from the other portion, so that the disk spring has an end opposite to the fulcrum in the direction in which the fulcrum protrudes. Even if it is flattened in a state where it is pressed, no close contact occurs. As described above, the same effect as that of the related art can be obtained without providing a step in the supporting member that supports the fulcrum, so that the processing cost of the supporting member is reduced.

[Brief description of the drawings]

FIG. 1 is a plan view of a clutch disk assembly as a basic structure to which a disc spring as one embodiment of the present invention can be applied.

FIG. 2 is a partially enlarged view of FIG. 1;

FIG. 3 is a sectional view taken along the line III-III in FIG. 1;

FIG. 4 is a sectional view taken along line 0-IV of FIG. 1;

FIG. 5 is a sectional view taken along the line OV in FIG. 1;

FIG. 6 is a mechanical circuit diagram as a damper mechanism of the clutch disk assembly of the present invention.

FIG. 7 is a torsional characteristic diagram of a clutch disk assembly.

FIG. 8 is a plan view of a fixing plate.

FIG. 9 is a sectional view taken along the line IX-IX in FIG. 8;

FIG. 10 is a view taken in the direction of the arrow X in FIG. 8;

FIG. 11 is a view taken in the direction of the arrow XI in FIG. 8;

FIG. 12 is a plan view of a bush.

FIG. 13 is a view as seen from the arrow XIII in FIG. 12;

FIG. 14 is a sectional view taken along the line XIV-XIV of FIG. 12;

FIG. 15 is a partially enlarged view of FIG. 14;

FIG. 16 is a sectional view taken along the line XVI-XVI in FIG. 17;

FIG. 17 is a rear view of the bush.

FIG. 18 is a view as seen from the arrow XVIII in FIG. 17;

19 is a view taken in the direction of the arrow XIX in FIG. 17;

FIG. 20 is a plan view of a friction bush.

21 is a sectional view taken along line XXI-XXI of FIG. 20.

FIG. 22 is a partially enlarged view of FIG. 21;

FIG. 23 is a view corresponding to FIG. 3 in another embodiment.

FIG. 24 is a schematic longitudinal sectional view showing a state where the disc spring according to the present invention is incorporated in a clutch disk assembly.

FIG. 25 is a plan view of a disc spring.

FIG. 26 is a sectional view of a disc spring.

FIG. 27 is a view corresponding to FIG. 24;

FIG. 28 is a view corresponding to FIG. 24;

FIG. 29 is a view corresponding to FIG. 24;

FIG. 30 is a view corresponding to FIG. 24;

FIG. 31 is a plan view of a disc spring according to another embodiment.

FIG. 32 is a sectional view of FIG. 31;

FIG. 33 is a plan view of a disc spring according to another embodiment.

FIG. 34 is a sectional view of FIG. 33;

FIG. 35 is a plan view of a disc spring according to another embodiment.

FIG. 36 is a sectional view of FIG. 35;

FIG. 37 is a plan view of a disc spring according to another embodiment.

FIG. 38 is a sectional view taken along the line XXXVIII-XXXVIII of FIG. 37;

FIG. 39 is a diagram showing load characteristics of the disc spring according to the present invention.

[Explanation of symbols]

 Reference Signs List 101 second cone spring (disc spring) 102 plate body 103 lever part 104 slit 105 fulcrum part

Claims (5)

[Claims] 1. A disc spring for press-contacting relatively rotating members in a friction mechanism for generating friction to attenuate torsional vibration, comprising: an annular plate body having a predetermined width in a radial direction; And a fulcrum formed on at least one of the inner and outer peripheral portions of the plate body, protruding from other portions, and supported by one of the two members. 2. The disc spring according to claim 1, wherein a plurality of said fulcrum portions are formed side by side in a circumferential direction. 3. A plurality of lever portions are formed on one of the inner and outer peripheral portions of the plate body by a plurality of slits extending in a radial direction, and the fulcrum portion is formed on the lever portion.
Disc springs according to the above. 4. The disc spring according to claim 1, wherein said plate body has a conical shape in a free state. 5. The disc spring according to claim 1, wherein said fulcrum portion is curved such that a surface on a protruding side is convex.