KR101191528B1

KR101191528B1 - Dry Double Clutch

Info

Publication number: KR101191528B1
Application number: KR1020100070780A
Authority: KR
Inventors: 강석민
Original assignee: 주식회사평화발레오
Priority date: 2009-12-17
Filing date: 2010-07-22
Publication date: 2012-10-15
Also published as: KR20110069687A

Abstract

The present invention damper flywheel 300 is coupled to the engine side; And a set double clutch 200 coupled to the damper flywheel 300 to transmit power of the engine to the transmission, wherein the dry double clutch 100 comprises: a connection plate 400 of the set double clutch 200. A connector 600 coupled to the drive plate 320 of the damper flywheel 300 to be splined; A cover 700 coupled to the connector 600 so as to be relatively rotatable in a circumferential direction to compensate for backlash between the connection plate 400 and the connector 600; And a first elastic member (616) mounted on the connector (600) to elastically press the cover (700) in the circumferential direction of the connector (600). According to the present invention, the backlash of the connector can be compensated by attaching a cover to the connector for transmitting power from the damper flywheel connected to the engine side to the set double clutch connected to the transmission side.

Description

Dry Double Clutch {Dry Double Clutch}

The present invention relates to a dry double clutch, and more particularly, to a dry double clutch including a cover for compensating for backlash from a damper flywheel connected to an engine side to a connector transmitting power to a set double clutch connected to a transmission side. It is about.

The present invention relates to a double clutch for a transmission having two input shafts arranged coaxially. Since conventionally a transmission with one input shaft is used, a clutch disc for transmitting or disconnecting power from the engine to the transmission is also used. However, a double clutch transmission with two shafts (Double Clutch T / M) requires the use of a double clutch with two clutch discs to transfer power from the engine. Such a double clutch requires two clutches, the gear system is also operated dually, and the dual shaft is changed every time the gear is shifted one by one, so the speed of change is fast and the fuel efficiency is also helpful.

1 is a view in which the set double clutch and the damper flywheel are separated from a conventional dry double clutch.

Referring to Figure 1, the dry double clutch (Dry Double Clutch), unlike the conventional wet double clutch (Wet Double Clutch) does not use oil, and transmits the engine power to the transmission by friction of the clutch disk and the pressure plate. Done. The dry double clutch 10 can reduce the power loss by ensuring power transmission of the engine, and as described above, the gear shift speed of the double clutch transmission (DCT) connected to the dry double clutch 10 is high, thereby reducing fuel consumption. Has an excellent effect on

Dry double clutch 10 is composed of a set double clutch (20) and a damper flywheel (Damper Flywheel) 30, the set double clutch 20 is coupled to the double clutch transmission side, Damper flywheel 30 is coupled to the engine side. In this case, the coupling plate 40 is used for coupling to guide the coupling when the set double clutch 20 and the damper flywheel 30 are coupled and to facilitate assembly.

The damper flywheel 30 includes a primary wheel coupled by the crankshaft and bolts of the engine, a primary cover covering the upper portion of the primary wheel, and a drive plate for transmitting power of the engine from the primary wheel and the primary cover. It consists of. In addition, in order to transfer the power from the engine from the damper flywheel 30 to the set double clutch 20 by a spline type connector, a spline gear is formed on the outer circumferential surface of the connector. In addition, the connection plate 40 for spline coupling with the connector 50 is coupled to the set double clutch 20 in the set double clutch 20 which is coupled to the power transmission. At this time, the connection plate 40 is circular with a hole 46 formed in the center, and includes an extension portion 42 coupled with the set double clutch 20 in the radial direction. The hole 46 has a hub structure and forms a spline gear corresponding to the connector 60. Therefore, the damper flywheel 30 and the set double clutch 20 transmit power through the spline coupling of the connector 60 and the connecting plate 40.

However, in the case of spline coupling, a backlash occurs due to the tolerance between the teeth of the gear and the impact of the tooth of the gear during the rotational movement clockwise or counterclockwise. In particular, in the power transmission of the vehicle, the damper flywheel and the set double clutch are rotated in a relative clockwise or counterclockwise direction during acceleration and deceleration, and the backlash causes shock and noise to the connector and the connection plate. The damping ability in the rotational direction is lowered, and the durability life of the vehicle is shortened. In addition, there has been a problem that the shock and vibration transmitted to the driver, etc. during driving, the ride comfort is also reduced.

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a dry double clutch, comprising: a connector coupled to a damper flywheel for transmitting power from an engine to a transmission, and a spline coupling of a connecting plate coupled to a set double clutch, wherein the cover and washer are coupled to the connector to backlash. The purpose is to reduce the pressure and improve the axial damping ability.

The present invention to achieve this object is a damper flywheel coupled to the engine side; And a set double clutch coupled to the damper flywheel to transfer power of the engine to the transmission, the dry double clutch comprising: a connector coupled to the drive plate of the damper flywheel to be splined to a connection plate of the set double clutch; A cover that is elastically rotatably coupled to the connector in a circumferential direction to compensate for backlash between the connection plate and the connector; A first elastic member mounted on the connector to elastically press the cover in the circumferential direction of the connector; And a second elastic member mounted on the connector to elastically press the cover in the axial direction of the connector.

In addition, the second elastic member is preferably a plurality of washers arranged in the circumferential direction of the connector between the connector and the cover.

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In addition, the second elastic member is preferably a ring washer coaxially arranged with the connector between the connector and the cover.

In addition, the ring washer is preferably formed with a plurality of cutouts in the circumferential direction along the outer peripheral end of the inclined portion.

In addition, the second elastic member is restrained by the cover in the axial direction so as not to be removed from the connector, the circumferential rotation of the cover by allowing the relative rotation with respect to the connector by a rivet penetrating the cover by It is preferable to be respectively coupled to the connector.

In addition, the cover is preferably formed with at least one protrusion in a direction perpendicular to the outer periphery, the protrusion is preferably formed so as to face the spline gear tooth surface of the connector outer periphery.

In addition, it is preferable that the tooth width of the teeth covered with the protrusions among the tooth widths of the spline gear is equal to or larger than the tooth width of the gear teeth formed on the inner circumference of the connecting plate.

Further, of the distance between the teeth of the spline gear and the teeth, the distance between the teeth between the protrusions is preferably greater than the distance between the teeth without the protrusions.

In addition, the projections are formed at equal intervals on the outer periphery of the ring portion of the cover, it is preferable that the teeth of the spline gear to be covered by the projections are also formed at the same intervals on the outer periphery of the connector.

In addition, the first elastic member is a coil spring, the cover is preferably a spring support protruding toward the connector to impart an elastic force to the coil spring in the circumferential direction.

The force of the force applied by the first elastic member and the force applied by the second elastic member to the cover is preferably adapted to act on the cover in an oblique direction.

According to the configuration of the first embodiment, the present invention reduces the backlash in the spline coupling by coupling the cover to the connector of the damping flywheel, thereby reducing the impact, noise and vibration on the teeth between the connector and the connecting plate.

In addition, reducing backlash reduces the risk of tooth breakage and increases the endurance life of the vehicle.

In addition, by coupling the washer to the connector to impart damping performance in the axial direction, and by configuring the torque in the circumferential direction by the coil spring it is possible to compensate for the misalignment of the engine shaft and the transmission shaft.

In addition, by applying a load in such an axial and circumferential direction, it is possible to absorb bending and pumping vibration of the engine crankshaft.

In addition, spline coupling between the set double clutch and the damping flywheel facilitates assembly of the engine and transmission, thereby reducing assembly time and improving assembly.

In addition, according to the configuration of the second embodiment, the present invention imparts axial damping performance to the connector by a ring washer so that the washers having different centers of gravity like the general washers of the first embodiment are misaligned due to the influence of centrifugal force at high speed. There is no fear of deformation or deformation, no fear of loss during assembly, and the assembly work can be made more easily and accurately.

1 is a view showing the set double clutch and the damping flywheel separately according to the prior art.
2 is a cross-sectional view of a dry double clutch according to the present invention.
3 is a view illustrating a connector coupled to a damping flywheel in a set double clutch and a damping flywheel according to the present invention.
4 is a view showing a connector coupled to the cover according to the present invention.
5 is a view showing a separate cover and the connector according to the present invention.
6 is a view showing a cover coupled to the connector according to the present invention.
7 is a diagram illustrating a cover and a connector according to another embodiment of the present invention.

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

Figure 2 is a cross-sectional view of the dry double clutch according to the present invention, Figure 3 is a view showing a state in which the set double clutch and the damper flywheel of the dry double clutch according to the present invention is separated.

2 is a cross-sectional view of a dry double clutch according to the present invention. Dry double clutch (Dry Double Clutch) 100 is largely divided into a set double clutch (200) and a damper flywheel (Damper flywheel) (300). First, the damper flywheel 300 is coupled to the engine side, and is composed of a primary wheel 310, a drive plate 320, a primary cover 330, a connector 600, and the like. The set double clutch 200 is a part connected to the transmission side, and includes a first pressure plate 210, a second pressure plate 220, a center plate 215, a first diaphragm spring 230, and a second diaphragm spring 240. And a first clutch disc 250 and a second clutch disc 260, a snap ring 267, a support bearing 268, a connecting plate 400, and the like. The set double clutch 200 and the damper flywheel 300 configured as described above are coupled to the transmission and the engine side, respectively, and then the connector on the connection plate 400 and the damper flywheel 300 side of the set double clutch 200 side ( 600 is connected via spline coupling.

Damper flywheel 300 is composed of a primary wheel 310 and the primary cover 330, the primary wheel 310 is coupled by the engine side and the bolt. The drive plate 320 is accommodated between the primary wheel 310 and the primary cover 330, the drive plate 320 is annular, the flange portion (not shown) extending from the outer peripheral portion, the torsion spring (Not shown) is in contact. The drive plate 320 and the connector 600 are connected by the rivet 315 to transmit the rotational force of the drive plate 320 to the connection plate 400. That is, the damper flywheel 300 may be referred to as a structure similar to the double mass flywheel (DMF).

Looking at the configuration of the set double clutch 200, the center plate 215 of the set double clutch 200 is coupled by the connecting plate 400 and the connecting bolt 217, the center plate 215 is the first The pressure plate 210 and the second pressure plate 220 may compress and rotate the facings 257 and 267 of the clutch disc. The center plate 215 is supported and rotated by the support bearing 268 between the center ring 215 and the snap ring 267 fitted to the second hub 265. The snap ring 267 serves to support and prevent the hollow shaft of the two shafts of the double clutch transmission (not shown). Below the center plate 215 is a first clutch disk 250 having a first hub 255 fitted in the center thereof, and the solid shaft of the transmission is coupled to the first hub 255. On the upper side of the center plate 215 is a second clutch disk 260 into which the second hub 265 is fitted, and the hollow shaft of the two shafts of the transmission is coupled.

The transmission housing 500 accommodates the set double clutch 200 and the damper flywheel 300 and is connected to the cylinder block of the engine. The transmission housing 500 is coupled with a guide tube 515 for guiding the first and second clutch release actuating bearings 510, 520 in the engine direction. The guide tube 515 is coupled to the transmission housing 500 by a bolt, and the shaft of the transmission penetrates through the hollow hole. At this time, the first actuating bearing 510 slides on the outer diameter surface of the guide tube 515, and the second actuating bearing 520 slides on the inner diameter surface of the guide tube 515. Each clutch release actuating bearing 510, 520 strokes the first and second diaphragm springs 230, 240 to pull or push the pressure plates 210, 220 toward the center plate 215 so that the facings of the clutch discs 257, 267 cause friction. Make sure to transfer power. Here, when the first actuating bearing 510 pushes the first diaphragm spring 230, the first pressure plate 210 under the center plate 215 is pulled out to compress the facing 257 with the center plate 215. Let's go. On the other hand, the second actuating bearing 520 pushes the second diaphragm spring 240, and in this case, the second pressure plate 220 is pressed to compress the facing 267 with the center plate 215. The set double clutch 200 of the present invention is a case in which the clutch release actuating bearings 510 and 520 push the diaphragm springs 230 and 240 in a manner of transmitting engine power to the transmission.

3 is a view showing a separated state of the set double clutch and the damper flywheel according to the present invention.

The connection plate 400 having a hollow hole in the set double clutch 200 includes a plurality of extension portions 460 in a radial direction, and the extension portions 460 extend from the outer circumference of the center plate 215. Connected and fixed. In addition, the hollow hole of the connecting plate is formed with teeth for spline coupling in a hub structure.

Damper flywheel 300 is coupled to a ring gear 340 for rotating the damper flywheel when the engine start motor (not shown) the engine start on the outer periphery, the sensor ring 350 for sensing the rotation angle of the crankshaft on the outer periphery This is combined. A connector 600 having a shaft structure for spline coupling with the set double clutch 200 is coupled to the drive plate 320 through the rivet 315 as shown in FIG. 2. Therefore, the connector 600 receives the rotation of the drive plate 320, and the rotational force is transmitted to the connection plate 400 through the connector 600.

4 is a view showing a state in which the connector and the cover according to the present invention is coupled, Figure 5 is a view showing a state in which the connector and the cover is separated. 6 is a view showing a cover according to the present invention.

Connector 600 has a hollow ring shape, consisting of a ring portion 610, a spline gear 620 for spline coupling is formed on the outer peripheral surface of the ring portion 610. The ring portion 610 is provided with a plurality of fastening holes 619 for coupling through the drive plate 320 and the rivet 315 in the circumferential direction. In addition, a plurality of grooves 617 are formed in the inner circumferential surface 650 of the connector 600 in the circumferential direction, and in order to reduce backlash in the spline coupling of the connector 600 and the connecting plate 400, the coil spring 616 and A spring seat 615 that can accommodate the same first elastic member is formed in the radial direction of the groove 617. Therefore, the cover 700 coupled to the upper portion of the connector 600 is supported in the circumferential direction by the coil spring 616.

In addition, the connector 600 has a second elastic member such as a washer 614 for supporting an axial load to compensate for misalignment on the upper side of the ring portion 610 between the cover 700, A seating groove 630 is formed to receive the washer 614 so that the washer 614 can impart an elastic force in the axial direction. The seating groove 630 may be formed according to the shape of the washer 614. The washer 614 may be any shape as long as it can support the axial load, but a shape in which the center portion is convexly raised is preferable. In the present invention, the washer 614 is composed of four legs and convex portions in an H shape, and the central convex portion can support the axial load. The washer 614 is coupled to the connector 600 by the rivet 613, the rivet 613 is simultaneously passed through the cover coupling hole 735 and the washer fastening hole 635 formed in the cover 700, the cover, Tighten the washer and connector at the same time. That is, the washer 614 is accommodated in the seating groove 630 of the connector 600, the cover coupling hole 735 for fastening the cover 700 and the connector 600 and the washer fastening hole of the connector 600 ( 635 is formed to correspond to each other is coupled through the rivet 613. Therefore, the cover 700, the washer 614 and the connector 600 are connected in a simple manner.

The cover 700 has a hollow ring shape, and includes a ring portion 710 and a protrusion 740 extending in the axial direction on an outer circumferential surface of the ring portion. In addition, a support part 730 extending in the axial direction along the circumferential direction may be formed on the inner circumferential surface of the ring part 710. The ring portion 710 is formed with a cover coupling hole 735 through which the rivet penetrates when the connector 600 and the rivet are coupled to each other. ) Is prevented from being removed from the connector 600. The cover coupling hole 735 is formed in plural in the circumferential direction so that the cover 700 can be stably fastened to the connector 600. In addition, the upper surface of the ring portion 710 has a seating portion 720 is formed so that the rotational movement is not hindered by the head of the rivet when the cover 700 rotates relative. At this time, the cover coupling hole 735 formed in the seating portion 720 is preferably formed to be larger than the outer diameter of the rivet 613, in particular is formed in an oval shape by preventing the cover 700 from interfering with the movement of the cover 700 Allows circumferential rotation of the cover 700 to allow relative rotation in the clockwise or counterclockwise direction relative to the connector 700. Meanwhile, after the cover 700 is fastened to the connector 600 in the ring part 710, the rivet 613 is not disturbed when the connector 600 is riveted to the drive plate 320 through the fastening hole 619. A semicircular groove 717 is formed toward the outer circumferential surface so as to prevent it.

In addition, a support part 730 extending along the circumferential direction may be formed on an inner circumferential surface of the ring part 710 to support the cover 700 in the radial direction when the cover 700 and the connector 600 are fastened. The support part 730 is formed to correspond to the inner circumferential surface 650 of the connector 600, and the stepped portion 715 that enters the radial direction corresponding to the inner circumferential surface groove 617 of the connector is positioned along the circumferential direction. 715 may prevent the coil spring 616 of the connector 600 from being removed. In addition, a spring support 718 for supporting the coil spring 616 is formed over the upper side and the stepped portion 715 of the ring portion 710, which is formed by embossing the mold when injecting the cover 700 do.

In addition, the protrusion 740 facing the tooth surface of the gear 620 formed on the outer circumference of the connector 600 is extended in the axial direction on the outer circumferential surface of the ring portion 710 is formed in plural at the same interval, the spline gear 620 of the connector outer circumference It is preferable to form a rectangular plate shape so as to correspond to the tooth surface 640 of the gear while facing the tooth surface 640 to be matched. In addition, a plurality of teeth of the connector 600 facing the protrusion 740 may be formed along the circumferential direction. Accordingly, when the cover 700 and the connector 600 are coupled, the protrusion 740 may face the tooth surface of the gear 620. At this time, the cover 700 has a gap between the protrusion 740 and the tooth surface 640 of the connector 600, because the cover 700 is elastically pressed in the circumferential direction by the coil spring 616, spline coupling No backlash occurs.

On the other hand, if the tooth width of the teeth of the inner circumference of the connecting plate 400 is "w" tooth width (w ") of the teeth of the connector gear 620 may be smaller than" w "to be assembled. The tooth width w 'of the tooth covered with the protrusion 740 in the connector 600 gear 620 has a dimension value equal to or greater than "w", so that the cover 700 is assembled with respect to the connector 600 when assembled. It is assembled while compressing the coil spring 616 to counterclockwise rotate, so that backlash can be reduced, that is, when the cover 700 is coupled to the connector 600, the cover 700 by the coil spring 616 ) Is elastically pushed in the circumferential direction (clockwise), when the three double clutch 200 and the damper flywheel 300 is spline-coupled while pressing the cover 700 in a counterclockwise direction.

In addition, it is preferable that the distance l 'between the teeth sandwiching the protrusion 740 is greater than the distance l between the teeth that are not. This is because a certain distance is required between the tooth surface 640 of the tooth covered with the protrusion 740 and the protrusion 740.

Looking at the operation of the connector 600 coupled to the cover 700, the power generated from the engine is transmitted to the connector 600 coupled to the drive plate, and to the connection plate 400 spline-coupled with the connector 600 do. At this time, although there is a backlash between the spline coupling teeth, the cover 700 is coupled to the connector 600, and the protrusion 740 of the cover 700 faces the tooth surface 640 of the gear 620 of the connector 600. While providing elastic force in the circumferential direction by the coil spring 616, while reducing the backlash when the connecting plate 400 is engaged with the connector 600. Although the rotation direction of the engine is constant, when the vehicle accelerates and decelerates, the spline coupling of the connector 600 and the connecting plate 400 generates relative rotation in a clockwise or counterclockwise direction. Therefore, by reducing the backlash by the protrusion 740 it is possible to prevent the impact, vibration and noise between the spline-coupled connector 600 and the connecting plate 400, thereby increasing the endurance life of the vehicle. Will be. In addition, the washer 614 installed between the connector 600 and the cover 700 imparts axial damping to the cover 700 and can compensate for misalignment that may occur when the engine and the transmission are coupled. In addition, the force of the tangential force of the coil spring 616 and the vertical force of the rivet 613 exerts a force on the cover 600 in an oblique direction such as a diagonal direction.

Now, another embodiment of the present invention will be described with reference to the accompanying drawings.

7 is a view showing a state in which the connector and the cover of the dry double clutch according to another embodiment of the present invention are separated.

As can be seen in FIG. 7, the connector 600, the cover 700, and the first elastic member 616 of this embodiment are similar to those of the first embodiment described above, and thus the description of the same configuration will be omitted. In the following, the difference is as follows.

In the dry double clutch of the present embodiment, since the second elastic member is different from the previous embodiment, the dry double clutch has a gap between the cover 700 and the cover 700 at the upper side of the ring portion 610 of the connector 600 to compensate for misalignment. The ring washers 614 'are arranged coaxially and mounted to support the axial load.

To this end, the connector 600 has a ring portion 610 protruding radially inward to form an annular locking jaw, and a spring support portion 718 for supporting the coil spring 616 in the circumferential direction is fixed on the ring portion 610. Protruding radially inwardly at intervals, except for this is almost the same as the connector 600 of the previous embodiment. In addition, the cover 700 pressurized in the circumferential direction by the coil spring 616 is also made flat except that it is flush with the same height except for the spring seat 615 that protrudes upward to accommodate the coil spring 616. The cover 700 of one embodiment has the same configuration.

On the other hand, the ring washer 614 ′ is formed to have elasticity in the axial direction by forming an inclined portion 621 whose inner circumferential end rises upward and is inclined toward the outer circumferential end, and thus has a plurality of cutouts in the circumferential direction along the outer circumferential end ( 623 is concave inwardly in the outer circumferential end to reduce the overall rigidity of the inclined portion 621 during the celebration to have greater elasticity in the axial direction than the inclined portion 621 of the same shape without the cutout 623. have.

In the above, the present invention has been described in detail with reference to the embodiments of the present invention and the accompanying drawings. However, the scope of the present invention is not limited by the above embodiments and drawings, and the scope of the present invention will be limited only by the contents described in the claims below.

100: dry double clutch 200: three double clutch
300: damper flywheel 400: connection plate
500: transmission housing 600: connector
614: Washer 614 ': Ring Washer
616: coil spring 700: cover

Claims

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Damper flywheel 300 coupled to the engine side; And
In the dry double clutch (100) consisting of: a set double clutch (200) coupled to the damper flywheel (300) for transmitting power of an engine to a transmission;
A connector (600) coupled to the drive plate (320) of the damper flywheel (300) so as to spline and couple to the connection plate (400) of the set double clutch (200);
A cover 700 coupled to the connector 600 so as to be relatively rotatable in a circumferential direction to compensate for backlash between the connection plate 400 and the connector 600;
A first elastic member 616 mounted on the connector 600 to elastically press the cover 700 in the circumferential direction of the connector 600; And
And a second elastic member mounted on the connector (600) to elastically press the cover (700) in the axial direction of the connector (600).

The method of claim 2,
And the second elastic member is a plurality of washers (614) arranged in the circumferential direction of the connector (600) between the connector (600) and the cover (700).

The method of claim 2,
And the second elastic member is a ring washer (614 ') arranged coaxially with the connector (600) between the connector (600) and the cover (700).

5. The method of claim 4,
The ring washer (614 ') is a dry double clutch, characterized in that a plurality of cutouts (623) are formed concave in the circumferential direction along the outer peripheral end of the inclined portion (621).

6. The method according to any one of claims 3 to 5,
The second elastic members 614 and 614 'restrict the cover 700 in the axial direction so as not to be detached from the connector 600, and allow the circumferential rotation of the cover 700 to the connector 600. Dry double clutch, characterized in that coupled to the connector 600 by a rivet 613 penetrating the cover 700 while allowing relative rotation.

The method according to any one of claims 2 to 5,
The cover 700 has at least one protrusion 740 formed in a direction perpendicular to an outer circumference thereof, and the protrusion 740 may face the spline gear 620 of the outer circumference of the connector 600 so as to be able to mate. Dry double clutch, characterized in that formed.

The method of claim 7, wherein
Among the tooth widths of the spline gear 620, the tooth width w 'of the teeth covered by the protrusion 740 is equal to or larger than the tooth width w of the gear teeth formed on the inner circumference of the connecting plate 400. Dry double clutch.

The method of claim 7, wherein
Among the distances between the teeth of the spline gear 620 and the teeth, the distance l 'between the teeth between the protrusions 740 is the distance between the teeth without the protrusions 740 between them. A dry double clutch, characterized in that greater than l).

The method of claim 7, wherein
The protrusions 740 are formed at equal intervals on the outer circumference of the ring portion 710 of the cover 700, and teeth of the spline gear 620 covered by the protrusions 740 are also identical on the outer circumference of the connector 600. Dry double clutch, characterized in that formed at intervals.

The method of claim 7, wherein
The first elastic member 616 is a coil spring, the cover 700 is characterized in that the spring support portion 718 protrudes toward the connector 600 to impart an elastic force to the coil spring in the circumferential direction. Dry double clutch.

The method of claim 7, wherein
The force of the force exerted by the first elastic member 616 and the force exerted by the second elastic members 614 and 614 'with respect to the cover 700 acts on the cover 700 in an oblique direction. Dry double clutch.