JP2001132781A - Rotary clutch - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent increase in the size of a rotary clutch, and simultaneously to perform sure cacellation of a centrifugal oil pressure with the increase in transmission torque. SOLUTION: This rotary clutch comprises a piston 91, to partition a piston press chamber 80 and a centrifugal oil pressure cancel chamber 81 from each other, and a press member 92 to slidably extend through the inner periphery of a centrifugal oil pressure cancel piston 95 and be brought at one end into contact with the piston 91 fronting on the centrifugal oil pressure cancel piston 95 and at the other end side into contact with and separation from a clutch plate 93. The outside diameter of the centrifugal oil pressure cancel piston 95 is set to a value equal to the outside diameter of the piston 91, and the inside diameter of the piston 91 is set to a value equal to the inside diameter of the press member 92.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an improvement in a rotary clutch used for an automatic transmission of a vehicle.

[0002]

2. Description of the Related Art Conventionally, in an automatic transmission for a vehicle or the like, the rotation direction of each rotary element and the power transmission path are switched by engaging or releasing a friction member of a hydraulic clutch or a hydraulic brake.

In such a hydraulic clutch, a rotary clutch which engages or disengages according to the oil pressure while rotating the clutch itself is widely used.

In this rotary clutch, a hydraulic pressure due to centrifugal force (hereinafter, referred to as centrifugal hydraulic pressure) acts on the piston pressing chamber in addition to the supplied hydraulic pressure, so that the friction member is not quickly released. In some cases, the clutch may be dragged, and a method for canceling the centrifugal oil pressure is known, for example, from Japanese Patent Application Laid-Open No. Hei 5-202053.

As shown in FIG. 7, the piston pressing chamber 180 for driving the piston 191 to the side of engagement between the clutch plate 193 and the clutch disk 197, which are friction members, in accordance with the increase of the supplied oil pressure, It is defined between the circumference and the piston 191. On the other hand, a centrifugal oil pressure canceling chamber 181 that drives the piston 191 to the friction member releasing side in response to an increase in centrifugal oil pressure is provided with a pressing force that extends axially from the outer periphery of the piston 191 and supports the clutch plate 193 at the end. A centrifugal oil pressure cancel piston 195 and a piston 191 are in sliding contact with the inner periphery of the portion 192. The axial displacement of the centrifugal hydraulic pressure canceling piston 195 is restricted on the inner periphery on the axial side, while the outer periphery is in sliding contact with the inner periphery of the pressing portion 192 of the piston 191.

A piston pressing chamber 180 and a centrifugal hydraulic pressure canceling chamber 181 are defined on both sides of the piston 191. In addition, the outer diameter of the piston pressure receiving surface desired for the centrifugal hydraulic pressure canceling chamber 181 and the piston pressing chamber 180 desired. By equalizing the outer diameter of the piston pressure receiving surface, the centrifugal hydraulic pressure is canceled without excess or deficiency.

[0007]

However, in the conventional rotary clutch, the clutch plate 19 is attached to the end of the pressing portion 192 extending from the outer periphery of the piston 191.
In addition, the centrifugal hydraulic pressure canceling piston 195 is provided on the inner periphery of the pressing portion 192, so that the pressure receiving area of the piston 191 is increased to increase the transmission torque, and the centrifugal hydraulic pressure is canceled to accurately cancel the centrifugal hydraulic pressure. To match or approximate the outer diameter of the cancel piston 195 to the outer diameter of the piston 191,
And the outer diameter of the centrifugal hydraulic cancel piston 195 increases, the outer diameter of the clutch drum 190 also increases, the transmission becomes larger, and the mountability on a vehicle or the like decreases. Was.

SUMMARY OF THE INVENTION The present invention has been made in view of the above problems, and has as its object to prevent the size of the rotary clutch from increasing, to increase the transmission torque, and to surely cancel the centrifugal hydraulic pressure. .

[0009]

According to a first aspect of the present invention, there is provided a piston which is housed in a rotatable clutch drum and is displaceable in a rotation axis direction, and a piston defined between the piston and the clutch drum. A pressing chamber, a centrifugal hydraulic cancel piston disposed on the opposite side of the piston pressing chamber across the piston, a centrifugal hydraulic cancel chamber defined between the piston and the centrifugal hydraulic cancel piston,
A rotary clutch that is pressed by the piston and includes a friction member that interrupts a power transmission path, and performs engagement and release according to the hydraulic pressure supplied to the piston pressing chamber while canceling the centrifugal hydraulic pressure on both sides of the piston. The piston receives a pressure receiving member defining a piston pressing chamber and a centrifugal hydraulic canceling chamber, and penetrates the inner periphery of the centrifugal hydraulic canceling piston and abuts on one end with a pressure receiving member facing the centrifugal hydraulic canceling piston. On the other hand, at the other end side, the friction member and the pressing member which can be separated and contacted are constituted.

According to a second aspect of the present invention, in the first aspect, a seal member is interposed between the clutch drum and the centrifugal hydraulic cancel piston and between the centrifugal hydraulic cancel piston and the pressing member. Is done.

In a third aspect based on the second aspect, the clutch drum is disposed on an outer periphery of a rotating shaft, and the piston pressing chamber and the centrifugal hydraulic pressure are passed through an oil passage provided inside the rotating shaft. A hydraulic pressure is supplied to each of the cancel chambers, and a seal member is provided between the pressing member and the rotating shaft.

According to a fourth aspect of the present invention, a piston housed in a rotatable clutch drum and displaceable in the direction of a rotation axis, a piston pressing chamber defined between the piston and the clutch drum are provided. A centrifugal hydraulic cancel piston disposed on the opposite side of the piston pressing chamber with the piston interposed therebetween, a centrifugal hydraulic cancel chamber defined between the piston and the centrifugal hydraulic cancel piston, and pressed by the piston, A friction member that interrupts the power transmission path, and cancels the centrifugal oil pressure on both sides of the piston while engaging and releasing the piston in accordance with the oil pressure supplied to the piston pressing chamber. A pressure receiving member defining a chamber and a centrifugal hydraulic cancellation chamber;
A pressure member which can be brought into contact with and separated from the friction member; and a cylindrical portion projecting from the pressure receiving member and penetrating through the inner periphery of the centrifugal hydraulic cancel piston, and being able to contact the pressure member.

According to a fifth aspect, in the fourth aspect, between the clutch drum and the centrifugal hydraulic cancel piston and between the centrifugal hydraulic cancel piston and a cylindrical portion protruding from the pressure receiving member, Each is provided with a seal member.

In a sixth aspect based on the fifth aspect, the clutch drum is disposed on an outer periphery of a rotating shaft, and the piston pressing chamber and the centrifugal hydraulic pressure are passed through an oil passage provided inside the rotating shaft. A hydraulic pressure is supplied to each of the cancel chambers, and a seal member is provided between the cylindrical portion and the rotating shaft.

[0015]

According to the first aspect of the present invention, when the piston is displaced in the axial direction in accordance with the increase or decrease of the oil pressure in the piston pressing chamber, the pressing member penetrating the inner periphery of the centrifugal hydraulic canceling piston is also driven in the axial direction, and the friction member is moved. Can be concluded and released,
At this time, if the clutch drum is rotating, centrifugal hydraulic pressure is generated in the piston pressing chamber, but this can be offset by the centrifugal hydraulic pressure acting in the centrifugal hydraulic pressure canceling chamber.

The piston presses the friction member via a separately formed pressing member, and the pressing member penetrates the inner peripheral side of the centrifugal hydraulic cancel piston. It can be displaced integrally, and the outer diameters of the piston and the centrifugal hydraulic cancel piston can be effectively used within the range allowed by the inner diameter of the clutch drum. Without increasing, the capacity of the transmission torque can be easily increased while increasing the pressure receiving area of the piston and canceling the centrifugal hydraulic pressure to reliably prevent the dragging of the clutch.

Further, the second invention secures the sealing property of the cancel hydraulic pressure at the inner peripheral position of the clutch drum where the centrifugal hydraulic pressure is maximum, that is, the outer peripheral position of the centrifugal hydraulic cancel piston, and displaces in the axial direction. The pressing member is
Since the sliding contact is made via a seal provided on the inner periphery of the centrifugal hydraulic cancel piston, the outer diameter of the seal between the centrifugal hydraulic cancel piston and the sliding member can be reduced, and the sliding area can be reduced. The dynamic resistance can be reduced, and the sliding resistance generated in the centrifugal hydraulic cancel piston is reduced as compared with the case where the piston slides on the outer periphery of the centrifugal hydraulic cancel piston as in the conventional example,
The transmission torque of the rotary clutch is increased by reducing the size of the return spring and the like, and at the same time, the hysteresis loss of the seal can be reduced by reducing the diameter of the seal, and the control accuracy of the clutch engagement force can be improved.

Further, in the third invention, when hydraulic pressure is supplied to the piston pressing chamber from the shaft center side of the rotary shaft, leakage of hydraulic oil from the rotary shaft and the pressing member is prevented, and the amount of offset of the centrifugal hydraulic pressure is reduced. Can be secured.

In a fourth aspect of the present invention, when the piston is displaced in the axial direction in response to an increase or decrease in the oil pressure in the piston pressing chamber, the pressing member is also moved in the axial direction via a cylindrical portion penetrating the inner periphery of the centrifugal hydraulic cancel piston. When the clutch drum is rotated, centrifugal oil pressure is generated in the piston pressing chamber and the centrifugal oil pressure canceling chamber, and is acted on both oil chambers. Centrifugal oil pressure can be offset.

The piston presses the friction member via a pressing member formed separately, and the cylindrical portion protruding from the pressure receiving member penetrates the inner peripheral side of the centrifugal hydraulic cancel piston. The piston and the pressing member can be integrally displaced, and the outer diameters of the piston and the centrifugal hydraulic cancel piston can be effectively used within the range of the inner diameter of the clutch drum. Without increasing the outer diameter of the drum, the pressure receiving area of the piston can be increased, and the centrifugal hydraulic pressure can be canceled to reliably prevent the clutch from being dragged, but the transmission torque capacity can be easily increased.

According to a fifth aspect of the present invention, the cylindrical portion which displaces in the axial direction while ensuring the sealing property of the cancel hydraulic pressure at the inner circumferential position of the clutch drum where the centrifugal hydraulic pressure is maximized,
Since the sliding contact is made via a seal provided on the inner circumference of the centrifugal hydraulic cancel piston, the outer diameter of the seal between the centrifugal hydraulic cancel piston and the sliding cylindrical portion can be reduced, and the sliding area can be reduced. The sliding resistance can be reduced, and the sliding resistance generated in the centrifugal hydraulic cancel piston is reduced by an amount corresponding to the decrease in the sliding resistance compared to the case where the piston is slid on the outer periphery of the centrifugal hydraulic cancel piston as in the conventional example.
The transmission torque of the rotary clutch is increased by reducing the size of the return spring and the like, and at the same time, the hysteresis loss of the seal can be reduced by reducing the diameter of the seal, and the control accuracy of the clutch engagement force can be improved.

According to a sixth aspect of the present invention, when hydraulic pressure is supplied to the piston pressing chamber from the axial center of the rotary shaft, leakage of hydraulic oil from the rotary shaft and the pressing member is prevented, and the centrifugal hydraulic pressure is offset. Can be secured.

[0023]

An embodiment of the present invention will be described below with reference to the accompanying drawings.

FIGS. 1 to 4 show an example in which a rotary clutch to which the present invention is applied is applied to a rotary clutch.

As shown in FIGS. 1 and 2, a rotary clutch is provided on a unit input shaft 1a, 1b which is directly connected to a crankshaft (not shown) of an engine. The machine 2 is connected in parallel with a constant transmission 3 (reduction gear) composed of gears 3a and 3b, and these output shafts 4 and 3c are arranged coaxially on a unit output shaft 6 and a planetary gear. The output shaft 4 of the continuously variable transmission 2 is connected to a sun gear 5a of the planetary gear mechanism 5, and the output shaft 3c of the fixed transmission 3 is connected via a power circulation mode clutch 9 as a rotary clutch. It is connected to the carrier 5b of the planetary gear mechanism 5.

The continuously variable transmission output shaft 4 connected to the sun gear 5a receives the driving force of the continuously variable transmission 2 from the sprocket 4a and the chain 40, and receives a unit output, which is the output shaft of the rotary clutch via the direct connection mode clutch 10. While being connected to the shaft 6, the ring gear 5c is also connected to the unit output shaft 6.

A transmission output gear 7 is provided on the right side of the unit output shaft 6 in the figure, and the transmission output gear 7 meshes with the final gear 12 of the differential gear 8 and is connected to the drive shaft 11 a connected to the differential gear 8. , 11b
The driving force is transmitted at a predetermined total reduction ratio.

As shown in FIG. 1, the continuously variable transmission 2 is a double-cavity half-toroidal type that sandwiches and presses the power rollers 20, 20 with two sets of input disks 21 and output disks 22, respectively. The output sprocket 2a interposed between the pair of output discs 22 is formed on the continuously variable transmission output shaft 4 of the unit output shaft 6 arranged in parallel with the unit input shafts 1a and 1b via the chain 40. Connects to sprocket 4a.

As shown in FIG. 2, the unit input shafts 1a and 1b are arranged coaxially and connected in the rotational direction via a loading cam device 23 of the continuously variable transmission 2. , The unit input shaft 1a is a flywheel,
The unit input shaft 1b is connected to a crankshaft of the engine via a damper, and forms a gear 3a of the constant transmission 3. The unit input shaft 1b is connected to two sets of input disks 21 and 21 to receive an input from the unit input shaft 1a. The power rollers 20, 20 shown in FIG. 1 are nipped and pressed between the input and output disks by the axial pressing force generated by the loading cam device 23 according to the torque.

In this rotary clutch, while the power circulation mode clutch 9 is released, the direct connection mode clutch 10 is engaged and the driving force is transmitted according to the speed ratio of the continuously variable transmission 2; 9 while the direct coupling mode clutch 10 is disengaged, the unit speed ratio of the entire rotary clutch (the unit input shaft 1a and the unit output A power circulation mode in which the gear ratio of the shaft 6 is controlled almost continuously from a negative value to a positive value, including infinity, can be selectively used.

The unit input shafts 1a and 1b, the unit output shaft 6 and the drive shafts 11a and 11b are arranged in parallel on the inner periphery of the casing 14, and as shown in FIGS. The output gear 7 and the final gear 12 and the gear 3a and the gear 3b of the fixed transmission 3 are arranged so as to be shifted in the axial direction, and the outer periphery of the large-diameter gear 3b is close to the differential gear 8.

Next, the gear 3b of the constant transmission 3 is formed in an annular shape, and the inner periphery of the gear 3b is formed to have an inner diameter through which the unit output shaft 6 and the transmission output gear 7 can be inserted. 3b is a flange portion 3 of the output shaft 3c via a bolt.
d.

As shown in FIG. 2, the unit output shaft 6 has an oil retainer 17, a direct-coupled mode clutch 10, a sprocket 4a, a continuously variable transmission output shaft 4, and a planetary gear mechanism 5 in that order from the left end in the figure. , A power circulation mode clutch 9, a constant transmission output shaft 3c and a gear 3b, and a transmission output gear 7 are sequentially arranged.

2 and 3, two oil passages are formed inside the unit output shaft 6 via a cylindrical centrifugal hydraulic cancel piston 64. , Power circulation mode clutch 9
An oil passage 61 for supplying a hydraulic pressure for canceling the centrifugal hydraulic pressure of the centrifugal hydraulic pressure is defined.
An oil passage 60 for supplying a hydraulic pressure for driving the power circulation mode clutch 9 is defined on the inner periphery of the oil passage 4.
61 receives supply of hydraulic pressure from the casing 14 side via an oil passage in an oil retainer 17 provided on the left side of the unit output shaft 6 in the drawing.

Next, the details of the power circulation mode clutch 9 composed of a rotary clutch will be described with reference to FIG.

In FIG. 3, the gear 3b of the constant transmission 3
The power transmission mode clutch 9 is connected to the unit output shaft 6 via a constant transmission output shaft 3c coaxially and rotatably disposed on the unit output shaft 6.
c is a flange portion 3d on the transmission output gear 7 side on the right side in the figure.
And a gear 3b is fastened to the end face of the flange portion 3d, while a cylindrical portion 3e constituting the inner periphery of the power circulation mode clutch 9 is formed on the other end side.

The constant transmission output shaft 3c has a flange 3d
Are rotatably supported by a bearing 18 interposed between the inner circumference of the unit and the outer circumference of the unit output shaft 6, and a needle bearing 19 interposed between the cylindrical portion 3e and the outer circumference of the unit output shaft 6.

The clutch drum 90 of the power circulation mode clutch 9 is formed of a cylindrical member having an inverted L-shaped cross section. The base end having a small inner diameter is connected to the flange 3d. The inner 96 connected to the carrier 5b of the planetary gear mechanism 5 is inserted.

A clutch disk 94 provided on the outer circumference of the inner 96 and a clutch plate 93 provided on the inner circumference of the clutch drum 90 are in sliding contact with the outer circumference of the cylindrical portion 3e of the fixed transmission output shaft 3c and are displaced in the axial direction. Pressing member 9
The engagement and release of the power circulation mode clutch 9 are performed by the contact and separation of the pressing surface 92a on the outer periphery of the second.

Here, the pressing member 92 has a cylindrical portion 3 on the inner periphery.
e, while the outer peripheral end surface 92a which can be in contact with and separated from the clutch plate 93 (or the clutch disk 94) forms a predetermined gap with the inner periphery of the clutch drum 90.

The pressing member 92 has a cylindrical portion 9 slidably in contact with the outer periphery of the cylindrical portion 3e of the fixed transmission output shaft 3c via a seal 74.
2b, a wall portion 92e rising in the radial direction from the left side of the cylindrical portion 92b toward the outer periphery in the figure, and a clutch plate after temporarily going from the outer periphery of the wall portion 92e to the flange portion 3d side of the constant transmission output shaft 3c. Almost "reverse J" toward 93 side
The pressing surface 92a is formed by bending the pressing plate 92 with a U-shaped cross section.
3.

The cylindrical portion 92b on the inner periphery of the pressing member 92 extends toward the flange portion 3d of the fixed transmission output shaft 3c, and the end portion 92d of the cylindrical portion 92b on the flange portion 3d side is formed inside the flange portion 3d. A piston pressing chamber 80 is defined between the circumference and the inner circumference of the bottom of the clutch drum 90, and is in contact with the inner circumference side (axial side) of the annular piston 91 that can be displaced in the axial direction.

The outer periphery of the piston 91 is in sliding contact with the inner periphery of the clutch drum 90 via the seal 70, and the inner periphery is in sliding contact with the outer periphery of the cylindrical portion 3e of the constant transmission output shaft 3c via the seal 71.

When the oil pressure in the piston pressing chamber 80 increases, the piston 91 is displaced to the left in FIG. 3 and becomes integral with the pressing member 92 via an end 92d abutting on the inner periphery of the piston 91. To the left in the drawing, and the pressing surface 92a presses the clutch plate 93 to fasten to the clutch disk 94.

On the other hand, a return spring 97 abuts against the wall portion 92e of the pressing member 92, and constantly urges the pressing member 92 rightward in the drawing to press the piston 91 via the end portion 92d of the cylindrical portion 92b. I do.

When the oil pressure in the piston pressing chamber 80 decreases,
By the urging force of the return spring 97, the pressing member 92 presses the piston 91 to the right in FIG. 3, and the pressing member 92 and the piston 91 are united to form the piston pressing chamber 8
The clutch is displaced in the contraction direction of 0 to release the clutch.

The return spring 97 is disposed in balance with the axis 6c of the unit output shaft 6.
The base end of the return spring 97 is locked to the cylindrical portion 3e of the fixed transmission output shaft 3c via a locking member 98.

Next, between the piston 91 and the pressing member 92, a centrifugal hydraulic pressure canceling piston 95, which is in sliding contact with the cylindrical portion 92 b of the pressing member 92 on the inner periphery, and abuts the outer periphery on the inner periphery of the clutch drum 90. A centrifugal hydraulic cancellation chamber 81 is defined between the piston 91 and the centrifugal hydraulic cancellation piston 95. The cylindrical portion 92b of the pressing member 92 facing the centrifugal hydraulic pressure canceling chamber 81 has an end 9
On the 2d side, the inner periphery of the centrifugal hydraulic cancellation chamber 81 and the cylindrical portion 92
An opening 92c is formed in the radial direction to communicate the inner circumference of the b and suck and discharge the hydraulic pressure.

The centrifugal hydraulic cancel piston 95 contacts the inner periphery of the clutch drum 90 via the seal 72 on the outer peripheral side, and presses the pressing member 9 via the seal 73 on the inner peripheral side.
It comes into sliding contact with the inner periphery of the second cylindrical portion 92b.

The outer periphery of the centrifugal hydraulic cancel piston 95 is located on the clutch drum 90 on the clutch plate 93 side.
The axial displacement is regulated by a snap ring 75 disposed on the inner periphery, and the centrifugal hydraulic cancel piston 95
Of the piston 91 facing the centrifugal hydraulic pressure cancel chamber 81 can be acted upon.

Here, the outer diameter of the piston 91 and the outer diameter of the centrifugal hydraulic cancel piston 95 are set equal, and the inner diameter of the piston 91 and the inner circumference of the centrifugal hydraulic cancel piston 95 are engaged with the outer periphery of the cylindrical portion 92b. Pressing member 9
2, the centrifugal oil pressure generated in the piston pressing chamber 80 and the centrifugal oil pressure generated in the centrifugal oil pressure cancel chamber 81 are made equal to cancel the centrifugal oil pressure applied to the piston 91, as described later.

The supply of pressure oil to the piston pressing chamber 80 and the centrifugal hydraulic pressure canceling chamber 81 is performed as follows.

The piston pressing chamber 80 is provided radially with the opening 30 penetrating through the cylindrical portion 3c of the constant transmission output shaft 3c, and is provided in the radial direction so as to communicate the inner circumference and the outer circumference of the unit output shaft 6. A passage 62, a supply hole 65 formed through a centrifugal hydraulic cancel piston 64 defining an inner periphery of the unit output shaft 6 at a position opposed to the oil passage 62, and an oil passage inside the centrifugal hydraulic cancel piston 64. It communicates with a hydraulic control circuit on the casing 14 side via 60 and receives supply of hydraulic pressure.

The centrifugal hydraulic pressure canceling chamber 81 is provided with an opening 92c of the pressing member 92, an opening 31 penetrating in a radial direction of the cylindrical portion 3c of the fixed transmission output shaft 3c, and a radial unit. An oil passage 63 communicating the inner periphery and the outer periphery of the output shaft 6, and a casing 14 via an oil passage 61 outside the centrifugal hydraulic cancel piston 64 defining the inner periphery of the unit output shaft 6 via the oil passage 63. It communicates with the hydraulic supply circuit on the side and receives supply of hydraulic pressure.

The operation as described above will now be described.

In order to engage the power circulation mode clutch 9, the hydraulic pressure supplied to the piston pressing chamber 80 is increased.

As shown in FIGS. 3 and 4, when the hydraulic pressure in the piston pressing chamber 80 increases, the piston 91 comes into contact with the cylindrical portion 9 on the inner peripheral side facing the centrifugal hydraulic pressure canceling chamber 81.
The end 92d of 2b is pressed in the axial direction, and the piston 91 displaces the pressing surface 92a toward the clutch plate 93 side.

Further, when the piston 91 is displaced against the return spring 97, the pressing surface 92a of the pressing member 92 displaced integrally with the piston 91 comes into contact with the clutch plate 93, and the clutch plate 93 and the clutch disc 94 Is engaged by frictional engagement of the clutch.

Conversely, to release the power circulation mode clutch 9, the hydraulic pressure supplied to the piston pressing chamber 80 is reduced.

As shown in FIGS. 3 and 4, the pressing member 92
A return spring 97 abuts against the wall portion 92e of the cylindrical portion 92e to constantly urge the pressing member 92 rightward in the drawing.
The piston 91 is pressed through the end 92d of b.

When the hydraulic pressure of the piston pressing chamber 80 decreases,
The pressing member 92 is pressed by the urging force of the return spring 97.
The piston 91 is displaced in the contracting direction of the piston pressing chamber 80 to release the clutch. At the time of this release, the supply pressure to the centrifugal hydraulic pressure cancel chamber 81 may be increased.

Since the clutch drum 90 is constantly rotating when the power circulation mode clutch 9 is engaged and released, the piston pressing chamber 80 and the centrifugal hydraulic pressure canceling chamber 81
4, the outer diameter r2 and the inner diameter r1 of the piston 91 and the outer diameter r2 and the pressing member 92 of the centrifugal hydraulic cancel piston 95 facing the centrifugal hydraulic cancel chamber 81 are generated as shown in FIG. Since the inner diameters r1 are set to be equal, the centrifugal oil pressures acting on both the oil chambers 80 and 81 can be made substantially equal, and can be mutually offset.

The piston 91 presses the clutch plate 93 via a separately formed pressing member 92, and the cylindrical portion 92 b of the pressing member 92 causes the centrifugal hydraulic pressure to define the centrifugal hydraulic pressure canceling chamber 81. When the seal 74 provided inside the centrifugal hydraulic cancel piston 95 and the outer periphery of the cylindrical portion 92b slide through the inner peripheral side of the cancel piston 95, the piston 91 and the pressing member 92 are displaced integrally. And the outer diameter r2 of the piston 91 and the centrifugal hydraulic cancel piston 95 can be used effectively within the range of the inner diameter of the clutch drum 90, so that the outer diameter of the clutch drum 90 is increased as in the conventional example. Without increasing the pressure receiving area of the piston 91, the centrifugal hydraulic pressure is canceled to reliably prevent the clutch from dragging. Also, it is possible to easily increase the capacity of transmission torque.

In the conventional example, as shown in FIG. 7, the seal 172 provided on the outer periphery of the centrifugal hydraulic cancel piston 195 is in sliding contact with the piston 191. On the other hand, in the present invention, FIG. As shown in FIG. 4, the seal 73 provided on the inner periphery of the centrifugal hydraulic cancel piston 95 is slidably in contact with the outer periphery of the cylindrical portion 92b of the pressing member 92 which is displaced integrally with the piston 91. Can be reduced, the sliding area can be reduced, and the sliding resistance can be reduced.

Therefore, the return spring 97 is reduced in size by an amount corresponding to the decrease in the sliding resistance generated in the centrifugal hydraulic cancel piston 95 as compared with the conventional example, and the transmission torque of the power circulation mode clutch 9 is increased. Simultaneously with the propulsion, the hysteresis loss of the seal 73 can be reduced by reducing the diameter of the seal, and the control accuracy of the clutch engagement force can be improved.

As shown in FIGS. 3 and 4, the centrifugal oil pressure acting on the centrifugal oil pressure canceling chamber 81 also applies to the cylindrical portion 92b and the seal 74 of the pressing member 92 responsive to the centrifugal oil pressure canceling piston 95. Therefore, the offset amount of the centrifugal oil pressure is reduced by an amount corresponding to the pressure receiving area of the pressing member 92 facing the centrifugal oil pressure cancellation chamber 81,
As described later, the pressing member 92 facing the centrifugal hydraulic pressure canceling chamber 81 is connected to the cylindrical portion 92b on the shaft center 6c side and the seal 7.
Since only 4 is set, the offset amount of the centrifugal oil pressure does not become 0, and the centrifugal oil pressure acting on both sides of the piston 91 can be canceled by the large centrifugal oil pressure acting on the outer peripheral side as described later.

Here, the centrifugal hydraulic pressure generated in the power circulation mode clutch 9 to which the present invention is applied will be described.

As described above, the power circulation mode clutch 9
Are the piston pressing chamber 80 and the centrifugal hydraulic canceling chamber 81
In both cases, an oil passage 6 formed on the shaft center side of the unit output shaft 6
5, the piston pressing chamber 80 receives the hydraulic pressure from the shaft center 6c side of the rotating unit output shaft 6 as shown in the explanatory view of FIG. The pressing force F due to the centrifugal oil pressure acting on both sides of the oil chambers is, as shown by the dashed line in the figure, a quadratic function from the inner peripheral side (radius = r1) to the outer peripheral side (radius = r2) of each oil chamber. And the centrifugal oil pressure becomes maximum at the inner circumferential position of the clutch drum 90.

Therefore, the centrifugal hydraulic cancel piston 9
The pressing force F acting on the piston 91 facing the centrifugal hydraulic pressure canceling chamber 81 is higher than the pressing force F on the piston pressing chamber 80 side by the seal 73 provided on the inner periphery of the piston 5 and the seal 74 provided on the pressing member 92. It is possible to suppress the reduction in the size and to secure the offset amount of the centrifugal hydraulic pressure.

Here, as described above, the offset amount of the centrifugal oil pressure acting on the piston 91 is reduced by the pressure receiving area of the pressing member 92 facing the centrifugal oil pressure cancellation chamber 81. When the seal 74 of the pressing member 92 for sealing the hydraulic pressure canceling chamber 81 is abolished, hydraulic oil leaks from the inner periphery of the cylindrical portion 92b of the pressing member 92 at the position of radius = r1 in FIG. The pressing force acting on the piston 91 decreases as indicated by F 'shown by the broken line in FIG.

For this reason, the piston pressing chamber 80 has the shaft center 6c.
In the case where the hydraulic pressure is supplied from the clutch, the provision of the seal 74 on the inner periphery of the pressing member 92 can increase the offset amount of the centrifugal hydraulic pressure as compared with the case where the seal 74 is not provided, and can reduce the drag of the clutch. Can be reliably prevented.

In FIG. 5, when the pressure oil is supplied to the piston pressing chamber 80 from a non-rotating member other than the shaft 6c side, the seal 74 on the inner periphery of the pressing member 92 and the centrifugal hydraulic cancel piston The seal 73 on the inner periphery of the 95 may be omitted, and a seal may be provided only on the outer periphery side where the centrifugal oil pressure increases.

FIG. 6 shows a second embodiment in which a cylindrical portion 91a is provided on the piston 91 side of the first embodiment in sliding contact with the inner periphery of the centrifugal hydraulic cancel piston 95, while a cylindrical portion 92b of the pressing member 92 is provided. Are abolished, and the other configuration is the same as that of the first embodiment.

A return spring 97 is provided on the piston 91 ′ facing the centrifugal hydraulic pressure canceling chamber 81 so as to be in sliding contact with the inner periphery of the centrifugal hydraulic pressure canceling piston 95.
It protrudes toward the side.

In the cylindrical portion 91a, at a predetermined position facing the centrifugal hydraulic pressure canceling chamber 81 and the opening 31 as an oil passage provided in the cylindrical portion 3e of the constant transmission output shaft 3c,
A through-hole 91b is formed so that the opening 31 on the side of the shaft center 6c and the centrifugal hydraulic pressure cancel chamber 81 are always in communication.

The cylindrical portion 91a projecting from the piston 91 'slides on the outer periphery of the cylindrical portion 3e at a position straddling the opening 31 of the fixed transmission output shaft 3c, and returns from the centrifugal hydraulic cancel piston 95. Spring 9
The end surface 91c of the cylindrical portion 91a abuts on the end surface 92f of the annular pressing member 92 '.

The piston 91 'slidingly in contact with the cylindrical portion 3e of the fixed transmission output shaft 3c at a position straddling the opening 31.
A seal member 74 ′ is provided on the inner periphery of the cylindrical portion 91 a to prevent the hydraulic oil supplied to the centrifugal hydraulic pressure cancel chamber 81 from the opening 31 from leaking to the pressing member 92 ′, A decrease in the hydraulic pressure applied to the hydraulic pressure cancel chamber 81 is suppressed.

In this case, when the hydraulic pressure of the piston pressing chamber 80 changes and the piston 91 'is displaced, the cylindrical portion 91
The pressing member 92 ′ abutting against the end surface 91 c of FIG.
Can be fastened and released.

The centrifugal oil pressure can be offset by the seal member 74 'provided on the inner periphery of the cylindrical portion 91a, as in the first embodiment.

In the above embodiment, when the supply of the pressurized oil to the piston pressing chamber 80 is made from a non-rotating member other than the shaft 6c side, the inner circumference of the cylindrical portion 91a protruding from the piston 91 'is formed. The seal member 74 ′ and the seal 73 on the inner circumference of the centrifugal hydraulic cancel piston 95 may be omitted.

[Brief description of the drawings]

FIG. 1 is a schematic configuration diagram of a rotary clutch showing an embodiment of the present invention.

FIG. 2 is a sectional view of a main part of the rotary clutch.

FIG. 3 is an enlarged sectional view of a power circulation mode clutch as a rotary clutch.

FIG. 4 is a conceptual diagram of a power circulation mode clutch.

FIG. 5 is an explanatory diagram showing an operation, showing a relationship between a magnitude of a pressing force F due to centrifugal hydraulic pressure acting on a piston and a radius from an axis.

FIG. 6 is a conceptual diagram of a power circulation mode clutch showing a second embodiment.

FIG. 7 is a conceptual diagram showing a conventional rotary clutch.

[Explanation of symbols]

 Reference Signs List 3 constant transmission 3c constant transmission output shaft 3d flange 6 unit output shaft 6c shaft center 9 power circulation mode clutch 30, 31 opening 60, 61 oil passage 62, 63 oil passage 64 centrifugal oil pressure cancel piston 65 supply hole 70, 71 seal 72, 73 seal 74 seal 75 snap ring 80 piston pressing chamber 81 centrifugal hydraulic pressure canceling chamber 90 clutch drum 91 piston 91a cylindrical portion 91b through hole 92 pressing member 92a pressing surface 92b cylindrical portion 92c opening 92d end 93 clutch plate 94 Clutch disc 95 Centrifugal hydraulic cancel piston 96 Clutch inner 97 Return spring

Claims (6)

[Claims] A piston that is housed in a rotatable clutch drum and is displaceable in the direction of the rotation axis; a piston pressing chamber defined between the piston and the clutch drum; A centrifugal hydraulic cancel piston disposed on the opposite side of the pressing chamber; a centrifugal hydraulic cancel chamber defined between the piston and the centrifugal hydraulic cancel piston; and A friction member that performs engagement and disengagement in accordance with the hydraulic pressure supplied to the piston pressing chamber while canceling the centrifugal hydraulic pressure on both sides of the piston. A pressure-receiving member defining an inner periphery of the centrifugal hydraulic cancel piston, and having at one end the centrifugal hydraulic cancel piston While contact with the pressure receiving member facing the emission, rotary clutch, characterized in that at the other side is composed of said friction member and detachably pressing member. 2. The seal according to claim 1, wherein seal members are interposed between the clutch drum and the centrifugal hydraulic cancel piston, and between the centrifugal hydraulic cancel piston and the pressing member. Rotating clutch. 3. The clutch drum is disposed on the outer periphery of a rotating shaft, and while a hydraulic pressure is supplied to the piston pressing chamber and the centrifugal hydraulic pressure canceling chamber from an oil passage provided inside the rotating shaft, The rotary clutch according to claim 2, wherein a seal member is provided between the pressing member and the rotation shaft. 4. A piston housed in a rotatable clutch drum and displaceable in the direction of a rotation axis, a piston pressing chamber defined between the piston and the clutch drum, and a piston sandwiching the piston. A centrifugal hydraulic cancel piston disposed on the opposite side of the pressing chamber; a centrifugal hydraulic cancel chamber defined between the piston and the centrifugal hydraulic cancel piston; and A friction member that performs engagement and disengagement in accordance with the hydraulic pressure supplied to the piston pressing chamber while canceling the centrifugal hydraulic pressure on both sides of the piston. A pressure member that defines the following: a pressure member that can be brought into contact with and separated from the friction member; As well as through the inner periphery of the piston, rotary clutch, characterized in that constructed from the pressing member and can contact the cylindrical portion. 5. A seal member is interposed between the clutch drum and the centrifugal hydraulic cancel piston, and between the centrifugal hydraulic cancel piston and the cylindrical portion protruding from the pressure receiving member. The rotary clutch according to claim 4. 6. The clutch drum is disposed on an outer periphery of a rotating shaft, and while a hydraulic pressure is supplied from an oil passage provided inside the rotating shaft to the piston pressing chamber and the centrifugal hydraulic pressure canceling chamber, The rotary clutch according to claim 5, wherein a seal member is provided between the cylindrical portion and the rotation shaft.