JPH0742761A - Hydraulic clutch - Google Patents

Abstract

PURPOSE:To prevent a clutch piston from being energized by hydraulic pressure to be produced by means of centrifugal force acting on oil in a control hydraulic chamber of a hydrailic clutch. CONSTITUTION:This hydraulic clutch is provided with a clutch plate 5 engaging with a clutch outer 2 through a spline, another clutch plate 6 engaging with a clutch inner 4 through another spline, and a clutch piston 8 making both these clutch plates 5, 6 comes into contact with each other with hydraulic pressure to be fed to a control hydraulic chamber 12, respectively. In this constitution, a lubricating oil sump chamber 13 to be supplied with lubricating oil is formed in the opposite side of the control hydraulic chamber 12 holding the clutch piston in between, while hydraulic pressure being produced by centrifugal force acting on oil in the control hydraulic chamber 12 and energizing the clutch piston 8 to the right is offset by another hydraulic pressure being produced by the centrifugal force acting on oil in the oil sum chamber 13 and energizing the clutch piston 8 to the left.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hydraulic clutch used in a continuously variable transmission of an automobile, and more particularly to a clutch piston which is moved in the axial direction by a hydraulic pressure supplied to a control hydraulic chamber. Hydraulic clutch of the type in which the clutch plates are pressed and brought into contact with each other.

[0002]

By the way, since the control hydraulic chamber of such a hydraulic clutch rotates around a rotating shaft together with the clutch piston, a hydraulic pressure is generated by a centrifugal force acting on the oil in the control hydraulic chamber, and the hydraulic pressure causes the clutch piston to move in the axial direction. There is a problem that is urged by.

In the structure conventionally adopted to solve such a problem, a through hole is formed in the clutch piston for communicating the inside and outside of the control hydraulic chamber, and the through hole is formed by a reed valve having a weight at its free end. When the hydraulic pressure is supplied to the control hydraulic chamber to engage the hydraulic clutch, the reed valve is closed by the supplied hydraulic pressure to close the through hole. When the hydraulic pressure in the control hydraulic chamber is released to release the engagement of the hydraulic clutch, the reed valve is opened by the centrifugal force acting on the weight to open the through hole, and the hydraulic pressure generated by the centrifugal force is released from the control hydraulic chamber. It's designed to escape.

[0004]

However, in the structure using the above-mentioned conventional reed valve, the oil hole has to be formed radially inward of the outer peripheral end of the clutch piston, so that the radius of the oil hole is larger than that of the oil hole. The effect of centrifugal force acting on the oil remaining outside the direction could not be removed. The hydraulic clutch is provided with a clutch spring that opposes the hydraulic pressure due to the centrifugal force.However, the hydraulic pressure due to the centrifugal force depends on the rotational speed even though the elastic force of the clutch spring is set to a certain magnitude. Therefore, even if a hydraulic pressure is supplied to the hydraulic clutch so as to exert a desired engaging force, there is a problem that the engaging force changes according to the rotation speed.

The present invention has been made in view of the above circumstances, and eliminates the influence of the centrifugal force acting on the oil in the control hydraulic chamber of the hydraulic clutch, thereby enabling the engagement force of the hydraulic clutch to be precisely controlled. With the goal.

[0006]

In order to achieve the above object, a hydraulic clutch according to a first aspect of the present invention includes a first rotating member which is supported by a first rotating member so as to be relatively non-rotatable and axially movable.
In order to press the clutch plate, the second clutch plate supported by the second rotating member so as to be relatively non-rotatable and axially movable, and the first clutch plate and the second clutch plate to come into contact with each other, the first rotation A clutch piston supported by a member so as to be movable in the axial direction, and formed on one side surface of the clutch piston,
It is characterized by including a control hydraulic chamber for moving the clutch piston in one axial direction and an oil reservoir chamber formed on the other side surface of the clutch piston.

According to a second aspect of the present invention, in addition to the structure of the first aspect, the hydraulic clutch is such that the oil sump chamber is supplied with lubricating oil for lubricating the first clutch plate and the second clutch plate. It is characterized by being a pool room.

A hydraulic clutch according to a third aspect of the present invention includes a first clutch plate and a second clutch plate which are supported by the first rotating member so as to be relatively non-rotatable and axially movable, and a second clutch plate.
A third clutch plate supported by the rotating member so as to be relatively non-rotatable and axially movable, a fourth clutch plate supported by the third rotating member so as to be relatively non-rotatable and axially movable, a first clutch plate and a first clutch plate The first clutch piston, which is axially movably supported by the first rotating member, and the second clutch plate and the fourth clutch plate, are pressed against each other to press the three clutch plates against each other. A second clutch piston supported by the first rotating member so as to be movable in the axial direction,
A first control hydraulic chamber formed on one side surface of the first clutch piston for moving the first clutch piston in one axial direction, and one side surface of the second clutch piston for moving the second clutch piston in the other axial direction. It is characterized in that it is provided with a formed second control hydraulic chamber and a connecting means for connecting the first clutch piston and the second clutch piston such that they are relatively immovable in the axial direction.

A hydraulic clutch according to a fourth aspect of the present invention includes a first clutch plate and a second clutch plate which are supported by a first rotating member so as to be relatively non-rotatable and axially movable, and a second clutch plate.
A third clutch plate supported by the rotating member so as to be relatively non-rotatable and axially movable, a fourth clutch plate supported by the third rotating member so as to be relatively non-rotatable and axially movable, and a shaft for the first rotating member. Are movably supported in the axial direction, and are moved in one axial direction to press the first clutch plate and the third clutch plate so as to abut against each other, and are moved in the other axial direction to move the second clutch plate and the fourth clutch plate. A clutch piston that presses them into contact with each other, a first control hydraulic chamber formed on one side surface of the clutch piston to move the clutch piston in one axial direction, and a clutch piston that moves the clutch piston in the other axial direction. Second formed on the other side
And a control hydraulic chamber.

[0010]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT An embodiment in which the present invention is applied to a hydraulic clutch of an automatic transmission for an automobile will be described below with reference to the drawings.

FIG. 1 shows a first embodiment corresponding to the invention described in claims 1 and 2. The hydraulic clutch C is a clutch outer 2 as a first rotating member that is spline-coupled to a rotary shaft 1, and a second clutch that is rotatably supported by the rotary shaft 1 via a needle bearing 3.
And a clutch inner 4 as a rotating member. A plurality first clutch plate 5 ... of the inner peripheral engaging axially slidably spline 2 ₁ formed on the clutch outer 2, the outer periphery to form splines 4 ₁ axially sliding of the clutch inner 4 A plurality of second clutch plates 6 that are movably engaged are superposed so as to be able to abut each other. Internally by the first clutch plate 5 is clip 7 for engaging the spline 2 ₁ of the clutch outer 2 positioned at the right end are regulated axial movement, also the first clutch plate 5 located at the left end of the clutch outer 2 It comes into contact with a pressure plate 9 provided on a clutch piston 8 which is slidably fitted in the axial direction.

A partition member 1 is provided inside the clutch piston 8.
0 is fitted, and the inner peripheral end of the partition member 10 is locked by the clip 11 that engages with the boss portion of the clutch outer 2 to restrict the movement in the axial direction. A control hydraulic chamber 12 is defined between the left side surface of the clutch piston 8, that is, between the clutch piston 8 and the clutch outer 2, and the right side surface of the clutch piston 8, that is, between the clutch piston 8 and the partition member 10. A lubricating oil sump chamber 13 is defined. The control hydraulic chamber 12 and the lubricating oil sump chamber 13 are connected to the clutch piston 8
On both left and right sides of each other with a substantially equal projected area. A clutch spring 14 whose both ends are in contact with the clutch piston 8 and the partition wall member 10 is contracted in the lubricating oil sump chamber 13.

A hydraulic oil passage 1 formed in the rotating shaft 1 in the axial direction.
5 communicates with the control hydraulic chamber 12 via a hydraulic oil passage 16 extending in the radial direction. A lubricating oil passage 17 axially bored in the rotary shaft 1 communicates with the lubricating oil reservoir chamber 13 and the inner peripheral surface of the clutch inner 4 via a pair of radially extending lubricating oil passages 18 and 19. . A part of the lubricating oil that has flowed into the lubricating oil sump chamber 13 from the lubricating oil passage 18 is used as the first clutch plate 5
, And a plurality of notches 10 ₁ are formed on the inner circumference of the partition wall member 10 so as to be guided to the second clutch plate 6 and the oil holes 4 ₂ that penetrate the clutch inner 4 and the clutch outer 2 in the radial direction. 2 ₂ ... Is formed.

Reference numerals 20 and 21 denote the clutch outer 2
And a washer and thrust bearing arranged between the clutch inner 4 and the clutch inner 4.

Next, the operation of the first embodiment having the above construction will be described.

When the hydraulic pressure is not supplied to the control hydraulic chamber 12, the clutch piston 8 is biased leftward in the figure by the elastic force of the clutch spring 14, and the first clutch plate 5 ... 6 are separated from each other. Therefore, the torque input from the rotating shaft 1 to the clutch outer 2 is not transmitted to the clutch inner 4, and the hydraulic clutch C is disengaged. When hydraulic pressure is supplied from this state to the control hydraulic chamber 12 via the hydraulic oil passages 15 and 16, the clutch piston 8 and the pressure plate 9 move to the right in the drawing, and the first clutch plate 5 ... and the second clutch plate 6 Press to bring them into contact with each other. As a result, the torque input from the rotary shaft 1 to the clutch outer 2 is transferred to the first clutch plate 5 ...
And transmitted to the clutch inner 4 via the second clutch plates 6 ... And the hydraulic clutch C is brought into an engaged state.

A part of the lubricating oil supplied through the lubricating oil passages 17 and 18 is supplied to the lubricating oil sump chamber 13, and the remaining part passes through the notches 10 of the partition member 10 and moves to the outside in the radial direction. Then, the first clutch plates 5 and the second clutch plates 6 are lubricated. Further, the lubricating oil supplied through the lubricating oil passages 17 and 19 lubricates the needle bearing 3 and the thrust bearing 21.

A centrifugal force acts on the hydraulic oil in the control hydraulic chamber 12 defined between the clutch outer 2 and the clutch piston 8 which rotate integrally with the rotary shaft 1, and the hydraulic pressure generated by the centrifugal force is The clutch piston 8 is biased to the right (engagement direction). However, centrifugal force also acts on the lubricating oil in the lubricating oil sump chamber 13 defined between the clutch piston 8 and the partition member 10 that rotate integrally with the rotating shaft 1,
The hydraulic pressure generated by the centrifugal force urges the clutch piston 8 to the left (non-engagement direction). Therefore, the hydraulic pressure generated in the control hydraulic chamber 12 by the centrifugal force and the hydraulic pressure generated in the lubricating oil sump chamber 13 by the centrifugal force can be canceled, and the influence of the centrifugal force can be removed.

As a result, it is not necessary to increase the set load of the clutch spring 14 in order to counteract the hydraulic pressure generated in the control hydraulic chamber 12 due to the centrifugal force, which not only enables the clutch spring 14 to be small and lightweight. It is possible to reduce the maximum hydraulic pressure supplied to the control hydraulic chamber 12. Moreover, by removing the influence of the centrifugal force, the hydraulic clutch C is generated based on the hydraulic pressure supplied to the control hydraulic chamber 12 and the elastic force of the clutch spring 14.
It is possible to precisely control the magnitude of the engaging force of.

Next, a second embodiment corresponding to the invention described in claim 3 will be described with reference to FIG.

In the second embodiment, the left first hydraulic clutch C _L and the right second hydraulic clutch C _R are arranged back to back.
And the structures of the first hydraulic clutch C _L and the second hydraulic clutch C _R are substantially symmetrical. Hereinafter, the same reference numerals are used to designate members corresponding to the components of the hydraulic clutch C in the first embodiment described above, the subscript _"L" as its sign represents the component of the first hydraulic clutch C _L second A subscript " _R " representing a constituent member of the hydraulic clutch C _R is added.

[0022] rotary shaft 1 is spline-coupled and the clutch outer 2 _R of the clutch outer 2 _L and the second hydraulic clutch C _R of the first hydraulic clutch C _L back to back, the two clutch outer 2 _L, 2 _R is The first rotating member of the present invention is configured as substantially one member. A clutch inner 4 _L cooperating with a clutch outer 2 _L is supported on the rotary shaft 1 via a needle bearing 3 _{L so as} to be relatively rotatable, and
A clutch inner 4 _R cooperating with the clutch outer 2 _R is supported rotatably via a needle bearing 3 _R. The clutch inner 4 _L constitutes the second rotating member of the present invention, and the clutch inner 4 _R constitutes the third rotating member of the present invention.

A plurality of first clutch plates 5 _L are supported by the splines 2 _L1 of the clutch outer 2 _{L so} as to be slidable in the axial direction, and the clutch inners are superposed on the first clutch plates 5 _L. A plurality of third clutch plates 6 _L ... Are supported by the 4 _L spline 4 _L1 so as to be slidable in the axial direction.
Similarly, a plurality of second clutch plates 5 _R ... Is axially slidably supported by the spline 2 _R1 of the clutch outer 2 _R , and the clutch inners are arranged so as to be superposed on the second clutch plates 5 _R. A plurality of fourth clutch plates 6 _R ... Are supported by the 4 _R spline 4 _R1 so as to be slidable in the axial direction.

Clutch outer 2_LNo. 1 control oil inside
Pressure chamber 12_LIt moves to the left by the hydraulic pressure supplied to
First clutch plate 5_L... and the third clutch plate 6_LTo each other
Clutch piston 8 to contact_LIs slidable in the axial direction
It is installed and the clutch outer 2_RSecond inside
Control hydraulic chamber 12_RIs moved to the right by the hydraulic pressure supplied to
The second clutch plate 5_R... and the fourth clutch plate 6_RTo
Clutch piston 8 to abut each other_RIs the axial sliding
Is located there. Both clutch piston 8_L, 8 _RKura
Touch outer 2_L, 2_ROn clip 31_L, 31_RFixed by
Spring seat 32 _L, 32_RClutch spring locked on
Gu 14_L, 14_RSo as to get closer to each other
It is biased to the right and left.

The left and right clutch pistons 8 _L , 8 _R are collars 33 fitted to the left and right clutch outers 2 _L , 2 _R.
Through a clip 34, which is fixed by a clip 34.

A pair of actuations axially bored on the rotary shaft 1.
Oil passage 15_L, 15_RActuates each extending radially
Oil passage 16_L, 16_RThrough the first and second control hydraulic chambers
12 _L, 12_RCommunicate with. In addition, the rotary shaft 1 is drilled in the axial direction.
The lubricating oil passage 17 is provided with a pair of lubricating oils extending in the radial direction.
Oil passage 18_L, 18_RClutch outer 2 through_L, 2 _R
And clutch inner 4_L, 4_RCommunicate with the space between
Pair of lubricating oil passage 19_L, 19_RClutch inner 4 through
_L, 4_RCommunicate with the inner circumference of.

Next, the operation of the second embodiment having the above construction will be described.

[0028] When hydraulic pressure is applied to the first hydraulic clutch C _L and to engage the hydraulic oil passage 15 _L, 16 via the _L first control hydraulic chamber 12 _L, the clutch piston 8 _L moves in the left direction in the drawing , The first clutch plate 5 _L, and the third clutch plate 6
_{Press L} ... to bring them into contact with each other. As a result, the torque input from the rotary shaft 1 to the clutch outer 2 _L is transmitted to the clutch inner 4 _L , and the first hydraulic clutch C _L is in the engaged state. Further, when hydraulic pressure is applied to the second control hydraulic chamber 12 _R via the hydraulic fluid passage 15 _R, 16 _R, the second hydraulic clutch C ₂ is engaged in the same manner as described above. As described above, when the clutch piston 8 _L of the first hydraulic clutch C _L moves to the left, the second hydraulic clutch C is moved through the connecting pins 35.
Clutch piston 8 _R of _R is also moved to the left together, also when the clutch piston 8 _R of the second hydraulic clutch C _R is shifted rightward,
The clutch piston 8 _{L of} the first hydraulic clutch C _L also moves rightward integrally via the connecting pin 35, but the first and second hydraulic clutches C _L and C _R are simultaneously engaged in the automatic transmission. There is no problem, so there is no problem.

Now, the first hydraulic clutch C_LNo. 1 control oil
Pressure chamber 12_LGenerated by the centrifugal force acting on the hydraulic oil inside
Hydraulic pressure is clutch piston 8_LTo the left,
2 hydraulic clutch C_RSecond control hydraulic chamber 12_RHydraulic oil inside
The hydraulic pressure generated by the centrifugal force acting on the clutch fix
8_RUrging the clutch to the right,
8 _L, 8_RAre integrated by connecting pins 35 ...
Therefore, the oil pressures due to the centrifugal force cancel each other out and
1st, 2nd hydraulic clutch C_L, C_RAffect the engagement force of
Is prevented.

Thus, the second embodiment can also obtain the same effect as the first embodiment, and the partition for defining the lubricating oil sump chamber 13 of the first embodiment. The member 10 is not necessary and the structure is simplified.

Next, a third embodiment corresponding to the invention described in claim 4 will be described with reference to FIG.

The third embodiment is asymmetrically arranged on the left side of the first embodiment.
1 hydraulic clutch C_LAnd the second hydraulic clutch C on the right side_RTo
And the first hydraulic clutch of the second embodiment described above.
Chi C _LAnd the second hydraulic clutch C_RCorresponding to the components of
The same reference numerals are given to the constituent members.

A rotary shaft 41 is coaxially supported at the right end of the rotary shaft 1 via a needle bearing 42, and a clutch inner 2 _{L serving} as a second rotary member is provided at the left end of the rotary shaft 41.
Is splined, and a clutch inner 4 _R as a third rotating member is supported adjacent to the right side of the clutch inner 4 _{L so} as to be rotatable relative to the rotating shaft 41 via a needle bearing 43.

A flange is integrally formed on the right end of the rotary shaft 1.
The outer end of the control hydraulic chamber partition wall 44 in the radial direction is axially
The extending clutch outer 2 is integrally formed. Crutchia
Uta 2 Spline 2₁A plurality of first clutch plates 5
_L... are supported slidably in the axial direction, and these first clutches
Board 5_LClutch inner 4 so that _L
Spline 4_L1A plurality of third clutch plates 6_L… Is the axis
It is supported so that it can slide in any direction. Similarly, the clutch outer 2
Spline 2₁A plurality of second clutch plates 5_R…But
These second clutch plates 5 are supported so as to be slidable in the axial direction._R
Clutch inner 4 so that_RThe sp
Line 4_R1A plurality of fourth clutch plates 6 _R… Axial sliding
It is movably supported. In the third embodiment, the rotary shaft
1 and the clutch outer 2 constitute a first rotating member.

The first clutch plate 5 _L located at the left end opposes the control hydraulic chamber partition wall 44 on the right side, and the second clutch plate 5 _R located at the right end is a clip 7 locked at the right end of the clutch outer 2. Facing the left side of. Clutch outer 2
A pressure plate 9 is slidably supported inside the third clutch plate 6 whose left side surface is located at the right end.
_While facing the right side surface of _L, the right side surface faces the left side surface of the fourth clutch plate 6 _R located at the left end.

A control hydraulic chamber partition wall 45 is splined to the rotary shaft 1, and a first piston is provided between the clutch piston 8 slidably supported on the rotary shaft 1 and both control hydraulic chamber partition walls 44 and 45. Control hydraulic chamber 12 _L and second control hydraulic chamber 12 _R
Is defined. Clutch piston 8 and control hydraulic chamber partition wall 4
5, the clutch spring 14 _L is contracted, and the clutch spring 14 _R is contracted between the clutch piston 8 and the control hydraulic chamber partition wall 44.

A plurality of projections 8 ₁ formed at the outer end of the clutch piston 8 in the radial direction has a clip 47 at the left end of a tubular connecting member 46 arranged so as to be fitted to the outer periphery of the clutch outer 2. Fixed. Further, the projections 9 ₁ of the pressure plate 9 protruding outward in the radial direction from the plurality of notches 2 ₃ formed in the clutch outer 2 are the connecting members 46.
The clip 48 is fixed to the right end of the.

A pair of actuations axially bored on the rotary shaft 1.
Oil passage 15_L, 15_RActuates each extending radially
Oil passage 16_L, 16_RThrough the first and second control hydraulic chambers
12 _L, 12_RCommunicate with. Further, the rotary shaft 41 was drilled.
Lubricating oil passages 17, 18_LThe lubricating oil supplied via
Needle bearing 42, rotating shaft 1 and clutch inner
Four_LNeedle bearing 49 and control disposed between and
Hydraulic chamber partition wall 44 and clutch inner 4_LPlaced between
The thrust bearing 50 is lubricated, and a lubricating oil passage is provided.
17,18_RThe lubricating oil supplied via
Bearing 43 and clutch inner 4_LAnd clutchie
Anna 4_RLubricate the thrust bearing 51 placed between
It

Next, the operation of the third embodiment having the above construction will be described.

When hydraulic pressure is supplied to the first control hydraulic chamber 12 _L via the hydraulic oil passages 15 _L and 16 _L to engage the first hydraulic clutch C _L , the clutch piston 8 causes the clutch piston 8 to move.
And the pressure plate 9 move to the left in the figure,
The pressure plate 9 includes the first clutch plate _5L ... and the third clutch plate.
The clutch plates 6 _L are pressed to bring them into contact with each other. As a result, the torque input from the rotary shaft 1 to the clutch outer 2 via the control hydraulic chamber partition wall 44 is transmitted to the clutch inner 4 _L , and the first hydraulic clutch C _L is brought into the engaged state. In addition, the second control hydraulic chamber 1 is operated via the hydraulic oil passages 15 _R and 16 _R.
When the hydraulic pressure is supplied to 2 _R , the second hydraulic clutch C ₂ is brought into the engaged state in the same manner as described above. In the automatic transmission, since the first and second hydraulic clutches C _L and C _R are not engaged at the same time, even if both hydraulic clutches C _L and C _R share the clutch piston 8 and the pressure plate 9. , No trouble occurs.

Therefore, according to the third embodiment, the hydraulic pressure generated by the centrifugal force acting on the hydraulic oil in the first control hydraulic chamber 12 _{L of} the first hydraulic clutch C _{L and} the second hydraulic clutch C _L. it is possible to cancel the hydraulic pressure generated by a centrifugal force acting on the hydraulic fluid in the second control hydraulic chamber 12 _R in _R mutually, yet the first and second hydraulic clutch C _L, the clutch piston 8 C _R The number of parts can be reduced by sharing.

Although the embodiments of the present invention have been described in detail above, the present invention is not limited to the above embodiments, and various design changes can be made.

For example, although the hydraulic clutch for an automatic transmission of an automobile is illustrated in the embodiment, the present invention can be applied to any other hydraulic clutch. Further, in the second embodiment, the left and right clutch outers 2 _L and 2 _R are formed by separate members, but they may be formed by one member.

[0044]

As described above, according to the invention described in claim 1, the control hydraulic chamber and the oil sump chamber are formed on one side surface and the other side surface of the clutch piston, respectively.
The hydraulic pressures generated by the centrifugal force acting on the oil in the two chambers are mutually offset, the movement of the clutch piston due to the centrifugal force can be prevented, and the engagement force of the hydraulic clutch can be precisely controlled.

According to the invention described in claim 2,
Since the oil sump chamber is formed by utilizing the lubricating oil sump chamber to which the lubricating oil for lubricating the first clutch plate and the second clutch plate is supplied, it is not necessary to form a special oil sump chamber, and the number of parts is reduced. Can contribute to the reduction of

According to the invention described in claim 3,
A first control hydraulic chamber and a second control hydraulic chamber are formed on one side surface of the first clutch piston and one side surface of the second clutch piston, respectively.
By connecting the clutch pistons so that the clutch pistons cannot move relative to each other in the axial direction, the hydraulic pressures generated by the centrifugal forces acting on the oil in both control hydraulic chambers cancel each other out, and the clutch pistons are prevented from moving due to the centrifugal force. The engaging force of the clutch can be precisely controlled.

According to the invention described in claim 4,
By forming the first control hydraulic chamber and the second control hydraulic chamber on both side surfaces of the clutch piston, the hydraulic pressures generated by the centrifugal force acting on the oil in both control hydraulic chambers cancel each other out, and the clutch piston by the centrifugal force is cancelled. It is possible to precisely control the engagement force of the hydraulic clutch by preventing the movement of the.

[Brief description of drawings]

FIG. 1 is a sectional view of a hydraulic clutch according to a first embodiment.

FIG. 2 is a sectional view of a hydraulic clutch according to a second embodiment.

FIG. 3 is a sectional view of a hydraulic clutch according to a third embodiment.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 rotating shaft (1st rotating member) 2 clutch outer (1st rotating member) 2 _L clutch outer (1st rotating member) 2 _R clutch outer (1st rotating member) 4 clutch inner (2nd rotating member) 4 _L 2 Rotating member 4 _R 3rd rotating member 5 1st clutch plate 5 _L 1st clutch plate 5 _R 2nd clutch plate 6 2nd clutch plate 6 _L 3rd clutch plate 6 _R 4th clutch plate 8 Clutch piston 8 _L 1st Clutch piston 8 _R Second clutch piston 12 Control oil pressure chamber 12 _L First control oil pressure chamber 12 _R Second control oil pressure chamber 13 Lubricating oil sump chamber (oil sump chamber) 35 Connection pin (connection means)

Claims (4)

[Claims] 1. A first clutch plate (5) supported by a first rotating member (2) so as not to be relatively rotatable and axially movable,
A second clutch plate (6) supported by the second rotating member (4) so as not to be relatively rotatable and axially movable, and the first clutch plate (5) and the second clutch plate (6) are pressed against each other. A clutch piston (8) that is axially movably supported by the first rotating member (2) so as to abut, and is formed on one side surface of the clutch piston (8) so that the clutch piston (8) moves in one axial direction. The control oil pressure chamber (12) to be moved and the oil sump chamber (1) formed on the other side surface of the clutch piston (8).
3) A hydraulic clutch comprising: 2. The oil sump chamber (13) is a lubricating oil sump chamber to which lubricating oil for lubricating the first clutch plate (5) and the second clutch plate (6) is supplied. The hydraulic clutch according to claim 1. 3. A first rotating member (2)_L, 2_R) Relative rotation
First clutch plate supported so as to be immovable and axially movable
(5_L) And the second clutch plate (5_R) And the second rotating member
(4_L) Is supported so that it cannot rotate relative to it and can move in the axial direction.
3rd clutch plate (6_L) And a third rotating member (4_R) To
The fourth clutch supported so that it cannot rotate relative to it but can move in the axial direction.
Touch plate (6_R) And the first clutch plate (5_L) And third
Latch plate (6_L) So that they come into contact with each other.
1 rotating member (2_L, 2_R) Is supported so that it can move in the axial direction.
1st clutch piston (8_L) And the second clutch plate
(5 _R) And the fourth clutch plate (6_R) Press each other
The first rotating member (2_L, 2_R) To the axial direction
A second clutch piston (8_R)
And the first clutch piston (8_L) Is moved in one axial direction
The first clutch piston (8_L) Shaped on one side
The first control hydraulic chamber (12_L) And the second clutch pin
Stone (8_R) To move in the other axial direction
Touch piston (8 _R) A second control oil formed on one side surface
Pressure chamber (12_R) And the first clutch piston (8_L)as well as
Second clutch piston (8_R) To make the axial relative movement impossible
And a connecting means (35) for connecting.
Hydraulic clutch. 4. A first clutch plate (5 _L ) and a second clutch plate (5 _R ) which are supported by a first rotating member (2) such that they cannot rotate relative to each other and are movable in the axial direction, and a second rotating member (4). _L ), a third clutch plate (6 _L ) which is supported in a non-rotatable and axially movable manner, and a fourth clutch plate which is supported by a third rotating member (4 _R ) in a non-rotatable manner and axially movable. (6
_R ) and the first rotating member (1) are movably supported in the axial direction and move in one axial direction to press the first clutch plate (5 _L ) and the third clutch plate (6 _L ) to each other. The clutch piston (8) and the clutch piston (8) that are brought into contact with each other and are moved in the other axial direction to press the second clutch plate (5 _R ) and the fourth clutch plate (6 _R ) so as to contact each other. A first control hydraulic chamber (12 _L ) formed on one side surface of the clutch piston (8) to move in one axial direction, and a clutch control piston (8) other than the first control hydraulic chamber (12 _L ) to move the clutch piston (8) in the other axial direction. A hydraulic clutch comprising a second control hydraulic chamber (12 _R ) formed on a side surface.