JP2021181804A - Sealing device - Google Patents

Abstract

To provide a sealing device that reduces sliding resistance of a canceller plate during operation of a piston plate and improves operability of the piston plate.SOLUTION: A sealing device 100 includes an annular piston plate 11 that is disposed in a housing 20, forms a piston pressure chamber 21 together with the housing 20, and has a bottomed recess 10, an annular canceller plate 12 that forms a canceller hydraulic chamber 23 together with the recess 10 of the piston plate 11 and reciprocates along a central axis O of the piston plate 11, and a canceller seal 30 that is disposed on an outer peripheral portion of the canceller plate 12 in axially-slidable contact with a side surface 10a of the recess 10 of the piston plate 11. The piston plate 11 has a diameter expansion tapered surface 40 expanding in diameter from an opening 18 side of the recess 10 toward a bottom surface 19 side on the side surface 10a of the recess 10 of the piston plate 11, and the canceller seal 30 slidably contacts the diameter expansion tapered surface 40.SELECTED DRAWING: Figure 2

Description

The present invention relates to a sealing device. More specifically, the present invention relates to a sealing device used for an automatic transmission of an automobile or the like.

Conventionally, for example, an automatic transmission for an automobile or the like is provided with a hydraulically actuated piston mechanism in order to switch the engagement and disengagement of a clutch in order to turn on / off the transmission of rotational torque. A piston (piston plate) and a canceller (canceller plate) are used in this piston mechanism. The piston operates in the axial direction by the supply hydraulic pressure, and the clutch pushing surface engages and releases the clutch plate to shift gears. It is carried out.

A seal lip is baked in this canceller to seal the oil in the oil chamber, and a sealing device having a structure in which the seal lip of the canceller slides with the piston to seal the oil is known (for example,). See Patent Document 1).

Japanese Unexamined Patent Publication No. 2006-242311

Here, the sealing device as described in Patent Document 1 is required to reduce the sliding resistance of the canceller plate when the piston plate is operated. In response to such a requirement, the sealing device described in Patent Document 1 still has room for improvement in reducing the sliding resistance of the canceller plate when the piston plate is operated.

For these reasons, it has been desired to develop a sealing device that reduces the sliding resistance of the canceller plate when the piston plate is operated.

The present invention has been made in view of such a prior art, and an object thereof is a sealing in which the sliding resistance of the canceller plate is reduced when the piston plate is operated and the operability of the piston plate is improved. It is to develop the equipment.

According to the present invention, the sealing device shown below is provided.

[1] An annular piston plate arranged in a housing, forming a piston pressure chamber together with the housing, and having a bottomed recess.
An annular canceller plate that forms a canceller hydraulic chamber together with the recess of the piston plate and reciprocates along the central axis of the piston plate.
A canceller seal is provided on the outer peripheral portion of the canceller plate so as to be slidably contacted with the side surface of the recess of the piston plate in the axial direction.
The piston plate has a tapered surface on the side surface of the concave portion of the piston plate whose diameter increases from the opening side of the concave surface toward the bottom surface side, and the canceller seal is slidably contacted with the tapered surface. Is a sealing device.

[2] The side surface of the recess of the piston plate has a tapered surface where the canceller seal is slidably contacted, and the other portion is a cross section of the piston plate in the central axial direction. The sealing device according to the above [1], which has a plane parallel to the central axis.

[3] The sealing device according to the above [2], wherein there is a step between the tapered surface and the surface of the piston plate parallel to the central axis.

[4] The sealing device according to the above [2], wherein the tapered surface and a surface of the piston plate parallel to the central axis are continuous surfaces.

[5] The sealing device according to any one of [1] to [4] above, which is used for a clutch switching unit of an automatic transmission.

The sealing device of the present invention has the effect of reducing the sliding resistance of the canceller plate when the piston plate is operated and improving the operability of the piston plate.

It is a top view which shows typically one Embodiment of the sealing apparatus of this invention. It is sectional drawing which shows typically the state which viewed the cross section AA in FIG. 1 in the direction of an arrow. It is a partial cross-sectional view schematically showing by enlarging a part of FIG. FIG. 3 is a partial cross-sectional view corresponding to FIG. 3, which schematically shows another embodiment of the sealing device of the present invention. FIG. 3 is a partial cross-sectional view corresponding to FIG. 3, which schematically shows still another embodiment of the sealing device of the present invention. FIG. 3 is a partial cross-sectional view corresponding to FIG. 3, which schematically shows still another embodiment of the sealing device of the present invention. FIG. 2 is a partial cross-sectional view corresponding to FIG. 2, which schematically shows a conventional sealing device.

Hereinafter, embodiments of the present invention will be described with reference to the drawings. It should be noted that the present invention is not limited to the following embodiments, and it is understood that design changes, improvements, etc. may be appropriately made based on ordinary knowledge of those skilled in the art without departing from the spirit of the present invention. It should be.

(1) Sealing device:
One embodiment of the sealing device of the present invention is the sealing device 100 shown in FIGS. 1 and 2. The sealing device 100 is arranged in a housing 20, forms a piston pressure chamber 21 together with the housing 20, and has an annular piston plate 11 having a bottomed recess 10 and a canceller hydraulic chamber together with the recess 10 of the piston plate 11. An annular canceller plate 12 that forms 23 and reciprocates along the central axis O of the piston plate 11 and is slidable axially with the side surface 10a of the recess 10 of the piston plate 11 on the outer peripheral portion of the canceller plate 12. It is provided with a canceller seal 30 arranged in contact with the. The piston plate 11 has a tapered surface (diameter-expanded tapered surface 40) whose diameter increases from the opening 18 side of the recess 10 toward the bottom surface 19 on the side surface 10a of the recess 10 of the piston plate 11. The canceller seal 30 is slidably in contact with the enlarged diameter tapered surface 40). Note that FIG. 1 shows the sealing device 100 by omitting the housing 20.

Such a sealing device 100 reduces the sliding resistance of the canceller plate 12 when the piston plate 11 operates, and improves the operability of the piston plate 11.

This sealing device 100 is used, for example, in a clutch switching unit of an automatic transmission, and can be used as a sealing device such as a hydraulic actuator that operates a clutch.

(1-1) Piston plate:
The piston plate 11 is an annular one that is arranged in a housing 20, forms a piston pressure chamber 21 together with the housing 20, and has a bottomed recess 10. Then, as shown in FIG. 3, the piston plate 11 has a diameter-expanded tapered surface 40 on the side surface 10a of the recess 10 of the piston plate 11 that expands in diameter from the opening 18 side of the recess 10 toward the bottom surface 19. There is. The canceller seal 30 is slidably in contact with the enlarged diameter tapered surface 40.

Having the enlarged diameter tapered surface 40 in this way reduces the sliding resistance of the canceller plate 12 when the piston plate 11 operates, and improves the operability of the piston plate 11.

The inclination angle of the enlarged diameter tapered surface 40 of the piston plate 11 can be appropriately set. That is, the angle θ formed by the straight line L parallel to the central axis O and the enlarged diameter tapered surface 40 in the cross section of the piston plate 11 in the central axis O direction can be appropriately set based on the diameter dimension, the stroke, and the like.

The diameter of the recess 10 of the piston plate 11 is larger than the diameter of the recess of the conventional piston plate on the enlarged taper surface 40. FIG. 7 shows a conventional sealing device 200 using a conventional piston plate 111. In the piston plate 111 of the sealing device 200, the side surface 110a of the recess 110 is parallel to the central axis O in the cross section of the piston plate 111 in the central axis O direction.

The piston plate 11 has a recess 10 in the central portion thereof, and specifically, as shown in FIG. 2, an example having the following portions can be exemplified. That is, the piston plate 11 includes an inner peripheral flange portion 31, an inner cylinder portion 32 extending from the outer periphery thereof toward the piston pressure chamber 21, and a pressure receiving plate portion 33 extending radially from the end portion on the piston pressure chamber 21 side. It is possible to exemplify a device having an outer cylinder portion 34 extending from the outer periphery of the pressure receiving plate portion 33 to the side opposite to the piston pressure chamber 21, and a clutch pressing portion 35 bent and formed at the tip of the outer cylinder portion 34. .. The piston plate 11 has a through hole 11a formed in the center thereof (see FIG. 1).

The outer cylinder portion 34 is a side wall of the bottomed recess 10 of the piston plate 11, and in the present invention, a predetermined tapered surface 40 is formed on the inner peripheral surface 34a (that is, the side surface 10a of the recess 10) of the outer cylinder portion 34. Is formed. By forming the enlarged diameter tapered surface 40, as described above, the sliding resistance of the canceller plate 12 can be reduced when the piston plate 11 is operated. That is, when the piston plate 11 or the canceller plate 12 moves so that the piston plate 11 and the canceller plate 12 come close to each other, the gap between the piston plate 11 and the canceller plate 12 gradually widens. Therefore, the force that the canceller seal 30 receives from the piston plate 11 and the canceller plate 12 becomes small. Therefore, the sliding resistance of the canceller plate 12 when the piston plate 11 is operated is reduced.

The diameter-expanded tapered surface 40 needs to be expanded from the opening 18 side of the recess 10 toward the bottom surface 19. Here, if a tapered surface whose diameter is reduced from the opening 18 side of the recess 10 toward the bottom surface 19 side is adopted, the sliding resistance of the canceller plate 12 at the start of piston fastening increases. That is, it is desired to reduce the resistance during sliding at the start of piston fastening, but the sliding resistance of the canceller plate 12 increases at the start of piston fastening.

The enlarged diameter tapered surface 40 may be formed on the entire side surface 10a of the recess 10, or may be formed on a part of the side surface 10a of the recess 10. That is, the enlarged diameter tapered surface 40 may be formed at least in the working distance S (see FIGS. 3 and 4) of the piston plate 11, and the working distance S (canceller seal 30 is slidably contacted). The surface other than the portion to be formed) may be a tapered surface or a straight surface (that is, a surface parallel to the central axis O of the piston plate 11). As shown in FIG. 5, in the case where only the inner peripheral surface 34a of the outer cylinder portion 34 is inclined and the outer peripheral surface is not inclined (that is, parallel to the central axis O), if the straight surface 61 is provided. The thickness of the outer cylinder portion 34 of the piston plate 11 is thicker than that in the case where the entire inner peripheral surface 34a is an inclined surface. Therefore, even when the pressure of the piston hydraulic chamber 21 becomes high, the pressure resistance is further exhibited. The pressure resistance is further exhibited even when the pressure in the canceller hydraulic chamber 23 becomes high. FIG. 3 shows an example in which the enlarged diameter tapered surface 40 is formed on the entire side surface 10a of the recess 10 including the working distance S. Within the working distance S of the enlarged diameter tapered surface 40, the canceller seal 30 is in sliding contact with the canceller seal 30. Therefore, in the range of the working distance S of the enlarged diameter tapered surface 40 of the piston plate 11, the tightening allowance with the canceller seal 30 is large on the opening 18 side of the recess 10, and the tightening allowance with the canceller seal 30 is small on the bottom surface 19 side. Alternatively, there may be no tightening allowance. In the present specification, the "straight surface" includes not only a surface parallel to the central axis O but also a slightly positively tapered surface or a reversely tapered surface (that is, a substantially parallel surface) with respect to the central axis O. It is a concept.

When the straight surface 61 is provided on a surface other than the portion of the working distance S, as shown in FIG. 5 described above, there is no step between the enlarged diameter tapered surface 40 and the straight surface 61 (boundary), and the enlarged diameter tapered surface 40 And the straight surface 61 may be continuous surfaces, or as shown in FIG. 6, there may be a mode in which a step 62 is provided between the enlarged diameter tapered surface 40 and the straight surface 61. In this aspect, the straight surface 61 is preferably located on the central axis O side of the enlarged diameter tapered surface 40. In the embodiment shown in FIG. 6, since the outer cylinder portion 34 of the piston plate 11 is thick, the pressure resistance is further exhibited even when the pressure of the piston hydraulic chamber 21 becomes high. Further, when the piston plate 11 having the enlarged diameter tapered surface 40 is manufactured, the portion corresponding to the enlarged diameter tapered surface 40 may be machined after the normal piston plate is manufactured, so that the manufacturing is easy. ..

The inner peripheral flange portion 31 of the piston plate 11 is provided with an annular inner peripheral seal lip 37 made of a rubber-like elastic material that is slidably closely adhered to the surface of the inner peripheral tubular portion 41 of the housing 20. .. Further, on the outer peripheral portion of the pressure receiving plate portion 33 of the piston plate 11, an annular outer peripheral seal lip 38 made of a rubber-like elastic material slidably closely adhered to the surface of the outer peripheral cylinder portion 42 of the housing 20 is arranged. .. The inner peripheral seal lip 37 and the outer peripheral seal lip 38 ensure the sealing property between the housing 20 and the housing 20. An oil passage 41a for introducing the oil pressure into the piston pressure chamber 21 is formed in the inner peripheral cylinder portion 41 of the housing 20.

The piston plate 11 has a curved surface (R surface 29) formed on the inner surface of the root portion of the outer cylinder portion 34, that is, the intersection portion between the pressure receiving plate portion 33 and the outer cylinder portion 34. That is, an R surface is formed at the corner of the recess 10 formed at the center of the piston plate 11. By providing the R surface 29, the piston plate 11 can withstand the high pressure state even when the inside of the piston pressure chamber 21 becomes high pressure, and the piston plate 11 is less likely to be damaged. The radius of curvature of the R surface can be in a conventionally known range.

The inner peripheral seal lip 37 and the outer peripheral seal lip 38 can be integrally cross-linked and bonded to the piston plate 11.

As described above, the piston plate 11 may have a diameter-expanded tapered surface 40 whose diameter increases from the opening 18 side of the recess 10 toward the bottom surface 19. That is, as shown in FIG. 3, only the inner peripheral surface 34a of the outer cylinder portion 34 may be inclined and the outer peripheral surface may not be inclined (parallel to the central axis O), or as shown in FIG. In addition, the outer cylinder portion 34 itself may be inclined so as to expand in diameter toward the pressure receiving plate portion 33 (bottom surface 19 of the recess 10).

The piston plate 11 having the embodiment shown in FIG. 3 can be manufactured as follows. That is, a method of pressing the piston plate as in the conventional case and then cutting the inner surface of the recess can be mentioned. Further, the piston plate 11 having the embodiment shown in FIG. 4 can be manufactured as follows. That is, a method of pressing the piston plate by inclining the outer cylinder portion 34 itself so as to expand the diameter toward the pressure receiving plate portion (bottom surface 19 of the recess 10) can be mentioned.

The piston plate 11 can be made of a metal such as a steel plate, and can be manufactured by punching and pressing a metal plate.

(1-2) Canceller plate:
The canceller plate 12 is an annular shape that forms a canceller hydraulic chamber 23 together with the recess 10 of the piston plate 11 and reciprocates along the central axis O of the piston plate 11.

As such a canceller plate 12, conventionally known ones can be appropriately adopted. The canceller plate 12 can be made of a metal such as a steel plate, and can be manufactured by punching and pressing a metal plate.

The canceller plate 12 has a through hole 12a formed in the central portion thereof, and has an outer ring portion 12b on the outer peripheral portion thereof.

(1-3) Canceller seal:
The canceller seal 30 is arranged on the outer peripheral portion of the canceller plate 12, and is arranged in contact with the side surface 10a of the recess 10 of the piston plate 11 so as to be slidable in the axial direction. The canceller seal 30 is for ensuring the sealing property between the piston plate 11 and the canceller plate 12.

The material of the canceller seal 30 is not particularly limited, and the same material as the conventionally known canceller seal (that is, the seal lip) can be appropriately selected and used. Examples of the material of the canceller seal 30 include rubber-like elastic materials, and in particular, cross-linked and bonded rubber-like elastic materials.

The canceller seal 30 can be integrally cross-linked and bonded to the canceller plate 12.

(1-4) Bouncer:
The sealing device 100 is provided in the canceller hydraulic chamber 23 and has an urging member 15 for urging the piston plate 11 away from the canceller plate 12. As the urging member 15, conventionally known ones can be appropriately adopted, and examples thereof include a spring.

The urging member 15 moves so that the piston plate 11 reduces the volume of the piston pressure chamber 21 due to its repulsive force.

(2) How to use the sealing device:
The method of using the sealing device of the present invention will be described below based on the sealing device 100. First, the sealing device 100 can be arranged and used in the vehicle as a hydraulic actuator for operating the clutch of the automatic transmission of the vehicle. Then, in the sealing device 100, the piston plate 11 is displaced in the axial direction by the application of the electric pressure by the lubricating oil for the automatic transmission (ATF (Automatic Transmission Fluid)) to the piston pressure chamber 21 and the release of the electric pressure. The clutch 50 is engaged or disengaged.

More specifically, when the piston pressure chamber 21 is pressurized by the oil pressure of the ATF supplied through the oil passage 41a, the piston plate 11 is displaced toward the canceller plate 12 while compressing the urging member 15. At that time, the clutch pressing portion 35 of the piston plate 11 presses the drive plate 51 of the clutch 50 to frictionally engage the drive plate 51 with the driven plate 52. In such a state, the clutch 50 is in the connected state.

Then, when the oil pressure of the piston pressure chamber 21 is released in the connected state of the clutch 50, the piston plate 11 is displaced so as to reduce the volume of the piston pressure chamber 21 due to the repulsive force of the compressed urging member 15. .. As a result, the clutch pressing portion 35 is separated from the drive plate 51, the pressing on the clutch 50 by the piston plate 11 is released, and the clutch 50 is disengaged.

Here, the piston plate 11 and the canceller plate 12 rotate together with the drive shaft, and the ATF introduced in the piston pressure chamber 21 is pressed toward the outer peripheral side by centrifugal force. Therefore, centrifugal pressure is generated in the piston pressure chamber 21, and this centrifugal pressure acts so as to prevent the return operation of the piston plate 11 by the urging member 15.

At this time, centrifugal hydraulic pressure is also generated in the ATF introduced through the oil passage 41b in the canceller hydraulic chamber 23 between the piston plate 11 and the canceller plate 12. Then, the centrifugal pressure in the canceller hydraulic chamber 23 and the centrifugal hydraulic pressure in the piston pressure chamber 21 are substantially in equilibrium. Therefore, when the application of the hydraulic pressure to the piston pressure chamber 21 is released, it is possible to avoid hindering the return operation of the piston plate 11 due to the centrifugal hydraulic pressure in the piston pressure chamber 21, and the return of the piston plate 11 by the urging member 15 can be avoided. The operation (that is, the disengagement of the clutch 50) is smoothly performed.

As described above, the piston plate 11 is displaced in the axial direction thereof, and the clutch 50 is engaged or disengaged. When the piston plate 11 operates in this way, the enlarged diameter tapered surface 40 is formed on the side surface 10a of the recess 10 of the piston plate 11, so that the sliding resistance of the canceller plate 12 is reduced. As a result, the sealing device 100 improves the operability of the piston plate 11.

Hereinafter, the present invention will be specifically described based on examples, but the present invention is not limited to these examples.

(Example 1)
A disk-shaped sealing device as shown in FIG. 1 was manufactured. The sealing device was equipped with a piston plate, a canceller plate, and a canceller seal. The side surface of the concave portion formed in the central portion of the piston plate has a tapered surface whose diameter increases from the opening side of the concave surface toward the bottom surface side. The canceller seal was slidably in contact with the tapered surface (diameter-expanded tapered surface). Specifically, the canceller seal was slidably contacted within the working distance S of the enlarged diameter tapered surface. That is, in the range of the working distance S of the enlarged diameter tapered surface of the piston plate, the tightening allowance with the canceller seal was large on the opening side of the recess, and the tightening allowance with the canceller seal was small on the bottom surface side.

In the sealing device of the first embodiment, the tapered surface as described above is formed in the piston plate, so that the sliding resistance of the canceller plate is reduced when the piston plate is operated, and the operability of the piston plate is improved.

The sealing device of the present invention can be adopted as a sealing device used for, for example, a clutch switching unit of an automatic transmission.

10,110: concave part, 10a, 110a: side surface of concave part, 11,111: piston plate, 11a, 12a: through hole, 12b: outer ring part, 12: canceller plate, 15: urging member, 18: opening, 19 : Bottom surface, 20: Housing, 21: Piston pressure chamber, 23: Canceller hydraulic chamber, 29: R surface, 30: Canceller seal, 31: Inner peripheral flange part, 32: Inner cylinder part, 33: Pressure receiving plate part, 34: Outer cylinder part, 34a: inner peripheral surface, 35: clutch pressing part, 37: inner peripheral seal lip, 38: outer peripheral seal lip, 40: enlarged diameter tapered surface, 41: inner peripheral cylinder part, 41a, 41b: oil passage, 42: Outer cylinder, 50: Clutch, 51: Drive plate, 52: Driven plate, 61: Straight surface, 62: Step, 100, 200: Sealing device, L: Straight line parallel to central axis O, O: Central axis , S: Working distance.

Claims (5)

An annular piston plate disposed in a housing that forms a piston pressure chamber with the housing and has a bottomed recess.
An annular canceller plate that forms a canceller hydraulic chamber together with the recess of the piston plate and reciprocates along the central axis of the piston plate.
A canceller seal is provided on the outer peripheral portion of the canceller plate so as to be slidably contacted with the side surface of the recess of the piston plate in the axial direction.
The piston plate has a tapered surface on the side surface of the concave portion of the piston plate whose diameter increases from the opening side of the concave surface toward the bottom surface side, and the canceller seal is slidably contacted with the tapered surface. Is a sealing device. In the side surface of the recess of the piston plate, the portion where the canceller seal is slidably contacted is the tapered surface, and the other portion is the central axis in the cross section of the piston plate in the central axis direction. The sealing device according to claim 1, which has a plane parallel to the above. The sealing device according to claim 2, wherein there is a step between the tapered surface and the surface of the piston plate parallel to the central axis. The sealing device according to claim 2, wherein the tapered surface and a surface of the piston plate parallel to the central axis are continuous surfaces. The sealing device according to any one of claims 1 to 4, which is used for a clutch switching unit of an automatic transmission.

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