JP2768133B2 - Fluid pressure clutch device - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a fluid pressure clutch device.

[0002]

2. Description of the Related Art An automatic transmission mounted on an automobile is provided with a plurality of hydraulic clutch devices, and a shift of the automatic transmission is performed by switching a hydraulic clutch device to be operated by a controller. Conventionally, a hydraulic clutch device may be arranged around an input shaft of an automatic transmission and a sleeve-like member surrounding the input shaft, and in this case, the clutch retainer slides with respect to the sleeve-like member. While rotating together with the input shaft. A clutch piston is provided in the clutch retainer. A hydraulic chamber is provided on one side of the clutch piston, and a balance chamber (reservoir) is provided on the other side. Hydraulic chamber can be supplied with working oil through an oil passage formed in the sleeve member.In the balance chamber, oil is supplied from the gap between the sleeve member and the input shaft during driving of the engine. Is supplied. The hydraulic chamber and the balance chamber are connected by a hole provided in the clutch piston.

Since the hydraulic clutch device rotates at high speed integrally with the input shaft, the pressure of the working oil in the hydraulic chamber increases due to centrifugal force. In this state, undesired movement of the clutch piston is prevented, and so-called clutch drag torque is prevented from being generated.

[0004]

By the way, in the above-mentioned conventional hydraulic clutch device, even when the supply of the working oil to the hydraulic chamber is stopped in the operation release state, a pressure difference may occur between the respective chambers. is there. In other words, the effect of the centrifugal force on the oil in each room due to the difference in the radial position of the oil supply port to each room and the oil leakage due to the rattling of the structure of the balance room that does not require so high oil tightness. And the method of increasing the pressure are different. For this reason, even when the operation of the hydraulic clutch device is released and the supply of the working oil to the hydraulic chamber is stopped, the pressure of the working oil in the hydraulic chamber may be larger than the pressure of the oil in the balance chamber. is there.

[0005] Structurally, the hydraulic chamber and the balance chamber are in communication with each other. When the pressure of the working oil in the hydraulic chamber becomes larger than the pressure of the oil in the balance chamber, the hydraulic chamber and the hydraulic chamber necessary for moving the clutch piston are moved. The operating oil in the oil passage flows out to the balance chamber side through the hole of the clutch piston, and the rise of the hydraulic pressure is delayed at the next operation of the clutch piston, which causes a problem that the responsiveness of the hydraulic clutch device is deteriorated.

SUMMARY OF THE INVENTION The present invention has been made to solve the above problems, and has as its object to provide a fluid pressure clutch device having excellent responsiveness.

[0007]

According to the present invention, in order to achieve the above-mentioned object, a fluid pressure is arranged around a rotary shaft and a cylindrical body surrounding the rotary shaft, and rotates integrally with the rotary shaft. In the clutch device, a first fluid passage that is provided in the tubular body and supplies the working fluid, a second fluid passage that is positioned radially inward from the tubular body, and is fixed to the rotation shaft, and An annular clutch retainer that rotates by rotating the clutch piston, an annular space provided in the clutch retainer, a clutch piston disposed in the annular space, a hole communicating one side of the clutch piston with the other side, and one side of the clutch piston. And a fluid pressure chamber disposed radially outside the cylindrical body and communicating with the first fluid passage, and provided on the other side of the clutch piston, and capable of storing fluid through the second fluid passage. Fluid due to centrifugal force compared to pressure chamber And it constitutes and an increase in large reservoirs.

[0008]

When the rotating shaft rotates at high speed, the clutch retainer also rotates at high speed, and the pressure of the fluid in the fluid pressure chamber and the storage chamber increases due to centrifugal force. Since the increase in the pressure of the fluid in the storage chamber is greater than the increase in the pressure of the fluid in the hydraulic chamber, the working fluid in the hydraulic chamber and the first fluid passage flows out to the storage chamber through the hole of the clutch piston. Can be prevented.

[0009]

An embodiment of the present invention will be described below with reference to the accompanying drawings. FIG. 1 shows an embodiment of a hydraulic clutch device according to the present invention. This hydraulic clutch device is provided, for example, in an automatic transmission of an automobile. Reference numeral 1 in the figure denotes an input shaft of the automatic transmission, which rotates at a high speed integrally with a turbine (not shown). A portion in the middle of the input shaft 1 is surrounded by a sleeve-like member 2, and a gap therebetween is formed by an oil passage 3.
It has become. The sleeve-shaped member 2 is fixed to, for example, a casing (not shown) of the automatic transmission. The sleeve member 2 has an oil passage 4 extending in the axial direction and opening at a predetermined position on the outer peripheral surface. The oil passage 3 extends to a clutch operating hydraulic circuit (not shown), and the oil passage 4 extends to a lubricating oil supply system.

The hydraulic clutch device 10 includes a clutch retainer 11, a friction engagement portion 12, an annular partition 13, a clutch piston 14, and the like. Clutch retainer 1
Numeral 1 includes a retainer hub 17, a holding portion 18, and the like, and is formed in an annular shape. The retainer hub 17 is spline-fitted to the input shaft 1 and the snap ring 2
1 and is thus fixed to the input shaft 1 and rotates integrally therewith. The retainer hub 17 extends in the radial direction while leaving a predetermined gap 19 between the retainer hub 17 and the end surface of the sleeve-shaped member 2, and further extends to one side in the axial direction of the input shaft 1, and An inner peripheral wall 22 that is in contact is formed. A space between the inner peripheral wall 22 and the sleeve-shaped member 2 is oil-tightly sealed by a pair of seal members 23. In addition, the oil hole 2 that opens to the gap 19 is formed in the inner peripheral wall 22.
5 and an oil hole 26 opening toward the oil passage 4.

The innermost portion of the oil hole 25 (solid line A in the figure)
The position (position) is located radially inward of the innermost portion (solid line B position) of the oil hole 26. The holding portion 18 includes an annular side wall 31 and a plate mounting wall 32, which are integrally formed. The annular side wall 31 is provided on the retainer hub 1.
7 is fixed irremovably to the front end of the cable 7 and extends radially outward. Further, the plate mounting wall 32 is
After a predetermined distance from the outer peripheral edge of the input shaft 1 toward the other side in the axial direction of the input shaft 1, the diameter of the input shaft 1 is increased in the shape of a flange, and further extended toward the other side in the axial direction.

The friction engagement portion 12 is composed of a plurality of clutch plates 34 and clutch disks 35 and the like. For example, a torque transmitting member 37 extending from a planetary gear transmission (not shown) of an automatic transmission, a clutch retainer 11 is interposed. Each clutch plate 34 is mounted on the plate mounting wall 32 and each clutch disc 35 is mounted on the rotational force transmitting member 37 so as to be relatively non-rotatable in the circumferential direction.

The annular partition 13 is fitted near the base end of the inner peripheral wall 22, extends radially outward while avoiding interference with the rotational force transmitting member 37, and has an annular space 38 between itself and the annular side wall 31. Has been stipulated. The space between the annular partition 13 and the inner peripheral wall 22 is oil-tightly sealed by an O-ring 41. The annular partition 13 is provided with a snap ring 4.
2 makes it impossible to drop.

The clutch piston 14 extends from the outer peripheral edge of the piston body 44 toward the friction engagement portion 12 with the piston body 44 disposed in the annular space 38, and frictionally engages each clutch plate 34 and clutch disc 35. And a hole 4 provided in the piston body 44 for allowing one side of the piston body 44 to communicate with the other side.
6 and so on. The piston main body 44 partitions the annular space 38 into a hydraulic chamber 48 and a balance chamber 49.

A hydraulic chamber 48 (cylinder chamber) provided on one side of the piston body 44 communicates with the oil passage 4 through the oil hole 26. Therefore, when the working oil is supplied into the hydraulic chamber 48 via the oil passage 4, the clutch piston 14 moves forward against the spring force of the return spring 51 provided in the balance chamber 49, and The clutch plate 34 and the clutch disk 35 are frictionally engaged. On the other hand, when the supply of the working oil is stopped, the clutch piston 14 is pressed by the return spring 51 and moves backward while discharging the working oil in the hydraulic chamber 48 to the oil passage 4 or the like. Further, a balance chamber 49 (oil reservoir) provided on the other side of the piston main body 44 communicates with the gap 19 and the oil passage 3 through the oil hole 25, and oil is recirculated with the reciprocation of the clutch piston 14. Discharge or inflow.

Next, the flow of oil in the hydraulic chamber 48 and the balance chamber 49 will be described. Input shaft 1 of automatic transmission
Rotates at a high speed, the hydraulic clutch device 10 also rotates at a high speed. On the other hand, the sleeve member 2 is fixed to the casing side as described above, and does not rotate. When the hydraulic clutch device 10 rotates at a high speed, the pressure of the oil in the hydraulic chamber 48 and the balance chamber 49 increases due to the centrifugal force. At this time, on the hydraulic chamber 48 side, the inner peripheral wall 22 rotates at a high speed while sliding with respect to the fixed sleeve-shaped member 2, so that the oil positioned radially outward from the position near the solid line B in the drawing is centrifugal force Pressure. On the other hand, on the balance chamber 49 side, since the gap 19 exists between the retainer hub 17 and the sleeve-shaped member 2, the oil located radially outward from near the position of the solid line A in the drawing is increased in pressure by centrifugal force. You.

Since the position of the solid line A is deviated radially inward from the position of the solid line B, near the hole 46 of the piston body 44, the pressure of the oil in the balance chamber 49 increases.
It becomes larger than the pressure of the oil in the hydraulic chamber 48. Therefore, the oil in the balance chamber 49 flows into the hydraulic chamber 48 through the hole 46, further flows from the hydraulic chamber 48 into the oil passage 4,
Alternatively, when the inside of the oil passage 4 is filled with the working oil, the above-described actual flow does not occur, but the working oil is prevented from flowing out from the hydraulic chamber 48 to the balance chamber 49.

As a result, it is possible to prevent the operating oil from leaking out of the oil passage 4 for supplying the operating oil of the clutch piston 14, thereby improving the responsiveness of the hydraulic clutch device 10 and smoothing the shift change of the automatic transmission. , The shift feeling is improved. The oil holes 25 and 26 may be provided at a plurality of locations at equal intervals in the circumferential direction of the retainer hub 17, and the holes 46 may be provided at a plurality of locations at equal intervals in the circumferential direction of the piston body 44. It is good also as a structure to pierce.

Further, as shown in FIGS. 2 and 3, a passage 53 may be provided in the retainer hub 17. That is, the passage 53 is disposed on the inner peripheral wall 22 at a predetermined distance from the oil hole 25 in the circumferential direction, extends radially inward from the surface facing the balance chamber 49, and then extends to the innermost side of the oil hole 26. Position (solid line D position) radially inward of the part (solid line B position)
From the other side in the axial direction. Therefore, the passage 53 communicates the inside of the balance chamber 49 with the space between the retainer hub 17 and the rotational force transmitting member 37.

The balance chamber 4 is separated from the oil passage 3 through the gap 19.
When the oil flows into the balance chamber 9, the oil accumulates from the radial outside of the balance chamber 49 due to centrifugal force, so that the air in the balance chamber 49 is discharged from the passage 53 and enters the balance chamber 49. Oil flow smoothly. On the other hand, when the inside of the balance chamber 49 is filled with oil, the oil increased in pressure by the centrifugal force flows out of the balance chamber 49 through the passage 53, and therefore, from the vicinity of the position indicated by the solid line D in FIG. The outer oil will be intensified by centrifugal force. However, the position of the solid line D is deviated radially inward from the position of the solid line B.
As in the case of FIG. 1, near the hole 46 of the piston body 44, the oil pressure in the balance chamber 49 becomes larger than the oil pressure in the hydraulic chamber 48.

[0021]

As described above, according to the present invention,
A first fluid passage provided in the tubular body and supplying a working fluid;
A second fluid passage located radially inward of the cylindrical body, an annular clutch retainer fixed to the rotating shaft and rotating with respect to the cylindrical body, an annular space provided in the clutch retainer, and an annular space. And a hole that communicates one side of the clutch piston with the other side, and a fluid that is provided on one side of the clutch piston and that is disposed radially outside the cylindrical body and communicates with the first fluid path. A fluid pressure clutch including a pressure chamber and a storage chamber provided on the other side of the clutch piston, the fluid chamber being capable of storing fluid through the second fluid passage, and having a greater increase in fluid pressure due to centrifugal force than the fluid pressure chamber. Since the device is configured, when the operation of the fluid pressure clutch device is released, the working fluid for moving the clutch piston is
It is possible to prevent the fluid from flowing out of the fluid pressure chamber and the first fluid path to the storage chamber side.

As a result, the responsiveness of the fluid pressure clutch device can be improved, and when this fluid pressure clutch device is used in an automatic transmission for automobiles, the shift feeling during shifting can be improved. There are excellent effects such as being able to achieve.

[Brief description of the drawings]

FIG. 1 is a sectional view showing an embodiment of a hydraulic clutch device to which the present invention is applied.

FIG. 2 is a sectional view showing another embodiment of FIG. 1;

FIG. 3 is a cross-sectional view of the retainer hub taken along a line III-III in FIG. 2;

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Input shaft 2 Sleeve-shaped member 3, 4 Oil passage 10 Hydraulic clutch device 11 Clutch retainer 14 Clutch piston 17 Retainer hub 25, 26 Oil hole 38 Annular space 41 O-ring 46 Hole 48 Hydraulic chamber 49 Balance chamber 53 Passage

Claims (1)

(57) [Claims] 1. A fluid pressure clutch device disposed around a rotating shaft and a tubular body surrounding the middle of the rotating shaft and rotating integrally with the rotating shaft, a fluid pressure clutch device provided on the tubular body and supplying a working fluid. One fluid path,
A second fluid passage located radially inward of the cylindrical body, an annular clutch retainer fixed to the rotating shaft and rotating with respect to the cylindrical body, an annular space provided in the clutch retainer, and an annular space. And a hole that communicates one side of the clutch piston with the other side, and a fluid that is provided on one side of the clutch piston and that is disposed radially outside the cylindrical body and communicates with the first fluid path. A pressure chamber, and a storage chamber provided on the other side of the clutch piston, capable of storing fluid through the second fluid passage, and having a large increase in fluid pressure due to centrifugal force as compared with the fluid pressure chamber. Fluid pressure clutch device.