JP4969169B2 - Sealing device - Google Patents

Sealing device Download PDF

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JP4969169B2
JP4969169B2 JP2006196532A JP2006196532A JP4969169B2 JP 4969169 B2 JP4969169 B2 JP 4969169B2 JP 2006196532 A JP2006196532 A JP 2006196532A JP 2006196532 A JP2006196532 A JP 2006196532A JP 4969169 B2 JP4969169 B2 JP 4969169B2
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oil
piston seal
sealing device
flow
opening
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JP2008025652A (en
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政則 亀岡
俊彰 山本
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Koyo Sealing Techno Co Ltd
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Koyo Sealing Techno Co Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D25/00—Fluid-actuated clutches
    • F16D25/06—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch
    • F16D25/062—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces
    • F16D25/063—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially
    • F16D25/0635—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs
    • F16D25/0638—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs with more than two discs, e.g. multiple lamellae
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2300/00—Special features for couplings or clutches
    • F16D2300/08—Details or arrangements of sealings not provided for in group F16D3/84

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
  • Sealing With Elastic Sealing Lips (AREA)

Description

この発明は、軸方向に摺動可能なピストンシールを備えた密封装置に関する。   The present invention relates to a sealing device provided with a piston seal slidable in the axial direction.

従来、例えば自動車などの自動変速機（ＡＴ）の動力接続部において、特許文献１に示しているように、作動油の供給と排出とにより軸方向に摺動可能な環状のピストンシールを備えた密封装置が用いられている。図８はこのような密封装置の従来例を示す断面図である。この密封装置は、環状のキャンセルプレート４１及び環状のピストンシール４２が軸方向に対向して軸部４３に外嵌し、両者の間にキャンセル室４４を形成している。そして、このキャンセル室４４に通じる油孔４５が軸部４３に形成されており、この油孔４５を通じてキャンセル室４４への作動油の供給とキャンセル室４４から作動油の排出とを選択的に行うことにより、ピストンシール４２を軸方向に往復摺動させることができる。そして、このピストンシール４２が多板クラッチ４８を押圧し、動力接続部において駆動力の伝達がなされる。   Conventionally, for example, in a power connection part of an automatic transmission (AT) such as an automobile, as shown in Patent Document 1, an annular piston seal that can slide in an axial direction by supplying and discharging hydraulic oil has been provided. A sealing device is used. FIG. 8 is a sectional view showing a conventional example of such a sealing device. In this sealing device, an annular cancel plate 41 and an annular piston seal 42 are externally fitted to a shaft portion 43 so as to face each other in the axial direction, and a cancel chamber 44 is formed therebetween. An oil hole 45 communicating with the cancel chamber 44 is formed in the shaft portion 43, and the supply of hydraulic oil to the cancel chamber 44 and the discharge of hydraulic oil from the cancel chamber 44 are selectively performed through the oil hole 45. As a result, the piston seal 42 can be slid back and forth in the axial direction. The piston seal 42 presses the multi-plate clutch 48, and the driving force is transmitted at the power connection portion.

特開２００２−１３９１５５号公報JP 2002-139155 A

しかし、従来の密封装置では、ピストンシール４２のキャンセルプレート４１側への摺動のストロークが大きくなると、図８の破線で示しているように、ピストンシール４２の内周側にある短筒部４６の先端部が油孔４５の開口部４７の径方向外側に位置して当該開口部４７を覆ってしまう。この場合、キャンセル室４４と油孔４５との間における作動油の流れが阻害され、ピストンシール４２の作動応答性が低下し、自動変速機の動力接続部における動力伝達の応答性が低下してしまうおそれがある。
そこでこの発明は、前記問題点に鑑みてなされたものであり、ピストンシールがキャンセルプレート側に摺動し、ピストンシールの短筒部が油孔の開口部の径方向外側に位置しても、キャンセル室と油孔との間における作動油の流れを確保でき、作動応答性が低下してしまうことを防止できる密封装置を提供することを目的とする。 However, in the conventional sealing device, when the stroke of sliding of the piston seal 42 toward the cancel plate 41 increases, as shown by a broken line in FIG. The front end of the oil hole 45 is located on the radially outer side of the opening 47 of the oil hole 45 and covers the opening 47. In this case, the flow of hydraulic oil between the cancel chamber 44 and the oil hole 45 is obstructed, the operation responsiveness of the piston seal 42 is lowered, and the responsiveness of power transmission at the power connection portion of the automatic transmission is lowered. There is a risk that.
Therefore, the present invention has been made in view of the above problems, and even when the piston seal slides toward the cancel plate and the short cylinder portion of the piston seal is located radially outside the opening of the oil hole, It is an object of the present invention to provide a sealing device that can secure a flow of hydraulic oil between a cancellation chamber and an oil hole and can prevent a reduction in operation responsiveness.

前記目的を達成するためのこの発明の密封装置は、軸部に外嵌する環状のキャンセルプレートと、円板状の本体部とこの本体部の内周に前記キャンセルプレート側に延びる短筒部とを有し、この短筒部を前記軸部に外嵌した状態で前記キャンセルプレートとの間で環状のキャンセル室を形成する環状のピストンシールとを備え、前記軸部の外周面に開口部を有する油孔を通じて前記キャンセル室への作動油の供給と当該キャンセル室からの作動油の排出とを選択的に行うことにより、前記ピストンシールを軸方向に往復摺動させる密封装置であって、前記開口部は、前記軸部に周方向等間隔で複数形成され、前記ピストンシールの前記短筒部の先端部に、当該ピストンシールが前記キャンセルプレート側に摺動した状態で前記油孔の開口部に臨ませて作動油を流通させる流油路が周方向に等間隔で複数設けられ、前記流油路は、前記先端部の内周面から外周面へと直線的に連続した流路であって、前記ピストンシールが前記キャンセルプレート側に摺動した状態で、前記油孔から作動油を当該流油路を通じて前記キャンセル室へ径方向外側に向かって直線的に流す流路であり、前記流油路の数は、前記開口部の数よりも多く、前記流油路の周方向の寸法は、前記開口部の周方向の寸法よりも大きいことを特徴とする。
この構成によれば、ピストンシールがキャンセルプレート側に摺動することにより、ピストンシールの短筒部が油孔の開口部の径方向外側に位置しても、その短筒部に形成した流油路を油孔の開口部に臨ませて、当該流油路によって油孔とキャンセル室との間で作動油を流通させることができる。このため、ピストンシールの短筒部が油孔の開口部を塞いでしまうことを防ぎ、油孔とキャンセル室との間の作動油の流れを確保でき、ピストンシールの作動応答性が低下することを防止できる。 In order to achieve the above object, a sealing device of the present invention includes an annular cancel plate that fits around a shaft portion, a disc-shaped main body portion, and a short cylinder portion that extends toward the cancel plate on the inner periphery of the main body portion. And an annular piston seal that forms an annular cancellation chamber with the cancel plate in a state in which the short cylindrical portion is fitted on the shaft portion, and an opening is formed on the outer peripheral surface of the shaft portion. by selectively to perform the discharge of the working oil from the supply and the cancel chamber of hydraulic oil to the cancel chamber through the oil hole with, a sealing device for reciprocally sliding the piston seal in the axial direction, the A plurality of openings are formed in the shaft portion at equal intervals in the circumferential direction, and the opening of the oil hole is in a state where the piston seal slides toward the cancel plate at the tip of the short cylinder portion of the piston seal. In Mase equidistantly plurality provided in the flow oil passage for circulating hydraulic fluid circumferentially, said flow oil path is a flow path for linearly successive to the outer peripheral surface from the inner peripheral surface of the tip, in a state where the piston seal is slid on the cancel plate side, Ri flow channel der flow linearly hydraulic fluid radially outward into the cancellation chamber through the flow the oil passage from the oil hole, the flow oil The number of paths is larger than the number of the openings, and the circumferential dimension of the fluid flow path is larger than the circumferential dimension of the openings .
According to this configuration, even if the short cylinder part of the piston seal is positioned radially outside the opening of the oil hole by sliding the piston seal to the cancel plate side, the fluid oil formed in the short cylinder part The hydraulic oil can be circulated between the oil hole and the cancellation chamber through the flow oil path with the path facing the opening of the oil hole. For this reason, it is possible to prevent the short cylinder portion of the piston seal from blocking the opening of the oil hole, to ensure the flow of hydraulic oil between the oil hole and the cancellation chamber, and to reduce the operation responsiveness of the piston seal. Can be prevented.

また、前記流油路の数は、前記軸部に周方向に等間隔で複数形成した前記開口部の数よりも多く、前記流油路の周方向の寸法は、前記開口部の周方向の寸法よりも大きいことから、軸部の油孔の開口部と、ピストンシールの短筒部の流油路との間に位相のずれがあっても、キャンセル室といずれかの開口部とが流油路を介して通じる構成とすることが可能となる。 In addition, the number of the flow oil passages is larger than the number of the openings formed at equal intervals in the circumferential direction on the shaft portion, and the circumferential dimension of the flow oil passages is the circumferential direction of the openings. Therefore, even if there is a phase shift between the oil hole opening in the shaft part and the flow oil passage in the short cylinder part of the piston seal, the cancellation chamber and any of the openings will flow. It becomes possible to set it as the structure connected through an oil path.

また、前記密封装置において、前記流油路は切欠溝であるのが好ましい。Moreover, in the sealing device, it is preferable that the flow oil passage is a notch groove.
これによれば、切欠溝が油孔とキャンセル室との間で作動油を流通させることができる。また、流油路の形成が容易である。According to this, the cutout groove can circulate the hydraulic oil between the oil hole and the cancel chamber. In addition, it is easy to form a flowing oil passage.

また、前記密封装置において、前記ピストンシールは自動変速機の動力接続部で用いられるのが好ましい。これによれば、ピストンシールの作動応答性が低下することを防止できることから、自動変速機の動力接続部における動力伝達の応答性を高く維持できる。   In the sealing device, the piston seal is preferably used in a power connection portion of an automatic transmission. According to this, since it is possible to prevent the operation responsiveness of the piston seal from being lowered, it is possible to maintain high responsiveness of power transmission in the power connection portion of the automatic transmission.

この発明によれば、ピストンシールの短筒部に形成した流油路によって、キャンセル室と油孔との間における作動油の流れを確保でき、ピストンシールの作動応答性が低下することを防止できる。   According to the present invention, the flow of the hydraulic oil between the cancellation chamber and the oil hole can be secured by the flow oil passage formed in the short cylinder portion of the piston seal, and the deterioration of the operation responsiveness of the piston seal can be prevented. .

以下、この発明の実施の形態について図面を参照しながら説明する。
図１はこの発明の密封装置の実施の一形態（第１実施形態）を示す要部断面図であり、密封装置が自動車の自動変速機の動力接続部に用いられている場合を示している。図１において、この動力接続部には、ハウジング１０と、環状のピストンシール（ボンデッドシール）１と、環状のキャンセルプレート２６と、ピストンシール１とキャンセルプレート２６との間に介在した弾性部材１２と、多板クラッチ１１とが配設されている。 Embodiments of the present invention will be described below with reference to the drawings.
FIG. 1 is a cross-sectional view of a main part showing an embodiment (first embodiment) of a sealing device of the present invention, and shows a case where the sealing device is used in a power connection portion of an automatic transmission of an automobile. . In FIG. 1, the power connection portion includes a housing 10, an annular piston seal (bonded seal) 1, an annular cancel plate 26, and an elastic member 12 interposed between the piston seal 1 and the cancel plate 26. And the multi-plate clutch 11 is arrange | positioned.

ハウジング１０は、径方向内側の軸部１３と、この軸部１３から径方向外側へ延びる径方向部１４と、この径方向部１４から多板クラッチ１１側の軸方向へ延びる軸方向部１５とを有しており、これらの部分で断面が略コ字形の凹部７となる。そして、この凹部７に前記ピストンシール１の一部が設けられている。軸方向部１５の内壁面（内周面）２１と軸部１３の外周面２０とは径方向で対向した配置となる。   The housing 10 includes a radially inner shaft portion 13, a radial portion 14 extending radially outward from the shaft portion 13, and an axial portion 15 extending from the radial portion 14 in the axial direction on the multi-plate clutch 11 side. In these portions, the concave portion 7 having a substantially U-shaped cross section is formed. A part of the piston seal 1 is provided in the recess 7. The inner wall surface (inner peripheral surface) 21 of the axial direction portion 15 and the outer peripheral surface 20 of the axial portion 13 are arranged to face each other in the radial direction.

ピストンシール１は、金属製の環状部材２と、この環状部材２に固定した環状のシール部材３とを有している。環状部材２は所定形状にプレス成形されたものであり、段付き円板状である本体部２ａと、この本体部２ａの径方向外側部から軸方向に延びた円筒部分２ｄを有する筒状の外周部２ｂと、この本体部２ａの径方向内側部からキャンセルプレート２６側へ軸方向に延びて形成した筒状の短筒部２ｃとを有している。そして、前記外周部２ｂの先端部が前記多板クラッチ１１と接触する。短筒部２ｃはピストンシール１の軸線に平行な方向に直線である筒形状であり、短筒部２ｃが軸部１３に外嵌し、当該短筒部２ｃの内周面が軸部１３の外周面２０に接触する。そして、シール部材３は弾性材からなり、例えばゴム製であり、環状部材２に加硫接着されている。このシール部材３は外周側にシールリップ５を有しており、シールリップ５は本体部２ａ側から前記軸方向部１５の周壁面２１に向かって延び当該周壁面２１に接触する。   The piston seal 1 has a metal annular member 2 and an annular seal member 3 fixed to the annular member 2. The annular member 2 is press-molded into a predetermined shape, and is a cylindrical shape having a main body portion 2a having a stepped disk shape and a cylindrical portion 2d extending in the axial direction from a radially outer portion of the main body portion 2a. The outer peripheral part 2b and the cylindrical short cylinder part 2c formed in the axial direction from the radially inner part of the main body part 2a toward the cancel plate 26 are provided. And the front-end | tip part of the said outer peripheral part 2b contacts the said multi-plate clutch 11. FIG. The short cylindrical portion 2 c has a cylindrical shape that is straight in a direction parallel to the axis of the piston seal 1, the short cylindrical portion 2 c is fitted on the shaft portion 13, and the inner peripheral surface of the short cylindrical portion 2 c is the shaft portion 13. Contact the outer peripheral surface 20. The seal member 3 is made of an elastic material, and is made of, for example, rubber, and is vulcanized and bonded to the annular member 2. The seal member 3 has a seal lip 5 on the outer peripheral side, and the seal lip 5 extends from the main body 2 a side toward the peripheral wall surface 21 of the axial direction portion 15 and contacts the peripheral wall surface 21.

キャンセルプレート２６は、軸部１３に外嵌している金属製の環状部材２７と、この環状部材２７に固定した環状のシール部材２８とを有している。環状部材２７は所定形状にプレス成形されたものである。シール部材２８は弾性材からなり、例えばゴム製であり、環状部材２７に加硫接着されている。シール部材２８はシールリップを有しており、このシールリップはピストンシール１の外周部２ｂの円筒部分２ｄの内周面に接触する。そして、このキャンセルプレート２６は、軸部１３に固定の止め輪２９によって軸方向の移動が規制されている。   The cancel plate 26 includes a metal annular member 27 that is externally fitted to the shaft portion 13, and an annular seal member 28 that is fixed to the annular member 27. The annular member 27 is press-molded into a predetermined shape. The seal member 28 is made of an elastic material, and is made of, for example, rubber, and is vulcanized and bonded to the annular member 27. The seal member 28 has a seal lip, and this seal lip contacts the inner peripheral surface of the cylindrical portion 2 d of the outer peripheral portion 2 b of the piston seal 1. The cancel plate 26 is restricted from moving in the axial direction by a retaining ring 29 fixed to the shaft portion 13.

これにより、ハウジング１０の凹部７において、ピストンシール１と、ハウジング１０の断面略コ字形の部分との間に環状の油圧室８が形成され、ピストンシール１は、高圧側となる油圧室８と低圧側であり多板クラッチ１１がある外部９との間を仕切ることができる。この油圧室８には、軸部１３の外周面２０に開口部３１ａを有して作動油を当該油圧室８に供給し又は作動油を当該油圧室８から排出するための第１油孔３１が繋がっている。   Thereby, in the recess 7 of the housing 10, an annular hydraulic chamber 8 is formed between the piston seal 1 and the substantially U-shaped section of the housing 10, and the piston seal 1 is connected to the hydraulic chamber 8 on the high pressure side. It is possible to partition between the low pressure side and the outside 9 with the multi-plate clutch 11. The hydraulic chamber 8 has an opening 31 a on the outer peripheral surface 20 of the shaft portion 13 to supply hydraulic oil to the hydraulic chamber 8 or discharge the hydraulic oil from the hydraulic chamber 8. Are connected.

また、キャンセルプレート２６とピストンシール１とは軸方向に対向して設けられており、キャンセルプレート２６とピストンシール１との間に環状のキャンセル室３０が形成される。このキャンセル室３０には、軸部１３の外周面２０に開口部３２ａを有して作動油を当該キャンセル室３０に供給し又は作動油を当該キャンセル室３０から排出するための第２油孔３２が繋がっている。前記弾性部材１２は、キャンセルプレート２６に対してピストンシール１を離反させる方向に弾性力を付与するものであり、コイルバネとしている。   The cancel plate 26 and the piston seal 1 are provided to face each other in the axial direction, and an annular cancel chamber 30 is formed between the cancel plate 26 and the piston seal 1. The cancel chamber 30 has an opening 32 a on the outer peripheral surface 20 of the shaft portion 13, and supplies a second working oil hole 32 for supplying hydraulic oil to the cancel chamber 30 or discharging the hydraulic oil from the cancel chamber 30. Are connected. The elastic member 12 applies an elastic force in the direction in which the piston seal 1 is separated from the cancel plate 26, and is a coil spring.

以上の構成により、作動油を第１油孔３１から油圧室８に供給し当該油圧室８の油圧を高めると共に、キャンセル室３０の作動油を第２油孔３２から排出することで、ピストンシール１は弾性部材１２の弾性力に抗して多板クラッチ１１側（キャンセルプレート２６側）へ軸方向に摺動できる。また、弾性部材１２の弾性復元力が作用した状態で、油圧室８の作動油を第１油孔３１から排出し当該油圧室８の油圧を低下させると共に、第２油孔３２からキャンセル室３０へ作動油を供給することで、ピストンシール１は多板クラッチ１１から離れる側へ軸方向に移動できる。   With the above configuration, the hydraulic oil is supplied from the first oil hole 31 to the hydraulic chamber 8 to increase the hydraulic pressure of the hydraulic chamber 8, and the hydraulic oil in the cancel chamber 30 is discharged from the second oil hole 32. 1 can slide in the axial direction toward the multi-plate clutch 11 side (cancel plate 26 side) against the elastic force of the elastic member 12. Further, in the state where the elastic restoring force of the elastic member 12 is applied, the hydraulic oil in the hydraulic chamber 8 is discharged from the first oil hole 31 to reduce the hydraulic pressure of the hydraulic chamber 8 and the cancel chamber 30 from the second oil hole 32. By supplying the hydraulic oil to the piston seal 1, the piston seal 1 can move in the axial direction away from the multi-plate clutch 11.

第２油孔３２の開口部３２ａは、軸部１３の外周面２０の内、キャンセルプレート２６の近傍の軸方向位置に形成されている。そして、ピストンシール１は、その短筒部２ｃの先端部４がキャンセルプレート２６の側周面の内周側部に接近する位置まで、軸方向に摺動でき、これにより、ピストンシール１の軸方向の摺動のストロークを長く取ることができる。そして、ピストンシール１がキャンセルプレート２６に近いストローク終端位置まで摺動すると、その短筒部２ｃの先端部４は、第２油孔３２の開口部３２ａの軸方向形成位置にまで達し、開口部３２ａの径方向外側位置にある状態（図１の状態）となる。   The opening 32 a of the second oil hole 32 is formed at an axial position in the vicinity of the cancel plate 26 in the outer peripheral surface 20 of the shaft portion 13. The piston seal 1 can slide in the axial direction until the tip portion 4 of the short cylinder portion 2c approaches the inner peripheral side portion of the side peripheral surface of the cancel plate 26, whereby the shaft of the piston seal 1 is The sliding stroke in the direction can be taken longer. When the piston seal 1 slides to the stroke end position close to the cancel plate 26, the tip portion 4 of the short cylinder portion 2c reaches the axial formation position of the opening portion 32a of the second oil hole 32, and the opening portion It will be in the state (state of FIG. 1) which exists in the radial direction outer side position of 32a.

そこで、このピストンシール１の短筒部２ｃの先端部４には流油路６が設けられており、ピストンシール１がキャンセルプレート２６側に摺動した状態（図１の状態）で、この流油路６を第２油孔３２の開口部３２ａに臨ませて、第２油孔３２とキャンセル室３０との間で作動油を阻害することなく流通させることができる。つまり、流油路６は、第２油孔３２からキャンセル室３０へ径方向外側に向かって直線的に作動油を流すことができる。図２は、ピストンシール１の短筒部２ｃの先端部４の拡大斜視図であり、この流油路６の具体的な構成は、短筒部２ｃの先端部４に形成した切欠溝６ａである。この切欠溝６ａは、ピストンシール１の軸心に交差（直交）した先端部４の先端面４ａに形成されており、かつ、この先端面４ａにおいて先端部４の内周面から外周面へと連続している。   Therefore, a fluid flow path 6 is provided at the distal end portion 4 of the short cylinder portion 2c of the piston seal 1, and this flow is achieved when the piston seal 1 is slid toward the cancel plate 26 (the state shown in FIG. 1). The oil passage 6 faces the opening 32 a of the second oil hole 32, and the hydraulic oil can be circulated between the second oil hole 32 and the cancel chamber 30 without obstructing. That is, the fluid flow path 6 can flow the hydraulic oil linearly from the second oil hole 32 to the cancellation chamber 30 toward the radially outer side. FIG. 2 is an enlarged perspective view of the distal end portion 4 of the short cylindrical portion 2c of the piston seal 1, and the specific configuration of the fluid flow path 6 is a notch groove 6a formed in the distal end portion 4 of the short cylindrical portion 2c. is there. This notch groove 6a is formed in the front end surface 4a of the front end portion 4 intersecting (orthogonal) with the axis of the piston seal 1, and in the front end surface 4a from the inner peripheral surface of the front end portion 4 to the outer peripheral surface. It is continuous.

また、図３と図４と図５とはピストンシール１の短筒部２ｃの先端部４、及び軸部１３を軸方向から見た図である。軸部１３には複数の第２油孔３２が周方向に等間隔で形成されており、外周面２１において開口部３２ａが周方向に等間隔にある。この実施の形態では、軸部１３において、径方向にまっすぐ延びる四本の第２油孔３２が等間隔で形成されている（９０°離れて形成されている）。そして、ピストンシール１の短筒部２ｃの先端部４には、第２油孔３２の開口部３２ａの数（四つ）よりも多い数の切欠溝６ａが周方向に等間隔で形成されており、この実施の形態では、五つの切欠溝６ａが等間隔で形成されている（７２°離れて形成されている）。さらに、各切欠溝６ａの周方向の寸法Ａ（先端面４ａにおける寸法Ａ）は、第２油孔３２の開口部３２ａの周方向の寸法ｄよりも大きく設定されている（Ａ＞ｄ）。例えば、直径がφ３５ｍｍの軸部１３の外周面２１において周方向で等間隔に四つの開口部３２ａを形成し、その開口部３２ａの直径ｄをφ２ｍｍの円形とした場合、短筒部２ｃの先端部４に五つの切欠溝６ａを周方向で等間隔に形成し、この切欠溝６ａの周方向の寸法Ａを前記直径ｄの４倍以上（８ｍｍ以上）でかつ８倍以下（１６ｍｍ以下）としている。このように、開口部３２ａの数ｎに対して、切欠溝６ａの数をこれよりも一つ多い数ｎ＋１とすることによって、少ない数の切欠溝６ａにより構成し、切欠溝６ａの形成のための製造コストの低減を図っている。   3, 4, and 5 are views of the distal end portion 4 of the short cylindrical portion 2 c of the piston seal 1 and the shaft portion 13 as viewed from the axial direction. A plurality of second oil holes 32 are formed in the shaft portion 13 at equal intervals in the circumferential direction, and the opening portions 32 a are equally spaced in the circumferential direction on the outer peripheral surface 21. In this embodiment, four second oil holes 32 extending straight in the radial direction are formed at equal intervals in the shaft portion 13 (formed 90 ° apart). In addition, a larger number of notch grooves 6a than the number (four) of the openings 32a of the second oil holes 32 are formed at equal intervals in the circumferential direction at the distal end portion 4 of the short cylinder portion 2c of the piston seal 1. In this embodiment, the five notch grooves 6a are formed at equal intervals (72 ° apart). Furthermore, the circumferential dimension A of each notch groove 6a (dimension A at the front end surface 4a) is set to be larger than the circumferential dimension d of the opening 32a of the second oil hole 32 (A> d). For example, when four openings 32a are formed at equal intervals in the circumferential direction on the outer peripheral surface 21 of the shaft portion 13 with a diameter of 35 mm, and the diameter d of the openings 32a is a circle with 2 mm, the tip of the short cylinder portion 2c Five cutout grooves 6a are formed in the portion 4 at equal intervals in the circumferential direction, and the circumferential dimension A of the cutout groove 6a is 4 times (8 mm or more) and 8 times (16 mm or less) of the diameter d. Yes. In this way, the number of notch grooves 6a is set to a number n + 1 which is one more than the number n of openings 32a, thereby forming a smaller number of notch grooves 6a and forming notch grooves 6a. The manufacturing cost is reduced.

これによれば、図３と図４と図５とに示しているように、軸部１３の第２油孔３２の開口部３２ａと、ピストンシール１の短筒部２ｃに形成した切欠溝６ａとの間に位相のずれがあっても、いずれかの第２油孔３２（開口部３２ａ）に切欠溝６ａを臨ませることができ、キャンセル室３０といずれかの第２油孔３２（開口部３２ａ）とが切欠溝６ａを介して通じる構成となる。したがって、図１に示しているように、キャンセル室３０から作動油を第２油孔３２を通じて排出しつつ、ピストンシール１の短筒部２ｃの先端部４が、第２油孔３２の開口部３２ａの軸方向形成位置まで摺動しても、その短筒部２ｃの先端部４に形成した切欠溝６ａによって第２油孔３２とキャンセル室３０との間で作動油を流すことができる。これにより、ピストンシール１の短筒部２ｃの先端部４が第２油孔３２の開口部３２ａを塞いでしまうことを防ぎ、作動油の流れを確保でき、ピストンシール１の作動応答性が低下することを防止できる。そして、このピストンシール１を自動変速機の動力接続部で用いていることで、当該動力接続部における動力伝達の応答性を高く維持できる。また、流油路６として切欠溝６ａを採用していることで、短筒部２ｃの先端部４を切削やプレスなどによって形成でき、製造が容易となる。   According to this, as shown in FIGS. 3, 4, and 5, the notch groove 6 a formed in the opening 32 a of the second oil hole 32 of the shaft portion 13 and the short cylinder portion 2 c of the piston seal 1. Even if there is a phase shift between the cancel chamber 30 and any one of the second oil holes 32 (opening), the notch groove 6a can be exposed to any one of the second oil holes 32 (opening 32a). The portion 32a) communicates with the cutout groove 6a. Accordingly, as shown in FIG. 1, the hydraulic oil is discharged from the cancel chamber 30 through the second oil hole 32, and the distal end portion 4 of the short cylinder portion 2 c of the piston seal 1 is opened to the second oil hole 32. Even if it slides to the axial direction formation position of 32a, hydraulic fluid can be flowed between the 2nd oil hole 32 and the cancellation chamber 30 by the notch groove 6a formed in the front-end | tip part 4 of the short cylinder part 2c. Thereby, it can prevent that the front-end | tip part 4 of the short cylinder part 2c of the piston seal 1 block | closes the opening part 32a of the 2nd oil hole 32, can ensure the flow of hydraulic fluid, and the action | operation responsiveness of the piston seal 1 falls. Can be prevented. And by using this piston seal 1 in the power connection part of an automatic transmission, the responsiveness of the power transmission in the said power connection part can be maintained highly. In addition, since the notch groove 6a is employed as the oil flow path 6, the tip portion 4 of the short cylindrical portion 2c can be formed by cutting, pressing, or the like, which facilitates manufacture.

図６はこの発明の密封装置の第２の実施の形態を示す要部断面図である。この第２の実施の形態は、第１の形態と比べてピストンシールが異なるが、その他は同じである。この第２の実施の形態では、ピストンシール１６は、金属製の環状部材１７と、この環状部材１７に固定した環状のシール部材１８とを有しており、このシール部材１８は、円板状の本体部１８ｃと、この本体部１８ｃの内径側からキャンセルプレート２６側に延びる短筒部１８ｂとを有し、この短筒部１８ｂの先端部が軸部１３に外嵌する。そして、この短筒部１８ｂの先端部に、前記実施の形態と同様の流油路２３を形成している。なお、この図６では、油圧室８に繋がる第１油孔は図示省略している。   FIG. 6 is a cross-sectional view of an essential part showing a second embodiment of the sealing device of the present invention. This second embodiment is the same as the first embodiment except for the piston seal. In the second embodiment, the piston seal 16 has a metal annular member 17 and an annular seal member 18 fixed to the annular member 17, and the seal member 18 is disc-shaped. The main body 18 c and a short cylinder 18 b extending from the inner diameter side of the main body 18 c to the cancel plate 26 side, and the tip of the short cylinder 18 b is fitted on the shaft 13. And the fluid flow path 23 similar to the said embodiment is formed in the front-end | tip part of this short cylinder part 18b. In FIG. 6, the first oil hole connected to the hydraulic chamber 8 is not shown.

具体的に説明すると、ピストンシール１６の環状部材１７は所定形状にプレス成形されたものであり、段付き円板状である本体部１７ａと、この本体部１７ａの径方向外側部から軸方向に延びた円筒部分１７ｆを有する筒状の外周部１７ｂと、本体部１７ａの径方向内側部からキャンセルプレート２６側へ延びた短筒部１７ｃとを有している。この短筒部１７ｃは、本体部１７ａの径方向内側部から軸方向に延びた基端部としての円筒部１７ｄと、先端部としての内鍔部１７ｅとを有している。   More specifically, the annular member 17 of the piston seal 16 is press-molded into a predetermined shape, and has a main body portion 17a having a stepped disk shape, and an axial direction from a radially outer portion of the main body portion 17a. It has a cylindrical outer peripheral portion 17b having an extended cylindrical portion 17f, and a short cylindrical portion 17c extending from the radially inner side of the main body portion 17a to the cancel plate 26 side. The short cylinder portion 17c has a cylindrical portion 17d as a base end portion extending in the axial direction from the radially inner portion of the main body portion 17a, and an inner flange portion 17e as a distal end portion.

シール部材１８は弾性材からなり、例えばゴム製であり、環状部材１７に加硫接着されている。シール部材１８は、外シールリップ１８ｄのある外周部１８ａと、内周側にある前記短筒部１８ｂと、これらを繋ぐ前記本体部１８ｃとを有している。シール部材１８の短筒部１８ｂは環状部材１７の短筒部１７ｃに接着されている。   The seal member 18 is made of an elastic material, and is made of, for example, rubber, and is vulcanized and bonded to the annular member 17. The seal member 18 includes an outer peripheral portion 18a having an outer seal lip 18d, the short cylindrical portion 18b on the inner peripheral side, and the main body portion 18c connecting them. The short cylinder portion 18 b of the seal member 18 is bonded to the short cylinder portion 17 c of the annular member 17.

図７は環状部材１７の短筒部１７ｃの先端部（内筒部１７ｅ）、及びシール部材１８の短筒部１８ｂの先端部を示す拡大斜視図である。シール部材１８の短筒部１８ｂの先端部は、油圧室８側でかつ軸部１３の外周面２０側に向かって延び当該外周面２０に接触している内シールリップ１８ｅと、環状部材１７の内鍔部１７ｅを内径側から覆っている第１被覆部１８ｆと、内鍔部１７ｅの内径側部分をキャンセルプレート２６側から（軸方向から）覆っている第２被覆部１８ｇとを有している。   FIG. 7 is an enlarged perspective view showing the distal end portion (inner cylindrical portion 17 e) of the short cylindrical portion 17 c of the annular member 17 and the distal end portion of the short cylindrical portion 18 b of the seal member 18. The distal end portion of the short cylindrical portion 18 b of the seal member 18 extends toward the outer peripheral surface 20 side of the shaft portion 13 on the hydraulic chamber 8 side, and the inner seal lip 18 e that is in contact with the outer peripheral surface 20 and the annular member 17. A first covering portion 18f covering the inner flange portion 17e from the inner diameter side; and a second covering portion 18g covering the inner diameter side portion of the inner flange portion 17e from the cancel plate 26 side (from the axial direction). Yes.

そして、前記第１の実施の形態と同様に、作動油を第１油孔（図示せず）から油圧室８に供給し当該油圧室８の油圧を高めると共に、キャンセル室３０の作動油を第２油孔３２から排出することで、ピストンシール１６は弾性部材１２の弾性力に抗して多板クラッチ１１側へ軸方向に摺動できる。また、弾性部材１２の弾性復元力が作用している状態で、油圧室８の作動油を第１油孔（図示せず）から排出し当該油圧室８の油圧を低下させると共に、第２油孔３２からキャンセル室３０へ作動油を供給することで、ピストンシール１６は多板クラッチ１１から離れる側へ軸方向に移動できる。そして、ピストンシール１６がキャンセルプレート２６に近いストローク終端位置まで摺動すると、シール部材１８の短筒部１８ｂの先端部は、第２油孔３２の開口部３２ａの軸方向形成位置にまで達し、開口部３２ａの径方向外側位置にある状態（図６の状態）となる。   As in the first embodiment, hydraulic oil is supplied from a first oil hole (not shown) to the hydraulic chamber 8 to increase the hydraulic pressure of the hydraulic chamber 8, and the hydraulic oil in the cancel chamber 30 is supplied to the hydraulic chamber 8. By discharging from the two oil holes 32, the piston seal 16 can slide in the axial direction toward the multi-plate clutch 11 against the elastic force of the elastic member 12. In addition, while the elastic restoring force of the elastic member 12 is acting, the hydraulic oil in the hydraulic chamber 8 is discharged from the first oil hole (not shown) to reduce the hydraulic pressure in the hydraulic chamber 8 and the second oil By supplying the hydraulic oil from the hole 32 to the cancel chamber 30, the piston seal 16 can move in the axial direction to the side away from the multi-plate clutch 11. When the piston seal 16 slides to the stroke end position close to the cancel plate 26, the tip of the short cylindrical portion 18b of the seal member 18 reaches the axial formation position of the opening 32a of the second oil hole 32, It will be in the state (state of FIG. 6) in the radial direction outer side position of the opening part 32a.

そこで、短筒部１８ｂの第２被覆部１８ｇに流油路２３として切欠溝２３ａが形成されており、ピストンシール１６がキャンセルプレート２６側に摺動した状態（図６の状態）で、この切欠溝２３ａを第２油孔３２の開口部３２ａに臨ませて、第２油孔３２とキャンセル室３０との間で作動油を阻害することなく流通させることができる。切欠溝２３ａは、第２被覆部１８ｇの内のピストンシール１６の軸心に交差（直交）した先端面１８ｈに形成されており、かつ、この先端面１８ｈにおいて第２被覆部１８ｇの内周面から外周面へと連続している。   Therefore, a notch groove 23a is formed as a flow oil passage 23 in the second covering portion 18g of the short cylindrical portion 18b, and this notch is in a state where the piston seal 16 is slid toward the cancel plate 26 (state of FIG. 6). The groove 23 a faces the opening 32 a of the second oil hole 32, and the hydraulic oil can be circulated between the second oil hole 32 and the cancel chamber 30 without hindering. The notch groove 23a is formed in the tip surface 18h that intersects (orthogonally) the axis of the piston seal 16 in the second cover portion 18g, and the inner peripheral surface of the second cover portion 18g in the tip surface 18h. To the outer peripheral surface.

そして、第１の実施の形態と同様に、図３と図４と図５において、軸部１３には第２油孔３２の開口部３２ａが周方向に等間隔で四つ形成されており、ピストンシール１６の第２被覆部１８ｇには、この第２油孔３２の開口部３２ａの数よりも多い数である五つの切欠溝２３ａが周方向に等間隔で形成されている。そして、各切欠溝２３ａの周方向の寸法Ａ（図７の先端面１８ｈにおける寸法Ａ）は、第２油孔３２の開口部３２ａの周方向の寸法ｄ（開口部３２ａの直径）よりも大きく設定されている。   As in the first embodiment, in FIGS. 3, 4 and 5, the shaft portion 13 has four openings 32 a of the second oil holes 32 formed at equal intervals in the circumferential direction. In the second covering portion 18g of the piston seal 16, five cutout grooves 23a that are larger in number than the number of the opening portions 32a of the second oil hole 32 are formed at equal intervals in the circumferential direction. The circumferential dimension A of each notch groove 23a (dimension A at the tip end surface 18h in FIG. 7) is larger than the circumferential dimension d of the opening 32a of the second oil hole 32 (diameter of the opening 32a). Is set.

また、この発明は、図示する形態に限らずこの発明の範囲内において他の形態であっても良く、流油路としての切欠溝の形状を円弧形状や矩形とできる。また、第２油孔３２の開口部３２ａ数も五つ以上であってもよく、この場合、切欠溝の数を６本以上とすればよい。   Further, the present invention is not limited to the illustrated form, and may be other forms within the scope of the present invention, and the shape of the notch groove as the fluid flow path can be an arc shape or a rectangle. Further, the number of the opening portions 32a of the second oil hole 32 may be five or more. In this case, the number of the notch grooves may be six or more.

この発明の密封装置の実施の一形態を示す要部の断面図である。It is sectional drawing of the principal part which shows one Embodiment of the sealing device of this invention. 図１のピストンシールの短筒部の先端部の拡大斜視図である。It is an expansion perspective view of the front-end | tip part of the short cylinder part of the piston seal of FIG. ピストンシールの内周部の先端部、及び軸部を軸方向から見た図である。It is the figure which looked at the front-end | tip part of the inner peripheral part of a piston seal, and the axial part from the axial direction. ピストンシールの内周部の先端部、及び軸部を軸方向から見た図である。It is the figure which looked at the front-end | tip part of the inner peripheral part of a piston seal, and the axial part from the axial direction. ピストンシールの内周部の先端部、及び軸部を軸方向から見た図である。It is the figure which looked at the front-end | tip part of the inner peripheral part of a piston seal, and the axial part from the axial direction. この発明の密封装置の第２の実施の形態を示す要部の断面図である。It is sectional drawing of the principal part which shows 2nd Embodiment of the sealing device of this invention. 図６のピストンシールの短筒部の先端部の拡大斜視図である。It is an expansion perspective view of the front-end | tip part of the short cylinder part of the piston seal of FIG. 従来の密封装置の断面図である。It is sectional drawing of the conventional sealing device.

符号の説明Explanation of symbols

１ ピストンシール
２ｃ 短筒部
４ 先端部
６ 流油路
６ａ 切欠溝
８ 油圧室
１３ 軸部
１６ ピストンシール
１８ｂ 短筒部
１８ｆ 第１被覆部
１８ｇ 第２被覆部（先端部）
２０ 外周面
２３ 流油路
２３ａ 切欠溝
２６ キャンセルプレート
３０ キャンセル室
３１ 第１油孔
３１ａ 開口部
３２ 第２油孔
３２ａ 開口部 DESCRIPTION OF SYMBOLS 1 Piston seal 2c Short cylinder part 4 Tip part 6 Fluid flow path 6a Notch groove 8 Hydraulic chamber 13 Shaft part 16 Piston seal 18b Short cylinder part 18f 1st coating | coated part 18g 2nd coating | coated part (tip part)
20 outer peripheral surface 23 oil flow path 23a notch groove 26 cancel plate 30 cancel chamber 31 first oil hole 31a opening 32 second oil hole 32a opening

Claims (3)

軸部に外嵌する環状のキャンセルプレートと、
円板状の本体部とこの本体部の内周に前記キャンセルプレート側に延びる短筒部とを有し、この短筒部を前記軸部に外嵌した状態で前記キャンセルプレートとの間で環状のキャンセル室を形成する環状のピストンシールと、を備え、
前記軸部の外周面に開口部を有する油孔を通じて前記キャンセル室への作動油の供給と当該キャンセル室からの作動油の排出とを選択的に行うことにより、前記ピストンシールを軸方向に往復摺動させる密封装置であって、
前記開口部は、前記軸部に周方向等間隔で複数形成され、
前記ピストンシールの前記短筒部の先端部に、当該ピストンシールが前記キャンセルプレート側に摺動した状態で前記油孔の開口部に臨ませて作動油を流通させる流油路が周方向に等間隔で複数設けられ、
前記流油路は、前記先端部の内周面から外周面へと直線的に連続した流路であって、前記ピストンシールが前記キャンセルプレート側に摺動した状態で、前記油孔から作動油を当該流油路を通じて前記キャンセル室へ径方向外側に向かって直線的に流す流路であり、
前記流油路の数は、前記開口部の数よりも多く、
前記流油路の周方向の寸法は、前記開口部の周方向の寸法よりも大きいことを特徴とする密封装置。 An annular cancel plate that fits around the shaft;
It has a disc-shaped main body part and a short cylinder part extending toward the cancel plate on the inner periphery of the main body part, and the short cylinder part is annularly connected between the cancel plate and the shaft part. An annular piston seal that forms a cancellation chamber of
The piston seal is reciprocated in the axial direction by selectively supplying hydraulic oil to the cancellation chamber and discharging hydraulic oil from the cancellation chamber through an oil hole having an opening in the outer peripheral surface of the shaft portion. A sealing device for sliding,
A plurality of the openings are formed in the shaft portion at equal intervals in the circumferential direction
An oil flow passage is provided in the circumferential direction at the tip of the short cylinder portion of the piston seal so that the hydraulic oil flows through the opening of the oil hole while the piston seal slides toward the cancel plate. A plurality are provided at intervals ,
The fluid flow path is a flow path that is linearly continuous from the inner peripheral surface to the outer peripheral surface of the tip, and the hydraulic oil is discharged from the oil hole in a state where the piston seal slides toward the cancel plate side. the Ri flow path der flow linearly outward in the radial direction to the cancellation chamber through the flow oil passage,
The number of the flowing oil passages is larger than the number of the openings,
The sealing device according to claim 1, wherein a dimension in the circumferential direction of the flow oil passage is larger than a dimension in the circumferential direction of the opening . 前記流油路は切欠溝である請求項１に記載の密封装置。   The sealing device according to claim 1, wherein the oil flow passage is a notch groove. 前記ピストンシールは自動変速機の動力接続部で用いられる請求項１又は２に記載の密封装置。 The sealing device according to claim 1 , wherein the piston seal is used in a power connection portion of an automatic transmission.
JP2006196532A 2006-07-19 2006-07-19 Sealing device Active JP4969169B2 (en)

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