JP4754958B2 - Clutch cover assembly - Google Patents

Description

  The present invention relates to a clutch cover assembly, and more particularly, to a clutch cover assembly for pressing and releasing a friction member of a clutch disk assembly against a flywheel of an engine.

  The clutch cover assembly is generally mounted on an engine flywheel and used to transmit the driving force of the engine to the transmission side. Such a clutch cover assembly mainly includes a clutch cover fixed to the flywheel, a pressure plate for sandwiching the friction member of the clutch disk assembly between the flywheel, and the pressure plate on the flywheel side. It is comprised from the diaphragm spring for pressing. The diaphragm spring includes an annular elastic portion and a plurality of lever portions extending radially inward from the inner peripheral edge of the annular elastic portion. The diaphragm spring has a function of pressing the pressure plate and a lever function for releasing the pressure on the pressure plate.

  Here, the pressing load characteristic of the clutch cover assembly will be described. The pressing load characteristic represents a use area as a pressing load in the load characteristic of the diaphragm spring. For example, as shown in FIG. 6, in the pressing load characteristic 20, the effective use area (wear allowance) of the clutch cover assembly is an area where a constant pressing load can be obtained (from the new set line 25 to the wear limit of the friction member). To the wear line 26).

  Next, the release load characteristics of the clutch cover assembly will be described. The release load characteristic represents the relationship between the operation amount (lever stroke amount) of the release lever and the load (release load) acting on the tip of the release lever. For example, as shown in FIG. 9, the release load characteristic 60 has a first portion 61 that increases linearly from zero lever operation amount, and a second portion 62 that gradually decreases. The load balance point 63 has a peak at both contact points. The first portion 61 represents the lever rigidity of the diaphragm spring, and the second portion 62 corresponds to a change in the pressing load characteristic from the set line to the right side in the figure.

  As shown in FIG. 6, the pressing load characteristic 20 increases at a constant rate as the displacement amount of the diaphragm spring increases from zero. However, when the deflection amount exceeds a certain point (peak point), the pressing load characteristic 20 gradually increases. It decreases gradually, and when it exceeds a certain amount of deflection, it gradually increases. For this reason, in the effective use area | region, it is the peak part 21 (part which becomes convex upward), and the pressing load becomes large as wear of a friction member becomes large (as a set line moves to the left side of a figure). . That is, when the friction member wears, the release load increases and the clutch pedal depression force also increases.

  Therefore, conventionally, as a structure for cutting the peak in the pressing load characteristic, a peak cut clutch using an elastic member that generates a load that acts to counteract the load of the diaphragm spring when the friction member is worn is known. Yes. In the peak cut clutch, the peak portion opposite to the elastic member is superimposed on the peak portion of the diaphragm spring. As a result, a flat portion is obtained in the combined load.

  A peak cut clutch has been proposed that is provided with a low release load mechanism for the purpose of further reducing the release load (see, for example, Patent Document 1).

Here, the reduction of the release load by the cushioning function in the friction member will be described. When there is no cushioning function, in the release load characteristic of FIG. 9, the release load characteristic 60 linearly changes up to the load balance point 63, and gradually decreases and increases gradually. Further, the pressure plate has a zero cut amount up to the load balance point 63. When the friction member has a cushion function, the pressure plate starts moving at the same time as the release starts due to the repulsive force of the cushion, and moves to some extent at the load balance point 63. This means that the pressing load at the load balance point is shifted to the right in FIG. As a result, the release load at the load balance point 63 in FIG. 9 is significantly smaller than when there is no cushioning function. The above result is obtained because the pressure plate moves in the negative gradient portion during the release operation in the pressing load characteristic of FIG. Therefore, if the position of the set line changes due to wear of the friction member, it may be possible to move the flat portion or the positive gradient portion. In that case, a low release load due to the cushioning function in the friction member cannot be obtained. Therefore, in the clutch disc assembly described in Patent Document 1, the second low release load characteristic realizing mechanism realizes a low release load by the cushioning plate function in the friction member even when the friction member is worn.
Japanese Patent Application No. 2004-224342

  FIG. 12 is a schematic longitudinal sectional view of a clutch cover assembly provided with the second low release load characteristic realizing mechanism 230 described in Patent Document 1, and FIG. 13 is a diagram of the second low release load characteristic realizing mechanism 230 described in Patent Document 1. A longitudinal cross-sectional schematic diagram is shown. The second low release load characteristic realizing mechanism 230 includes a support bolt 231, a holder 232, a first support member 233, a snap ring 234, a second support member 235, a pair of first cone springs 236, The second cone spring 237, a support ring 238, and an adjustment spring 239 are included.

  As shown in FIG. 13, the adjustment spring 239 is wound around the head 231 c of the support bolt 231, and is arranged on the axially opposite side of the friction member 253 of the holder 232 (the right side of the holder 32 in FIG. 12). . For this reason, the adjustment spring 239 and the head 231c of the support bolt 231 greatly protrude in the axial direction opposite to the friction member 253 of the clutch cover 202, and the axial dimension of the clutch cover assembly increases.

  As shown in FIG. 13, in the second low release load characteristic realizing mechanism 230, the adjustment spring 239, the support bolt 231, and the screwed portion of the second support member 235 are exposed to the outside of the clutch cover 202. Therefore, it is necessary to attach the dust cover 250 in consideration of dust intrusion into the screwed portion and rust of each member. As a result, the number of parts increases and the axial dimension of the clutch cover assembly further increases.

  The subject of this invention is shortening the axial direction dimension of the clutch cover assembly provided with the peak cut mechanism and the low release load mechanism.

  Another object of the present invention is to reduce the number of parts of a clutch cover assembly including a peak cut mechanism and a low release load mechanism.

  A clutch cover assembly according to claim 1 is for pressing and releasing a friction member with a cushioning function of a clutch disassembly against an engine flywheel, the clutch cover, a pressure plate, and a diaphragm spring. And a first elastic member, a second elastic member, and a wear compensation mechanism. The clutch cover is fixed to the flywheel. The pressure plate is connected to the clutch cover so as not to rotate relative to the clutch cover, and is a member for sandwiching the friction member with the flywheel. The diaphragm spring is supported by the clutch cover and biases the pressure plate toward the flywheel. The first elastic member is a member that is supported by the clutch cover and generates a load that opposes the urging force of the diaphragm spring, thereby flattening a change in the pressing load on the pressure plate with respect to the displacement amount of the diaphragm spring. . The second elastic member is supported by the clutch cover, and generates a load that opposes the urging force of the diaphragm spring during the release operation. In this process, the displacement amount of the diaphragm spring increases due to the cushioning function of the friction member. It is a member for reducing the pressing load to the. The wear compensation mechanism is a mechanism for maintaining the posture of the second elastic member against the wear of the friction member, and includes a support member, a support engagement member, and a third elastic member. The support member is a member extending from the pressure plate to the clutch cover side. The support engagement member is a member that is screwed onto the outer peripheral side of the support member and receives a load from the second elastic member to the friction member side and the axially opposite side. The third elastic member is a member for always applying a torque to the support engagement member so that the support engagement member rotates in a direction in which the support engagement member moves in the axial direction opposite to the friction member side. The third elastic member is disposed on the axial friction member side of the support engagement member.

  In this clutch cover assembly, since the third elastic member is disposed on the axial friction member side of the support engagement member, the third elastic member does not protrude to the outside of the clutch cover. Thereby, it can suppress that a wear compensation mechanism protrudes from a clutch cover, and the axial direction dimension of a clutch cover assembly can be shortened significantly.

  In the clutch cover assembly according to the second aspect, the third elastic member is disposed between the clutch cover and the pressure plate in the axial direction.

  In this clutch cover assembly, since the third elastic member is disposed between the clutch cover and the pressure plate in the axial direction, the third elastic member does not protrude outside the clutch cover. Accordingly, the wear compensation mechanism can be prevented from protruding from the clutch cover, and the axial dimension of the clutch cover assembly can be further shortened.

  The clutch cover assembly according to claim 3 is for pressing and releasing the friction member with a cushioning function of the clutch disassembly against the flywheel of the engine, and includes a clutch cover, a pressure plate, and a diaphragm spring. And a first elastic member, a second elastic member, and a wear compensation mechanism. The clutch cover is fixed to the flywheel. The pressure plate is connected to the clutch cover so as not to rotate relative to the clutch cover, and is a member for sandwiching the friction member with the flywheel. The diaphragm spring is supported by the clutch cover and biases the pressure plate toward the flywheel. The first elastic member is a member that is supported by the clutch cover and generates a load that opposes the urging force of the diaphragm spring, thereby flattening a change in the pressing load on the pressure plate with respect to the displacement amount of the diaphragm spring. . The second elastic member is supported by the clutch cover, and generates a load that opposes the urging force of the diaphragm spring during the release operation. In this process, the displacement amount of the diaphragm spring increases due to the cushioning function of the friction member. It is a member for reducing the pressing load to the. The wear compensation mechanism is a mechanism for maintaining the posture of the second elastic member against the wear of the friction member, and includes a support member, a support engagement member, and a third elastic member. The support member is a member extending from the pressure plate to the clutch cover side. The support engagement member is a member that is screwed onto the outer peripheral side of the support member and receives a load from the second elastic member to the friction member side and the axially opposite side. The third elastic member is a member for always applying a torque to the support engagement member so that the support engagement member rotates in a direction in which the support engagement member moves in the axial direction opposite to the friction member side. The third elastic member is disposed between the clutch cover and the pressure plate in the axial direction.

  In this clutch cover assembly, since the third elastic member is disposed between the clutch cover and the pressure plate in the axial direction, the third elastic member does not protrude outside the clutch cover. Thereby, it can suppress that a wear compensation mechanism protrudes from a clutch cover, and the axial direction dimension of a clutch cover assembly can be shortened significantly.

  According to a fourth aspect of the present invention, in any one of the first to third aspects, the support engagement member covers the end portion of the support member.

  In this clutch cover assembly, since the support engagement member covers the end portion of the support member, the screw portion of the support member can be covered by the support engagement member. That is, the support engagement member serves as a dust cover. This eliminates the need for a dust cover, which has been necessary conventionally, and can reduce the number of parts and further reduce the axial dimension.

  The clutch cover assembly according to claim 5 is for pressing and releasing the friction member with a cushioning function of the clutch disassembly against the flywheel of the engine, and includes a clutch cover, a pressure plate, and a diaphragm spring. And a first elastic member, a second elastic member, and a wear compensation mechanism. The clutch cover is fixed to the flywheel. The pressure plate is connected to the clutch cover so as not to rotate relative to the clutch cover, and is a member for sandwiching the friction member with the flywheel. The diaphragm spring is supported by the clutch cover and biases the pressure plate toward the flywheel. The first elastic member is a member that is supported by the clutch cover and generates a load that opposes the urging force of the diaphragm spring, thereby flattening a change in the pressing load on the pressure plate with respect to the displacement amount of the diaphragm spring. . The second elastic member is supported by the clutch cover, and generates a load that opposes the urging force of the diaphragm spring during the release operation. In this process, the displacement amount of the diaphragm spring increases due to the cushioning function of the friction member. It is a member for reducing the pressing load to the. The wear compensation mechanism is a mechanism for maintaining the posture of the second elastic member against the wear of the friction member, and includes a support member, a support engagement member, and a third elastic member. The support member is a member extending from the pressure plate to the clutch cover side. The support engagement member is a member that is screwed onto the outer peripheral side of the support member and receives a load from the second elastic member to the friction member side and the axially opposite side. The third elastic member is a member for always applying a torque to the support engagement member so that the support engagement member rotates in a direction in which the support engagement member moves in the axial direction opposite to the friction member side. The support engagement member covers the end of the support member.

  In this clutch cover assembly, since the support engagement member covers the end portion of the support member, the screw portion of the support member can be covered by the support engagement member. That is, the support engagement member serves as a dust cover. This eliminates the need for a dust cover, which has been necessary conventionally, and can reduce the number of parts and further reduce the axial dimension.

A clutch cover assembly according to a sixth aspect of the present invention is the clutch cover assembly according to the fifth aspect, wherein the support engagement member is formed at one end of the support engagement member main body and a cylindrical support engagement member main body that is screwed with the outer peripheral side of the support member And an annular engaging portion that receives torque from the third elastic member, and a head that closes the other end of the support engaging member main body.

  In this clutch cover assembly, since the support engagement member has the head, the screw portion of the support member can be reliably covered.

  According to a seventh aspect of the present invention, in the clutch cover assembly according to the sixth aspect, the outer shape of the head section in the axial direction is a polygon.

  In this clutch cover assembly, since the outer shape of the axial section of the head is polygonal, it is easy to grasp the head with a tool. Accordingly, the support engagement member can be easily tightened with the tool with respect to the support member, and the work for assembling the wear compensation mechanism is facilitated.

The clutch cover assembly according to claim 8 is the clutch cover assembly according to any one of claims 5 to 7, wherein the wear compensation mechanism is engaged with one end of the third elastic member between the support engagement member and the third elastic member in the axial direction. And a guide plate.

  In this clutch cover assembly, since one end of the third elastic member is engaged with the guide plate, the end of the third elastic member can be positioned by the guide plate. Thereby, the assembly work of the support engagement member and the third elastic member is facilitated, and the assembly work of the friction compensation mechanism is facilitated.

  According to a ninth aspect of the present invention, in the clutch cover assembly according to the eighth aspect, the engaging portion has a first hole with which one end of the third elastic member is engaged. The guide plate has a second hole with which one end of the third elastic member is engaged. The radial position of the first hole is substantially the same as the radial position of the second hole.

  In this clutch cover assembly, since the radial position of the first hole of the engaging portion is substantially the same as the radial position of the second hole, one end of the third elastic member can be fitted into the first hole. In this case, the positioning of the one end of the third elastic member and the second hole is facilitated. Thereby, the assembly work of the support engagement member and the third elastic member is facilitated, and the assembly work of the wear compensation mechanism is facilitated.

  In the clutch cover assembly according to the present invention, the axial dimension can be shortened by changing the arrangement of the third elastic member and the shape of the support engagement member.

  In the clutch cover assembly according to the present invention, the number of parts can be reduced by changing the arrangement of the third elastic member and the shape of the support engagement member.

(1) Overall Structure of Clutch Cover Assembly The pull type diaphragm spring type clutch cover assembly 1 shown in FIGS. 1 to 3 presses the friction member 53 of the clutch disc assembly 52 against the flywheel 51 of the engine. This is a device for disengaging the clutch by connecting or releasing the clutch. The friction member 53 includes a friction facing 53a and a cushioning plate 53b, and has a cushioning function that can be deflected within a predetermined range in the axial direction.

  The OO line shown in FIGS. 1 and 2 is the rotational axis of the flywheel 51 and the clutch cover assembly 1. Hereinafter, the left side of the figure is referred to as the axial engine side, and the right side of the figure is referred to as the axial transmission side.

  The clutch cover assembly 1 is mainly composed of a clutch cover 2, a pressure plate 3, and a diaphragm spring 4.

  The clutch cover 2 is a substantially dish-shaped plate member, and an outer peripheral portion thereof is fixed to the flywheel 51 by bolts, for example. The clutch cover 2 has a disk-shaped portion that faces the outer peripheral portion of the flywheel 51 with a gap in the axial direction.

  The pressure plate 3 is an annular member having a pressing surface 3 a formed on the side facing the flywheel 51. A friction member 53 of the clutch disk assembly 52 is disposed between the pressing surface 3a and the flywheel 51. The pressure plate 3 is formed with a plurality of protruding portions 3b that protrude in the axial direction on the side opposite to the pressing surface 3a. The pressure plate 3 is connected to the clutch cover 2 by a plurality of strap plates 7 so as to be movable in the axial direction but not relatively rotatable.

  The diaphragm spring 4 is a disk-shaped member disposed between the pressure plate 3 and the clutch cover 2, and includes an annular elastic portion 4a and a plurality of lever portions extending radially inward from the inner peripheral portion of the annular elastic portion 4a. 4b. The inner peripheral portion of the annular elastic portion 4 a is in contact with the protruding portion 3 b of the pressure plate 3. The outer peripheral portion of the annular elastic portion 4 a is supported by the clutch cover 2 via the wire ring 5. In this state, the annular elastic portion 4a biases the pressure plate 3 toward the flywheel 51. A slit is formed between the lever portions 4b of the diaphragm spring 4, and an oval hole 4c is formed in the outer peripheral portion of the slit. A pull-type release device (not shown) is engaged with the tip of the lever portion 4 b of the diaphragm spring 4. This release device is composed of a release bearing or the like.

(2) First Low Release Load Characteristics Realizing Mechanism Next, the first low release load characteristics realizing mechanism 8 will be described. The first low release load characteristic realizing mechanism 8 is a mechanism for realizing a low release load characteristic even when wear of the friction member 53 progresses by achieving flattening of the pressing load characteristic. As illustrated in FIG. 3, the mechanism 8 includes a first unit 9 and a second unit 10 that are arranged side by side in the circumferential direction. Two each of the first unit 9 and the second unit 10 are provided, and are arranged alternately in the circumferential direction. For this reason, the mechanism 8 generates a load in a balanced manner in the circumferential direction.

  As shown in FIG. 1, the first unit 9 includes a support bolt 12, a spring seat 13, two cone springs 14 (first elastic members), and two support nuts 15. The support bolt 12 extends from the inner peripheral portion of the pressure plate 3 on the protruding portion 3b side to the axial transmission side. The support bolt 12 has a trunk portion 12a and a screw portion 12b. The trunk portion 12 a of the support bolt 12 extends further in the axial direction through the oblong hole 4 c of the diaphragm spring 4. The screw portion 12b of the support bolt 12 is a portion where a screw is formed in a spiral shape on the surface, and is disposed on the axial transmission side of the trunk portion 12a. In the clutch cover 2, a hole 16 is formed at a position corresponding to the support bolt 12. The hole 16 has a circular shape larger than the oval hole 4c. The screw part 12b extends in the axial direction through the hole 16, and a support nut 15 is screwed to the end part. The spring seat 13 is an annular member, and is in contact with the surface of the one support nut 15 on the axial engine side. The cone spring 14 is arranged so that two springs act in parallel, and is arranged on the clutch cover 2 on the axial transmission side of the hole 16. A preferable load can be set in each first unit 9 by combining each spring. The outer peripheral edge of the cone spring 14 is supported by the edge portion of the hole 16 of the clutch cover 2. The spring seat 13 has a tapered surface 13a on the axial engine side. The inner peripheral edge of the cone spring 14 is supported by the tapered surface 13 a of the spring seat 13.

  When the clutch is not worn, the cone spring 14 does not generate a load when the clutch is engaged. On the other hand, when the friction member 53 of the clutch disk assembly 52 is worn, the pressure plate 3 and the support bolt 12 move to the axial engine side, so that the cone spring 14 is compressed between the clutch cover 2 and the spring seat 13, A load is applied to both members 2 and 13 in the axial direction. The load that the cone spring 14 applies to the support bolts 12 and the like acts on the side opposite to the pressing load that the diaphragm spring 4 applies to the pressure plate 3, and the pressing load of the diaphragm spring 4 is reduced. The effect of keeping it low is realized (described later).

  The second unit 10 has the same basic structure as the first unit 9. However, as shown in FIG. 5, a gap 19 is secured in the axial direction between the inner peripheral edge of the cone spring 14 and the spring seat 13. That is, the cone spring 14 of the second unit 10 does not generate a load at the initial stage of wear of the friction member 53. In other words, the compression start timing of the cone spring 14 of the second unit 10 is shifted by the gap 19 from the compression start timing of the cone spring 14 of the first unit 9.

  The pressing load characteristic of FIG. 6 will be described. The characteristic 20 of the diaphragm spring 4 has a peak portion 21 as already described. On the other hand, the characteristic 22 of the cone spring 14 of the first unit 9 and the characteristic 23 of the cone spring 14 of the second unit 10 have opposite peak portions (portions protruding downward) that cancel the peak portions 21. The composite load flat portion 24 is formed. More specifically, the cone spring 14 of the first unit 9 generates a load from the set line 25, and the valley portion is located at the end of the wear allowance. The cone spring 14 of the second unit 10 generates a load after being somewhat displaced from the set line 25, and the valley portion is somewhat displaced from the end of the wear allowance. As described above, the combined load flat portion 24 having a sufficiently large wear allowance is realized by using two types of cone springs in combination. Thereby, even when the friction member 53 is worn, the clutch pedal depression force is hardly changed compared to when the friction member 53 is not worn, and the operation feeling during the release operation is improved.

(3) Second Low Release Load Characteristic Realization Mechanism The second low release load characteristic realization mechanism 30 will be described with reference to FIGS. 2 and 3. The second low release load characteristic realizing mechanism 30 is a release assisting mechanism for realizing the low release load by the cushioning function in the friction member 53 even when the friction member 53 is worn.

  First, the reduction in the release load by the cushioning function in the friction member will be described with reference to FIG. When there is no cushioning function, the release load characteristic 60 changes linearly up to the peak, that is, the load balance point 63, and gradually decreases and increases gradually. Further, the pressure plate breakage 65 is zero up to the load balance point 63. When the friction member has a cushion function, the pressure plate moves quickly at the time of release, and the pressure plate breakage amount 65 increases faster than when there is no cushioning plate. Further, the peak at the load balance point 63 in FIG. 9 is significantly reduced, and a low release load characteristic is realized. The above result is obtained because the position of the pressure plate moves in the negative gradient direction (right direction) in the pressing load characteristic of FIG. 6 during the release operation. Therefore, if the position of the set line changes due to wear of the friction member, the pressure plate may move in a flat portion or a positive gradient portion during the release operation. Therefore, the second low release load characteristic realizing mechanism 30 realizes that the pressure plate moves in the negative gradient direction of the load characteristic even when the friction member is worn.

  As shown in FIG. 3, the second low release load characteristic realizing mechanism 30 is alternately arranged in the same radial direction position as the first unit 9 and the second unit 10 of the first low release load characteristic realizing mechanism 8. Yes. The second low release load characteristic realizing mechanism 30 is arranged in a total of four places in the present embodiment. As shown in FIG. 4, each mechanism 30 includes a support bolt 31 (support member), a holder 32 (support engagement member), a first support member 33, a snap ring 38a, an intermediate member 38b, and a second member. A support member 35, three first cone springs 36 (second elastic members), a second cone spring 37 (second elastic member), a support ring 38, and an adjustment spring 39 (third elastic member). It is configured.

  The support bolt 31 extends from the surface of the pressure plate 3 on the protruding portion 3b side to the axial transmission side. The support bolt 31 has a trunk portion 31a and a screw portion 31b. The body portion 31a passes through the oval hole 4c of the diaphragm spring 4 in the axial direction. An adjustment spring 39 (third elastic member) is wound around the outer peripheral side of the body portion 31a (described later). The screw part 31 b is a part in which a screw is formed in a spiral shape on the surface, and is disposed in the hole 11 formed in the clutch cover 2. The hole 11 has a substantially circular shape.

  The holder 32 is a member for receiving a load from the first corn spring 36 and the second corn spring 37 in the axial direction opposite side to the friction member 53 side. (Engagement part) and the head part 32c. The holder main body 32a is a cylindrical portion extending in the axial direction, and a screw 32d that is screwed into the screw portion 31b is formed on the inner peripheral surface. The holder main body 32 a is screwed with the threaded portion 31 b of the support bolt 31. In addition, in the state of FIG. 4, the screw part 31b is also formed in the axial direction transmission side from the holder main body 32a.

  The flange portion 32b is an annular portion extending from the end of the holder main body 32a on the engine side in the axial direction to the outer peripheral side, and is integrally formed with the holder main body 32a. The flange portion 32b is formed with a plurality of holes 32e (first holes) penetrating in the axial direction. The first engagement end 39 a of the adjustment spring 39 passes through the hole 32 e, and the flange portion 32 b is a portion that receives torque from the adjustment spring 39.

  The head portion 32c is a portion formed so as to close the end portion on the axial transmission side of the holder main body 32a, and the outer shape of the axial cross section has a hexagonal shape. The outer shape of the head 32c may be a polygon other than a hexagon. As shown in FIG. 4, the holder 32 covers the end portion of the support bolt 31 in a state of being screwed to the screw portion 31 b of the support bolt 31.

  The first support member 33 is a cylindrical member and is disposed on the outer peripheral side of the holder 32. A snap ring 38a is fitted on the outer peripheral surface of the end of the holder 32 on the axial direction engine side, and an intermediate member 38b is sandwiched between the end of the first support member 33 and the snap ring 38a. That is, the first support member 33 is held so as not to move in the axial direction with a slight gap from the holder 32. In addition, a radial clearance is secured between the inner peripheral surface of the first support member 33 and the outer peripheral surface of the holder 32, so that both can rotate relative to each other. The second support member 35 is an annular member, and is fixed to the outer peripheral surface of the first transmission member 33 on the axial transmission side portion by welding or caulking. As described above, the holder 32, the first support member 33, and the second support member 35 form a single assembly that moves integrally in the axial direction.

  The three first cone springs 36 are arranged so as to act in parallel. The inner peripheral edge of the first cone spring 36 is in contact with the second support member 35 from the axial engine side, and the outer peripheral edge is in contact with the annular protrusion 11a formed in the hole 11 of the clutch cover 2 from the axial transmission side. Yes. The second cone spring 37 is in contact with the annular protrusion 33a of the first support member 33 from the axial transmission side at the inner peripheral edge, and the outer peripheral edge is in contact with the first cone spring 36 from the axial engine side. That is, no spacer is arranged between the first corn spring 36 and the second corn spring 37 in the axial direction.

  As described above, the first cone spring 36 can apply a load to the axial transmission side with respect to the structure including the holder 32 and the like, and the second cone spring 37 is applied to the structure including the holder 32 and the like. It is possible to apply a load to the axial engine side. The cone springs 36 and 37 hardly apply a load to the holder 32 and the like when the clutch is engaged, but apply a load to the holder 32 and the like on the axial transmission side during the clutch release operation to reduce the release load. That is, the load of the first cone spring 36 is larger than the load of the second cone spring 37.

  The adjustment spring 39 is a torsion coil spring and is disposed between the clutch cover 2 and the pressure plate 3 in the axial direction, more specifically, on the axial engine side (the friction member 53 side) of the holder 32. Between the axial direction of the 2nd adjustment spring 39 and the holder 32, the guide plate 34 which is a circular plate member is arrange | positioned. The adjustment spring 39 is wound around the outer periphery of the body portion 31a of the support bolt 31, and the first engagement end 39a (one end) of the adjustment spring 39 passes through the hole 32e (second hole) of the guide plate 34. It is inserted into the hole 32 e of the holder 32. The second engagement end 39 b of the adjustment spring 39 is fitted into the hole 31 c of the support bolt 31, and the adjustment spring 39 is attached to the support bolt 31. That is, in a state where the adjustment spring 39 is wound up, the adjustment spring 39 applies a substantially constant load to the holder 32 on one side in the rotational direction. In this case, the load application direction from the adjustment spring 39 is a direction in which the holder 32 moves toward the axial transmission side along the screw portion 31b.

  As is clear from the above configuration, the adjustment spring 39 is disposed between the clutch cover 2 and the pressure plate 3 in the axial direction and on the engine side of the holder 32 in the axial direction. (More specifically, it does not protrude toward the axial transmission side of the clutch cover 2). Thus, the second low release load characteristic realizing mechanism 30 including the wear compensation mechanism can be prevented from protruding from the clutch cover 2, and the axial dimension of the clutch cover assembly 1 can be greatly shortened.

  Further, in this clutch cover assembly 1, since the holder 32 covers the end portion of the support bolt 31, the screw portion of the support bolt 31 can be covered by the holder 32. That is, the holder 32 serves as a dust cover. As a result, the dust cover that has been conventionally required is not required, the number of parts can be reduced, and the axial dimension of the clutch cover assembly can be further shortened. Moreover, since the holder 32 has the head part 32c, the thread part of the support bolt 31 can be covered reliably.

  Here, the operation of the second low release load characteristic realizing mechanism 30 will be described. As shown in FIG. 7, the characteristic 43 of the first cone spring 36 generates a load toward the positive side (axial transmission side), and the characteristic 44 of the second cone spring 37 is negative (shaft) A load is generated toward the direction engine side). The characteristic 43 of the first cone spring 36 has a large difference between the valley and the peak and has a large gradient, and the characteristic 44 of the second cone spring 37 has a small difference between the valley and the peak and has a small gradient. In the composite characteristic 45, the valley portion is disposed at the clutch engagement position, and the load there is zero. The valley load of the composite characteristic 45 is preferably designed to be zero or less. When moving from zero load to the maximum release position, the load gradually increases to the positive side. In view of the set load characteristics shown in FIG. 8, when the release operation is performed after the friction member 53 is worn, the set line is shifted to the large displacement side as lines 47 and 48 by the cushion function of the friction member 53. In other words, a negative gradient is always ensured in the pressing characteristics, and therefore a low release load is reliably realized by the cushion function.

  In the clutch engaged state, the force (torque) for rotating the holder 32 by the adjustment spring 39 is balanced with the frictional force of the thread surface due to the combined load (axial load) of the cone springs 36 and 37. Therefore, in this state, the support bolt The axial load applied to 31 is slightly larger than zero. When the friction member 53 is worn, the support bolt 31, the holder 32, etc. move to the axial direction engine side. Then, the cone springs 36 and 37 are deformed, and the load of these members is reduced to zero. At that time, the adjustment spring 39 rotates the holder 32 and moves it to the axial engine side. Then, the combined load in the axial direction by the cone springs 36 and 37 increases, and the frictional force of the thread surface increases in direct proportion thereto. Therefore, it becomes impossible to rotate the holder 32 by the torque of the adjustment spring 39, The axial movement of the holder 32 stops. Thus, even if the friction member 53 is worn, the postures of the cone springs 36 and 37 in the second low release load characteristic realizing mechanism 30 are restored to the original state. As a result, the postures of the cone springs 36 and 37 are maintained even when the friction member 53 is worn, and the load of the second low release load characteristic realizing mechanism 30 is maintained constant.

(4) Assembly Work of Second Low Release Load Characteristic Realizing Mechanism 30 The assembly work of the second low release load characteristic realizing mechanism 30 will now be described with reference to FIG.

  First, the cone spring assembly 40 including the first cone spring 36, the second cone spring 37, the first support member 33, and the second support member 35 is assembled in advance. Specifically, one second cone spring 37 and three first cone springs 36 are assembled on the outer peripheral side of the first support member 33. The second support member 35 is inserted into the first support member 33, and the first corn spring 36 and the second corn spring 37 are sandwiched between the first support member 33 and the second support member 35 in the axial direction. The second support member 35 is fixed to the first support member 33 by welding, for example, in a state where the first cone spring 36 and the second cone spring 37 are compressed. As a result, the cone spring assembly 40 including the first cone spring 36, the second cone spring 37, the first support member 33, and the second support member 35 is assembled.

  On the other hand, the support bolt 31 is screwed into the pressure plate 3. The adjustment spring 39 is inserted into the trunk portion 31a of the support bolt 31, and the second engagement end 39b of the adjustment spring 39 is fitted into the hole 31c of the trunk portion 31a. Then, the first engagement end 39a of the adjustment spring 39 is inserted into the hole 34a (second hole) of the guide plate 34.

  Next, in a state where the adjustment spring 39 and the guide plate 34 are assembled to the support bolt 31, the holder 32 is screwed into the screw portion 31b. At this time, since the adjustment spring 39 is disposed on the axial direction engine side of the holder 32, the screwing operation of the holder 32 is facilitated as compared with the conventional case. Further, since the outer shape of the axial section of the head portion 32c of the holder 32 has a hexagonal shape as described above, the 32 can be easily screwed with a wrench or the like, and the second low release load characteristic realizing mechanism 30 is assembled. Attaching work becomes easy.

  When the holder 32 is screwed into the screw portion 31b, the holder 32 moves to the pressure plate 3 side, and eventually the first engagement end 39a and the flange portion 32b of the holder 32 contact each other in the axial direction. At this time, since the first engagement end 39a of the adjustment spring 39 is inserted into the hole 34a of the guide plate 34, the radial position of the first engagement end 39a is determined. In addition, since the radial position of the hole 32e of the flange portion 32b and the radial position of the hole 34a of the guide plate 34 are substantially the same, the first engagement end 39a of the adjustment spring 39 and the flange portion 32b The radial direction position with the hole 32e substantially coincides. Therefore, compared with the case where there is no guide plate 34, the first engagement end 39a of the adjustment spring 39 is easily hooked into the hole 32e of the holder 32, and the assembly work of the holder 32 and the adjustment spring 39 is facilitated. In order to realize the arrangement of the adjustment spring 39 on the engine side of the holder 32 in the axial direction, it is difficult to wind the adjustment spring 39 or attach it to the holder 32. However, as described above, the guide plate 34 This solves these problems.

  With the first engagement end 39a of the adjustment spring 39 hooked into the hole 32e of the holder 32, the holder 32 is further screwed. The cone spring assembly 40 and the intermediate member 38 b are fitted on the outer peripheral side of the first support member 33 with the holder 32 screwed to the support bolt 31 to a predetermined axial position. Then, the snap ring 38 a is fitted on the outer peripheral side of the holder 32, and the cone spring assembly 40 is assembled to the holder 32.

  As described above, in the clutch cover assembly 1, the assembly workability of the second low release load characteristic realizing mechanism 30 is greatly improved by the arrangement of the adjustment spring 39 and the holder 32 and the installation of the guide plate 34. To do.

(5) Clutch connection / release operation In this clutch cover assembly 1, the annular elastic portion 4a presses against the pressure plate 3 while a release device (not shown) does not apply a load to the tip of the lever portion 4b of the diaphragm spring 4. Is given. As a result, the friction member 53 of the clutch disk assembly 52 is pressed against the flywheel 51, and torque is transmitted to the clutch disk assembly 52 (clutch engagement state).

  When a release device (not shown) pulls out the tip of the lever portion 4b of the diaphragm spring 4 to the transmission side, the inner peripheral portion of the annular elastic portion 4a of the diaphragm spring 4 is lifted to the axial transmission side with the wire ring 5 as a fulcrum. Thereby, the annular elastic portion 4a does not press the pressure plate 3, the pressure plate 3 is pulled away from the friction member 53 by the strap plate 7, and finally the friction member 53 is separated from the flywheel 51 (clutch release state).

(6) Another Embodiment of Second Low Release Load Characteristic Realization Mechanism A second low release load characteristic realization mechanism 130 according to the second embodiment of the present invention will be described with reference to FIG. The second low release load characteristic realizing mechanism 130 is a mechanism for realizing the same function as the mechanism 30 of the above-described embodiment, and is provided in the clutch cover 102. FIG. 10 shows the clutch engaged state.

  The second low release load characteristic realizing mechanism 130 of the present embodiment includes a support bolt 131 (support member), a holder 132 (support engagement member), a snap ring 135, an intermediate ring 137, and a cone spring 136 (second Elastic member) and an adjustment spring 139 (third elastic member).

  The support bolt 131 has a body portion 131a and a screw portion 131b as in the above-described embodiment. Since the configuration of each unit is the same as that of the above-described embodiment, detailed description thereof is omitted.

  The holder 132 includes a holder main body 132a (supporting engagement member main body), an engagement portion 132f, a head portion 132b, and an annular protrusion 132c. The holder main body 132a is a cylindrical portion extending in the axial direction, and a screw 132d that is screwed into the screw portion 131b is formed on the inner peripheral surface. The holder main body 132 a is screwed with the screw portion 131 b of the support bolt 131. The engaging portion 132f is a portion extending in the axial direction from the end of the holder main body 132a on the axial engine side, and the engaging end 139a of the adjustment spring 139 is engaged therewith. The head 132b is a part formed so as to close the end of the holder main body 132a on the axial transmission side, and penetrates the hole 111 of the clutch cover 102 in the axial direction. The annular protrusion 132c is an annular portion formed on the outer peripheral side of the head 132b. A hexagonal hole 132e is formed at the center of the head portion 132b on the axial transmission side.

  The cone spring 136 is disposed on the outer peripheral side of the head 132b. The inner peripheral edge of the cone spring 136 is in contact with the annular protrusion 132c from the axial engine side, and the outer peripheral edge is in contact with the annular protrusion 11a formed around the hole 111 of the clutch cover 102 from the axial transmission side. A snap ring 135 is fitted on the outer peripheral side of the head 132b, and an intermediate ring 137 is sandwiched between the inner peripheral edge of the cone spring 136 and the snap ring 135 in the axial direction.

  As described above, the cone spring 136 can apply a load toward the axial transmission side to the structure including the holder 132 and the like. However, unlike the above-described embodiment, the second low release load characteristic realizing mechanism 130 does not have an elastic member corresponding to the second cone spring 37. Therefore, the load characteristic corresponding to the combined load characteristic (FIG. 7) of the second low release load characteristic realizing mechanism of the first embodiment is as shown in FIG. In this case, as shown in FIG. 11, the load is set to be zero at the time of engagement (when the clutch is engaged). Similarly to the above-described embodiment, the second low release load characteristic realizing mechanism 130 has a function of reducing the release load by applying a load to the holder 132 and the like in the axial transmission side during the clutch release operation. Have.

  Further, in the second low release load characteristic realizing mechanism 130, only one first cone spring 36 is disposed, so that the number of cone springs is three smaller than that in the above-described embodiment. As a result, the axial dimension of the second low release load characteristic realizing mechanism 130 is further shortened, and the second low release load characteristic realizing mechanism 130 does not protrude outward from the clutch cover 102. Thereby, the axial dimension of the clutch cover assembly can be further shortened.

  Since the number of cone springs is small, the structure of the holder 132 can be simplified, and the number of parts can be further reduced.

  The operation of the second low release load characteristic realizing mechanism 130 of the present embodiment is the same as that of the first embodiment, and thus detailed description thereof is omitted.

(7) Other Embodiments The above-described embodiments are merely examples of the present invention, and various modifications can be made without departing from the spirit of the present invention. For example, the embodiment is a pull type clutch cover assembly, but the present invention can also be applied to a push type clutch cover assembly.

  The specific structure of the first low release load characteristic realization mechanism and the second low release load characteristic realization mechanism can be changed, and in particular, the first low release load characteristic realization mechanism is a conventional one-piece cone spring structure. May be.

  Moreover, although the 2nd low release load characteristic implementation | achievement mechanism 130 of 2nd Embodiment consists of one cone spring, you may be comprised from the some cone spring similarly to the thing of 1st Embodiment.

The longitudinal cross-sectional schematic of the clutch cover assembly which concerns on 1st Embodiment of this invention. The longitudinal cross-sectional schematic of the clutch cover assembly which concerns on 1st Embodiment of this invention. The top view of the clutch cover assembly which concerns on 1st Embodiment of this invention. It is the elements on larger scale of Drawing 2, and is a figure for explaining the 2nd low release load characteristic realization mechanism. The longitudinal cross-sectional schematic of the 2nd unit of a 1st low release load characteristic implementation | achievement mechanism. The figure for demonstrating the pressing load characteristic. The figure for demonstrating the synthetic | combination characteristic of a 2nd low release load characteristic implementation | achievement mechanism. The figure for demonstrating the negative gradient characteristic obtained when a cushioning function is exhibited in a set load characteristic. The figure for demonstrating a release load characteristic. The longitudinal cross-sectional schematic of the 2nd low release load characteristic implementation | achievement mechanism 130 which concerns on 2nd Embodiment of this invention. The figure for demonstrating the load characteristic of the 2nd low release load characteristic implementation | achievement mechanism. The longitudinal cross-sectional schematic of the conventional clutch cover assembly. The longitudinal cross-sectional schematic of the conventional 2nd low release load characteristic implementation mechanism 230. FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Clutch cover assembly 2 Clutch cover 3 Pressure plate 4 Diaphragm spring 30 2nd low release load characteristic implementation mechanism 31 Support bolt (support member)
32 Holder (supporting engagement member)
36 First cone spring (second elastic member)
37 Second cone spring (second elastic member)
39 Adjustment spring (third elastic member)
51 Flywheel 52 Clutch Disc Assembly 53 Friction Member

Claims (9)

A clutch cover assembly for pressing and releasing a friction member with a cushioning function of a clutch disk assembly on an engine flywheel,
A clutch cover fixed to the flywheel;
A pressure plate connected to the clutch cover so as not to rotate relative to the clutch cover and sandwiching the friction member with the flywheel;
A diaphragm spring supported by the clutch cover and biasing the pressure plate toward the flywheel;
A first elastic member that is supported by the clutch cover and generates a load that opposes the urging force of the diaphragm spring, thereby flattening a change in the pressing load to the pressure plate with respect to a displacement amount of the diaphragm spring; ,
In the process of increasing the displacement amount of the diaphragm spring due to the cushioning effect of the friction member by generating a load that is supported by the clutch cover and counteracts the urging force of the diaphragm spring during the release operation, the pressure plate A second elastic member that reduces the pressing load of
A wear compensation mechanism for maintaining the posture of the second elastic member against wear of the friction member,
The wear compensation mechanism includes a support member extending from the pressure plate to the clutch cover side, and a support member that is screwed to the outer peripheral side of the support member and receives a load from the second elastic member to the friction member side in the axial direction. An engagement member; and a third elastic member that constantly applies torque to the support engagement member so that the support engagement member rotates in a direction in which the support engagement member moves axially opposite to the friction member.
The third elastic member is disposed on the friction member side in the axial direction of the support engagement member.
Clutch cover assembly. The third elastic member is disposed between the clutch cover and the pressure plate in the axial direction.
The clutch cover assembly according to claim 1. A clutch cover assembly for pressing and releasing a friction member with a cushioning function of a clutch disk assembly on an engine flywheel,
A clutch cover fixed to the flywheel;
A pressure plate connected to the clutch cover so as not to rotate relative to the clutch cover and sandwiching the friction member with the flywheel;
A diaphragm spring supported by the clutch cover and biasing the pressure plate toward the flywheel;
A first elastic member that is supported by the clutch cover and generates a load that opposes the urging force of the diaphragm spring, thereby flattening a change in the pressing load to the pressure plate with respect to a displacement amount of the diaphragm spring; ,
In the process of increasing the displacement amount of the diaphragm spring due to the cushioning effect of the friction member by generating a load that is supported by the clutch cover and counteracts the urging force of the diaphragm spring during the release operation, the pressure plate A second elastic member that reduces the pressing load of
A wear compensation mechanism for maintaining the posture of the second elastic member against wear of the friction member,
The wear compensation mechanism includes a support member extending from the pressure plate to the clutch cover side, and a support member that is screwed to the outer peripheral side of the support member and receives a load from the second elastic member to the friction member side in the axial direction. An engagement member; and a third elastic member that constantly applies torque to the support engagement member so that the support engagement member rotates in a direction in which the support engagement member moves axially opposite to the friction member.
The third elastic member is disposed between the clutch cover and the pressure plate in the axial direction.
Clutch cover assembly. The support engagement member covers an end of the support member;
The clutch cover assembly according to any one of claims 1 to 3. A clutch cover assembly for pressing and releasing a friction member with a cushioning function of a clutch disk assembly on an engine flywheel,
A clutch cover fixed to the flywheel;
A pressure plate connected to the clutch cover so as not to rotate relative to the clutch cover and sandwiching the friction member with the flywheel;
A diaphragm spring supported by the clutch cover and biasing the pressure plate toward the flywheel;
A first elastic member that is supported by the clutch cover and generates a load that opposes the urging force of the diaphragm spring, thereby flattening a change in the pressing load to the pressure plate with respect to a displacement amount of the diaphragm spring; ,
In the process of increasing the displacement amount of the diaphragm spring due to the cushioning effect of the friction member by generating a load that is supported by the clutch cover and counteracts the urging force of the diaphragm spring during the release operation, the pressure plate A second elastic member that reduces the pressing load of
A wear compensation mechanism for maintaining the posture of the second elastic member against wear of the friction member,
The wear compensation mechanism includes a support member extending from the pressure plate to the clutch cover side, and a support member that is screwed to the outer peripheral side of the support member and receives a load from the second elastic member to the friction member side in the axial direction. An engagement member; and a third elastic member that constantly applies torque to the support engagement member so that the support engagement member rotates in a direction in which the support engagement member moves axially opposite to the friction member.
The support engagement member covers an end of the support member;
Clutch cover assembly. The support engagement member includes a cylindrical support engagement member main body that is screwed with an outer peripheral side of the support member, and an annular shape that is formed at one end of the support engagement member main body and receives torque from the third elastic member. Having an engaging portion and a head for closing the other end of the support engaging member main body,
The clutch cover assembly according to claim 5 . The outer shape of the axial cross section of the head is a polygon,
The clutch cover assembly according to claim 6. The wear compensation mechanism further includes a guide plate with which one end of the third elastic member is engaged between the support engagement member and the third elastic member in the axial direction.
The clutch cover assembly according to any one of claims 5 to 7. The engaging portion has a first hole with which one end of the third elastic member is engaged,
The guide plate has a second hole with which one end of the third elastic member is engaged,
The radial position of the first hole is substantially the same as the radial position of the second hole.
The clutch cover assembly according to claim 8.

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