JP2014129835A - Dry type multiple disc clutch device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a dry type multiple disc clutch device in which a double structure of a clutch drum and a motor rotor insertion drum part can be inexpensively manufactured in light weight.SOLUTION: The dry type multiple disc clutch device includes: a motor rotor insertion drum part 61 arranged at a clutch drum 6 and having a first cylindrical part 61c inserted into a motor rotor 92; and a second cylindrical part 62b arranged at the first cylindrical part 61c in the inside diameter direction via a communication passage 63 as a clearance, and spline-connected with a driven plate 72. The dry type multiple disc clutch device also includes: a clutch plate support drum part 62 which is connected at a one axial-direction end, with the motor rotor insertion drum part 61; and a support member 69 which is interposed in the communication passage 63 between the first cylindrical part 61c and the second cylindrical part 62b, and can regulate the relative movement of both cylindrical parts 61c, 62b in the radial direction.

Description

  The present invention relates to a dry multi-plate clutch device, and more particularly to a clutch drum portion having a double cylinder structure.

Conventionally, in a dry multi-plate clutch, a clutch drum having a double cylinder structure is known (for example, see Patent Document 1).
In this conventional structure, a clutch drum, on which the clutch plate is mounted on the inner periphery, has a double cylinder structure of a motor rotor insertion drum portion into which an outer motor rotor is inserted, and a clutch plate support drum portion to which an inner clutch plate is coupled. It has become. And the space | gap part between both drum parts is utilized for discharge | emission of abrasion powder.
When manufacturing such a double cylinder structure clutch drum, it is generally formed integrally by forging, but from the viewpoint of manufacturing capability, each drum portion is formed separately and joined by welding. In some cases.

JP 2011-112170 A

  However, in the conventional clutch device, when the clutch plate support drum portion of the clutch drum is formed thin, there is a problem that the strength is reduced and the deformation amount is increased. In particular, when the clutch plate support drum portion and the motor rotor insertion drum portion are formed separately, the clutch plate support drum can be formed thin, and this problem tends to become significant.

  The present invention has been made paying attention to the above problems, and a dry multi-plate clutch device capable of improving the strength of a clutch drum and suppressing deformation as a double cylinder structure of a motor rotor insertion drum portion and a clutch plate support drum portion. The purpose is to provide.

In order to achieve the above object, the present invention provides:
A motor rotor insertion drum portion provided on the clutch drum and provided with a first cylindrical portion inserted into the motor rotor;
The second cylindrical portion is arranged in the inner diameter direction of the first cylindrical portion with a gap and the second clutch plate is splined, and one end in the axial direction is coupled to the motor rotor insertion drum portion. A clutch plate support drum section,
A support member that is interposed in the gap between the first cylindrical portion and the second cylindrical portion, and is capable of restricting relative movement in the radial direction of both cylindrical portions;
A dry multi-plate clutch device is provided.

In the dry multi-plate clutch device of the present invention, in the clutch drum, a support member is interposed between the first cylindrical portion and the second cylindrical portion of the motor rotor insertion drum portion and the clutch plate support drum portion.
For this reason, even when at least one of both cylindrical portions is formed thin, it is possible to suppress the relative displacement in the radial direction of both cylindrical portions compared to the case where no support member is provided, and the strength of the clutch drum is improved. In addition, it is possible to suppress deformation.

It is sectional drawing of the principal part of the hybrid driving force transmission apparatus to which the dry multi-plate clutch apparatus of Embodiment 1 is applied. It is principal part sectional drawing which shows the structure of the motor & clutch unit in the said hybrid driving force transmission apparatus. FIG. 3 is a front view showing a drive plate in the dry multi-plate clutch device of the first embodiment. FIG. 3 is a plan view showing a support member in the dry multi-plate clutch device of the first embodiment. It is the front view which looked at the clutch drum in the dry type multi-plate clutch apparatus of Embodiment 1 from the opening end side of the communicating path. FIG. 3 is a vibration characteristic diagram showing an annular tertiary vibration characteristic of the clutch drum in the dry multi-plate clutch device of the first embodiment.

EMBODIMENT OF THE INVENTION Hereinafter, the form for implementing the control apparatus of the vehicle of this invention is demonstrated based on embodiment shown in drawing.
(Embodiment 1)

  First, the configuration of the hybrid driving force transmission device including the dry multi-plate clutch device 7 according to the first embodiment will be described.

[overall structure]
FIG. 1 is an overall schematic diagram showing a hybrid driving force transmission device. The overall configuration of the apparatus will be described below with reference to FIG.
As shown in FIG. 1, the hybrid driving force transmission device includes an engine Eng, a motor & clutch unit M / C, a transmission unit T / M, an engine output shaft 1, a clutch hub shaft 2, and a clutch hub 3. A clutch drum shaft 4, a transmission input shaft 5, a clutch drum 6, a dry multi-plate clutch device 7, a slave cylinder 8, and a motor / generator 9.
The slave cylinder 8 that hydraulically controls the engagement / release of the dry multi-plate clutch device 7 is generally called “CSC” (abbreviation of “Concentric Slave Cylinder”).

  The hybrid driving force transmission device connects the motor / generator 9 and the transmission input shaft 5 via the clutch drum 6 and the clutch drum shaft 4 when the dry multi-plate clutch device 7 that is normally open is opened. Car driving mode ”. When the dry multi-plate clutch device 7 is hydraulically engaged by the slave cylinder 8, the clutch hub 3 and the clutch drum 6 are connected via the dry multi-plate clutch device 7. As a result, the engine output shaft 1 and the clutch hub shaft 2 are connected via the damper 21, and a “hybrid vehicle travel mode” is established in which the engine Eng and the motor / generator 9 are connected.

The motor and clutch unit M / C provided with the dry multi-plate clutch device 7 includes a slave cylinder 8 and a motor / generator 9 in addition to the dry multi-plate clutch device 7.
The dry multi-plate clutch device 7 is connected to the engine Eng to connect and disconnect the driving force transmitted from the engine Eng.
The slave cylinder 8 hydraulically controls engagement / release of the dry multi-plate clutch device 7.
The motor / generator 9 is disposed at the outer peripheral position of the clutch drum 6 of the dry multi-plate clutch device 7 and transmits power to the transmission input shaft 5.

The motor / generator 9 is a synchronous AC motor and includes a rotor support frame 91, a motor rotor 92, a stator 94, and a stator coil 95.
The rotor support frame 91 is integrally coupled to a motor rotor insertion drum portion 61 provided on the outer periphery of the clutch drum 6 described later.
The motor rotor 92 is supported and fixed to the rotor support frame 91 and has permanent magnets embedded therein.
The stator 94 is disposed on the motor rotor 92 via the air gap 93 and is fixed to the cylinder housing 81.
The stator coil 95 is wound around the stator 94.
The cylinder housing 81 is formed with a water jacket 96 for circulating cooling water.

The transmission unit T / M is connected to the motor & clutch unit M / C and includes a transmission housing 41, a V-belt continuously variable transmission mechanism 42, and an oil pump O / P.
The oil pump O / P drives the pump by transmitting the rotational drive torque of the transmission input shaft 5 via the chain drive mechanism.

[Configuration of motor & clutch unit]
FIG. 2 is a cross-sectional view of the main part showing the configuration of the motor & clutch unit M / C provided with the dry multi-plate clutch device 7 of the first embodiment. Hereinafter, based on FIG. 2, the motor & clutch unit M / C The structure of will be described.

  The clutch hub 3 is connected to the engine output shaft 1 (see FIG. 1) via the clutch hub shaft 2. A drive plate 71 of the dry multi-plate clutch device 7 is held on the clutch hub 3 by spline coupling.

The clutch drum 6 is connected to the transmission input shaft 5 of the transmission unit T / M (see FIG. 1) via the clutch drum shaft 4.
The clutch drum 6 includes a motor rotor insertion drum portion 61 and a clutch plate support drum portion 62.

  The motor rotor insertion drum portion 61 includes a cylindrical first cylindrical portion 61c and a disk-shaped vertical wall portion 61a extending in the inner diameter direction from the substantially axial center of the first cylindrical portion 61c. The first cylindrical portion 61c is inserted into the inner circumference of the motor rotor 92 and the rotor support frame 91 described above. As shown in FIG. 5, the first cylindrical portion 61c of the motor rotor insertion drum portion 61 has a key that defines relative positions with respect to the motor roller at a plurality of circumferential locations (two locations in the first embodiment). A groove 61d is formed.

Returning to FIG. 2, the clutch plate support drum portion 62 is a press-molded product formed separately from the motor rotor insertion drum portion 61, and includes a cylindrical second cylindrical portion 62b and a shaft of the second cylindrical portion 62b. And a coupling flange 62a bent in the inner diameter direction from one end in the direction (left end in the figure).
The second cylindrical portion 62b is disposed via a gap in the inner diameter direction of the first cylindrical portion 61c of the motor rotor insertion drum portion 61, and a communication path 63 extending in the axial direction by the gap between both the cylindrical portions 61c and 62b. Is formed. The communication path 63 has an opening 63a at the end in the axial direction on the right side in the drawing.
The coupling flange 62a is coupled at its distal end in the inner diameter direction to the vertical wall 61a of the motor rotor insertion drum 61 by welding at a coaxial position that is in contact with or close to a step formed on the vertical wall 61a. Has been.

  The second cylindrical portion 62b is formed with a spline 621 in which a driven plate 72 described later is spline-coupled. In the spline groove portion 622 disposed between the splines 621 in the circumferential direction, a communication hole 623 communicating with the communication path 63 on the inner diameter side and the outer diameter side of the second cylindrical portion 62b is formed in the radial direction. Yes.

Next, the dry multi-plate clutch device 7 will be described.
The dry multi-plate clutch device 7 is a clutch for connecting and disconnecting transmission of driving force from the engine Eng, and is a clutch chamber formed by a sealed space surrounded by the clutch hub shaft 2, the clutch hub 3, the clutch drum 6, and the front cover 60. 60c. By fastening the dry multi-plate clutch device 7, torque can be transmitted between the clutch hub 3 and the clutch drum 6, and by opening the dry multi-plate clutch device 7, between the clutch hub 3 and the clutch drum 6. Torque transmission is cut off.

  The dry multi-plate clutch device 7 includes a drive plate 71 (first clutch plate), a driven plate 72 (second clutch plate), a friction facing 73, and a front cover 60.

  The drive plate 71 is spline-coupled to the clutch hub 3, and has a vent hole 74 through which the airflow flowing in the axial direction passes through the spline-coupled portion with the clutch hub 3. As shown in FIG. 3, the vent hole 74 is a position of a spline tooth protrusion 75 projecting to the inner diameter side among spline teeth meshing with the spline part of the clutch hub 3 in the drive plate 71, and a friction facing 73. It is provided at an inner position of the facing groove 76 formed in the above. As shown in FIG. 2, the drive plate 71 is set such that a plurality of (four in the first embodiment) vent holes 74 communicate in the axial direction.

  The driven plate 72 is splined to the second cylindrical portion 62 b of the clutch plate support drum portion 62.

  The driven plate 72 has a ring shape when viewed from the axial direction, and a tooth portion formed on the entire circumference of the driven plate 72 is fitted to the spline 621 of the second cylindrical portion 62b to support the clutch plate. The drum portion 62 is provided so as to be rotatable integrally with the second cylindrical portion 62 b of the drum portion 62.

  The friction facings 73 are provided on both surfaces of the drive plate 71, and the friction surface presses against the plate surface of the driven plate 72 when the clutch is engaged. As shown in FIG. 3, the friction facing 73 is an annular plate member, and has a facing groove 76 formed by a radial radial straight line from the inner diameter position toward the outer diameter position. The facing groove 76 has a depth that maintains the concave groove shape even if the facing wear proceeds to some extent.

Returning to FIG. 2, the slave cylinder 8 described above is a hydraulic actuator that controls the engagement and release of the dry multi-plate clutch device 7, and is located between the transmission unit T / M (see FIG. 1) side and the clutch drum 6. Is arranged.
The slave cylinder 8 includes a piston 82, a first clutch pressure oil passage 85, and a cylinder oil chamber 86.
The piston 82 is slidably provided in the cylinder hole 80 of the cylinder housing 81. The first clutch pressure oil passage 85 is formed in the cylinder housing 81 and guides the clutch pressure created by the transmission unit T / M (see FIG. 1). The cylinder oil chamber 86 is communicated with the first clutch pressure oil passage 85.
The piston arm 822b of the piston 82 is disposed through the through hole 61b formed in the vertical wall portion 61a.

Next, the front cover 60 will be described.
The front cover 60 is integrally fixed to a stationary cylinder housing 81 supported by the first bearing 12 with respect to the clutch drum shaft 4, and covers the motor / generator 9 and the dry multi-plate clutch device 7. That is, the front cover 60 is a stationary member that is supported by the second bearing 13 with respect to the clutch hub shaft 2 and sealed by the cover seal 15.

The internal space covered by the front cover 60 and the cylinder housing 81 is a dry space that blocks oil from entering, and has a motor chamber 60b on the outer diameter side and a clutch chamber 60c on the inner diameter side with the dust seal 60a interposed therebetween. It is divided into and.
The clutch chamber 60c is a space on the clutch rotating shaft CL (= rotor shaft) side in the internal space, and houses the dry multi-plate clutch device 7.
The motor chamber 60 b accommodates the motor / generator 9.

The front cover 60 includes an outside air suction hole 60d, an outside air discharge hole 60e, and a splash guard 60f.
The outside air intake hole 60d is a hole for taking outside air into the clutch chamber 60c by a sealed space. As shown in FIG. 2, among the front cover 60 disposed on the side surface of the dry multi-plate clutch device 7, both clutch plates 71, 72 is provided penetrating in the axial direction at a position near the inner diameter of 72. The specific radial direction setting position of the outside air suction hole 60d is made to coincide with the radial position of the dry multi-plate clutch device 7 in which the vent hole 74 for passing the airflow flowing in the axial direction is set.

  The outside air discharge hole 60e is a hole for discharging the airflow from the inside of the clutch chamber 60c by the sealed space toward the outside air. Is provided penetrating in the axial direction at a position in the vicinity of the outer diameter. The specific radial direction setting position of the outside air discharge hole 60 e is made to coincide with the radial position of the communication passage 63 of the clutch drum 6.

  The splash guard 60f is provided so as to cover both holes 60d and 60e of the front cover 60 in order to prevent water from entering the clutch chamber 60c from the outside air suction hole 60d and the outside air discharge hole 60e provided in the front cover 60. .

Here, the structure of the clutch drum 6 which is a feature of the first embodiment will be described.
As shown in FIG. 2, a support member 69 is interposed between the first cylindrical portion 61c and the second cylindrical portion 62b at the end on the right side in FIG. Has been. This support member 69 is made of metal, and is coupled to the first cylindrical portion 61c and the second cylindrical portion 62b which are also made of metal by welding. In addition to the welding, it is possible to use other means such as bonding or bonding that fits tightly into the first cylindrical portion 61c and the second cylindrical portion 62b. Resin or the like can be used.
Further, the support member 69 is formed in an isosceles triangle shape when viewed from the outer diameter direction of the clutch plate support drum portion 62 in the inner diameter direction as shown in FIG. The support member 69 has the apex portion 69a between the isosceles sides facing in the axial direction toward the back of the communication path 63, and the bottom portion 69b facing outward in the opening 63a of the communication path 63 in the axial direction. Is provided.

Further, as shown in FIG. 5, the support members 69 are arranged at six locations in the circumferential direction in the opening portion of the communication path 63.
And this arrangement | positioning is set to the location used as the peak and valley of a vibration in the annular vibration characteristic of the clutch drum 6. FIG. That is, FIG. 6 is an annular third-order vibration analysis diagram of the clutch drum in a state where the support member 69 is not installed. This clutch drum 6 was found to have vibration peaks pe1 to pe3 and valleys pe4 to pe6 at six locations in the circumferential direction. That is, the peaks pe1 to pe3 and the valleys pe4 to pe6 of the annular vibration characteristic of the clutch drum 6 are uniquely determined by the arrangement of the key grooves 61d and 61d shown in FIG. These peaks pe1 to pe3 and valleys pe4 to pe6 are alternately arranged in the circumferential direction, the peaks pe1 to pe3 show vibration peaks in the outer diameter direction, and the valleys pe4 to pe6 are vibrations in the inner diameter direction. It shows a peak.

  Therefore, the support members 69 are arranged at six locations, which are positions of crests pe1 to pe3 and valleys pe4 to pe6 in the circumferential direction in the opening 63a of the communication path 63.

(Operation of Embodiment 1)
Next, the operation of the first embodiment will be described.
[Wear powder discharge action by air flow effect]
In the first embodiment, the communication passage 63 of the clutch drum 6 is used for discharging the wear powder of the friction facing 73.
That is, if the dry multi-plate clutch device 7 is repeatedly engaged and released, the surface of the friction facing 73 peels off and falls off, which becomes wear powder and accumulates between the clutch plates 71 and 72. Must be discharged to the outside.

Therefore, in the first embodiment, the communication passage 63 of the clutch drum 6 is used for discharging wear powder, and this wear powder discharging action will be described below.
When at least one of the clutch hub 3 and the clutch drum 6 rotates about the clutch rotation axis CL, the friction powder moves in the outer diameter direction by the centrifugal force generated by the friction facing 73.

Further, since the friction facing 73 has the facing groove 76, a centrifugal fan effect is generated.
Due to this centrifugal fan effect, air is sent in the radial direction from the clutch hub 3 side to the clutch drum 6 side, the pressure on the clutch drum 6 side increases (positive pressure), and the pressure on the clutch hub 3 side decreases (negative pressure). . Due to this pressure difference, a radial airflow E is generated in which air moves radially from the clutch hub 3 side to the clutch drum 6 side. That is, the pressure on the inner diameter side of the dry multi-plate clutch device 7 decreases from the atmospheric pressure (negative pressure), and the pressure on the outer diameter side of the dry multi-plate clutch device 7 increases from the atmospheric pressure (positive pressure). The pressure relationship of “pressure on the diameter side> atmospheric pressure> pressure on the inner diameter side of the clutch” is shown.

Due to the generation of the radial airflow, the outside air taken in from the outside air suction hole 60d passes through each vent hole 74 and flows into the clutch hub 3 side where the atmospheric pressure is lowered as indicated by the arrow KR. Airflow is generated.
Furthermore, the spline coupling portion of the driven plate 72 has a low airflow resistance by having a clearance margin to ensure plate movement. In addition, since the spline coupling portion between the driven plate 72 and the second cylindrical portion 62b communicates with the communication path 63 via the communication hole 623, the ventilation resistance is low.
Therefore, as shown by the arrow KR, the airflow that has flowed from the inner diameter side axial direction to the clutch drum 6 while changing the direction from the inner diameter direction passes through the outside air discharge hole 60e from the communication passage 63 and is discharged to the outside air. A side axial airflow is generated.
By this air flow generation action, the wear powder peeled off from the surface of the friction facing 73 is discharged to the outside.

Next, the effect of Embodiment 1 is demonstrated.
In the dry plate clutch device of the first embodiment, the effects listed below can be obtained.
a) The dry plate clutch device of the first embodiment is
A drive plate 71 as a first clutch plate splined to the outer periphery of the clutch hub 3 and arranged in parallel in the axial direction;
A driven plate 72 as a second clutch plate that is alternately arranged in the axial direction with the drive plate 71 and is splined to the inner periphery of the clutch drum 6;
A motor rotor insertion drum portion 61 provided with a first cylindrical portion 61c provided in the clutch drum 6 and inserted into the motor rotor 92;
The first cylindrical portion 61c includes a second cylindrical portion 62b that is disposed via a communication path 63 serving as a gap in the inner diameter direction of the first cylindrical portion 61c. The driven plate 72 is spline-coupled, and one end in the axial direction is coupled to the motor rotor insertion drum portion 61. Clutch plate support drum portion 62,
A support member 69 that is interposed in the communication path 63 between the first cylindrical portion 61c and the second cylindrical portion 62b, and that can restrict the relative movement in the radial direction of both the cylindrical portions 61c and 62b;
It is characterized by having.
Thus, since the support member 69 is interposed on the other end side of the first cylindrical portion 61c and the second cylindrical portion 62b of both the drum portions 61 and 62, even when both the cylindrical portions 61c and 62b are formed thin, It is possible to suppress the vibration in the radial direction of the both 61c and 62b and to suppress the deformation amount.
Thereby, the rigidity and strength of the clutch drum 6 can be improved, and deformation can be suppressed.
Further, the motor rotor insertion drum portion 61 and the clutch plate support drum portion 62 are formed separately, and one end of the clutch plate support drum portion 62 is coupled to the motor rotor insertion drum portion 61. For this reason, it is possible to manufacture the drum parts 61 and 62 at a lower cost than when the drum parts 61 and 62 are integrally formed, and it is possible to reduce the weight by forming a thin thickness. Specifically, in the first embodiment, since a press-molded product is used as the clutch plate support drum portion 62, the clutch drum 6 is of course lighter in weight as compared to using an integral forged product, Processing costs can also be reduced.
And even if both the drum parts 61 and 62 are formed thin in this way and the weight is reduced, the rigidity and strength can be improved and the deformation can be suppressed as described above.

b) The dry multi-plate clutch device of Embodiment 1 is
A plurality of support members 69 are provided at intervals in the circumferential direction of the communication path 63 as a gap.
By disposing the support members 69 at intervals in the circumferential direction, the support members 69 can be prevented from obstructing wear powder discharge in the communication path 63.

c) The dry multi-plate clutch device of Embodiment 1 is
The support member 69 is characterized in that it is arranged on at least one of the circular vibration peaks pe1 to pe3 and the valleys pe4 to pe6 of the clutch drum 6.
As described above, the support member 69 is disposed on at least one of the crests pe1 to pe3 and the valleys pe4 to pe6 of the annular start of the clutch drum 6 to thereby vibrate in the radial direction of both cylindrical portions 61c and 62b of the clutch drum 6. It can be suppressed efficiently.
Furthermore, in this Embodiment 1, since it has arrange | positioned in all of the peaks pe1-pe3 and troughs pe4-pe6 of the ring vibration of the support member 69, ring vibration can be reduced more reliably.

d) The dry multi-plate clutch device of Embodiment 1 is
The communication path 63 as a gap includes an opening 63 a at the end in the axial direction opposite to the direction in which the clutch plate support drum portion 62 is coupled to the motor rotor insertion drum portion 61.
The support member 69 is arranged in the vicinity of the opening 63a in the axial direction.
Thereby, the vibration in the radial direction of the distal end portion of the second cylindrical portion 62b in the free state can be reliably suppressed by the support member 69.
In other words, the support member 69 is disposed at a position in the vicinity of the opening 63a where the vibration at the tip of the second cylindrical portion 62b can be reduced by a desired amount.

e) The dry multi-plate clutch device of the first embodiment is
The support member 69 is characterized in that the width in the circumferential direction is wider toward the opening 63a side in the axial direction, and the width in the circumferential direction is narrower toward the side opposite to the opening 63a in the axial direction.
That is, since the support member 69 has a shape in which the cross-sectional area on the upstream side is narrower in the axial direction than the downstream side in the movement direction of the friction powder in the communication path 63, it is difficult to prevent the discharge of the friction powder. In particular, since the isosceles triangle shape is used, friction powder does not easily accumulate in the apex portion 69a, and the flow in the direction orthogonal to the axial direction can be made equal to the left and right, and the movement of the friction powder is not adversely affected.

As mentioned above, although the driving force transmission device of the present invention has been described based on the embodiments, the specific configuration is not limited to these embodiments, and the invention according to each claim of the claims Design changes and additions are permitted without departing from the gist of the present invention.
In the embodiment, an example using a dry multi-plate clutch as a dry clutch is shown, but an example using a single-plate dry clutch or the like may be used.
In the embodiment, an example of a dry clutch by normal opening has been shown. However, it may be an example of a dry clutch that is normally closed using a diaphragm spring or the like.
In the embodiment, the drive plate is splined to the clutch hub, and the driven plate is splined to the clutch drum. However, the drive plate may be splined to the clutch drum, and the driven plate may be splined to the clutch hub.
In the embodiment, an example in which the drive plate has friction facing has been described. However, the driven plate may have a friction facing.
In the embodiment, an example in which a vent hole, a facing groove, and the like are set in order to secure an air flow path in the dry multi-plate clutch has been shown. However, even if there is no vent hole or fading groove, the communication path of the spline coupling portion becomes an axial airflow passage, and the gap between the plates becomes a radial airflow passage. For this reason, it is not always necessary to set a vent hole or a facing groove.
In the embodiment, an example of application to a hybrid driving force transmission device in which an engine and a motor / generator are mounted and a dry multi-plate clutch is used as a travel mode transition clutch has been described. However, the present invention can also be applied to an engine driving force transmission device in which only an engine is mounted as a driving source and a dry clutch is used as a starting clutch, such as an engine vehicle. Further, the present invention can be applied to a motor driving force transmission device in which only a motor / generator is mounted as a driving source and a dry clutch is a starting clutch, such as an electric vehicle or a fuel cell vehicle.

Further, in the embodiment, the example in which the gap formed between the first cylindrical portion and the second cylindrical portion is used as a communication path for exhausting wear powder is shown. It is applicable also to what is not used. That is, even in this case, it is possible to reduce the weight and reduce the cost.
In the embodiment, the motor rotor insertion drum portion and the clutch plate support drum portion are separately formed and joined by welding. However, a coupling structure in which both are integrally formed may be used. In this case, as explained in the prior art, it can be formed by forging.

In the embodiment, the example in which the supporting members are provided at six locations in the circumferential direction has been described. However, the number and the position thereof are not limited to this, and the supporting members may be installed at optimum positions according to the specifications. In addition, in the embodiment, as the position, the example in which all the peaks and valleys of the circular third-order vibration are arranged has been shown. However, the present invention is not limited to this. And may be selectively provided in a part of the valley.
Further, the shape of the support member is not limited to the shape of an isosceles triangle shown in the embodiment. As described above, when the gap is not used as a communication path for discharging wear powder, the shape opposite to the opening of the communication path may be widened.
Further, when narrowing the upstream side of the communication path, it may be narrowed by an arc shape, or a structure in which apexes of a triangle or more such as a pentagon are arranged upstream.
Moreover, although the example which showed the example which provided the supporting member in the opening part of the communicating path as a clearance gap was shown in embodiment, you may arrange | position to the back | inner side of a communicating path rather than this opening part. Or you may provide in the multiple places of an axial direction.

3 Clutch hub 6 Clutch drum 61 Motor rotor insertion drum portion 61c First cylindrical portion 62 Clutch plate support drum portion 62b Second cylindrical portion 63 Communication path (gap)
63a Opening 69 Support member 71 Drive plate (first clutch plate)
72 Driven plate (second clutch plate)
pe1 to pe3 (for ring vibration) mountain pe4 to pe6 (for ring vibration) valley

Claims (5)

A first clutch plate splined to the outer periphery of the clutch hub and arranged in parallel in the axial direction;
A second clutch plate that is alternately arranged in the axial direction with the first clutch plate and is splined to the inner periphery of the clutch drum;
A motor rotor insertion drum portion provided on the clutch drum and having a first cylindrical portion inserted into the motor rotor;
The second cylindrical portion is arranged in the inner diameter direction of the first cylindrical portion with a gap and the second clutch plate is splined, and one end in the axial direction is coupled to the motor rotor insertion drum portion. A clutch plate support drum section,
A support member that is interposed in the gap between the first cylindrical portion and the second cylindrical portion, and is capable of restricting relative movement in the radial direction of both cylindrical portions;
A dry multi-plate clutch device characterized by comprising: In the dry multi-plate clutch device according to claim 1,
The dry multi-plate clutch device, wherein a plurality of the support members are provided at intervals in the circumferential direction of the gap. In the dry multi-plate clutch device according to claim 2,
The dry multi-plate clutch device according to claim 1, wherein the support member is disposed in at least one of a peak and a valley of annular vibration of the clutch drum. In the dry multi-plate clutch device according to any one of claims 1 to 3,
The gap includes an opening at the end in the axial direction opposite to the clutch plate support drum portion coupled to the motor rotor insertion drum portion,
The dry multi-plate clutch device, wherein the support member is disposed in the vicinity of the opening in the axial direction. In the dry multi-plate clutch device according to any one of claims 1 to 4,
The support member is formed so that a width in a circumferential direction is wider toward an opening side in the axial direction and a width in a circumferential direction is narrower toward a side opposite to the opening in the axial direction. Plate clutch device.