JP7419940B2 - Drive force transmission device - Google Patents

Description

The present invention relates to a driving force transmission device.

Patent Document 1 discloses a driving force transmission device in which an arm tip of a piston arm and a multi-plate dry clutch come into contact when the clutch is engaged.

Japanese Patent Application Publication No. 2013-29199

In the driving force transmission device disclosed in Patent Document 1, when the friction surface of the multi-disc dry clutch is slid and the multi-disc dry clutch is engaged with a large pressing force, the μ-V characteristic of the multi-disc dry clutch has a negative slope. , self-excited vibration in which the natural mode of the piston arm structure diverges occurs, and this self-excited vibration becomes an excitation source, which may generate abnormal noise.
An object of the present invention is to provide a driving force transmission device that suppresses the generation of abnormal noise.

The driving force transmission device of the present invention includes a plurality of drive plates that are spline-coupled to a clutch hub of a drive force transmission system and a plurality of driven plates that are spline-coupled to a clutch drum, which are arranged alternately. A multi-disc dry clutch that connects and disconnects driving force, a piston that is slidably provided on the housing member and strokes in the clutch engagement direction by hydraulic pressure when the multi-disc dry clutch is engaged, and a piston that is formed on the side wall of the clutch drum. A piston whose arm tip, which is slidably provided in a through hole and protrudes into a clutch chamber containing a dry clutch, strokes following the stroke motion of the piston to press a plurality of drive plates and a plurality of driven plates. an arm, and a return spring that is interposed between the side wall of the clutch drum and the piston and applies a biasing force to the piston arm in the direction of clutch release when the multi-plate dry clutch is released, and includes at least one of the plurality of driven plates. One driven plate is divided into two pieces, a first driven plate and a second driven plate, and the thicknesses of the first driven plate and the second driven plate in the rotational axis direction are made to be different.

Therefore, generation of abnormal noise can be suppressed.

1 is an overall schematic diagram showing a driving force transmission device of Embodiment 1. FIG. FIG. 2 is a cross-sectional view of essential parts showing the configuration of a multi-plate dry clutch of the motor and clutch unit in the driving force transmission device of Embodiment 1. FIG. 2 is an exploded side view showing the piston assembly of the multi-disc dry clutch in the driving force transmission device of Embodiment 1. 1 is an exploded perspective view showing a piston assembly of a multi-plate dry clutch in the driving force transmission device of Embodiment 1. FIG. FIG. 3 is a diagram showing vibration transmission characteristics of the first driven plate and the second driven plate of Embodiment 1. FIG. 3 is a cross-sectional view of essential parts showing the configuration of a multi-plate dry clutch of a motor and clutch unit in a driving force transmission device according to a second embodiment.

[Embodiment 1]
FIG. 1 is an overall schematic diagram showing a driving force transmission device according to a first embodiment.
Hereinafter, the overall configuration of the driving force transmission device of the first embodiment will be explained based on FIG. 1.

(Overall configuration of driving force transmission device)
The driving force transmission device of Embodiment 1 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, a clutch hub 3, and a clutch drum. It includes a shaft 4, a transmission input shaft 5, a clutch drum 6, a multi-plate dry clutch 7, a slave cylinder 8, and a motor/generator (motor) 9.
The slave cylinder 8 that hydraulically controls the engagement and disengagement of the multi-disc dry clutch 7 is generally called a "CSC" (abbreviation for Concentric Slave Cylinder).

The driving force transmission device of the first embodiment connects the motor/generator 9 and the transmission input shaft 5 via the clutch drum 6 and the clutch drum shaft 4 when the normally open multi-plate dry clutch 7 is released. Set to "electric vehicle driving mode".
When the multi-disc dry clutch 7 is hydraulically engaged by the slave cylinder 8, the engine Eng and the motor/generator 9 are coupled together, and the engine output shaft 1 and the clutch hub shaft 2 are coupled via the damper 21.
Then, the clutch hub 3 and the clutch drum 6 are connected via the fastened multi-disc dry clutch 7 to enter the "hybrid vehicle driving mode."

The motor and clutch unit M/C includes a multi-plate dry clutch 7, a slave cylinder 8, and a motor/generator 9.
The multi-plate dry clutch 7 is connected to the engine Eng, and connects and disconnects the transmission of driving force from the engine Eng.
The slave cylinder 8 hydraulically controls the engagement and disengagement of the multi-disc dry clutch 7.
The motor/generator 9 is disposed on the outer periphery of the clutch drum 6 of the multi-disc dry clutch 7 and transmits power to and from the transmission input shaft 5.
This motor and clutch unit M/C is provided with a cylinder housing (housing member) 81 having a first clutch pressure oil passage 85 to the slave cylinder 8 while maintaining sealing performance with an O-ring 10.

The motor/generator 9 is a synchronous AC motor, and includes a rotor support frame 91 that is provided integrally with the clutch drum 6, and a rotor 92 that is supported and fixed to the rotor support frame 91 and has permanent magnets embedded therein.
The rotor 92 includes a stator 94 that is disposed on the rotor 92 via an air gap 93 and fixed to the cylinder housing 81, and a stator coil 95 that is wound around the stator 94.
Note that the cylinder housing 81 is formed with a water jacket 96 through which cooling water flows.

The transmission unit T/M is connected to the motor and clutch unit M/C, and includes a transmission housing 41, a V-belt type continuously variable transmission mechanism 42, and an oil pump O/P.
The V-belt type continuously variable transmission mechanism 42 is built into the transmission housing 41, and a V-belt is stretched between two pulleys to obtain a continuously variable transmission ratio by changing the belt contact diameter.
The oil pump O/P is a hydraulic source that generates hydraulic pressure to the necessary parts.The oil pump pressure is the source pressure, and the oil pump O/P is a hydraulic source that generates hydraulic pressure to the necessary parts.The oil pump O/P is a hydraulic source that generates hydraulic pressure to the necessary parts. Guides hydraulic pressure to the required area.
This transmission unit T/M is further provided with a forward/reverse switching mechanism 43, an oil tank 44, and an end plate 45. The end plate 45 has a second clutch pressure oil passage 47 (see FIG. 2).

The oil pump O/P is pump-driven by transmitting rotational drive torque of the transmission input shaft 5 via a chain drive mechanism.
The chain drive mechanism includes a driving sprocket 51 that rotates as the transmission input shaft 5 rotates around the rotation axis P, a driven sprocket 52 that rotationally drives the pump shaft 57, and a chain that spans both sprockets 51 and 52. It has a chain 53.
The drive side sprocket 51 is interposed between the transmission input shaft 5 and the end plate 45 and is rotatable around the rotation axis P via a bush 55 with respect to a stator shaft 54 fixed to the transmission housing 41. Supported.
Then, the rotational drive torque from the transmission input shaft 5 is transmitted through the first adapter 56 which is spline-fitted to the transmission input shaft 5 and is claw-fitted to the drive side sprocket 51 .

FIG. 2 is a cross-sectional view of main parts showing the configuration of the multi-plate dry clutch of the motor and clutch unit in the driving force transmission device of Embodiment 1, and FIG. FIG. 4 is an exploded side view showing the piston assembly of the multi-disc dry clutch in the driving force transmission device of Embodiment 1. FIG.
The configuration of the multi-disc dry clutch 7 and slave cylinder 8 of the motor & clutch unit M/C will be explained below based on FIGS. 2 to 4.

(Composition of multi-plate dry clutch and slave cylinder of motor & clutch unit)
Clutch hub 3 is connected to engine output shaft 1 of engine Eng (see FIG. 1).
As shown in FIG. 2, the clutch hub 3 holds four drive plates 71 with friction facings 73 attached to both sides of the multi-plate dry clutch 7 by spline connection.

Clutch drum 6 is connected to transmission input shaft 5 of transmission unit T/M.
As shown in FIG. 2, the clutch drum 6 holds four sets of driven plates 72 and one retainer plate 74 of the multi-plate dry clutch 7 by spline connection.
Note that each driven plate 72 includes a first driven plate 72a made of the same material and a second driven plate 72b that is thinner in the direction of the rotation axis P than the first driven plate 72a.
Further, a groove 6a is formed in the inner peripheral surface of the clutch drum 6 on the right side of the retainer plate 74 in the figure, and a C ring 75 for preventing the four sets of driven plates 72 and one retainer plate 74 from coming off is inserted into the groove 6a. is fitted.

The multi-plate dry clutch 7 is a driven plate 71 that is placed between the clutch hub 3 and the clutch drum 6 and has friction facings 73, 73 attached to both sides, and a first driven plate 72a and a second driven plate 72b. The plates 72 are interposed by alternately arranging them.
In other words, by engaging the multi-disc dry clutch 7, torque can be transmitted between the clutch hub 3 and the clutch drum 6, and by disengaging the multi-disc dry clutch 7, the torque can be transmitted between the clutch hub 3 and the clutch drum 6. Cut off torque transmission.

The slave cylinder 8 is a hydraulic actuator that controls engagement and disengagement of the multi-plate dry clutch 7, and is arranged at a position between the transmission unit T/M side and the clutch drum 6.
As shown in FIG. 2, this slave cylinder 8 includes a piston 82 slidably provided in a cylinder hole 80 of a cylinder housing 81, and a piston 82 formed in the cylinder housing 81, which transmits the clutch pressure created by the transmission unit T/M. It has a first clutch pressure oil passage 85 that leads to the first clutch pressure oil passage, and a cylinder oil chamber 86 that communicates with the first clutch pressure oil passage 85.
As shown in FIG. 2, a needle bearing 87, a piston arm 83, a return spring 84, and an arm fixing plate 88 are interposed between the piston 82 and the multi-plate dry clutch 7.

The piston arm 83 generates the pressing force of the multi-plate dry clutch 7 by the pressing force from the slave cylinder 8, and is provided so as to be slidable in the through hole 61 formed in the clutch drum 6.
A return spring 84 is interposed between the piston arm 83 and the clutch drum 6.
The needle bearing 87 is interposed between the piston 82 and the piston arm 83, and prevents the piston 82 from rotating as the piston arm 83 rotates.
The arm fixing plate 88 is provided integrally with the bellows elastic seal members 89, 89, and the outer peripheral portions of the bellows elastic seal members 89, 89 are press-fitted and fixed to the clutch drum 6.
The arm fixing plate 88 and the bellows elastic seal members 89, 89 block leakage oil from the piston arm 83 side from flowing into the multi-disc dry clutch 7.
That is, an arm fixing plate 88 and a bellows elastic seal member 89, which are sealed and fixed to the piston arm mounting position of the clutch drum 6, are used as partitions to separate a wet space in which the slave cylinder 8 is arranged and a dry space in which the multi-disc dry clutch 7 is arranged. It has a function.

As shown in FIGS. 3 and 4, the piston arm 83 includes an arm body 83a formed in a ring shape, and arm protrusions (arm tips) 83b protruding from the arm body 83a at four locations. ing.

As shown in FIGS. 3 and 4, the return spring 84 includes a ring-shaped spring support plate 84a and a plurality of (28 in the first embodiment) coil springs 84b fixed to the spring support plate 84a. It is configured.

As shown in FIG. 2, the leak oil recovery path of the first embodiment includes the first bearing 12, the first seal member 31, the leak oil path 32, the first recovery oil path 33, and the second recovery oil path. It is equipped with 34.
That is, the circuit returns leaked oil from the sliding portion of the piston 82 to the transmission unit T/M through the first recovery oil passage 33 and the second recovery oil passage 34 sealed by the first seal member 31. be.
In addition, leak oil from the sliding portion of the piston arm 83 is removed from the leak oil passage 32 sealed by the partition seal structure (arm fixing plate 88, bellows elastic seal members 89, 89) and the first seal member 31. This is a circuit that passes through the first recovery oil passage 33 and the second recovery oil passage 34 sealed by and returns to the transmission unit T/M.

As shown in FIG. 2, the bearing lubricating oil passage of the first embodiment includes the needle bearing 20, the second seal member 14, the first axial oil passage 19, the second axial oil passage 18, and the lubricating oil passage. 16 and a gap 17.
The bearing lubricating oil passage supplies bearing lubricating oil from the transmission unit T/M to the needle bearing 20, the first bearing 12 that rotatably supports the clutch drum 6 with respect to the cylinder housing 81, the piston 82, and the piston arm 83. Bearing lubrication is performed through a path that passes through the needle bearing 87 interposed between the transmission unit and the transmission unit T/M and returns to the transmission unit T/M.

The second seal member 14 is interposed between the clutch hub 3 and the clutch drum 6, as shown in FIG.
The second seal member 14 seals the bearing lubricating oil from flowing from the wet space where the slave cylinder 8 is arranged into the dry space where the multi-disc dry clutch 7 is arranged.

Next, the detailed configuration of the clutch engagement/disconnection operation system set in the motor & clutch unit M/C will be explained based on FIGS. 2 to 4.

(Detailed configuration of the clutch connection/disconnection operation system set in the motor & clutch unit)
As shown in FIG. 2, the clutch connection/disconnection operation system of the first embodiment includes a multi-plate dry clutch 7, a piston 82, a piston arm 83, a return spring 84, bellows elastic seal members 89, 89, and an arm fixing member. A plate 88 is provided.
As shown in FIG. 2, the multi-plate dry clutch 7 is provided between the clutch hub 3 and the clutch drum 6 of the driving force transmission system, and connects and disconnects the driving force by releasing and engaging the clutch.

As shown in FIG. 2, the piston 82 is slidably provided in the cylinder housing 81, and when the multi-disc dry clutch 7 is engaged, the piston 82 is stroked in the clutch engagement direction (rightward in FIG. 2) by hydraulic pressure.

The piston arm 83 is slidably provided in a through hole 61 formed in the side wall of the clutch drum 6, and four arm protrusions 83b of the piston arm 83 protrude into a clutch chamber 64 containing a multi-plate dry clutch. The stroke follows the stroke motion of the piston 82 (FIGS. 3 and 4).
The piston arm 83 is manufactured from an aluminum alloy material. Note that the dry chamber is defined by a seal member 62 into a clutch chamber 64 and a motor chamber 65.

The return spring 84 is interposed between the side wall of the clutch drum 6 and the piston arm 83, and when the multi-plate dry clutch 7 is released, it applies a biasing force to the piston arm 83 in the direction of clutch release (FIGS. 3 and 4). .

As shown in FIG. 2, the bellows elastic seal members 89, 89 are press-fitted and fixed to the side wall position of the clutch drum 6 that seals the through hole 61 and the arm protrusion 83b from the clutch chamber 64, and are responsive to the stroke movement of the arm protrusion 83b. It follows and elastically deforms.
The bellows elastic seal members 89, 89 are made of a rubber-based material and have an S-shaped bellows cross-sectional shape that provides the arm fixing plate 88 with an elastic restoring force that returns it to the clutch release side when the multi-plate dry clutch 7 is released.
The fixing positions of the bellows elastic seal members 89, 89 with respect to the arm fixing plate 88 are offset from the tip of the arm toward the cylinder housing 81, as shown in FIG.
That is, the middle position of the protruding amount of the arm protrusion 83b into the clutch chamber 64 is the fixed position of the bellows elastic seal members 89, 89, and the bellows elastic seal members 89, 89 are connected to the side wall surface of the clutch drum 6 and the tip of the arm. The setting is such that it fits within the axial region between.
With this configuration, even if the bellows elastic seal members 89, 89 have an S-shaped bellows cross section, the bellows elastic seal members 89, 89 do not interfere with the dry multi-disc clutch 7 during the engagement/disengagement operation of the dry multi-disc clutch 7. It can be done.

As shown in FIG. 2, the arm fixing plate 88 is provided integrally with the bellows elastic seal members 89, 89 by vulcanization adhesion, and is press-fitted and fixed to the tip of the arm protrusion 83b, so that the multi-disc dry clutch 7 can be fastened. When the clutch is in contact with the driven plate 72, the clutch engagement force is transmitted.
This arm fixing plate 88 is made of a metal material (eg, stainless steel material) that has a lower thermal conductivity than a steel plate.

(Clutch engagement/release action by slave cylinder)
Next, the effect will be explained.
The clutch engagement/disengagement action of engaging/disengaging the multi-plate dry clutch 7 using the slave cylinder 8 will be described below with reference to FIG.

When the multi-plate dry clutch 7 is engaged by the slave cylinder 8, the clutch oil pressure generated by the transmission unit T/M is passed through the first clutch pressure oil passage 85 formed in the cylinder housing 81 and into the cylinder oil chamber 86. supply
As a result, a hydraulic pressure obtained by multiplying the hydraulic pressure and the pressure receiving area acts on the piston 82, and the piston 82 is moved against the urging force of the return spring 84 interposed between the piston arm 83 and the clutch drum 6 as shown in FIG. stroke to the right.
The fastening force due to the difference between the hydraulic pressure and the urging force is transmitted from the piston 82 to the needle bearing 87 to the piston arm 83 to the arm fixing plate 88, and presses the drive plate 71 and driven plate 72 against the retainer plate 74, causing the multi-plate Dry clutch 7 is engaged.

When the multi-disc dry clutch 7 in the engaged state is released, the hydraulic oil supplied to the cylinder oil chamber 86 is discharged to the transmission unit T/M through the clutch pressure oil passage 85 and acts on the piston 82. When the hydraulic pressure is lowered, the biasing force by the return spring 84 exceeds the hydraulic pressure, causing the piston arm 83 and arm fixing plate 88, which are integrally formed, to move to the left in FIG. 2.
As a result, the fastening force transmitted to the arm fixing plate 88 is released, and the multi-plate dry clutch 7 is released.

FIG. 5 is a diagram showing the vibration transmission characteristics of the first driven plate and the second driven plate of the first embodiment.
The vertical axis is the vibration transmissibility τ, and the horizontal axis is the vibration frequency ratio (f/fo).

In the direction of the rotation axis P, the vibration transmission characteristics of the first driven plate 72a, which is thicker and has a larger mass than the second driven plate 72b, have a vibration transmission rate τ that peaks at the natural (resonant) frequency fo1, and a frequency (√2 *fo1), the vibration transmissibility τ becomes 0, and at frequencies equal to or higher than (√2*fo1), the vibration transmissibility τ becomes negative.
That is, at frequencies equal to or higher than (√2*fo1), the vibration transmission characteristic of the first driven plate 72a falls within the vibration isolation region.
Further, the independent vibration transmission characteristic of the second driven plate 72b, which has a smaller mass than the first driven plate 72a, has a natural (resonant) frequency fo2 higher than the natural (resonant) frequency fo1 of the first driven plate 72a, as shown by the broken line. The vibration transmissibility τ reaches a peak at a frequency of (√2*fo2), becomes 0 at a frequency of (√2*fo2), and becomes negative at a frequency equal to or higher than (√2*fo2).
Note that the natural (resonant) frequency fo2 of the second driven plate 72b is set to be 1.4 times or more the natural (resonant) frequency fo1 of the first driven plate 72a.
Therefore, due to the natural vibration of the first driven plate 72a and the second driven plate 72b, which are divided into two parts having different thicknesses in the direction of the rotational axis P while the multi-plate dry clutch 7 is engaged, the first driven plate 72a and the second driven plate 72b are separated. A friction force due to a dynamic minute slip is generated between the driven plates 72b, and a damping effect can be exerted, and the vibration transmissibility τ peaks at the natural (resonant) frequency fo2 of the second driven plate 72b. , the peak of the vibration transmissibility τ at the natural (resonant) frequency fo2 of the second driven plate 72b is vibration-isolated. As a result, the vibration transmissibility τ of a single vibration characteristic is attenuated to about half or less of the peak.

In this way, by configuring the driven plate 72 with the thick first driven plate 72a and the thin second driven plate 72b, the multi-disc dry clutch 7 is able to separate the two divided plates during engagement. Due to the natural vibration of the first driven plate 72a and the second driven plate 72b, a friction force due to a dynamic minute slip is generated between the first driven plate 72a and the second driven plate 72b, and a damping effect can be exerted. , generation of abnormal noise due to self-excited vibration can be suppressed.
Further, since the natural (resonant) frequency fo2 of the second driven plate 72b is set to be 1.4 times or more the natural (resonant) frequency fo1 of the first driven plate 72a, both driven plates 72a, 72b Since the energy that influences each other is halved and the natural (resonant) frequencies of both driven plates 72a and 72b are no longer coupled and amplified, it is possible to further suppress the generation of abnormal noise due to self-excited vibration.
Furthermore, in the direction of the rotation axis P, the thicker first driven plate 72a is arranged closer to the piston arm 83 than the thinner second driven plate 72b, so that the multi-plate dry clutch 7 is pressed during engagement. Following the shape of the four arm protrusions 83b of the piston arm 83, it is possible to prevent uneven contact between the frictional fastening surfaces of the first driven plate 72a and the second driven plate 72b, thereby reducing squealing. Squeal can be suppressed by preventing local μ-V characteristics caused by non-uniformity of the friction surface.

Next, the effects will be explained.
The driving force transmission device of the first embodiment has the following effects.

(1) Each driven plate 72 is composed of a first driven plate 72a made of the same material and a second driven plate 72b thinner than the first driven plate 72a.
Therefore, due to the natural vibration of the first driven plate 72a and the second driven plate 72b, which are divided into two parts having different thicknesses in the direction of the rotational axis P when the multi-plate dry clutch 7 is engaged, the first driven plate 72a and the second driven plate 72b are separated. Frictional force is dynamically generated between the plates 72b due to minute slips, and a damping effect can be exerted.

(2) The natural (resonant) frequency fo2 of the second driven plate 72b is set to be 1.4 times or more the natural (resonant) frequency fo1 of the first driven plate 72a.
Therefore, the energy that both driven plates 72a, 72b influence each other is halved, and the natural (resonant) frequencies of both driven plates 72a, 72b are no longer coupled and amplified, so that the generation of abnormal noise due to self-excited vibration is further suppressed. be able to.

(3) In the direction of the rotational axis P, the thicker first driven plate 72a is arranged closer to the piston arm 83 than the thinner second driven plate 72b.
Therefore, following the shape of the four arm protrusions 83b of the piston arm 83 that the plate dry clutch 7 presses during engagement, the contact between the frictional engagement surfaces of the first driven plate 72a and the second driven plate 72b becomes uneven. Therefore, it is possible to prevent local μ-V characteristics due to non-uniformity of the friction surface, which causes squeaking, and to suppress squeal.

[Embodiment 2]
FIG. 6 is a sectional view of a main part showing the configuration of a multi-plate dry clutch of a motor and clutch unit in a driving force transmission device according to a second embodiment.

In the first embodiment, each driven plate 72 is composed of a first driven plate 72a made of the same material and a second driven plate 72b thinner than the first driven plate 72a, but in the second embodiment, the atmosphere When the temperature is high and the surface temperature of the friction facing 73 is also high when the multi-plate dry clutch 7 is engaged, only the two sets of driven plates 72 located near the center in the direction of the rotational axis P where squeal is most likely to occur are It is constructed of a first driven plate 72a made of the same material and a second driven plate 72b thinner than the first driven plate 72a.
Except for this point, since the configuration is the same as that of the first embodiment, the same configurations are denoted by the same reference numerals, and the description thereof will be omitted.

As explained above, the second embodiment has the following effects in addition to the effects of the first embodiment.

(1) When the ambient temperature is high and the surface temperature of the friction facings 73 is also high when the multi-plate dry clutch 7 is engaged, only the central two sets of driven plates 72, which are most likely to generate squeal, are replaced with the first set of driven plates 72 made of the same material. It is made up of a driven plate 72a and a second driven plate 72b which is thinner than the first driven plate 72a.
Therefore, it is possible to suppress an increase in the number of parts and to effectively prevent squealing.

[Other Examples]
Although the mode for carrying out the present invention has been described above based on the embodiments, the specific configuration of the present invention is not limited to the configuration shown in the embodiments, and is within the scope of the gist of the invention. Even if there is a design change, etc., it is included in the present invention.
For example, in the first embodiment, all the plurality of driven plates 72 are divided into two, the first driven plate 72a and the second driven plate 72b, and in the second embodiment, only the two driven plates 72 located near the center are divided. is divided into two, the first driven plate 72a and the second driven plate 72b, but at least one driven plate 72 may be divided into two, the first driven plate 72a and the second driven plate 72b.

3 Clutch hub 6 Clutch drum 64 Clutch chamber 7 Multi-plate dry clutch 71 Drive plate 72 Driven plate 72a First driven plate 72b Second driven plate 81 Cylinder housing (housing member)
82 Piston 83 Piston arm 83a Arm body 83b Arm protrusion (arm tip)
84 Return spring 9 Motor/generator (motor)
Eng Engine P Rotation axis

Claims (5)

This multi-plate dry type is equipped with a plurality of drive plates that are spline-coupled to the clutch hub of the drive power transmission system and a plurality of driven plates that are spline-coupled to the clutch drum, which are arranged alternately, and the drive force is connected and disconnected by clutch release and clutch engagement. clutch and
a piston that is slidably provided on the housing member and that strokes in the clutch engagement direction by hydraulic pressure when the multi-plate dry clutch is engaged;
An arm distal end portion that is slidably provided in a through hole formed in a side wall of the clutch drum and that protrudes into a clutch chamber housing the multi-plate dry clutch moves in accordance with the stroke motion of the piston, and a piston arm that presses the drive plate and the plurality of driven plates;
a return spring that is interposed between a side wall of the clutch drum and the piston and applies a biasing force to the piston arm in the clutch opening direction when the multi-plate dry clutch is opened;
Equipped with
At least one driven plate among the plurality of driven plates is divided into two, a first driven plate and a second driven plate, and the first driven plate and the second driven plate have different thicknesses in the rotation axis direction. Ta,
A driving force transmission device characterized by: The driving force transmission device according to claim 1,
The first driven plate is thicker in the rotational axis direction than the second driven plate,
The natural frequency of the second driven plate is 1.4 times or more the natural frequency of the first driven plate.
A driving force transmission device characterized by: The driving force transmission device according to claim 1,
Of the plurality of driven plates, only the driven plate located near the center in the direction of the rotational axis is divided into two, a first driven plate and a second driven plate, and rotation of the first driven plate and the second driven plate is performed. With different thicknesses in the axial direction,
A driving force transmission device characterized by: The driving force transmission device according to any one of claims 1 to 3,
The first driven plate is thicker in the rotational axis direction than the second driven plate,
the first driven plate is arranged on the piston side;
A driving force transmission device characterized by: The driving force transmission device according to any one of claims 1 to 4,
The multi-disc dry clutch is a multi-disc dry clutch interposed between the engine and motor of the hybrid drive system,
The multi-disc dry clutch uses the engine and the motor as a power source when the clutch is engaged in a driving mode, and uses the motor as a power source when the clutch is released in a driving mode.
A driving force transmission device characterized by:

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