JP2006170388A - Friction generating mechanism - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a friction generating mechanism with a cone spring free of an assembling error. <P>SOLUTION: The friction generating mechanism 8 comprises a second bush 15 and the second cone spring 17. The second cone spring 17 has a plurality of first cutout portions 17a arranged at equal intervals in the circumferential direction and a plurality of second cutout portions 17b arranged between the adjacent first cutout portions 17a at equal intervals in the circumferential direction. The second bush 15 has at least one first protrusion portion 15c for engaging with the first cutout portion 17a in the rotating direction and at least one second protrusion portion 15d for engaging with the second cutout portion 17b in the rotating direction. When the second cone spring 17 is assembled inside out on the second bush 15, either the first cutout portion 17a cannot engage with the first protrusion portion 15c or the second cutout portion 17b cannot engage with the second protrusion portion 15d. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a friction generating mechanism, and more particularly to a mechanism for attenuating torsional vibration by generating frictional resistance when two rotating members rotate relative to each other.

  A damper mechanism used in a clutch disk assembly of a vehicle elastically connects a pair of disc-shaped input side plates, an output side hub having a flange on the outer periphery, and the pair of input side plates and the flange in the rotational direction. A torsion spring, and a friction generating mechanism disposed between the input side plate and the output side hub.

The friction generating mechanism includes, for example, a friction member that abuts on the flange of the output side hub, and a cone spring that is disposed between the friction member and one of the input side plates and presses the friction member against the flange. ing. The friction member has an annular main body and a plurality of protrusions that protrude in the axial direction from the main body and engage with the input side plate so as to rotate together. Each protrusion is inserted into a hole formed in the input side plate and engaged in the rotational direction. That is, both ends of the protrusion in the rotation direction are in contact with both ends of the hole in the rotation direction, so that the friction member can move in the axial direction with respect to the input side plate, but cannot move in the rotation direction. The cone spring is disposed so as not to rotate relative to the friction member. Specifically, the cone scone spring has a plurality of notches arranged in the circumferential direction on the inner peripheral side. The friction member has a plurality of protrusions arranged in the circumferential direction to engage with the notch. The cone spring is sandwiched between the input side plate and the friction member while being compressed in the axial direction. With these configurations, the cone spring engages with the friction member so as not to rotate relative to the friction member, and biases the friction member in the axial direction (see, for example, Patent Document 1).
JP 2001-355679 A

  In the cone spring described above, since the notches are arranged uniformly in the circumferential direction, the protrusions on the friction member side are also arranged uniformly in the circumferential direction. For this reason, the reverse side of the cone spring may be assembled reversely with respect to the friction member when the friction generating mechanism is assembled. On the other hand, the inner peripheral portion of the cone spring is in contact with the friction member in the axial direction, and the outer peripheral portion is in contact with the input side plate in the axial direction. Then, when the cone spring is assembled upside down, the portion of the cone spring that contacts the friction member and the input side plate is switched between the inner peripheral portion and the outer peripheral portion. On the other hand, since the friction member is an annular member, the friction member may not exist at a position corresponding to the outer periphery of the cone spring, and the outer periphery of the cone spring and the friction member may not contact in the axial direction. obtain. In the assembled state, the friction member cannot be urged in the axial direction with respect to the flange portion, which is not preferable because the friction generation mechanism does not perform its original function. Further, the conventional friction member and cone spring have a structure in which an operator is unaware of such misassembly.

  An object of the present invention is to prevent erroneous assembly of cone springs by devising the structure of a friction generating mechanism.

  The friction generating mechanism according to claim 1 is for generating friction between the first rotating member and the second rotating member arranged so as to be relatively rotatable to attenuate torsional vibration. The friction generating mechanism is an annular shape that engages with the first rotating member in the rotational direction and abuts against the second rotating member and slides on the second rotating member when the first and second rotating members rotate relative to each other to generate friction. And an annular elastic member disposed between the first rotating member and the friction member for biasing the friction member in the axial direction with respect to the second rotating member. The elastic member includes a plurality of first cutout portions arranged at equal intervals in the circumferential direction and a plurality of second cutout portions arranged at equal intervals in the circumferential direction between adjacent first cutout portions. Have. The friction member has at least one first protrusion that engages with the first notch in the rotation direction, and at least one second protrusion that engages with the second notch in the rotation direction. When the elastic member is assembled reversely with respect to the friction member, any one of the first notch and the first protrusion and the second notch and the second protrusion cannot be engaged.

  Since the cut-out portions of the conventional elastic member are arranged at equal intervals in the circumferential direction, there are cases where the front and back are assembled in reverse when assembled to the friction member as described above. However, in this friction generating mechanism, when the elastic member is assembled upside down with respect to the friction member, one of the first notch and the first protrusion, and the second notch and the second protrusion is engaged. Since it cannot be combined, the elastic member cannot be assembled to the friction member. Thereby, in this friction generating mechanism, it is possible to prevent erroneous assembly of the elastic members.

  According to a second aspect of the present invention, in the friction generating mechanism according to the first aspect, the circumferential distances from the first notch portion to the two adjacent second notch portions are different from each other.

  In this friction generating mechanism, since the circumferential distances from the first notch portion to the two adjacent second notch portions in the elastic member are different from each other, the elastic member is assembled reversely with respect to the friction generating mechanism. In this case, any one of the positions of the first protrusion and the first notch and the positions of the second protrusion and the second notch is not matched, and the elastic member cannot be assembled to the friction member. Thereby, in this friction generating mechanism, the erroneous assembly of the elastic member can be surely prevented.

  According to a third aspect of the present invention, there is provided the friction generating mechanism according to the first or second aspect, wherein a circumferential distance from one first notch to one adjacent second notch is related to one first notch. It is larger than the distance in the circumferential direction from the mating first protrusion to the second protrusion engaging the other second notch adjacent to one first notch.

  Since this friction generating mechanism has the above dimensional relationship, when the elastic member is assembled upside down with respect to the friction member, the first notch and the second notch are between the first protrusion and the second protrusion. The protruding part between the notches cannot be fitted. Thereby, in this friction generating mechanism, it is possible to more reliably prevent erroneous assembly of the elastic members.

  According to a fourth aspect of the present invention, there is provided the friction generating mechanism according to any one of the first to third aspects, wherein the circumferential direction from the circumferential center of the second notch portion to the circumferential center of the two adjacent first notch portions is the same. Each distance is different.

  According to a fifth aspect of the present invention, there is provided the friction generating mechanism according to any one of the first to fourth aspects, wherein the circumferential width of the first notch is larger than the circumferential width of the second notch. The circumferential width is greater than the circumferential width of the second notch.

  In this friction generating mechanism, since the circumferential width of the first protrusion is larger than the circumferential width of the second notch, the second protrusion with respect to the first protrusion when the elastic member is assembled to the friction member. The notch cannot be fitted. That is, only the first notch can be fitted into the first protrusion. As a result, when the elastic member is assembled reversely with respect to the friction member, the positions of the second protrusion of the friction member and the second notch of the elastic member are not surely matched, and the second notch is not aligned with the second notch. It cannot be fitted into the protrusion. Thereby, in this friction generating mechanism, the erroneous assembly of the elastic member can be surely prevented.

  According to a sixth aspect of the present invention, in the friction generating mechanism according to any one of the first to fifth aspects, the inner peripheral portion of the elastic member is in contact with the friction member in the axial direction, and the outer peripheral portion of the elastic member is in the axial direction with the first rotating member. The friction member has an annular portion that abuts the inner peripheral portion of the elastic member in the axial direction. The first and second cutouts are arranged on the inner peripheral side of the elastic member. The first and second protrusions protrude from the annular part in the axial direction.

  According to a seventh aspect of the present invention, in the friction generating mechanism according to any one of the first to sixth aspects, the first rotating member has at least one hole at a position corresponding to the first protrusion. The first protrusion is inserted into the hole.

  In this friction generating mechanism, since the first protrusion is inserted into the hole of the first rotating member, the friction member can be connected to the first rotating member so as not to be relatively rotatable.

  According to an eighth aspect of the present invention, in the friction generating mechanism according to any one of the first to seventh aspects, the first rotating member is composed of a pair of disk-shaped input side plates. The second rotating member is a cylindrical output hub arranged on the inner peripheral side of the pair of input side plates, and a disc shape arranged on the outer peripheral side of the output hub and between the pair of input side plates. The flange part is comprised. The pair of input side plates and the flange portion are elastically coupled in the rotation direction. The flange portion and the output side hub are elastically connected in the rotational direction. The friction member is arranged to slide on the flange portion. The elastic member is disposed between the friction member and one input plate.

  A friction generation mechanism according to a ninth aspect of the present invention is the friction generation mechanism according to any one of the first to eighth aspects, wherein the friction generation mechanism is disposed on the inner peripheral side of the friction member so as to slide with the output side hub and the flange portion, and engages the friction member in the rotational direction. An annular inner peripheral side disposed between the annular inner peripheral friction member and the inner peripheral friction member and the one input side plate for biasing the inner peripheral friction member in the axial direction against the flange portion It further includes an elastic member and an annular third friction member that is disposed between the other input side plate and the flange portion so as to slide with the flange portion and engages with the other input side plate in the rotational direction.

  In the friction generating mechanism and the damper mechanism according to the present invention, it is possible to reliably prevent the cone springs from being misassembled.

An embodiment of the present invention will be described with reference to the drawings.
1. Configuration of Clutch Disc Assembly (1) Overall Configuration FIG. 1 shows a clutch disc assembly provided with a friction generating mechanism as one embodiment of the present invention shown in FIG. The clutch disk assembly 1 is a device for transmitting and interrupting torque from an engine (not shown) arranged on the left side of FIG. 1 to a transmission (not shown) arranged on the right side of FIG. In FIG. 1, OO is the rotation axis of the clutch disk assembly 1. In FIG. 2, R1 is the rotational direction (circumferential direction) of the clutch disk assembly 1, and R2 is the opposite direction.

  The clutch disk assembly 1 mainly includes a hub 2 (second rotating member), a clutch plate 3 and a retaining plate 4 (first rotating member), a hub flange 5 (flange portion), a hub flange 5 and a hub. 2 and a large torsion spring 7 (torsion spring) for elastically connecting the clutch plate 3 and retaining plate 4 and the hub flange 5 in the rotational direction. ), And a friction generating mechanism 8 for generating a predetermined friction when relative rotation occurs between the clutch plate 3 and retaining plate 4 and the hub 2.

  The hub 2 is disposed at the center of the clutch disk assembly 1 and is connected to a transmission shaft (not shown). The hub 2 includes a cylindrical boss 2a extending in the axial direction and a flange 2b integrally formed on the outer periphery of the boss 2a. As shown in FIGS. 2 to 4, a plurality of protrusions 2 c are formed on the outer periphery of the flange 2 b at equal intervals in the rotation direction. As shown in FIG. 3, notches 2d for receiving both ends in the rotational direction of a small torsion spring 6 described later are formed at two locations facing the radial direction of the flange 2b. Further, a spline hole 2e is formed on the inner peripheral side of the boss 2a so as to engage with the transmission shaft.

  The hub flange 5 is a disk-shaped plate, and is disposed on the outer periphery of the flange 2 b of the hub 2. As is apparent from FIG. 2, the hub flange 5 has four protrusions 5 a extending outward in the radial direction. Each protrusion 5a is formed with a window hole 5b extending in the rotation direction. An outer notch 5c is formed between the protrusions 5a. An inner peripheral side annular portion 5f is provided on the inner peripheral side of the protruding portion 5a. On the inner peripheral edge of the inner peripheral side annular portion 5f, teeth 5d are formed at the corresponding portions between the protrusions 2c of the hub 2. A predetermined gap is secured in the rotation direction between the protrusion 2c and the tooth 5d, so that the hub 2 and the hub flange 5 can be rotated to a predetermined angle. Inner notches 5e are formed at two locations corresponding to the notches 2d of the hub 2 on the inner peripheral side of the hub flange 5. A small torsion spring 6 is disposed in the notch 2d and the inner notch 5e.

  The clutch plate 3 and the retaining plate 4 are disposed on both sides of the hub flange 5. The clutch plate 3 and the retaining plate 4 are a pair of generally disc-shaped members, and are rotatably disposed on the outer periphery of the boss 2a of the hub 2. The clutch plate 3 and the retaining plate 4 are fixed to each other by the contact pin 11 at the outer peripheral portion. The contact pin 11 is inserted through the outer notch 5 c formed in the hub flange 5. Since a predetermined gap is secured in the rotation direction between the contact pin 11 and the outer notch 5c, the clutch plate 3, the retaining plate 4 and the hub flange 5 can be relatively rotated within a predetermined angle.

  A friction coupling portion 10 is disposed on the outer periphery of the clutch plate 3. The friction coupling portion 10 mainly includes a cushioning plate 12 and an annular friction facing 13 fixed to both sides of the cushioning plate 12 in the axial direction. The cushioning plate 12 has an annular portion 12a that is continuous in an annular shape, and a plurality of cushioning portions 12b that are formed to protrude from the annular portion 12a to the outer peripheral side. A part of the annular portion 12 a protrudes toward the inner peripheral side, and the protruding portion is fixed to the clutch plate 3 by the contact pin 11.

  In the clutch plate 3 and the retaining plate 4, a window hole 3a and a window hole 4a are formed at positions corresponding to the window holes 5b of the hub flange 5, respectively. A large torsion spring 7 is disposed in the window hole 3a and the window hole 4a. On both sides in the radial direction of each window hole 3a and window hole 4a, a pressing portion 3b and a pressing portion 4b cut and raised outward in the axial direction are formed. The large torsion spring 7 includes two sets of a first spring assembly 7a and a second spring assembly 7b. The first spring assemblies 7a are respectively disposed in the window holes 5b of the hub flange 5 that are opposed to each other in the radial direction, and are configured by a large-diameter torsion spring and a small-diameter torsion spring disposed inside thereof. . Both ends of the first spring assembly 7a in the rotational direction abut against both ends of the hub flange 5 in the rotational direction of the window hole 5b, both ends of the clutch plate 3 in the rotational direction of the window hole 3a, and both ends of the retaining plate 4 in the rotational direction of the window hole 4a. ing. The second spring assembly 7b is disposed in the window hole 5b of the hub flange 5 facing in the radial direction, and includes a torsion spring and a flow traverser 7c disposed on the inside thereof. The rotation direction ends of the torsion spring of the second spring assembly 7b are the rotation direction ends of the window hole 5b of the hub flange 5, the rotation direction ends of the window hole 3a of the clutch plate 3, and the rotation direction of the window hole 4a of the retaining plate 4. It is in contact with both ends. However, the length of the flow traverser 7c is shorter than both ends in the rotational direction of each window hole. That is, the flow traverser 7c is movable in the rotational direction between both ends in the rotational direction of each window hole.

(2) Configuration of Friction Generation Mechanism As shown in FIGS. 1 and 5, the friction generation mechanism 8 is formed between the inner peripheral portion of the clutch plate 3 and the inner peripheral portion of the retaining plate 4 and on the outer peripheral side of the boss 2a. Is arranged. The friction generating mechanism 8 includes a first bush 14 (inner peripheral friction member), a second bush 15 (friction member), a first cone spring 16 (inner peripheral elastic member), and a second cone spring 17 ( Elastic member) and a third bush 18 (third friction member). The first to third bushes 14, 15, 18 are each formed of, for example, a nylon resin.

  The first bush 14 is a resin disk-like plate. As shown in FIGS. 5 to 7, the inner periphery of the first bush 14 is close to the boss 2 a, and one side surface is in contact with the side surface on the transmission side of the flange 2 b of the hub 2. The first bush 14 is mainly composed of a disk-shaped portion 14a and four protrusions 14d extending radially outward from the disk-shaped portion 14a. In addition, the inner peripheral portion of the disc-shaped portion 14a includes a first annular portion 14b that protrudes in the axial direction from other portions, and a second annular portion that protrudes further in the axial direction at the inner peripheral portion of the first annular portion 14b. Part 14c.

  A first cone spring 16 is disposed between the first bush 14 and the retaining plate 4. The first cone spring 16 has an outer peripheral portion supported by the retaining plate 4 and an inner peripheral portion in contact with the first annular portion 14 b of the first bush 14. The first cone spring 16 is disposed in a state compressed in the axial direction, and presses the first bush 14 against the flange 2 b of the hub 2. As shown in FIG. 11, the first cone spring 16 has a plurality of notches 16a formed on the outer peripheral side. This notch 16a is for reducing a change in the urging force of the first cone spring 16 when the posture of the first cone spring 16 changes due to wear of the first bush 14.

  The second bush 15 is a disk-like member as is apparent from FIGS. 8 to 10 and 13, and is substantially flush with the plane on which the first bush 14 is disposed on the outer peripheral side of the first bush 14. And are arranged concentrically. The 2nd bush 15 is mainly comprised from the disk-shaped main-body part 15a. An annular portion 15b is formed on the inner peripheral side of the main body portion 15a so as to protrude from the other portion toward the axial transmission side. The engine-side side surface 15f of the main body portion 15a is in contact with the axial-side transmission-side side surface 5g of the inner peripheral side annular portion 5f of the hub flange 5, and the first sliding surface 31 is formed by both. Four notches 15e are formed at equal intervals in the rotational direction on the side surface of the annular portion 15b on the transmission side. In this notch 15e, a projection 14d of the first bush 14 is engaged so as not to be relatively rotatable in the rotational direction and movable in the axial direction. A predetermined gap is secured between the projection 14d and the notch 15e in the axial direction.

  Four first protrusions 15c extending to the transmission side are formed between the adjacent notches 15e on the annular portion 15b. The first protrusion 15c is divided into two in the radial direction by a slit extending in the axial direction. The first protrusion 15 c is inserted into a hole 4 c formed in the retaining plate 4. The first protrusion 15c is in contact with the hole 4c in the rotational direction and the radial direction. As for the 1st projection part 15c, two projection parts are elastically urged | biased by the radial direction with respect to the hole 4c. Further, a claw is formed at the tip of the first protrusion 15c to prevent the first protrusion 15c from dropping out of the hole 4c. In the annular portion 15b, eight second protrusions 15d extending to the transmission side are further formed between the notches 15e and the first protrusions 15c. The second projecting portion 15 d is for preventing an erroneous assembly of the second cone spring 17 described later, and is engaged with the second notch portion 17 b of the second cone spring 17.

  The second cone spring 17 is disposed between the second bush 15 and the retaining plate 4. The biasing force of the second cone spring 17 is set to be larger than the biasing force of the first cone spring 16. The second cone spring 17 is compressed in the axial direction, and the outer peripheral portion is in contact with the retaining plate 4, and the inner peripheral portion is in contact with the transmission side surface of the annular portion 15 b of the second bush 15. In this way, the second cone spring 17 urges the second bush 15 against the transmission-side side surface 5 g of the inner peripheral side annular portion 5 f of the hub flange 5. As shown in FIG. 12, the second cone spring 17 is formed with a plurality of first notches 17a and second notches 17b on the inner peripheral side. The first notch 17a is formed to reduce the change in the urging force of the second cone spring 17 when the posture of the second cone spring 17 changes due to wear of the second bush 15.

  The first cutouts 17a are evenly arranged in the circumferential direction. The 2nd notch part 17b is arrange | positioned between adjacent 1st notch parts 17a, and is arrange | positioned at equal intervals in the circumferential direction. The circumferential distance from the circumferential center of the second notch 17b to the circumferential center of the two adjacent first notches 17a is different. Further, the circumferential distances from the first notch 17a to the two adjacent second notches 17b are different from each other.

  The first notch 17a of the second cone spring 17 corresponds to the first protrusion 15c and the notch 15e of the second bush 15, and the first notch 17a is fitted into the first protrusion 15c. The second cutout portion 17b corresponds to the second cutout portion 17b of the second bush 15, and the second cutout portion 17b is fitted into the second protrusion 15d. The circumferential distance from the first notch 17a to the adjacent one of the second notches 17b is such that the first protrusion 15c that engages with the first notch 17a engages with the other second notch 17b. The distance in the circumferential direction to the second protrusion is larger.

  The circumferential width of the first notch 17a is larger than the circumferential width of the second notch 17b, and the circumferential width of the first protrusion 15c is the circumferential width of the second notch 17b. Is bigger than. Further, a first projecting portion 17c and a second projecting portion 17d projecting inward in the radial direction are formed between the first notch portion 17a and the second notch portion 17b. The circumferential width of the first protrusion 17c is smaller than the circumferential width of the second protrusion 17d.

  Since the cut-out portions of the conventional elastic member are arranged at equal intervals in the circumferential direction, there are cases where the front and back are assembled in reverse when assembled to the friction member as described above. However, in the friction generating mechanism 8, the positional relationship between the first notch 17a and the second notch 17b and the positional relationship between the first protrusion 15c and the second protrusion 15d are as described above. When the second cone spring 17 is assembled to the friction generating mechanism in reverse, the positions of the second protrusion 15d of the second bush 15 and the second notch 17b of the second cone spring 17 are not aligned. The second notch 17b cannot be fitted into the second protrusion 15d. In addition, since the circumferential width of the first protrusion 15c is larger than the circumferential width of the second notch 17b, the first protrusion 15c is attached to the second bush 15 when the second cone spring 17 is assembled. On the other hand, the second notch 17b cannot be fitted. That is, only the first cutout portion 17a can be fitted into the first protrusion 15c. As a result, when the second cone spring 17 is assembled to the second bush 15 in reverse, the positions of the second protrusion 15d of the second bush 15 and the second notch 17b of the second cone spring 17 are The second notch portion 17b cannot be fitted into the second protrusion portion 15d. As a result, the friction generating mechanism 8 can prevent erroneous assembly of the second cone spring 17.

  The first bush 14, the second bush 15, the first cone spring 16 and the second cone spring 17 described above are assembled to the retaining plate 4 to constitute a sub-assembly. These members are prevented from coming off the retaining plate 4 in the axial direction by the engagement of the first protrusion 15 c of the second bush 15 and the hole 4 c of the retaining plate 4.

  As shown in FIG. 1, the third bush 18 is disposed between the inner peripheral portion of the clutch plate 3 and the flange 2 b of the hub 2 and the inner peripheral side annular portion 5 f of the hub flange 5. It has the main-body part 18a and the some snap protrusion 18b which protrudes in an axial direction from one side surface of the main-body part 18a. A transmission-side side surface 18d of the main body 18a is in contact with the side surface of the flange 2b and the side surface 5h of the inner peripheral side annular portion 5f of the hub flange 5 on the axial engine side. A second sliding surface 32 is formed by the side surface 18d and the side surface 5h on the axial engine side. Further, the side surface 18 e on the axial direction engine side of the main body 18 a is in contact with the clutch plate 3.

  The snap projection 18 b is engaged in a hole 3 c formed in the clutch plate 3. The shape of the snap protrusion 18b is the same as that of the first protrusion 15c described above. An annular projecting portion 18 c extending toward the axial engine side is formed on the inner peripheral portion of the third bush 18. The inner peripheral surface of the clutch plate 3 is in contact with the outer peripheral surface of the protruding portion 18c. The third bush 18 described above is assembled to the clutch plate 3 to constitute a sub-assembly.

  The structure for generating a high hysteresis torque in the second stage of torsional characteristics in the friction generating mechanism 8 will be described in more detail. The second cone spring 17 is compressed in the axial direction. As a result, the second bush 15 is biased to the hub flange 5, and the third bush is biased to the hub flange 5 via 3 and 4. When the 3 and the hub flange 5 rotate relative to each other, the second bush 15 and the third bush 18 rotate integrally with the plates 3 and 4 and slide relative to the hub flange 5.

2. As described above, the second cone spring 17 has a structure in which the second cone spring 17 cannot be assembled to the second bush 15 upside down. FIG. 14 shows a state in which the second bush 15 and the second cone spring 17 are correctly assembled, and FIG. 15 shows a state in which the second cone spring 17 is assembled with the second bush 15 upside down. As shown in FIG. 14, in the correct assembly state, the first notch 17a is fitted into the first projection 15c, and the second notch 17b is fitted into the second projection 15d. On the other hand, as shown in FIG. 15, in the state where the second bush 15 is assembled to the second cone spring 17 upside down, the one end 17e in the circumferential direction of the second protrusion 17d of the second cone spring 17 is It interferes with the second protrusion 15d. When the state shown in FIG. 15 is reached, the friction generating mechanism 8 cannot be assembled, and thus the second cone spring 17 can be prevented from being assembled incorrectly. Then, by appropriately setting the dimensions around the notches 17a and 17b and the protrusions 15c and 15d, when the second cone spring 17 is assembled to the second bush 15 upside down, the figure is surely shown. 15 can be obtained.

FIG. 16 shows a dimensional relationship diagram around the notch and the protrusion. In FIG. 16, the 2nd cone spring 17 is represented by the continuous line, and the 1st projection part 15c and the 2nd projection part 15d of the 2nd bush 15 are represented by the broken line. The dimensional relationship necessary for each part will be described below. In addition, each symbol shown in FIG. 16 indicates the following dimensions when the second cone spring 17 and the second bush 15 are arranged so that the circumferential centers of the first notch 17a and the first protrusion 15c coincide. Etc.
P: center line of the first notch 17a and the first protrusion 15c Q: second cut portion 17b and the center line of the second protrusion 15d _{A 1:} circumferential width of the first notch portion 17a (m)
A ₂ : Width in the circumferential direction of the second notch 17b [m]
L ₁ : A gap [m] formed between the first notch 17a and the first protrusion 15c in the circumferential direction.
L ₂ : A gap [m] formed between the second notch 17b and the second protrusion 15d in the circumferential direction.
α ₁ : Center angle [°] formed between adjacent first cutout portions 17a
α ₂ : Center angle [°] formed between the second notch and one of the adjacent first notches
X ₁ : a circumferential clearance [m] formed between the first protrusion 15c and the second protrusion 15d, with the first protrusion 17c being fitted therein.
X ₂ : circumferential width [m] of the second protrusion 17d adjacent to the first protrusion 17c
r: Radius [m] on the outer peripheral side of the first notch 17a and the second notch 17b
(1) Dimensions 1
Because a part of the second protrusion 17d of the second cone spring 17 interferes with the second protrusion 15d of the second bush 15 with the second cone spring 17 assembled to the second bush 15 upside down. First, the relationship shown below is required.
X ₁ <X ₂ (a)
Here, X ₁ and X ₂ can be represented by the following equations.
_{X 1 = α 2/360 ×} 2 × π × r-A 1/2 + L 1 -A 2/2 + L 2 ···· (b)
_{X 2 = (α 1 -α 2} ) / 360 × 2 × π × r-A 1/2-A 2/2 ···· (c)
From the above formulas (a) to (c), the following formula can be derived.
L ₁ + L ₂ <(α ₁ −2 × α ₂ ) × π × r / 180 (d)
Therefore, if the dimensions of each part are determined so that the relationship of the formula (d) is established, a part of the second projecting part 17d interferes with the second projecting part 15d, so that the second cone spring 17 is connected to the second bush 15 Can not be assembled against. As a result, the friction generating mechanism 8 can more reliably prevent erroneous assembly of the second cone spring 17 with respect to the second bush 15.

(2) Dimensions 2
In the conventional cone spring, the notch portions are evenly arranged in the circumferential direction, and the widths of the notch portions in the circumferential direction are all the same. However, the second cone spring 17, a first notch 17a and the second cut portion 17b has a different circumferential width _A 1, _{A 2,} respectively. Therefore, there is a possibility that the second cone spring 17 is misassembled with respect to the second bush 15 in the rotational direction. If the second cone spring 17 is misassembled in the rotational direction, the second cone spring 17 and the second bush 15 may not interfere with each other as described above even if the second cone spring 17 is misassembled upside down. Therefore, it is also important to prevent erroneous assembly of the second cone spring 17 in the rotational direction.

The second cone spring 17, the width _{A 1} of the circumferential direction of the first notch 17a is larger than the circumferential width _{A 2} of the second cut portion 17b, the width of the first protrusion 15c and the second notch It is larger than the width _{a 2} circumferentially of 17b. That is, the second notch portion 17b cannot be fitted into the first protrusion 15c. As a result, the friction generating mechanism 8 can prevent erroneous assembly in the rotational direction of the second cone spring 17, and thus more reliably prevent reverse assembly of the second cone spring 17 with respect to the second bush 15. be able to.

(3) Dimensional relation 3
Furthermore, satisfying the following dimensional relationship is effective in preventing erroneous assembly. FIG. 17A shows a state where the second corn spring 17 is correctly assembled, and FIG. 17B shows a state where the second corn spring 17 is assembled upside down. B ₁ shows a gap between the second protrusion 15d and the retaining plate 4 in the axial direction in FIG. B ₂ indicates the thickness of the second cone spring 17.

As shown in FIG. 17B, when the second corn spring 17 is assembled to the second bush 15 upside down, the second corn spring 17 becomes the second projection 15d of the retaining plate 4 and the second bush 15. It is sandwiched between. At this time, if, for example, B ₂ <B ₁ , the second bush 15 is placed at a predetermined position with respect to the retaining plate 4 even though the second protrusion 17d and the second protrusion 15d interfere with each other. Since it can be assembled, the friction generating mechanism 8 can be assembled. However, when B ₁ <B ₂ , the second bush 15 cannot be assembled at a predetermined position with respect to the retaining plate 4 when the second projecting portion 17d interferes with the second projecting portion 15d. Thus, the following formula (e)
B ₁ <B ₂ ... (E)
By determining the dimensions of each part so that the above relationship is established, the friction generating mechanism 8 cannot be assembled when the second cone spring 17 is misassembled. As a result, the friction generating mechanism 8 is more effective in preventing erroneous assembly of the second cone spring 17 with respect to the second bush 15.

  As described above, if the dimensions of the respective parts are determined so as to satisfy the dimensional relationships 1 to 3, erroneous assembly of the second cone spring 17 can be prevented more reliably.

3. Assembling Work Procedure of Friction Generating Mechanism The assembling work procedure of the friction generating mechanism 8, particularly the assembling work procedure of the second bush 15 and the second cone spring 17, will be described with reference to FIGS. 1 and 5. First, the first notch 17 a and the second notch 17 b of the second cone spring 17 are fitted into the first protrusion 15 c and the second protrusion 15 d of the second bush 15. At this time, the second cone spring 17 is assembled so that the inner peripheral portion thereof contacts the second bush 15 and the outer peripheral portion contacts the retaining plate 4. Here, even when the worker assembles the second cone spring 17 upside down, the circumferential one end 17e of the second notch 17b interferes with the second protrusion 15d as described above. For this reason, the second cone spring 17 cannot be assembled to the second bush 15. Thereby, the incorrect assembly with respect to the 2nd bush 15 of the 2nd cone spring 17 can be prevented reliably. After the second cone spring 17 is assembled to the second bush 15, the first bush 14 is assembled to the second bush 15. Specifically, the protrusion 14 d of the first bush 14 is fitted into the notch 15 e of the second bush 15. In this state, the first protrusion 15 c of the second bush 15 is inserted into the hole 4 c of the retaining plate 4. As a result, the first bush 14, the second bush 15, and the second cone spring 17 are assembled to the retaining plate 4 without being misassembled.

4). Operation of Clutch Disc Assembly Next, the operation of the clutch disc assembly 1 will be described.

  When the friction facing 13 is pressed against a flywheel (not shown) on the engine side, the torque of the flywheel is input to the clutch plate 3 and the retaining plate 4. This torque is transmitted to the hub 2 via the large torsion spring 7, the hub flange 5, and the small torsion spring 6, and is further output to a transmission-side shaft (not shown).

  When torque fluctuation is transmitted from the engine-side flywheel (not shown) to the clutch disc assembly 1, relative rotation occurs between the plates 3, 4 and the hub flange 5 and the hub 2, and the small torsion spring 6 and The large torsion spring 7 is compressed in the rotational direction.

  More specifically, in the region where the torsion angle is small, only the small torsion spring 6 is compressed, and the first bush 14 and the third bush 18 slide relative to the flange 2b of the hub 2. As a result, characteristics of low rigidity and low hysteresis torque can be obtained.

  When the torsional angle of the clutch disk assembly 1 increases, the compression of the small torsion spring 6 is stopped, and relative rotation occurs between the hub flange 5 and the hub 2 that rotate integrally with the plates 3 and 4. At this time, the large torsion spring 7 is compressed, and the second bush 15 and the third bush 18 slide on the hub flange 5. Here, characteristics of high rigidity and high hysteresis torque can be obtained as compared with the case where the small torsion spring 6 is compressed.

5. Other Embodiments The friction generating mechanism of the present invention is not limited to the above-described embodiments, and various changes or modifications can be made without departing from the scope of the present invention. Other embodiments will be described below.

(1) Clutch disk assembly In the above-described embodiment, the clutch disk assembly 1 has been described as an example, but the present invention is not limited to this. Therefore, the friction generating mechanism 8 according to the present invention is applicable as long as it attenuates the torsional vibrations of the two rotating bodies.

(2) Second Cone Spring In the above-described embodiment, the first cutout portion 17a and the second cutout portion 17b of the second cone spring 17 are disposed on the inner peripheral side, but may be disposed on the outer peripheral side. . In this case, the 1st projection part 15c and the 2nd projection part 15d of the 2nd bush 15 will be arrange | positioned in the position corresponding to the 1st notch part 17a and the 2nd notch part 17b.

1 is a schematic longitudinal sectional view of a clutch disk assembly according to an embodiment of the present invention. The II arrow line view in FIG. 1 where a part was cut off. The top view of a hub. IV-IV sectional drawing of FIG. The enlarged view of the circle A part of FIG. The top view of the 1st bush. VI-VI sectional drawing of FIG. The top view of a 2nd bush. XI-XI sectional drawing of FIG. XX sectional drawing of FIG. The top view of a 1st cone spring. The top view of a 2nd cone spring. The elements on larger scale of FIG. The right assembly state figure of the 2nd bush 15 and the 2nd cone spring 17. FIG. The assembly state figure in the case of assembling the 2nd cone spring 17 with respect to the 2nd bush 15 upside down. The top view which shows the dimensional relationship of a notch part and a projection part periphery. The longitudinal cross-sectional view which shows the dimensional relationship of a notch part and a projection part periphery.

Explanation of symbols

1 Clutch disc assembly 2 Hub (second rotating member)
3 Clutch plate (first rotating member)
4 Retaining plate (first rotating member)
5 Hub flange 8 Friction generating mechanism 14 First bush (inner peripheral friction member)
15 Second bush (friction member)
15c 1st projection part 15d 2nd projection part 16 1st cone spring (inner peripheral side elastic member)
17 Second cone spring (elastic member)
17a 1st notch part 17b 2nd notch part 17c 1st protrusion part 17d 2nd protrusion part 18 3rd bush (3rd friction member)

Claims (9)

A friction generating mechanism for attenuating torsional vibration by generating friction between a first rotating member and a second rotating member arranged to be relatively rotatable,
An annular ring that engages with the first rotating member in the rotational direction and contacts the second rotating member, and slides on the second rotating member to generate friction when the first and second rotating members rotate relative to each other. A friction member;
An annular elastic member disposed between the first rotating member and the friction member for biasing the friction member in the axial direction with respect to the second rotating member;
The elastic member includes a plurality of first cutout portions arranged at equal intervals in the circumferential direction and a plurality of second cutout portions arranged at equal intervals in the circumferential direction between the adjacent first cutout portions. And
The friction member has at least one first protrusion that engages with the first notch in the rotation direction, and at least one second protrusion that engages with the second notch in the rotation direction,
When the elastic member is assembled upside down with respect to the friction member, any one of the first notch and the first protrusion and the second notch and the second protrusion cannot be engaged. ,
Friction generating mechanism. The circumferential distances from the first notch part to the two adjacent second notch parts are different from each other,
The friction generating mechanism according to claim 1. The circumferential distance from one said 1st notch part to the said one adjacent 2nd notch part is the said 1st notch part from the said 1st projection part engaged with the said 1st notch part. Greater than the circumferential distance to the second protrusion engaging the other second notch adjacent to
The friction generating mechanism according to claim 1 or 2. The circumferential distance from the circumferential center of the second notch to the circumferential center of two adjacent first notches is different, respectively.
The friction generating mechanism according to any one of claims 1 to 3. The circumferential width of the first notch is greater than the circumferential width of the second notch,
The circumferential width of the first protrusion is greater than the circumferential width of the second notch,
The friction generating mechanism according to any one of claims 1 to 4. The inner peripheral portion of the elastic member abuts the friction member in the axial direction,
The outer peripheral portion of the elastic member is in contact with the first rotating member in the axial direction,
The friction member has an annular portion that is in axial contact with the inner peripheral portion of the elastic member,
The first and second cutouts are disposed on the inner peripheral side of the elastic member,
The first and second protrusions protrude in the axial direction from the annular part,
The friction generating mechanism according to any one of claims 1 to 5. The first rotating member has at least one hole at a position corresponding to the first protrusion,
The first protrusion is inserted into the hole;
The friction generating mechanism according to any one of claims 1 to 6. The first rotating member is composed of a pair of disc-shaped input side plates,
The second rotating member is disposed between the cylindrical output side hub disposed on the inner peripheral side of the pair of input side plates and the outer peripheral side of the output side hub and between the pair of input side plates. A disc-shaped flange part,
The pair of input side plates and the flange portion are elastically coupled in the rotation direction,
The flange portion and the output hub are elastically connected in the rotational direction,
The friction member is arranged to slide on the flange portion,
The elastic member is disposed between the friction member and one of the input plates.
The friction generating mechanism according to any one of claims 1 to 7. An annular inner peripheral friction member which is arranged on the inner peripheral side of the friction member so as to slide with the output side hub and the flange, and engages the friction member in the rotation direction;
An annular inner peripheral elastic member disposed between the inner peripheral friction member and one of the input side plates, for biasing the inner peripheral friction member in the axial direction against the flange portion;
An annular third friction member disposed between the other input side plate and the flange portion so as to slide with the flange portion and engaging with the other input side plate in the rotational direction;
The friction generating mechanism according to any one of claims 1 to 8.

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