JP2003139162A - Sealing device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce the weight of a sealing device while preventing the deformation of an end wall of a piston or an oil chamber for operating a clutch portion of an automatic transmission for an automobile. SOLUTION: In this sealing device, a pair of annular oil chambers 26, 33 is provided around an input shaft 11 with the piston 25 held therebetween. The oil chamber 26 is supplied with a pressurised oil to permit the movement of the piston 25. The oil chamber 33 is provided for generating oil pressure which cancels centrifugal oil pressure in the oil chamber 26. The end wall 72 defining the axial end of the oil chamber 33 consists of a defining plate 29 which has a thick portion 52 formed close to an inner diameter portion. Even when the oil pressure is applied to the end wall 72 for cancellation, the deformation of the defining plate 29 resulting from the oil pressure is prevented. The remaining portion 53 requiring low strength is made thinner and lighter. The sealing device 31 is utilized for a hydraulic linear motion mechanism 18 which operates a clutch 17 for switching power transmission of the automatic transmission 1 for the automobile.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a sealing device for sealing an oil chamber for operating a clutch portion in an automatic transmission of an automobile, for example.

[0002]

2. Description of the Related Art For example, the oil chamber for operating the clutch portion of the above-mentioned automatic transmission has a so-called one-piece structure in order to simplify and downsize the hydraulic oil supply path. It is configured as a working cylinder.
That is, the piston is slidably provided at the end of the oil chamber to which the pressure oil is supplied, and the spring for pushing the piston back to the opposite side of the oil chamber is provided. Also,
The above-mentioned oil chamber (also referred to as a piston hydraulic chamber) is formed in an annular shape around the rotary shaft, and the hydraulic oil supplied inside rotates with the rotation of the rotary shaft and receives a centrifugal force. Has become.

When the hydraulic oil receives a centrifugal force in this manner, a hydraulic pressure obtained due to this, a so-called centrifugal hydraulic pressure, is generated. This centrifugal oil pressure increases as the rotation speed of the rotating shaft increases. On the other hand, the pressing force of the spring that urges the piston is almost constant regardless of the rotation speed.
When the rotation speed of the rotating shaft increases, the force of the centrifugal hydraulic pressure becomes larger than the pressing force of the spring, and the operation of the piston becomes unstable. In order to prevent this, as shown in the schematic view of FIG. 5, there is a type in which a cancel hydraulic chamber 33 is provided on the opposite side of the piston hydraulic chamber 26 with the piston 25 interposed therebetween.

The cancel hydraulic chamber 33 is formed in an annular shape around the rotary shaft and is partitioned between the piston 25 and the disk-shaped end wall 72 facing the piston 25 so that oil flows in and accumulates therein. Has become. When the rotary shaft rotates, the hydraulic oil in the cancel hydraulic chamber 33 rotates together with the rotary shaft. As a result, centrifugal oil pressure is generated in the cancel oil pressure chamber 33. The centrifugal hydraulic pressure in the cancel hydraulic chamber 33 and the centrifugal hydraulic pressure in the piston hydraulic chamber 26 cancel each other in the axial direction.

However, the centrifugal hydraulic pressure in the cancel hydraulic chamber 33 increases as it goes radially outward of the end wall 72 that receives it. Therefore, for example, when only the inner diameter portion of the end wall 72 is supported, the maximum moment is generated in the portion of the end wall 72 near the inner diameter portion, and as a result, the deformation of the end wall 72 becomes large. In order to prevent such deformation, the end wall 72
It is necessary to increase the strength of the inner diameter of the. However, the end wall 7
2 is usually formed of a sheet metal member and has a uniform thickness as a whole. As a result, if the wall thickness is determined according to the portion requiring strength, the entire end wall 72 becomes thicker than necessary and becomes heavy. As a result, the entire device becomes large.

The above-mentioned piston has the same problem. Furthermore, there is a demand for weight reduction in automobiles. Further, a sealing device for general industrial equipment has the same problem. Therefore, an object of the present invention is to solve the above technical problems and to provide a sealing device that can be reduced in size and weight while suppressing the adverse effects of centrifugal hydraulic pressure.

[0007]

According to the invention described in claim 1, there is provided an annular oil chamber which is provided around a rotary shaft and in which internal oil receives a centrifugal force as the rotary shaft rotates. ,
And a ring-shaped partition plate made of sheet metal that partitions the axial end of the annular oil chamber extending in the radial direction of the rotating shaft, and the portion near the inner diameter of the partition plate is thicker than the rest. A sealing device is provided. It is possible to reduce the overall size and weight of the partition plate by thickening only the part of the partition plate that requires strength to prevent deformation and thinning the remaining part that does not require much strength. . Further, since the weight of the partition plate closer to the inner diameter portion can be suppressed more than that of the portion closer to the outer diameter portion, it is preferable to reduce the weight of the partition plate.

According to a second aspect of the present invention, there is provided the sealing device according to the first aspect, characterized in that axial movement of the inner circumference of the partition plate is restricted. A large bending moment may be applied to the inner circumference of such a partition plate due to the centrifugal hydraulic pressure, but the present invention can effectively prevent deformation due to this, and also achieve weight reduction. Therefore, the present invention can be effectively implemented. According to a third aspect of the present invention, in the sealing device according to the second aspect, the annular oil chamber includes annular first and second oil chambers arranged on both sides of the piston. Of the oil chamber moves the piston to the side of the second oil chamber by the pressure oil supplied to the second oil chamber, and the second oil chamber cancels the oil pressure caused by the centrifugal force of the oil in the first oil chamber. A partition plate constituted by an end wall of the second oil chamber facing the piston has a thicker portion near the inner diameter than the remaining portion. To provide a sealing device.

According to the present invention, the adverse effect of centrifugal oil pressure can be suppressed by a simple structure in which a pair of oil chambers are arranged. Moreover, it is possible to prevent the end wall of the second oil chamber from being deformed due to the centrifugal hydraulic pressure and to reduce the size of the pair of oil chambers, which tend to be bulky, with the lightweight end wall. According to a fourth aspect of the present invention, in the sealing device according to the third aspect, a second spring member is interposed between the end wall of the second oil chamber and the piston and biases the piston and the piston in a direction to move them away from each other. Provided is a sealing device which is housed in an oil chamber. According to the present invention, the space for accommodating the spring member is also used as the second oil chamber, so that further miniaturization can be achieved, and the deformation of the end wall due to the spring member is small. This can be prevented by the lightweight end wall.

According to a fifth aspect of the present invention, in the sealing device according to the third or fourth aspect, a seal member for sealing the second oil chamber is provided on the outer circumference of the end wall of the second oil chamber. Provided is a sealing device characterized by being provided. According to the present invention, the hydraulic pressure for canceling out can be efficiently increased by the simple structure of the seal member, and the deformation of the end wall due to the increased hydraulic pressure can be prevented by the small and lightweight end wall. According to a sixth aspect of the invention, in the sealing device according to the first aspect, a piston that operates by receiving the pressure in the annular oil chamber is provided at an axial end portion of the annular oil chamber. A partition plate constituted by the above-mentioned partition plate has a portion closer to the inner diameter portion thicker than the remaining portion. According to the present invention, in order to prevent deformation due to centrifugal hydraulic pressure, it is possible to reduce the size and weight of a piston that tends to be heavy and large in size.

The invention according to claim 7 is the invention according to claims 3 to 6.
The sealing device according to any one of claims 1 to 4, wherein the piston operates a clutch for power transmission of an automobile. That is, by using the partition plate of the present invention for a clutch that is usually provided in an automobile, it is possible to contribute to weight reduction of the automobile. The invention described in claim 8 provides the sealing device according to claim 7, wherein the clutch is used in an automatic transmission. That is, in the automatic transmission, the clutch may be provided at a plurality of positions, and the weight saving effect of the present invention can be increased.

The invention according to claim 9 is the invention according to claims 1 to 8.
The sealing device according to any one of claims 1 to 5, wherein a portion of the partition plate near the inner diameter portion includes a bent portion having a crank-shaped cross section. According to the present invention, the bent portion has a three-dimensional structure and can effectively prevent the partition plate from being deformed. The invention according to claim 10 relates to claims 1 to 9.
The sealing device according to any one of claims 1 to 4, wherein a portion of the partition plate near the inner diameter portion includes a folded portion having a substantially U-shaped cross section. According to this invention, the folded-back portion has a three-dimensional structure and can effectively prevent the partition plate from being deformed.

[0013]

DETAILED DESCRIPTION OF THE INVENTION A clutch portion of an automatic transmission including a sealing device according to an embodiment of the present invention will be described below with reference to the drawings. FIG. 1 is a schematic diagram showing a schematic configuration of an automatic transmission. The automatic transmission 1 is provided for power transmission between the engine 3 of the automobile 2 and the drive wheels 4, and
Is transmitted to the wheel 4 in a gear shift state or a direct connection state. The input shaft 11 of the automatic transmission 1 is connected to the engine 3 via a torque converter 5 that functions as a fluid coupling so that power can be transmitted, and the output shaft 12 has a coupling 6,
It is connected to the drive wheels 4 via a shaft 7 or the like so as to be able to transmit power.

The automatic transmission 1 includes an input shaft 11 and an output shaft 1.
2, a transmission mechanism 13 including a planetary gear mechanism interposed between the input shaft 11 and the output shaft 12 to transmit power, and a clutch portion 14 provided in the transmission mechanism 13. The automatic transmission 1 includes a clutch portion 1 in a housing 15 thereof.
4 and the speed change mechanism 13 are accommodated. The planetary gear mechanism of the speed change mechanism 13 has a sun gear, a planetary gear and its carrier, and a ring gear. Depending on which of these gears is used as the input gear, the output gear, or the fixed gear,
By changing the power transmission path, it is possible to change the gear ratio and the output rotation direction during power transmission. The speed change mechanism 13 may have a single planetary gear mechanism or may have a plurality of planetary gear mechanisms. Further, the power transmission paths between the plurality of planetary gear mechanisms may be different. Further, a known mechanism other than the planetary gear mechanism may be used.

The clutch portion 14 selectively switches a plurality of switchable power transmission paths of the speed change mechanism 13. This makes it possible to change the gear ratio of the speed change mechanism 13 and switch the rotation direction of the output shaft 12. Figure 2
It is sectional drawing which shows the clutch part of an automatic transmission. The clutch portion 14 is provided at a plurality of locations corresponding to the power transmission path of the speed change mechanism 13. For example, the clutch unit 14 shown in FIG. 2 includes the input shaft 11 and the sun gear 16 of the planetary gear mechanism.
(Only a part is shown), and achieves or cuts off power transmission between them. The rotational force during power transmission is transmitted from the input shaft 11 to the output shaft 12 via the sun gear 16, planetary gear, and ring gear of the planetary gear mechanism, during which deceleration is performed.

The clutch section 14 shown in FIG. 2 will be described below. The present invention can be applied to the clutch portion 14 that is provided around the rotation shaft so as to be integrally rotatable with the rotation shaft. Such a clutch portion 14 can be applied to other clutch portions 14 included in the automatic transmission 1. The present invention may be applied. The clutch unit 14 includes a multi-plate clutch 17,
It has a hydraulic direct acting mechanism 18 as an operating mechanism for operating the clutch 17. Each of these parts 17 and 18 of the clutch part 14 has an annular outer shape around the input shaft 11. Hereinafter, the axial direction of the input shaft 11 is simply referred to as the axial direction, and the same applies to the circumferential direction and the radial direction. Further, in each drawing, a center axis C of the input shaft 11, an arrow S indicating the axial direction, and an arrow R indicating the radial direction are illustrated as necessary.

The clutch 17 has an input side member 21, an output side member 22 and an operating member 23. The input side member 21 includes a large number of discs connected to each other. The large number of discs are arranged along the axial direction so as to face each other, and are arranged at predetermined intervals. The output side member 22 includes a large number of discs that are connected to face each other and that are arranged in the axial direction at predetermined intervals. Output side member 2
The large number of disks of 2 and the large number of disks of the input side member 21 are
They are arranged alternately in the axial direction while facing each other. The operation member 23 is arranged to be engageable with the output side member 22 so that the output side member 22 can be moved in the axial direction. Further, the input member 21 may be moved by the operation member 23. By using the operating member 23 to move the output-side member 22 to one side along the axial direction, the disks of both members 21, 22 are brought into contact with each other, and power transmission of the clutch 17 is achieved. Further, the output side member 22 is moved in the opposite direction to separate the disks from each other,
Release power transmission.

The clutch 17 is arranged at a radially outer position inside the housing 15. Such an arrangement is advantageous in that the power transmission capacity is ensured and the space saving in the axial direction is achieved. The hydraulic direct drive mechanism 18 is arranged radially inward of the clutch 17. The hydraulic direct-acting mechanism 18 functions as a hydraulic cylinder for enabling the operating member 23 of the clutch 17 to be operated from the outside using hydraulic pressure. This hydraulic cylinder can axially reciprocate the extending portion 47 of the movable plate member 24 serving as an output member.

The hydraulic linear motion mechanism 18 has an annular first oil chamber 26 and a second oil chamber 33 which are arranged on both sides of the movable plate member 24 in the axial direction with the piston 25 interposed therebetween. The hydraulic direct-acting mechanism 18 is a so-called one-effect hydraulic cylinder, and the pressure oil is supplied only to the first oil chamber 26. The first oil chamber 26 moves the piston 25 to the second oil chamber 33 side by the pressure oil supplied inside. Then, the second oil chamber 33 is, as described later, the first oil chamber 2
A hydraulic pressure for canceling the centrifugal hydraulic pressure caused by the centrifugal force of the oil in 6 is generated. Here, the centrifugal hydraulic pressure is the total pressure generated by the influence of the centrifugal force exerted on the oil in the oil chamber.

The hydraulic linear motion mechanism 18 includes an oil chamber partition member 27 that partitions most of the first oil chamber 26, and the first oil chamber 26.
The movable plate member 24, which is slidably supported in the oil chamber partitioning member 27 along the axial direction while partitioning the remaining end portion of
A spring member 2 formed of a compression coil spring that biases the piston 25 in the axial direction toward the first oil chamber 26 side.
8 and a partition plate 29 that receives the spring member 28 on the opposite side of the piston 25. Each of these members 27,
25, 28 and 29 are arranged in this order in the axial direction.

An oil passage 30 is provided between the housing 15 and the inner circumference of the oil chamber partitioning member 27. This oil passage 30
Corresponding to the above, a communication hole 43 is formed on the inner circumference of the oil chamber partitioning member 27. The communication hole 43 communicates the oil passage 30 with the internal space 35 of the first oil chamber 26, and supplies hydraulic oil from the outside to the internal space 35. When high-pressure hydraulic oil is supplied to the first oil chamber 26 via the oil passage 30, the piston 25 moves axially in the second oil chamber 33 while resisting the elastic repulsive force of the spring member 28. Move to the side. In addition, the oil passage 30
When the pressure of the hydraulic oil therein is reduced, the piston 25 is urged by the elastic repulsive force of the spring member 28 and pushed back toward the first oil chamber 26 side along the axial direction. The operating member 23 of the clutch 17 is provided on the extending portion 47 of the movable plate member 24.
Is integrally formed, and the clutch 17 can be operated by controlling the pressure of the hydraulic oil in the oil passage 30.

The first oil chamber 26 is provided around the input shaft 11 as a rotary shaft and is divided into an annular shape. The first oil chamber 26 includes a pair of end walls 61 and 62 that define both axial ends and are opposed to each other, and an annular inner peripheral wall 63 and an outer peripheral wall 64 that define an inner circumference and an outer circumference and extend in the axial direction. , And the inner space 35 defined by surrounding each of the walls 61, 62, 63, 64. First oil chamber 2
6, one end wall 61, an inner peripheral wall 63, and an outer peripheral wall 64
Are integrally formed by the main body portion 40 of the oil chamber partitioning member 27. The other end wall 62 is formed by the piston 25. The first oil chamber 26 functions as a sealing device 31 that seals the internal space 35.

The oil chamber partitioning member 27 is an annular sheet metal member provided around the input shaft 11. Oil chamber partitioning member 27
The main body 40 has a groove-shaped cross section and is arranged in an inner portion in the radial direction, and an extending portion 42 extending from an outer peripheral edge of the main body 40. The input side member 21 of the clutch 17 is fixed to the extending portion 42. The piston 25 is fitted inside the groove of the main body 40. The inner circumference of the main body 40 is fixed so as to rotate integrally with the input shaft 11, and is restricted from moving in the axial direction with respect to the input shaft 11.

The movable plate member 24 is an annular sheet metal member provided around the input shaft 11. The movable plate member 24 includes the above-described piston 25 that extends in a curved shape in the radial direction, a cylindrical portion 48 that extends in the axial direction from the outer peripheral edge of the piston 25, and an outer side in the radial direction from the axial end portion of the cylindrical portion 48. It has the above-mentioned extended part 47 extended. The outer periphery of the cylinder portion 48 and the inner periphery of the piston 25 are arranged so that the main body portion 40 of the oil chamber partitioning member 27
It is in sliding contact with different parts of the inner circumference. The movable plate member 24 is
It has a bent cross-section and is reinforced.

The spring member 28 is housed in the second oil chamber 33, and is interposed between the piston 25 and the partition plate 29 in a compressed state so that the two members 25, 29 are separated from each other.
Energize 5,29. A plurality of spring members 28 are arranged dispersedly in the circumferential direction. The spring member 28 is provided to make the hydraulic cylinder a one-effect type. As a result, the path for supplying the pressure oil can be simplified, and thus the structure of the automatic transmission 1 can be simplified. In addition, the space for the route can be reduced, and the size can be reduced. The spring member 28 may be, for example, a leaf spring integrally formed with the partition plate 29, and in short, a known configuration that generates an elastic force that moves the piston 25 away from the partition plate 29 can be used.

The partition plate 29 is an annular sheet metal member provided around the input shaft 11. The partition plate 29 faces the piston 25 and is arranged side by side along the axial direction. The inner periphery 50 of the partition plate 29 rotates integrally with the input shaft 11 and its axial movement with respect to the input shaft 11 is restricted by the retaining ring 32. A seal member 34 that seals an internal space 36 of the second oil chamber 33 is provided on the outer periphery 56 of the partition plate 29. The seal member 34 seals between the outer circumference 56 of the partition plate 29 and the inner circumference of the tubular portion 48 of the movable plate member 24 over the entire circumference in the circumferential direction. The seal member 34 is slidable in the axial direction with respect to the inner circumference of the tubular portion 48, and can seal the second oil chamber 33 even if the piston 25 moves.

The second oil chamber 33 is provided around the input shaft 11 as a rotating shaft and is divided into an annular shape. The second oil chamber 33 has a pair of end walls 71 and 72 that partition both ends in the axial direction and face each other, an annular inner peripheral wall 73 and an outer peripheral wall 74 that partition the inner circumference and the outer circumference and extend in the axial direction, The interior space 36 is defined by surrounding each of these walls 71 to 74. One end wall 71 has a piston 25
It is composed of The outer peripheral wall 74 is the tubular portion 4 of the movable plate member 24.
It is composed of 8. The inner peripheral wall 73 is configured by a part of the piston 25 and a part of the inner peripheral portion 44 of the oil chamber partitioning member 27. The other end wall 72 is formed by the partition plate 29. The second oil chamber 33 functions as the sealing device 31 that seals the internal space 36.

The second oil chamber 33 is provided with a passage for allowing oil to flow into the internal space 36. That is, the inner peripheral wall 73 of the second oil chamber 33 and its adjacent portion, for example,
An opening 51 is formed on the inner periphery 50 of the partition plate 29. Through this opening 51, the internal space 36 communicates with the outside (the space on the right side of the partition plate 29 in FIG. 2) around it. The inside of the housing 15, which is the outside of the second oil chamber 33, is filled with oil, and this oil can enter and leave the internal space 36 through the opening 51. The passage may be communicated with the outside around the second oil chamber 33, or may be communicated with a low pressure side tank or the like.

As the input shaft 11 rotates, the second oil chamber 33
The hydraulic oil inside receives a centrifugal force and is pushed outward in the radial direction inside the second oil chamber 33. Along with this, the hydraulic oil enters the internal space 36 through the opening 51, while the outer periphery is sealed by the seal member 34, so the centrifugal hydraulic pressure in the second oil chamber 33 increases. As a result, the centrifugal oil pressure of the first oil chamber 26 and the centrifugal oil pressure of the second oil chamber 33 act on the piston 25 in opposite directions to cancel the axial components of the centrifugal oil pressure. As a result, the force exerted on the piston (the portion left unmarked in the arrow in FIG. 5) can be made to have a magnitude suitable for suppressing the influence of centrifugal force and stably operating the piston.

In the conventional clutch portion having no second oil chamber 33, a valve is provided in the first oil chamber so that the hydraulic oil in the first oil chamber is discharged when pressure oil is not supplied. , It prevents the hydraulic oil from being subjected to centrifugal oil pressure. But,
When the piston is moved to operate the clutch, it takes time to fill the empty first oil chamber with hydraulic oil, so that the responsiveness of the clutch operation is low. On the other hand, in the embodiment of the present invention, since the second oil chamber 33 can prevent the centrifugal hydraulic pressure from increasing, it is not necessary to provide a conventional valve or the like for discharging the oil from the first oil chamber, The structure can be simplified. Further, even if there is hydraulic oil in the first oil chamber 26 when pressure oil is not supplied, there is no possibility that the piston 25 will move due to the centrifugal hydraulic pressure of this oil. Therefore, with the piston 25 returned by the spring member 28, the first oil chamber 2
Since a minimum amount of oil can be contained in the hydraulic oil 6, the hydraulic pressure of the first oil chamber 26 can be quickly increased by supplying the hydraulic oil for a short time when the piston 25 is moved by the hydraulic oil. Therefore, the shift operation is not delayed, and the responsiveness of the clutch operation can be improved. Moreover, the operation of the piston 25, and thus the speed change operation, is performed as described above.
It can be made smooth without the influence of centrifugal oil pressure in the oil chamber 33.

On the other hand, in the end wall 72 of the second oil chamber 33, the centrifugal hydraulic pressure increases as it goes outward in the radial direction. As a result, the end wall 72 is easily deformed. Particularly, in the embodiment of the present invention, the partition plate 29 that constitutes the small and lightweight end wall 72 while achieving high strength capable of preventing such deformation due to centrifugal hydraulic pressure is realized. The present invention can be applied to the piston 25 as a partition plate that partitions the end wall 62 of the first oil chamber 26 as described later. Hereinafter, the partition plate 2 that constitutes the end wall 72
9 will be mainly described.

In the present invention, in the partition plate 29, the portion 52 near the inner diameter portion is made thicker than the remaining portion 53 excluding this portion 52. Here, the portion 52 near the inner diameter portion includes an inner diameter portion forming the inner circumference 50 and a portion adjacent to the inner diameter portion and having a predetermined distance in the radial direction. For example, in the end wall 29 shown in FIG. 3, a portion 52 within a range from the inner circumference 50 to a position separated by a predetermined distance B in the radial direction.
The thickness (in the range indicated by B) is set to a large value B1, and the entire portion except this portion is set to a thin value, for example, the thickness is set to a thin value B2.
(B1> B2).

As a result, only the portion 52 near the inner diameter of the partition plate 29, which requires strength, is thickened to prevent deformation, while the remaining portion 53, which does not require much strength, is thinned to reduce the thickness of the partition plate 29. The overall size and weight can be reduced. Further, the part 5 near the inner diameter of the partition plate 29
If it is 2, than the remaining portion 53 that is closer to the outer diameter portion,
It is preferable to reduce the weight of the partition plate 29 because it is possible to suppress an increase in weight due to the increase in thickness.

The thick portion 52 as described above can be easily and inexpensively realized by a plastic working method such as press forming of a metal plate material. In particular, when a thick part is realized by plastic working such as press forming, the metal structure on the surface can be maintained, and compared with the case of cutting,
High strength can be obtained. Also, high strength can be obtained by work hardening associated with plastic working. Partition board 29
The portion 52 closer to the inner diameter portion may be formed of a straight portion 57 having a constant wall thickness and extending straight in the radial direction, as in the embodiment shown in FIG. The wall thickness of the straight portion 57 may be constant in the radial direction, or may change linearly, for example. In this case, the structure can be simplified, and it is preferable to achieve miniaturization.

In the partition plate 29 having the straight portion 57, a step may be formed at the boundary between the thick portion and the thin portion. It is considered that this step is formed on the surface of the partition plate 29 which is at least one of the inside and the outside of the second oil chamber 33, and an inclined surface may be formed instead of the step. In the embodiment shown in FIG. 3, the portion 52 of the partition plate 29 near the inner diameter portion includes a bent portion 54 having a crank-shaped cross section. The bent portion 54 has a three-dimensional structure and has a partition plate 29.
Can be effectively prevented from being deformed. Moreover, the effect of improving the strength for preventing deformation can be increased.

Further, the crank shape of the bent portion 54 is axially oriented from the inside of the second oil chamber 33 to the outside through the partition plate 29 as it goes from the inner portion to the outer portion in the radial direction. It is formed so as to extend. In this case, the bending moment applied to the partition plate 29 by the centrifugal hydraulic pressure of the second oil chamber 33 can be relaxed by the moment due to the centrifugal force applied to the partition plate 29 itself. Also, FIG.
As shown in, the portion 52 near the inner diameter of the partition plate 29 is
You may make it include the folding | returning part 55 of a substantially U-shaped cross section. The folding part 55 has a three-dimensional structure and has a partition plate 2
The deformation of 9 can be effectively prevented. Moreover, the effect of improving the strength for preventing deformation can be further increased.

The folded-back portion 55 is preferably formed such that the top portion having a substantially U-shaped cross section projects toward the inside of the second oil chamber 33. Furthermore, the folded-back portion 55 has the same tendency as the crank shape of the bent portion 54 described above, that is,
It is preferable to have a shape that extends outward in both the radial direction and the axial direction. As a result, the second oil chamber 33
The bending moment generated by the centrifugal hydraulic pressure of
It can be relaxed by the moment generated by the centrifugal force applied to itself.

The cross-sectional shape of the folded-back portion 55 may be V-shaped, groove-shaped or the like in addition to the substantially U-shaped shape. Particularly, in the case of the substantially U-shaped shape,
It is preferable because stress concentration is unlikely to occur and press molding is easy. In addition, the bent portion 54 and the folded-back portion 55 have the partition plate 29.
It is preferable to dispose a predetermined distance radially outward from the inner circumference 50. That is, when the centrifugal hydraulic pressure is applied to the folded-back portion 55 and the like, stress concentration may occur. However, this stress concentration and the stress generated on the inner circumference 50 due to the bending moment are prevented from overlapping and the stress is dispersed. Can be made. For example, the radial positions of the bent portion 54 and the folded portion 55 are arranged at the outermost radial positions of the thick portion.

In each of the embodiments shown in FIGS. 2 to 4, the partition plate 29 extends in the direction orthogonal to the axial direction, but it may extend obliquely with respect to the axial direction. Further, only a part of the partition plate 29 may extend along the axial direction. Further, in the case of the partition plate 29 whose axial movement of the inner circumference 50 is restricted, a large bending moment is applied to the inner circumference 50 by the centrifugal hydraulic pressure, and the partition plate 29 tends to be easily deformed. In particular, when the inner periphery 50 of the partition plate 29 is regulated and the outer periphery 56 thereof is slidable, the above tendency becomes strong. Further, when the partition plate 29 is pressed by the spring member 28, the above-mentioned tendency is further strengthened. In the embodiment of the present invention, in accordance with this tendency, the portion 52 near the inner diameter portion including the inner circumference 50 is made thick, and the portion requiring strength can be directly and efficiently reinforced, deformation can be prevented, and the weight is light. Can be achieved. Therefore, the present invention can be effectively implemented.

Further, according to the present invention, the end wall 72 of the second oil chamber 33 is provided.
It is suitable for the partition plate 29 constituting the. That is, the adverse effect of the centrifugal hydraulic pressure can be suppressed by a simple configuration in which the pair of oil chambers 26 and 33 are arranged. Moreover, according to the present invention, the small and lightweight partition plate 29 can achieve the strength required to prevent the deformation of the end wall 72, which is necessary for the hydraulic pressure for canceling the centrifugal hydraulic pressure. Furthermore, the present invention can mitigate the tendency of the pair of oil chambers 26 and 33 to become bulky.

A partition plate 29 provided with a seal member 34 is also provided.
The present invention is especially preferred. That is, with the simple structure of the seal member 34, the centrifugal hydraulic pressure of the second oil chamber 33 can be efficiently increased, and the deformation of the partition plate 29 due to the increased hydraulic pressure is small and lightweight. Can be prevented with. The present invention is also preferable for the partition plate 29 that receives the spring member 28. That is, the partition plate 2 caused by the spring member 28
The deformation of 9 can be prevented by the small and lightweight partition plate 29. Moreover, the spring member 28 is accommodated in the second oil chamber 33, and the spring member 28
The second oil chamber 33 also serves as a space for accommodating the oil, so that further miniaturization can be achieved.

The present invention may be applied to the piston 25 described above. That is, it is conceivable to thicken the portion of the piston 25 near the inner diameter portion and thin the remaining portion. As a result, the strength and weight of the piston 25 can be increased. For example, by reducing the weight of the piston 25, quick operation of the piston 25 can be realized. Further, when the oil pressure for operating the piston 25 is applied, the centrifugal oil pressure of the first oil chamber 26 becomes high. Therefore, in order to prevent the deformation of the piston 25, the piston 25 becomes thick, and it is easy to be heavy and large in size. There is a tendency. However, according to the present invention, the deformation of the piston 25 can be prevented, and further, the weight and size reduction of the piston 25, the members 24 and 27 for supporting the piston 25, and the walls of the oil chambers 26 and 33 around the piston 25 can be achieved. it can.

Here, even when the second oil chamber 33 is provided, it is effective to apply the present invention to the piston 25. This is because any piston 25 receives high hydraulic pressure to operate. Further, a high pressure is applied to the first oil chamber 26 on one side of the piston 25, and a low pressure is applied to the second oil chamber 33. In this respect, it is assumed that the influence of centrifugal force generated on the hydraulic pressure is different on both sides of the piston 25. As a result, even when the second oil chamber 33 is provided, the hydraulic pressure applied to the piston 25 may change in the radial direction.

The piston 25 to which the present invention is applied and the partition plate 29 facing the piston 25 are preferably used for operating the clutch 17 for power transmission of the automobile. That is, since the clutch is usually provided in an automobile, the present invention can contribute to weight reduction of the automobile. Further, the clutch 17 is more preferably used for the automatic transmission 1. This is because the automatic transmission 1 may have the clutch 17 at a plurality of positions, and the weight saving effect can be increased.

The present invention may be applied to a sealing device for sealing a liquid chamber used in industrial equipment other than automobiles. In short, an annular oil chamber that is provided around the rotating shaft and receives the centrifugal force of the oil inside as the rotating shaft rotates and an axial end of the annular oil chamber that extends in the radial direction of the rotating shaft are defined. In the sealing device provided with an annular partition plate made of sheet metal, the part of the partition plate near the inner diameter portion may be thicker than the remaining part. The oil chamber here corresponds to the first oil chamber 26 and the second oil chamber 33 in the embodiment of the present invention, and the partition plate is the piston 2
5 and the partition plate 29, and the rotating shaft corresponds to the input shaft 11.

Besides, various modifications can be made within the scope of the claims of the present invention.

[Brief description of drawings]

FIG. 1 is a schematic diagram showing power transmission of an automobile having an automatic transmission including a sealing device according to an embodiment of the present invention.

FIG. 2 is an enlarged cross-sectional view of a main part including a clutch part of an automatic transmission.

3 is an enlarged cross-sectional view showing a modified example of a portion of the end wall near the inner diameter portion of FIG.

FIG. 4 is an enlarged cross-sectional view showing another modification of the inner wall portion of the end wall of FIG.

FIG. 5 is a schematic diagram of a cylinder and a piston for explaining centrifugal hydraulic pressure.

[Explanation of symbols]

1 automatic transmission 11 Input shaft (rotating shaft) 17 clutch 25 piston (compartment plate) 26 First oil chamber 28 Spring member 29 partition plates 31 Sealing device 33 Second oil chamber 34 Seal member 52 Part near the inner diameter of the partition plate 53 Remaining part of partition plate 54 Bend 55 Folding part 56 Perimeter of partition plate 62 End Wall of First Oil Chamber (Axial End of Oil Chamber) 72 End Wall of Second Oil Chamber (Axial End of Oil Chamber) R radial direction S axis direction

Continued front page    F term (reference) 3J057 AA04 BB04 CA09 DC05 DC07                       DC10 EE05 GA02 GA11 HH02                       JJ04

Claims (10)

[Claims] 1. An annular oil chamber which is provided around a rotary shaft and receives centrifugal force of internal oil as the rotary shaft rotates, and an axial end portion of the annular oil chamber which extends in a radial direction of the rotary shaft. An annular partition plate made of a sheet metal for partitioning the partition plate, wherein a portion near the inner diameter of the partition plate is thicker than the remaining portion. 2. The sealing device according to claim 1, wherein axial movement of an inner circumference of the partition plate is restricted. 3. The sealing device according to claim 2, wherein the annular oil chamber includes annular first and second oil chambers arranged on both sides of the piston, and the first oil chamber is , The piston is moved to the second oil chamber side by the pressure oil supplied inside, and the second oil chamber generates a hydraulic pressure for canceling the hydraulic pressure caused by the centrifugal force of the oil in the first oil chamber. The sealing device is characterized in that the partition plate constituted by the end wall of the second oil chamber facing the piston has a portion near the inner diameter portion thicker than the remaining portion. 4. The sealing device according to claim 3, wherein a spring member which is interposed between the end wall of the second oil chamber and the piston and biases the piston and the piston in a direction away from each other is housed in the second oil chamber. A sealing device characterized by being 5. The sealing device according to claim 3 or 4, wherein a seal member for sealing the second oil chamber is provided on the outer periphery of the end wall of the second oil chamber. Sealing device. 6. The sealing device according to claim 1, wherein a piston that operates by receiving the pressure in the annular oil chamber is provided at an axial end portion of the annular oil chamber, and is constituted by this piston. A sealing device, wherein the partition plate has a thicker portion near its inner diameter than the rest. 7. The sealing device according to claim 3, wherein the piston operates a clutch for power transmission of an automobile. 8. The sealing device according to claim 7, wherein the clutch is used in an automatic transmission. 9. The sealing device according to claim 1, wherein a portion of the partition plate near the inner diameter portion includes a bent portion having a crank-shaped cross section. 10. The sealing device according to any one of claims 1 to 9, wherein a portion of the partition plate near the inner diameter is substantially U-shaped in cross section.
A sealing device comprising a folded portion having a character shape.