WO2011062158A1

WO2011062158A1 - Power transmitting mechanism

Info

Publication number: WO2011062158A1
Application number: PCT/JP2010/070371
Authority: WO
Inventors: 三城鳥居; 大介林; 幸久高士
Original assignee: アイシン精機株式会社
Priority date: 2009-11-19
Filing date: 2010-11-16
Publication date: 2011-05-26
Also published as: CN102639893A; JPWO2011062158A1

Abstract

A power transmitting mechanism wherein the vibration attenuation function of a damper mechanism is improved. A power transmitting mechanism is provided with a drive plate which rotates and transmits power, coiled springs which are provided in series in the rotational direction of the drive plate and can be rotated together with the drive plate, a driven plate which is provided coaxially with the rotation axis of the drive plate and which can be rotated together with the drive plate and the coiled springs by power transmitted to the driven plate by the drive plate through the coiled springs, an annular member which is coaxial with the rotation axis and is provided so as to be rotatable relative to the drive plate and the driven plate. The annular member is provided with support sections disposed between the coiled springs and supporting the coiled springs.

Description

Power transmission mechanism

The present invention relates to a power transmission mechanism, and more particularly to a power transmission mechanism that transmits power from a side of an engine mechanism to a side of a transmission mechanism so as to absorb torque fluctuations.

(Description of related application)
The present invention is based on the claim of priority of Japanese Patent Application No. 2009-264392 (filed on November 19, 2009), and the entire contents of the same application are incorporated and described herein by reference. It shall be.
As an example of a conventional power transmission mechanism, a torque fluctuation absorber as a power transmission mechanism disclosed in Patent Document 1 is known. This device comprises a drive side member 18 for rotating and transmitting power, an arc-shaped spring 24 disposed in the rotation direction of the drive side member 18 and capable of rotating integrally with the drive side member 18, and the drive side member 18. The driven side member 20 is coaxially disposed with the rotary shaft of the above-mentioned, and motive power is transmitted by the drive side member 18 and the spring 24, and can rotate integrally with the drive side member 18 and the spring 24.

German patent DE19753557A1

The entire disclosure of the above patent documents is incorporated herein by reference thereto. The following analysis is given by the present invention.
However, in the torque fluctuation absorbing device of the type in which such an arc-shaped spring is disposed, when the spring is compressed, the intermediate portion of the spring moves radially outward to contact and slide on the driving side member There is. In such a case, the friction resistance is increased, and the vibration damping function of the damper mechanism by the spring is reduced.

In view of the above problems, the present invention aims to improve the vibration damping function of a damper mechanism in a power transmission mechanism.

According to one aspect of the present invention, in the power transmission mechanism, a plurality of driving side members for rotating and transmitting power, and a plurality of the driving side members arranged in series in the rotational direction of the driving side member are rotatable in unison with the driving side member. The elastic member is coaxially arranged with the rotation shaft of the drive side member, and the power is transmitted by the drive side member through the elastic member, and can be integrally rotated with the drive side member and the elastic member. A driven side member, and an annular member coaxially arranged with the rotation shaft and disposed so as to be relatively rotatable with respect to the drive side member and the driven side member, the annular member being interposed between the elastic members A support portion is provided to support the elastic member.

In the power transmission mechanism of the present invention, preferably, the annular member has a first restricting portion which restricts the radial movement of the annular member with respect to the annular member.

In the power transmission mechanism of the present invention, in any of the second technical means, it is preferable that the first restricting portion be a protrusion that protrudes in the radial direction.

In the power transmission mechanism of the present invention, in any one of the first to third technical means, one of the drive side member and the driven side member protrudes in the radial direction. The elastic member has a plurality of flanges, and the elastic member is disposed between the adjacent flanges, and the flange controls a second restricting portion that restricts the radial movement of the elastic member with respect to the annular member. It is preferable to have.

In the power transmission mechanism of the present invention, in any of the first to fourth technical means, the elastic member is preferably a coil spring exhibiting a straight shape.

According to the present invention, in compression of the elastic member caused by relative rotation between the drive side member and the driven side member, contact / sliding between the elastic member and the drive side member can be suppressed, and the vibration damping function of the damper mechanism can be improved. .

FIG. 2 is a side cross-sectional view of a clutch disc 100 according to an embodiment of the present invention. It is a top view of the clutch disc 100 of FIG. It is a sectional side view of the power transmission mechanism concerning one embodiment of the present invention. FIG. 4 is a top view when the power transmission mechanism is separated along line XX in FIG. 3; It is a top view of the driven plate 4 in FIG. It is a top view of the annular member 5 in FIG. FIG. 5 is a top view of the first drive plate 2a in FIG. 3; It is a top view of the 2nd drive plate 2b in FIG. It is the partially notched top view which showed typically the structure of the clutch disc containing the power transmission mechanism which concerns on Example 1 of this invention. FIG. 10 is a cross-sectional view taken along line XX ′ of FIG. 9 schematically showing a configuration of a clutch disk including a power transmission mechanism according to Embodiment 1 of the present invention. It is the top view which showed typically the structure of the power transmission mechanism (pre-damper part) which concerns on Example 1 of this invention. FIG. 12 is a cross-sectional view taken along line YY ′ of FIG. 11 schematically showing the configuration of the power transmission mechanism (pre-damper portion) according to the first embodiment of the present invention. It is the top view which showed typically the structure of the driven plate in the power transmission mechanism (pre-damper part) which concerns on Example 1 of this invention. It is the top view which showed typically the structure of the annular member in the power transmission mechanism (pre-damper part) which concerns on Example 1 of this invention. It is the top view which showed typically the structure of the 1st drive plate in the power transmission mechanism (pre-damper part) which concerns on Example 1 of this invention. It is the top view which showed typically the structure of the 2nd drive plate in the power transmission mechanism (pre-damper part) which concerns on Example 1 of this invention.

Hereinafter, an embodiment of the present invention will be described in detail with reference to the drawings.

FIG. 1 is a side sectional view of a clutch disc 100 according to an embodiment of the present invention, and FIG. 2 is a top view of the clutch disc 100 of FIG. FIG. 3 is a side cross-sectional view of the torque fluctuation absorbing device 1 according to an embodiment of the present invention, and FIG. 4 is a top view when the torque fluctuation absorbing device 1 is separated along line XX in FIG. It is.

Referring to FIGS. 1 to 4, torque fluctuation absorbing device 1 as a power transmission mechanism constitutes a clutch disk 100 and is disposed on a power transmission path between an output shaft of an engine and an input shaft of a transmission. It is A plurality of torque fluctuation absorbing devices 1 are provided in series in the direction of rotation (in the direction of the arrow in FIG. 4) of the drive plate (drive side member) 2 that transmits rotation and transmits power, and is integral with the drive plate 2 Is arranged coaxially with the rotatable coil spring (elastic member) 3 and the rotation axis O of the drive plate 2, and power is transmitted by the drive plate 2 through the coil spring 3 to drive plate 2 and the coil A driven plate (a driven side member) 4 rotatable integrally with the spring 3 and an annular member 5 coaxially arranged with the rotation axis of the drive plate 2 and arranged rotatably relative to the drive plate 2 and the driven plate 4 Is equipped.

The driven plate 4 is connected to an input shaft of a transmission (not shown) and rotates integrally with the input shaft of the transmission. FIG. 5 is a top view of the driven plate 4. As shown in FIG. 5, the driven plate 4 has an annular portion 4a engaged with the input shaft of the transmission through a hole provided in the central portion thereof, and the outer side in the radial direction of the driven plate 4 from the outer peripheral portion of the annular portion 4a. The flange portion 4b radially protrudes toward the Three flanges 4 b are provided at predetermined intervals in the circumferential direction of the driven plate 4 (or in the rotational direction of the driven plate 4 indicated by the arrow in FIG. 5).

Between adjacent flange portions 4b, housing portions 4c for housing the coil springs 3 are formed at three equally divided circumferential positions, and as shown in FIG. 4, the coil springs 3 are provided in the housing portions 4c. Two each are accommodated in series in the rotational direction of the drive plate 2. The flange portions 4 b have convex portions (second restricting portions) 4 d protruding in the circumferential direction of the driven plate 4 on both side surfaces facing in the rotational direction (the arrow direction in FIG. 5). The convex portion 4 d can support the outer peripheral portion of the coil spring 3. Further, as can be seen from FIGS. 4 and 5, the annular portion 4 a of the driven plate 4 is positioned on the inner side in the radial direction of the annular member 5 than the annular member 5.

FIG. 6 is a top view of the annular member 5. As shown in FIG. 6, the annular member 5 has an annular main body 5a, a protrusion (first regulating portion) 5b, and a support (support) 5c. The protrusion 5b having an arc shape has a diameter from the inner peripheral surface of the main body 5a at a predetermined interval in the circumferential direction of the annular member 5 (or in the rotational direction of the annular member 5 of the arrow in FIG. 6). Three are formed so as to protrude inward in the direction. Further, the support portions 5c are respectively formed so as to protrude further radially inward from the central portion of the inner side surface of the protrusion 5b.

As shown in FIGS. 3 to 6, the inner diameter of the main portion 5a of the annular member 5 is larger than the outermost diameter of the driven plate 4, and the innermost diameter of the annular member 5 is outside the annular portion 4a of the driven plate 4. The driven plate 4 is disposed inside the annular member 5 so as to be larger than the diameter and to position each support portion 5c in each accommodation portion 4c. Thereby, each accommodation part 4c is divided into a first accommodation part 4ca and a second accommodation part 4cb by the support part 5c, and one coil spring 3 is accommodated in the first accommodation part 4ca and the second accommodation part 4cb. Ru. Therefore, two coil springs 3 are accommodated in one accommodation portion 4c.

By arranging the coil spring 3 in the first housing portion 4 ca, one end of the coil spring 3 abuts on the other side surface facing the circumferential direction of the flange portion 4 b of the driven plate 4. The end is in contact with one side surface of the support portion 5 c of the annular member 5 facing the circumferential direction. Further, by disposing the coil spring 3 in the second housing portion 4 cb, one end of the coil spring 3 abuts on the other side surface facing the circumferential direction of the support portion 5 c of the annular member 5. The other end of the flange 4 abuts on one side surface of the flange portion 4 b of the driven plate 4 facing the circumferential direction.

Furthermore, the outer peripheral portion facing the radial direction outer side of the annular member 5 at one end of the coil spring 3 housed in the first housing portion 4 ca can be supported on the inner side surface of the convex portion 4 d of the flange portion 4 b The outer peripheral portion of the annular member 5 facing the radially outer side at the other end can be supported by the inner surface of the support portion 5 b of the annular member 5. Further, an outer peripheral portion facing the radial direction outer side of the annular member 5 at one end of the coil spring 3 accommodated in the second accommodation portion 4 cb is made supportable on the inner side surface of the support portion 5 b of the annular member 5. The outer peripheral portion of the annular member 5 at the other end, which faces radially outward, is supportable by the inner side surface of the convex portion 4 d of the flange portion 4 b.

As shown in FIG. 3, the drive plate 2 is connected to a crankshaft of an engine (not shown) and rotates integrally with the crankshaft, and comprises a first drive plate 2 a and a second drive plate 2 b. The first drive plate 2a and the second drive plate 2b have a coupling shaft 2ab (see FIG. 7) provided on the outer peripheral portion of the first drive plate 2a and a coupling hole 2bb provided on the outer periphery of the second drive plate 2b. Integrated by coupling to (see FIG. 8).

FIG. 7 is a top view of the first drive plate 2a, and FIG. 8 is a top view of the second drive plate 2b. As shown in FIGS. 7 and 8, the first drive plate 2a and the second drive plate 2b, which are integrally configured, have concave portions 2aa and 2ba for accommodating the coil spring 3, the driven plate 4 and the annular member 5, respectively. Respectively. Recesses 2aa and 2ba have an annular bottom, and the circumferential direction or rotational direction (arrow direction in FIGS. 7 and 8) corresponds to housing 4d of coil spring 3 of driven plate 4 at the bottom. Three window holes 2a1 and 2b1 are formed at predetermined intervals.

As can be seen from FIGS. 3 and 4, the first drive plate 2a and the second drive plate 2b are integrally configured, so that the coil spring 3, the driven plate 4 and the annular member 5 are formed by the respective recesses 2aa and 2ba. The housing space which accommodates is formed, and the coil spring 3, the driven plate 4 and the annular member 5 are arrange | positioned in this space. Thus, two coil springs 3 are accommodated in each of the window holes 2a1 and 2b1. The driven plate 4 and the annular member 5 are disposed coaxially with the rotation axis of the drive plate 2 and are relatively rotatable.

As shown in FIGS. 3 to 8, the coil spring 3 is accommodated in the window holes 2a1 and 2b1, so that one end of the coil spring 3 is the window holes 2a1 and 2b1 of the first drive plate 2a and the second drive plate 2b. And the other end of the coil spring 3 is on the other side of the peripheral wall surrounding the window holes 2a1 and 2b1 of the first drive plate 2a and the second drive plate 2b. The end faces 2a3 and 2b3 can be abutted.

The inner diameters of the peripheral portions 2ac and 2bc of the recesses 2aa and 2ba of the first drive plate 2a and the second drive plate 2b of the drive plate 2 are made larger than the outermost diameter of the annular member 5. That is, the peripheral wall portions 2ac and 2bc of the recessed portions 2aa and 2ba are located outside the annular member 5 in the radial direction of the annular member 5.

As shown in FIG. 4, in the assembled state of drive plate 2, coil spring 3, driven plate 4, and annular member 5, a portion supporting each end face of coil spring 3, that is, the side surface of flange portion 4 b and support The side surface of the portion 5c and the end surface of the peripheral wall surface surrounding the window holes 2a1 and 2b1 are configured to be parallel to each other.

The torque transmission of the clutch disc 100 configured as described above, and in turn the torque fluctuation absorbing device 1 will be described. During acceleration of a car, etc., the torque transmitted from the engine to the flywheel is transmitted to the drive plate 2 and relative rotation occurs between the drive plate 2 and the driven plate 4, so that the window holes 2 a 1 of the drive plate 2, The end faces 2a2 and 2b2 of 2b1 press one end of the coil spring 3 to compress the coil spring 3.

The other end of the compressed coil spring 3 presses the side surface of one side of the support 5 c of the annular member 5 by the restoring force, and the other side of the support 5 c presses one end of the coil spring 3. The other end of the compressed coil spring 3 presses the flange portion 4 d of the driven plate 4 by a restoring force to transmit torque to the driven plate 4. The torque is then input to the input shaft of the transmission.

That is, the torque of the engine is transmitted from the drive plate 2 to the transmission via the spring 3, the annular member 5 and the driven plate 4. Therefore, since the engine-specific periodic torque fluctuation is absorbed by the deflection of the coil spring 3, smooth rotational motion is transmitted.

According to the torque fluctuation absorbing device 1 of the present embodiment, in the compression of the coil spring 3 accompanying the relative rotation of the drive plate 2 and the driven plate 4, the coil spring 3 and, in particular, the radial direction of the annular member 5 of the coil spring 3 in particular. The outer peripheral portion facing outward does not contact or slide on the drive plate 2, and the vibration damping function of the damper mechanism of the torque fluctuation absorber 1 can be improved.

Furthermore, at the time of compression of the coil spring 3 accompanying relative rotation of the drive plate 2 and the driven plate 4, the component forces in the radial direction acting on the respective support portions 5 c of the annular member 5 are substantially balanced. The movement of the member 5 in the radial direction is suppressed. That is, in the ideal state, a predetermined clearance always exists between the outer peripheral surface of the annular member 5 and the peripheral wall portions of the recessed portions 2aa and 2ba of the driven plate 2, and the inner peripheral surface of the main body portion 5a of the annular member 5 is driven A predetermined clearance always exists between the outer peripheral surface of the plate 4 (the outer peripheral surface of the flange portion 4 b), and between the inner side surface of the support portion 5 c of the annular member 5 and the outer peripheral surface of the annular portion 4 a of the driven plate 4. There is always a predetermined clearance in the

Therefore, contact / sliding between the outer peripheral surface of annular member 5 and the peripheral wall portion of recess 2 aa or 2 ba of drive plate 2 is suppressed, and the inner peripheral surface of main body 5 a of annular member 5 and the outer peripheral surface of driven plate 4 The contact / sliding is suppressed, and the contact / sliding between the inner surface of the support portion 5c of the annular member 5 and the outer peripheral surface of the annular portion 4a of the driven plate 4 is suppressed, and vibration damping of the damper mechanism of the torque fluctuation absorbing device 1 Function can be improved.

When the device 1 rotates, the coil spring 3 is urged radially outward of the annular member 5 by centrifugal force. However, the radially outward movement of the coil spring 3 with respect to the annular member 5 is restricted by the convex portion 4 d of the flange portion 4 b of the driven plate 4 and the convex portion 5 b of the annular member 5. Thereby, the arrangement position of the coil spring 3 can be always maintained at a good position, and the vibration damping function can be exhibited stably.

Furthermore, by using a coil spring on a straight as an elastic member, in the compression of the coil spring 3, the radially outward extension of the annular member 5 of the middle part of the coil spring 3 is suppressed, for example, the middle of the coil spring 3 It is possible to suppress the contact and sliding of the portion with the annular member 5 and to improve the vibration damping function of the damper mechanism of the torque fluctuation absorbing device 1.

In the present embodiment, the drive plate 2 is described as the drive side member, and the driven plate 4 is described as the driven side member. However, the configuration may be reversed.

As mentioned above, although the present invention was explained according to the above-mentioned embodiment, the present invention is not limited only to the above-mentioned form, and includes various modes according to the principle of the present invention.

In addition, when drawing reference numerals are attached in the present application, they are only for the purpose of assisting understanding and are not intended to be limited to the illustrated embodiment.

A power transmission mechanism according to a first embodiment of the present invention will be described using the drawings. FIG. 9 is a partially cutaway plan view schematically showing the configuration of a clutch disc including the power transmission mechanism according to Embodiment 1 of the present invention. FIG. 10 is a cross-sectional view taken along line XX ′ of FIG. 9 schematically showing the configuration of a clutch disk including the power transmission mechanism according to the first embodiment of the present invention. FIG. 11 is a plan view schematically showing the configuration of the power transmission mechanism (pre-damper portion) according to the first embodiment of the present invention. FIG. 12 is a cross-sectional view taken along line YY ′ of FIG. 11 schematically showing the configuration of the power transmission mechanism (pre-damper portion) according to the first embodiment of the present invention. FIG. 13 is a plan view schematically showing the configuration of a driven plate in the power transmission mechanism (pre-damper portion) according to the first embodiment of the present invention. FIG. 14 is a plan view schematically showing the configuration of the annular member in the power transmission mechanism (pre-damper portion) according to the first embodiment of the present invention. FIG. 15 is a plan view schematically showing the configuration of the first drive plate in the power transmission mechanism (pre-damper portion) according to the first embodiment of the present invention. FIG. 16 is a plan view schematically showing the configuration of the second drive plate in the power transmission mechanism (pre-damper portion) according to the first embodiment of the present invention. In FIG. 11, the second drive plate (2b in FIG. 16) is omitted.

Referring to FIGS. 9 and 10, clutch disc 100 is provided in a clutch device disposed in a power transmission path between a crankshaft (not shown) of an engine and an input shaft (not shown) of a transmission. It is done. The clutch disc 100 has a mechanism (power transmission mechanism) that absorbs (reduces) fluctuation torque between the crankshaft and an input shaft (not shown) by buffering torsion between the crankshaft and the input shaft. The clutch disc 100 is detachably held between the pressure plate and the flywheel in the clutch device at the facing

portions

10 and 11. The clutch disc 100 has damper portions (101 and 102 in FIG. 9) that absorb the fluctuation torque by the spring force. The

damper units

101 and 102 buffer the twist between the crankshaft and the input shaft when the pre-damper unit 101 buffers the initial twist between the crankshaft and the input shaft and when the pre-damper unit 101 can not buffer the torque. And a main damper portion 102. The pre-damper portion 101 and the main damper portion 102 each have a substantially annular shape.

The clutch disc 100 includes, as main components, a first drive plate 2a, a second drive plate 2b, a coil spring 3, a driven plate 4, an annular member 5,

facings

10 and 11, and a disc spring 12 , Rivets 13 and 14,

side plates

15 and 16, coupling member 17, flange member 18, coil spring 19, thrust member 20, disc spring 21, hub member 23, and thrust

members

24 and 25. , And a disc spring 26.

The first drive plate 2a is a member formed in a ring shape, and is a component of the pre-damper portion 101 (see FIGS. 9 to 12 and 15). The first drive plate 2a is disposed between the side plate 15 and the second drive plate 2b. The first drive plate 2 a is slidably in contact with the side plate 15 on the side of the side plate 15. The first drive plate 2 a is formed with a recess 2 aa (step portion) so as not to interfere with the driven plate 4 and the annular member 5 on the surface on the second drive plate 2 b side. The recess 2 aa is formed in an annular shape, and has a cylindrical peripheral wall 2 ac formed at the radially outer end along the axial direction. The first drive plate 2a has three connecting shafts 2ab for locking the second drive plate 2b and the flange member 18. Each coupling shaft 2ab engages with a recess 2bb formed in the outer peripheral surface of the second drive plate 2b in a non-rotatable and axially movable manner. The coupling shaft 2 ab is nonrotatably and axially movably engaged (inserted) with a through hole formed in the flange member 18. The first drive plate 2a has three window holes 2a1 for accommodating a part of the coil spring 3 on the surface on the second drive plate 2b side. Each window hole 2 a 1 is disposed at a position on the inner peripheral side of the coil spring 19 in the main damper portion 102. One side end face 2a2 in the circumferential direction of each window hole 2a1 is in contact with the coil spring 3 so as to be capable of coming into and coming out of contact. The other side end face 2a3 in the circumferential direction of each window hole 2a1 is in contact with a coil spring 3 different from the coil spring 3 in contact with the one side end face 2a2. Each window hole 2 a 1 guides expansion and contraction of the coil spring 3. The three window holes 2a1 are disposed at positions shifted by 120 degrees with respect to the rotation center axis of the first drive plate 2a. The window holes 2a1 are arranged along the same circumference (the radial position is the same). The first drive plate 2a is in contact with the second drive plate 2b at a portion not interfering with the operation of the driven plate 4 and the annular member 5 on the surface on the second drive plate 2b side.

The second drive plate 2b is a member formed in a ring shape, and is a component of the pre-damper portion 101 (see FIGS. 10 to 12 and 16). The second drive plate 2b is disposed between the flange member 18 and the first drive plate 2a. The second drive plate 2 b is in contact with the flange member 18 at the surface on the flange member 18 side. The second drive plate 2 b is formed with a recess 2 ba (step portion) so as not to conflict with the driven plate 4 and the annular member 5 on the surface on the first drive plate 2 a side. The recess 2 ba is formed in an annular shape, and has a cylindrical peripheral wall 2 bc formed along the axial direction at the radially outer end. The peripheral wall portion 2 bc restricts the radial movement of the annular member 5. The second drive plate 2 b has a recess 2 bb that engages with the coupling shaft 2 ab of the first drive plate 2 a in a non-rotatable and axially movable manner on the outer peripheral surface. The second drive plate 2 b rotates integrally with the first drive plate 2 a and the flange member 18 via the coupling shaft 2 ab of the first drive plate 2 a. The second drive plate 2 b has three window holes 2 b 1 for housing a part of the coil spring 3 on the surface on the first drive plate 2 a side. Each window hole 2 b 1 is disposed at a position on the inner peripheral side of the coil spring 19 in the main damper portion 102. One side end surface 2b2 in the circumferential direction of each window hole 2b1 is in contact with the coil spring 3 so as to be capable of coming into and coming out of contact. The other side end face 2b3 in the circumferential direction of each window hole 2b1 is in contact with a coil spring 3 different from the coil spring 3 in contact with the one side end face 2b2. Each window hole 2 b 1 guides expansion and contraction of the coil spring 3. The three window holes 2b1 are disposed at positions shifted by 120 degrees with respect to the rotation center axis of the second drive plate 2b. The window holes 2b1 are arranged along the same circumference (the radial position is the same). The second drive plate 2b is in contact with the first drive plate 2a at a portion which does not conflict with the operation of the driven plate 4 and the annular member 5 on the surface on the first drive plate 2a side.

The coil spring 3 is a component of the pre-damper portion 2 (see FIGS. 9 to 12). Two coil springs 3 are accommodated in series in the circumferential direction in the window holes 2a1 and 2b1 formed in the

drive plates

2a and 2b. The coil spring 3 is in contact with the side end surfaces (2a2, 2b2 or 2a3, 2b3) of the window holes 2a1, 2b1 in the

drive plates

2a, 2b or the flange portion 4b of the driven plate 4 so that the other end can It is in contact with the support 5 c of the annular member 5. The coil spring 3 contracts when the pre-damper portion 101 twists (twist between the

drive plates

2a and 2b and the driven plate 4), and absorbs a shock due to a difference in rotation between the

drive plates

2a and 2b and the driven plate 4 . As the coil spring 3, it is possible to use a coil spring (straightly extending linearly) in the expansion and contraction direction (longitudinal direction). The spring force (spring coefficient) of the coil spring 3 is set smaller than the spring force (spring coefficient) of the coil spring 19 in the main damper portion 102.

The driven plate 4 is an annular plate-like member disposed on the outer periphery of the outer spline portion 23b of the hub member 23, and is a component of the pre-damper portion 101 (see FIGS. 9 to 13). The driven plate 4 is disposed rotatably with respect to the first drive plate 2a and the second drive plate 2b between the recess 2aa of the first drive plate 2a and the recess 2ba of the second drive plate 2b. The driven plate 4 is disposed so as to be rotatable in a range of a predetermined angle with respect to the annular member 5 radially inward of the annular member 5. The driven plate 4 has three flange portions 4 b extending radially outward from a predetermined position of the outer peripheral end face of the annular portion 4 a. The three flange portions 4 b are disposed at positions shifted by 120 degrees with respect to the rotation center axis of the driven plate 4. Between the circumferential direction of the adjacent flange part 4b, the accommodating part 4c for accommodating the two coil springs 3 and the support part 5c of the annular member 5 is provided. An end face of the housing portion 4 c in the circumferential direction is in contact with the coil spring 3 so as to be capable of coming into and coming out of contact. The housing portion 4c has a first housing portion 4ca for housing the coil spring 3 on one side in the circumferential direction of the support portion 5c, and a second one for housing the other coil spring 3 on the other side in the circumferential direction of the support portion 5c. It has the accommodation part 4cb. The driven plate 4 has two convex portions 4 d circumferentially projecting on both sides in the circumferential direction from a position radially outward of the position where it can contact the coil spring 3 at the end face in the circumferential direction of each flange portion 4 b. The convex portion 4 d regulates movement (movement in the radial direction) of the coil spring 3 in the pre-damper portion 101. The driven plate 4 has an inner spline portion 4e formed at an inner peripheral end. The inner spline portion 4 e is non-rotatably engaged with the outer spline portion 23 b of the hub member 23.

The annular member 5 is an annular plate-like member disposed radially outside the driven plate 4 and is a component of the pre-damper portion 101 (see FIGS. 9 to 12 and 14). The annular member 5 is disposed rotatably with respect to the first drive plate 2a and the second drive plate 2b between the recess 2aa of the first drive plate 2a and the recess 2ba of the second drive plate 2b. The annular member 5 is rotatably disposed in a range of a predetermined angle with respect to the driven plate 4 at a radially outer side of the driven plate 4. The annular member 5 has three support parts 5c which protrude inward in the radial direction from a predetermined position of the inner peripheral end of the main body part 5a formed in an annular shape. The three support portions 5 c are disposed at positions shifted by 120 degrees with respect to the rotation center axis of the annular member 5. Each support portion 5 c is disposed between the circumferential direction of the two coil springs 3 accommodated in each accommodation portion 4 c of the driven plate 4. Both sides of the end face of each support 5c in the circumferential direction support the end of the coil spring 3. The annular member 5 has two protrusions 5b that protrude in the circumferential direction from the position radially outward of the position where it can contact the coil spring 3 on the end face in the circumferential direction of each support 5c. The convex portion 5 b restricts the movement (movement in the radial direction outer side) of the coil spring 3 in the pre-damper portion 101.

The facing 10 is a friction material that can be frictionally engaged with a flywheel (or any other member) that rotates integrally with a crankshaft (not shown) of the engine (see FIGS. 9 and 10). The facing 10 is annularly formed. The facing 10 is fixed to one axial surface (surface on the left side in FIG. 10) of the disc spring 12 by a plurality of rivets 13. As the facing 10, those including rubber, resin, fibers (short fibers, long fibers), particles for adjusting the friction coefficient μ, and the like can be used.

The facing 11 is a friction material that can be frictionally engaged with a pressure plate that rotates integrally with a crankshaft (not shown) of the engine (see FIGS. 9 and 10). The facing 11 is annularly formed. The facing 11 is fixed to the other axial surface (the surface on the right side in FIG. 10) of the disk spring 12 by a plurality of rivets 14. As the facing 11, those containing rubber, resin, fibers (short fibers, long fibers), particles for adjusting the coefficient of friction μ, and the like can be used.

The disc spring 12 is an annular disc-like member having an elastic force against pressing against the disc surface (see FIGS. 9 and 10). The disc spring 12 has

facings

10 and 11 attached by

rivets

13 and 14 on both sides of the outer peripheral portion. The disk spring 12 is caulked and fixed to one end portion of the plurality of connecting members 17 together with the side plate 15 at the inner peripheral portion. The disc spring 12 rotates integrally with the

side plates

15 and 16.

The rivet 13 is a member for fixing the facing 10 to one surface (surface on the left side in FIG. 10) in the axial direction of the disk spring 12 (see FIGS. 9 and 10).

The rivet 14 is a member for fixing the facing 11 to the other axial surface (the surface on the right side in FIG. 10) of the disc spring 12 (see FIGS. 9 and 10).

The side plate 15 is an annular member disposed on one side (left side in FIG. 10) of the flange member 18 in the axial direction so as to be separated from the flange member 18 (see FIGS. 9 and 10). The side plate 15 is caulked and fixed to one end of the plurality of connecting members 17 together with the disc spring 12 at a portion near the outer peripheral end. The side plate 15 rotates integrally with the connecting member 17, the disc spring 12, and the side plate 16. The side plate 15 has six windows 15 a for accommodating the coil spring 19 in the main damper portion 102 of the middle portion. The circumferential end surface of the window portion 15 a is in contact with and separable from the end of the coil spring 19. The window 15 a guides expansion and contraction of the coil spring 19. The window portion 15a is disposed at a position shifted 50 degrees about the rotation center axis of the side plate 15 with respect to one of the window portions 15a adjacent in the circumferential direction, and the other window adjacent in the circumferential direction It is disposed at a position which is offset by 70 degrees with respect to the portion 15a about the central axis of rotation of the side plate 15. The side plate 15 is slidably in contact with the first drive plate 2 a at the pre-damper portion 101 on the inner peripheral side of the main damper portion 102. The side plate 15 is rotatably supported by the hub member 23 via the thrust member 24 at the inner peripheral end. The side plate 15 is rotationally fixed to the thrust member 24 at the inner peripheral end. The side plate 15 is in contact with the thrust member 24 at the surface on the side of the flange member 18 near the inner peripheral end.

The side plate 16 is an annular member disposed on the other side (right side in FIG. 10) of the flange member 18 in the axial direction so as to be separated from the flange member 18 (see FIGS. 9 and 10). The side plate 16 is caulked and fixed to the other end of the plurality of connecting members 17 at a portion near the outer peripheral end. The side plate 16 rotates integrally with the connecting member 17, the disc spring 12, and the side plate 15. The side plate 16 has six windows 16 a for accommodating the coil spring 19 in the main damper portion 102 of the middle portion. The circumferential end surface of the window portion 16 a is in contact with and separable from the end of the coil spring 19. The window portion 16 a guides expansion and contraction of the coil spring 19. The window portion 16a is disposed at a position shifted 50 degrees around the rotation center axis of the side plate 16 with respect to one of the window portions 16a adjacent in the circumferential direction, and the other window adjacent in the circumferential direction It is disposed at a position which is offset by 70 degrees with respect to the portion 16 a about the central axis of rotation of the side plate 16. The side plate 16 is engaged with the detent portion 20 a of the thrust member 20 in a non-rotatable and axially movable manner at a portion which does not conflict with the main damper portion 102. The side plate 16 supports one end of the disc spring 21 at a portion on the inner peripheral side of the anti-rotation portion 20 a of the thrust member 20. The side plate 16 supports one end of the disc spring 26 at a portion on the inner peripheral side of the disc spring 21. The side plate 16 is rotatably supported by the hub member 23 via the thrust member 25 at an inner peripheral end. The side plate 16 is rotationally fixed to the thrust member 25 at an inner peripheral end.

The connecting member 17 is a member for connecting the

side plates

15 and 16 and the disc spring 12 (see FIGS. 9 and 10). At one end of the connecting member 17, the side plate 15 and the disc spring 12 are fixed by caulking. At the other end of the connecting member 17, a side plate 16 is fixed by caulking. The middle portion (body portion) of the connecting member 17 serves as a spacer for keeping the space between the side plate 16 and the disc spring 12. The middle part of the connecting member 17 is inserted into the notch 18b of the blanking member 18, and when the main damper portion 102 is twisted (twist between the

side plates

15 and 16 and the flange member 18), the notch is cut out. By coming into contact with the end face in the circumferential direction of the portion 18 b, it becomes a stopper portion that restricts excessive twisting of the main damper portion 102. A plurality of (three in FIG. 9) connection members 17 are arranged at predetermined intervals in the circumferential direction of the

side plates

15 and 16.

The flange member 18 is an annular plate-like member disposed on the outer periphery of the outer spline portion 23b of the hub member 23 (see FIGS. 9 and 10). The flange member 18 has six windows 18 a for accommodating the coil spring 19 in the main damper portion 102. The circumferential end surface of the window portion 18 a is in contact with the end portion of the coil spring 19 so as to be able to be separated and attached. The window 18a is disposed at a position shifted 50 degrees around the rotation center axis of the flange member 18 with respect to one of the windows 18a adjacent in the circumferential direction, and the other window adjacent in the circumferential direction It is disposed at a position which is offset by 70 degrees with respect to the portion 18a around the central axis of rotation of the flange member 18. The flange member 18 has three notches 18 b cut out on the inner peripheral side from the outer peripheral end face of the flange member 18 at a position not interfering with the window 18 a. The three notches 18 b are disposed at positions shifted by 120 degrees with respect to the rotation center axis of the flange member 18. The middle portion (body portion) of the connection member 17 is inserted into each notch 18b. The end face of the notch 18b in the circumferential direction contacts the middle portion of the connecting member 17 when the main damper portion 102 is twisted (twist of the

side plates

15, 16 and the flange member 18), thereby the main damper It becomes a stopper part which controls excessive twist of section 102. The flange member 18 is sandwiched between the second drive plate 2 b and the thrust member 20 on the surface in the axial direction on the inner peripheral side of the main damper portion 102 and is slidable with the thrust member 20. The flange member 18 has an inner spline portion 18c in which an inner spline is formed at an inner peripheral end. The inner spline portion 18c engages with the outer spline portion 23b of the hub member 23 so that the hub member 23 and the flange member 18 can be twisted within a predetermined angle range.

The coil spring 19 is a component of the main damper portion 102, and is an elastic member housed in the

windows

15a, 16a, 18a formed in the

side plates

15, 16 and the flange member 18 (see FIGS. 9 and 10). ). Both ends of the coil spring 19 are in contact with and separable from the end faces of the

windows

15a, 16a, 18a in the circumferential direction. The coil spring 19 contracts when the

side plates

15 and 16 and the flange member 18 twist, and absorbs the shock due to the difference in rotation between the

side plates

15 and 16 and the flange member 18. As the coil spring 19, a coil spring that is straight (extending linearly) in the expansion and contraction direction (longitudinal direction) can be used. The spring force (spring coefficient) of the coil spring 19 is set larger than the spring force (spring coefficient) of the coil spring 3 in the pre-damper portion 101.

The thrust member 20 is an annular member disposed between the side plate 16 and the flange member 18 (see FIGS. 9 and 10). The thrust member 20 has a detent portion 20a that engages with a through hole formed in the side plate 16 in a non-rotatable and axially movable manner. The thrust member 20 is biased toward the flange member 18 by the disc spring 21 and is in pressure contact with the flange member 18 in a slidable manner. The thrust member 20 is also engaged with the thrust member 25 disposed on the inner periphery so as to be non-rotatable and axially movable.

The disc spring 21 is a disc-shaped spring which is disposed between the thrust member 20 and the side plate 16 and biases the thrust member 20 toward the flange member 18 (see FIGS. 9 and 10).

The hub member 23 is a member that outputs rotational power from the

dampers

2 and 3 toward an input shaft (not shown) of the transmission (see FIGS. 9 and 10). The hub member 23 has a flange portion 23a extending radially outward from a predetermined portion of the outer periphery of the cylindrical portion. The hub member 23 splines with an input shaft (not shown) on the inner peripheral surface of the cylindrical portion. The hub member 23 relatively rotatably supports the side plate 15 via the thrust member 24 on the outer periphery, and supports the side plate 16 relatively rotatably via the thrust member 25. The flange portion 23a has an outer spline portion 23b in which an outer spline is formed on the outer peripheral surface. The outer spline portion 23b engages with the inner spline portion 18c of the flange member 18 such that the hub member 23 and the flange member 18 can be twisted within a predetermined angle range. The outer spline portion 23 b is non-rotatably engaged with the inner spline portion (4 e in FIG. 11) of the driven plate 4. The flange portion 23 a is slidably held by the

thrust members

24 and 25.

The thrust member 24 is an annular member disposed between the side plate 15 and the hub member 23 (see FIGS. 9 and 10). The thrust member 24 is disposed between the side plate 15 and the flange portion 23a in the axial direction, is engaged with the side plate 15 so as to be not relatively rotatable and axially movable, and is slidable with the flange portion 23a. It is in pressure contact with The thrust member 24 is also interposed between the side plate 15 and the hub member 23 in the radial direction, and serves as a slide bearing (bush) for supporting the side plate 15 relatively rotatably on the hub member 23.

The thrust member 25 is an annular member disposed between the side plate 16 and the hub member 23 (see FIGS. 9 and 10). The thrust member 25 is disposed between the disc spring 26 and the flange portion 23a in the axial direction, is urged toward the flange portion 23a by the disc spring 26, and is slidably pressed against the flange portion 23a. There is. The thrust member 25 engages with the side plate 16 so as to be non-rotatable and axially movable. The thrust member 25 is also interposed between the side plate 16 and the hub member 23 in the radial direction, and serves as a slide bearing (bush) for supporting the side plate 16 relatively rotatably on the hub member 23.

The disc spring 26 is a disc-shaped spring which is disposed between the thrust member 25 and the side plate 16 and biases the thrust member 25 toward the flange portion 23a (see FIGS. 9 and 10). The disc spring 26 is rotationally locked to the thrust member 25.

Next, the operation of the torsional shock absorber according to the first embodiment of the present invention will be described.

9 and 10, the rotational power of the crankshaft of the engine is represented by

facings

10 and 11, rivets 13 and 14, disc spring 12, connecting member 17,

side plates

15 and 16, coil spring 19, flange member 18, The

drive plates

2a and 2b, the coil spring 3, the annular member 5, the coil spring 3, the driven plate 4, and the hub member 23 are sequentially transmitted and transmitted to the input shaft of the transmission.

At this time, if twisting occurs between the

facings

10 and 11 and the hub member 23, the pre-damper portion 101 absorbs the fluctuation torque due to the initial twist, and further twisting occurs and the pre-damper portion 101 can not absorb it. The main damper unit 102 absorbs the fluctuating torque.

In the pre-damper portion 101, a twist occurs between the

facings

10 and 11 and the hub member 23, and until the teeth of the outer spline portion 23b of the hub member 23 contact the teeth of the inner spline portion 18c of the flange member 18, the pre-damper portion At 101, only the coil spring 3 acts.

When the teeth of the outer spline portion 23b of the hub member 23 abut against the teeth of the inner spline portion 18c of the flange member 18 and further twisting occurs between the

facings

10 and 11 and the hub member 23, the predamper portion 101 is not twisted. , The main damper portion 102 is twisted. That is, when the hub member 23 is twisted, the teeth of the outer spline portion 23b of the hub member 23 press the teeth of the inner spline portion 18c of the flange member 18 and twist is caused between the flange member 18 and the

side plates

15, 16. As a result, the coil spring 19 acts until the middle part of the connecting member 17 connected to the

side plates

15 and 16 abuts on the circumferential end face of the notch 18 b of the flange member 18. At this time, the coil spring 3 of the pre-damper portion 101 rotates integrally with the flange member 18 in the maximum compression state.

The above operation has described the case where the hub member 23 rotates clockwise (clockwise in FIG. 1) with respect to the

facings

10 and 11, but the hub member 23 rotates counterclockwise with respect to the

facings

10 and 11. The same is true when you

According to the first embodiment, in compression of the coil spring 3 due to relative rotation between the

drive plates

2 a and 2 b and the driven plate 4, the outer peripheral portion of the coil spring 3, in particular, the coil spring 3 facing the radially outer side of the annular member 5. As a result, the contact / sliding of the

drive plates

2a and 2b can be suppressed, and the vibration damping function of the damper mechanism can be improved. Further, the movement of the coil spring 3 can be restricted by the convex portion 4 d of the driven plate 4 and the convex portion 5 b of the annular member 5. Furthermore, by using the coil spring 3 in a straight shape, contact and sliding of the coil spring 3 with other members can be further suppressed, and the vibration damping function of the damper mechanism can be improved.

Within the scope of the entire disclosure (including the claims and drawings) of the present invention, changes and adjustments of the embodiments or examples are possible based on the basic technical concept of the invention. In addition, various combinations or selections of various disclosed elements are possible within the scope of the claims of the present invention. That is, the present invention of course includes the entire disclosure including the claims and the drawings, various modifications and modifications that can be made by those skilled in the art according to the technical concept.

1 Torque fluctuation absorber (power transmission mechanism)
2 Drive plate (drive side member)
2a 1st drive plate 2a1 window hole 2a2 one side end face 2a3 other side end face 2aa recess 2ab joint shaft 2ac peripheral wall portion 2b second drive plate 2b1 window hole 2b2 one side end face 2b3 other side end face 2ba recess 2bb joint hole peripheral wall portion 2bc
3 Coil spring (elastic member)
4 Driven plate (driven side member)
4a annular portion 4b flange portion 4c accommodation portion 4ca first accommodation portion 4cb second accommodation portion 4d convex portion (second regulating portion)
4e inner spline portion 5 annular member 5a main body portion 5b protrusion (first regulating portion)
5c Support part 100 Clutch disc O Rotary shaft 101 Pre-damper part 102

Main damper part

10, 11 Facing 12

Disc spring

13, 14 Rivet 15 Side plate 15a Window part 16 Side plate 16a Window part 17 Connection member 18 Flange member

18a Window part

18b Notch Part 18c Inner spline part 19 Coil spring 20 Thrust member 20a Detent part 21 Disc spring 23 Hub member 23a Flange part 23b

Outer spline part

24 and 25 Thrust member 26 Disc spring

Claims

A driving side member that rotates and transmits power;
A plurality of elastic members disposed in series in the direction of rotation of the drive side member and capable of rotating integrally with the drive side member;
A driven side member disposed coaxially with the rotary shaft of the drive side member, the power being transmitted by the drive side member via the elastic member, and integrally rotatable with the drive side member and the elastic member When,
And an annular member coaxially arranged with the rotation shaft and disposed rotatably relative to the drive side member and the driven side member,
A power transmission mechanism having a support portion disposed between the elastic members and supporting the elastic members;
The power transmission mechanism according to claim 1, wherein the annular member has a first restricting portion that restricts the radial movement of the annular member with respect to the annular member.
The power transmission mechanism according to claim 2, wherein the first restricting portion is a protrusion that protrudes in the radial direction.
Of the drive side member and the driven side member, one member has a plurality of radially projecting flange portions,
The elastic member is disposed between the adjacent flanges,
The power transmission mechanism according to any one of claims 1 to 3, wherein the flange portion includes a second restricting portion that restricts the radial movement of the annular member with respect to the annular member.
The power transmission mechanism according to any one of claims 1 to 4, wherein the elastic member is a straight coil spring.