JP5413395B2 - Piston member - Google Patents
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- JP5413395B2 JP5413395B2 JP2011075703A JP2011075703A JP5413395B2 JP 5413395 B2 JP5413395 B2 JP 5413395B2 JP 2011075703 A JP2011075703 A JP 2011075703A JP 2011075703 A JP2011075703 A JP 2011075703A JP 5413395 B2 JP5413395 B2 JP 5413395B2
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Description
本発明は、油圧により軸方向に移動して摩擦係合要素を押圧する押圧部を有するピストン部材に関する。 The present invention relates to a piston member having a pressing portion that moves in an axial direction by hydraulic pressure to press a friction engagement element.
従来、この種のピストン部材としては、自動変速機が備える多板ブレーキを押圧して係合させるものが提案されている（例えば、特許文献１参照）。このピストン部材は、外径側で前方に突出する筒状の延出部が形成されており、油圧アクチュエータからの油圧により前方に移動し、延出部の前面で多板ブレーキを押圧している。また、ピストン部材の延出部は、内周側でプラネタリギヤの外径側を軸方向に若干オーバーラップするよう配置されており、プラネタリギヤのキャリアの外径側に一体に設けられたパーキングギヤを被嵌し、パーキングギヤに係止されるパーキングポールの干渉防止用の切り欠きが設けられている。 Conventionally, as this kind of piston member, one that presses and engages a multi-plate brake provided in an automatic transmission has been proposed (for example, see Patent Document 1). The piston member is formed with a cylindrical extending portion that protrudes forward on the outer diameter side, moves forward by the hydraulic pressure from the hydraulic actuator, and presses the multi-plate brake on the front surface of the extending portion. . Further, the extending portion of the piston member is arranged on the inner peripheral side so as to slightly overlap the outer diameter side of the planetary gear in the axial direction, and is covered with a parking gear integrally provided on the outer diameter side of the planetary gear carrier. A notch for preventing interference of the parking pole fitted and locked to the parking gear is provided.
ところで、上述したピストン部材では、比較的大きな力を受けることから、比較的薄肉の延出部に切欠きなど開口を設けると、開口の周囲に局所的に大きな応力が作用する場合が生じる。こうした局所的に応力が集中する状態は、部材の耐久性に悪影響を及ぼすことから、十分な対策が望まれる。 By the way, since the above-mentioned piston member receives a relatively large force, if an opening such as a notch is provided in a relatively thin extending portion, a large stress may locally act around the opening. Such a state in which stress is locally concentrated adversely affects the durability of the member, so that sufficient countermeasures are desired.
本発明のピストン部材は、耐久性を向上させることを主目的とする。 The main purpose of the piston member of the present invention is to improve durability.
本発明のピストン部材は、上述の主目的を達成するために以下の手段を採った。 The piston member of the present invention employs the following means in order to achieve the main object described above.
本発明のピストン部材は、
油圧を受けて軸方向に移動して摩擦係合要素を押圧する押圧部を有するピストン部材であって、
前記押圧部は、他の部材との干渉防止用の孔を側面に有する円筒状に形成され、
前記干渉防止用の孔は、前記押圧部の周方向の幅が前記他の部材を挿通可能に設定された第１の開口部と、前記押圧部の周方向の幅が前記第１の開口部よりも広く且つ該第１の開口部よりも前記押圧部の受圧部から離れた第２の開口部とが軸方向に沿って連続して一つの孔をなすよう段付き形状に形成されてなる
ことを要旨とする。
The piston member of the present invention is
A piston member that has a pressing portion that receives hydraulic pressure and moves in the axial direction to press the friction engagement element,
The pressing part is formed in a cylindrical shape having holes for preventing interference with other members on the side surface,
The interference preventing hole includes a first opening in which a circumferential width of the pressing portion is set to be able to pass through the other member, and a circumferential width of the pressing portion is the first opening. The second opening that is wider than the first opening and away from the pressure receiving portion of the pressing portion is formed in a stepped shape so as to continuously form one hole along the axial direction. This is the gist.
この本発明のピストン部材では、油圧を受けて軸方向に移動して摩擦係合要素を押圧する押圧部を、他の部材との干渉防止用の孔を側面に有する円筒状に形成し、この干渉防止用の孔を、押圧部の周方向の幅が他の部材を挿通可能に設定された第１の開口部と、押圧部の周方向の幅が第１の開口部よりも広く且つ第１の開口部よりも押圧部の受圧部から離れた第２の開口部とが軸方向に沿って連続して一つの孔をなすよう段付き形状に形成する。これにより、ピストン部材に作用する応力を、第１の開口部の開口縁に作用する応力と第２の開口部の開口縁に作用する応力とに分散させることができるから、ピストン部材の押圧部に干渉防止用の孔を形成するものとしても、部材の耐久性を向上させることができる。 In the piston member of the present invention, the pressing portion that receives the hydraulic pressure and moves in the axial direction to press the friction engagement element is formed in a cylindrical shape having a hole on the side surface to prevent interference with other members. The interference prevention hole includes a first opening in which the width in the circumferential direction of the pressing portion is set so that another member can be inserted, and a width in the circumferential direction of the pressing portion is wider than that of the first opening. A stepped shape is formed so that the second opening that is farther from the pressure receiving part of the pressing part than the one opening forms a single hole continuously along the axial direction. Accordingly, the stress acting on the piston member can be dispersed into the stress acting on the opening edge of the first opening and the stress acting on the opening edge of the second opening. Even if a hole for preventing interference is formed on the substrate, the durability of the member can be improved.
こうした本発明のピストン部材において、前記第２の開口部は、周方向側の開口縁が円弧状に形成されてなるものとすることもできる。こうすれば、第１の開口部の開口縁に作用する応力を第２の開口部の開口縁に効果的に分散させることができる。この態様の本発明のピストン部材において、前記第１の開口部は、開口縁の少なくとも一部が円弧状に形成され、前記第２の開口部は、前記第１の開口部よりも円弧の径が大きくなるよう形成されてなるものとすることもできる。こうすれば、第１の開口部に開口縁に作用する応力と第２の開口部の開口縁に作用する応力とをより適切な配分で分散させることができる。 In the piston member of the present invention, the second opening may be formed such that an opening edge on the circumferential side is formed in an arc shape. If it carries out like this, the stress which acts on the opening edge of a 1st opening part can be effectively disperse | distributed to the opening edge of a 2nd opening part. In this aspect of the piston member of the present invention, at least a part of the opening edge of the first opening is formed in an arc shape, and the second opening has an arc diameter larger than that of the first opening. It can also be formed so as to increase. If it carries out like this, the stress which acts on an opening edge in a 1st opening part and the stress which acts on the opening edge of a 2nd opening part can be disperse | distributed by more suitable distribution.
また、本発明のピストン部材において、前記第２の開口部は、軸方向の幅が前記第１の開口部よりも広くなるよう形成されてなるものとすることもできる。こうすれば、第１の開口部の開口縁に作用する応力を第２の開口部の開口縁に効果的に分散させることができる。 In the piston member of the present invention, the second opening may be formed so that the width in the axial direction is wider than that of the first opening. If it carries out like this, the stress which acts on the opening edge of a 1st opening part can be effectively disperse | distributed to the opening edge of a 2nd opening part.
さらに、本発明のピストン部材において、前記第１の開口部と前記第２の開口部は、軸方向に対して線対称に形成されてなるものとすることもできる。 Furthermore, in the piston member of the present invention, the first opening and the second opening may be formed symmetrically with respect to the axial direction.
また、本発明のピストン部材において、本発明のピストン部材において、前記他の部材は、前記押圧部の内周側に配置されたギヤ部材に該押圧部の外周側から前記干渉防止用の孔を介して噛み合う噛み合い機構であるものとすることもできる。 Further, in the piston member of the present invention, in the piston member of the present invention, the other member includes a gear member disposed on the inner peripheral side of the pressing portion, the hole for preventing interference from the outer peripheral side of the pressing portion. It can also be a meshing mechanism that meshes with each other.
次に、本発明の実施の形態を実施例を用いて説明する。 Next, embodiments of the present invention will be described using examples.
図１は自動変速機１０の一部の断面を示す部分断面図である。図中左方向が車両前方を示し、図中右方向が車両後方を示す。自動変速機１０は、原動機を備える自動車に搭載され、前進１速〜前進６速と後進とが可能な有段の変速機構として構成されており、図示するように、遊星歯車機構２０を含む複数の遊星歯車機構と、ブレーキ３０を含む複数のクラッチやブレーキと、油圧によりブレーキ３０の係合とその解除とを行なう油圧アクチュエータ４０を含む複数の油圧アクチュエータとを備える。 FIG. 1 is a partial cross-sectional view showing a cross section of a part of the automatic transmission 10. The left direction in the figure indicates the front of the vehicle, and the right direction in the figure indicates the rear of the vehicle. The automatic transmission 10 is mounted on a motor vehicle equipped with a prime mover, and is configured as a stepped transmission mechanism capable of forward 1st to 6th forward and reverse, and includes a planetary gear mechanism 20 as illustrated. Planetary gear mechanism, a plurality of clutches and brakes including the brake 30, and a plurality of hydraulic actuators including a hydraulic actuator 40 for engaging and releasing the brake 30 by hydraulic pressure.
遊星歯車機構２０は、外歯歯車のサンギヤ２１と、このサンギヤ２１と同心円上に配置された内歯歯車のリングギヤ２２と、サンギヤ２１に噛合すると共にリングギヤ２２に噛合する複数のピニオンギヤ２３と、複数のピニオンギヤ２３を自転かつ公転自在に保持するキャリア２４とを備え、キャリア２４は図示しない車軸に連結された自動変速機１０の出力軸１４に接続されている。また、キャリア２４には、パーキングギヤ２５が取り付けられており、このパーキングギヤ２５にパーキングポール２８が噛み合うことにより出力軸１４が回転不能にロックされるようになっている。 The planetary gear mechanism 20 includes an external gear sun gear 21, an internal gear ring gear 22 arranged concentrically with the sun gear 21, a plurality of pinion gears 23 that mesh with the sun gear 21 and mesh with the ring gear 22, The carrier 24 holds the pinion gear 23 so as to rotate and revolve freely. The carrier 24 is connected to the output shaft 14 of the automatic transmission 10 connected to an axle (not shown). Further, a parking gear 25 is attached to the carrier 24, and the output shaft 14 is locked so as not to rotate when the parking pawl 28 meshes with the parking gear 25.
ブレーキ３０は、複数枚の摩擦板３１と複数枚のセパレータ３２とが軸方向に沿って交互に配列された多板ブレーキとして構成されており、摩擦板３１は遊星歯車機構２０のリングギヤ２２の外周面に形成されたスプライン溝２２ａにスプライン係合され、セパレータ３２はケース１２の内周面に形成されたスプライン溝１２ａにアウタレース３３と共にスプライン係合されている。ケース１２の内周面には、アウタレース３３を前方側（図中の左側）から支持するスナップリング３４が嵌着されており、スナップリング３４によってセパレータ３２の軸方向の移動が規制されている。また、ブレーキ３０の後方（図中の右側）には、ケース１２の内周面に形成されたスプライン溝１２ａにスプライン係合されたプレッシャープレート３５を介して摩擦板３１とセパレータ３２とを前方（図中の左方向）に押圧するための油圧アクチュエータ４０が配置されている。 The brake 30 is configured as a multi-plate brake in which a plurality of friction plates 31 and a plurality of separators 32 are alternately arranged along the axial direction. The friction plate 31 is an outer periphery of the ring gear 22 of the planetary gear mechanism 20. The separator 32 is spline-engaged together with the outer race 33 in the spline groove 12 a formed on the inner peripheral surface of the case 12. A snap ring 34 that supports the outer race 33 from the front side (left side in the drawing) is fitted to the inner peripheral surface of the case 12, and the movement of the separator 32 in the axial direction is restricted by the snap ring 34. Further, on the rear side of the brake 30 (right side in the figure), the friction plate 31 and the separator 32 are moved forward (via a pressure plate 35 spline-engaged with a spline groove 12a formed on the inner peripheral surface of the case 12 ( A hydraulic actuator 40 for pressing in the left direction in the figure is arranged.
油圧アクチュエータ４０は、ケース１２の後方側の内壁をシリンダとして用いたダブルピストン構造のアクチュエータとして構成されており、シリンダに油密に挿入された本発明のピストン部材としての第１のピストン４１と、シリンダに油密に挿入された第２のピストン４２と、第１のピストン４１と第２のピストン４２との間に挟まれて二つの油密室を区画する中間部材４３と、支持プレート４４に支持されて第１のピストン４１を付勢するリターンスプリング４５と、を備える。第１のピストン４１には、第１のピストン４１の前端から軸方向に沿って遊星歯車機構２０とオーバーラップするように円筒部材５０が嵌着されており、第１のピストン４１から円筒部材５０を介してプレッシャープレート３５を押圧する。 The hydraulic actuator 40 is configured as an actuator having a double piston structure using the inner wall on the rear side of the case 12 as a cylinder, and a first piston 41 as a piston member of the present invention inserted into the cylinder in an oil-tight manner, A second piston 42 that is oil-tightly inserted into the cylinder, an intermediate member 43 that is sandwiched between the first piston 41 and the second piston 42 and defines two oil-tight chambers, and is supported by the support plate 44 And a return spring 45 that urges the first piston 41. A cylindrical member 50 is fitted to the first piston 41 so as to overlap the planetary gear mechanism 20 along the axial direction from the front end of the first piston 41, and from the first piston 41 to the cylindrical member 50. The pressure plate 35 is pressed via
図２は、円筒部材５０の外観を示す外観図であり、円筒部材５０は、図示するように、後方側の外径が内方に屈曲し、その内端が軸方向に沿って後方に延びる段差部５２が形成されており、この段差部５２が第１のピストン４１の前端に嵌着されている。また、円筒部材５０は、側面には、出力軸１４に取り付けられた図示しない車速センサとの干渉防止用の孔５４と、パーキングポール２６との干渉防止用の孔５６と、パーキングポール２６をパーキングギヤ２５側に押し付けるための後述するパーキングカム２８との干渉防止用の孔５８とが形成されている。図３に、パーキングポール２８の正面図を示し、図４に、図３のパーキングポール２８をＡ方向から見た上面図を示し、図５に、円筒部材５０とパーキングポール２８とパーキングカム２８とを自動変速機１０に組み付けたときの円筒部材５０とパーキングポール２８とパーキングカム２８との位置関係を示し、図６に、図４のＤ−Ｄ断面を示す。図示するように、パーキングカム２８はその一部が円筒部材５０の干渉防止用の孔５８を介して円筒部材５０の外周側から内周側に入り込んでおり（図６参照）、パーキングポール２６はパーキングカム２８の動作によって円筒部材５０の内方側に押し付けられて噛み合い部２６ａが干渉防止用の孔５６を介して円筒部材５０の外周側から内周側に入り込み、噛み合い部２６ａが円筒部材５０の内周側に配置されたパーキングギヤ２５に噛み合うことにより、パーキングギヤ２５、即ち、出力軸１４を回転不能にロックする。 FIG. 2 is an external view showing the external appearance of the cylindrical member 50. As shown in the figure, the cylindrical member 50 has an outer diameter that is bent inward, and an inner end thereof extends rearward along the axial direction. A step portion 52 is formed, and the step portion 52 is fitted to the front end of the first piston 41. Further, the cylindrical member 50 has a hole 54 for preventing interference with a vehicle speed sensor (not shown) attached to the output shaft 14, a hole 56 for preventing interference with the parking pole 26, and the parking pole 26 on the side surface. A hole 58 for preventing interference with a later-described parking cam 28 for pressing the gear 25 is formed. 3 shows a front view of the parking pole 28, FIG. 4 shows a top view of the parking pole 28 of FIG. 3 viewed from the direction A, and FIG. 5 shows a cylindrical member 50, a parking pole 28, a parking cam 28, 4 shows the positional relationship among the cylindrical member 50, the parking pole 28, and the parking cam 28 when assembled to the automatic transmission 10, and FIG. 6 shows a DD cross section of FIG. As shown in the drawing, a part of the parking cam 28 enters the inner peripheral side from the outer peripheral side of the cylindrical member 50 through the interference preventing hole 58 of the cylindrical member 50 (see FIG. 6). The operation of the parking cam 28 is pressed toward the inner side of the cylindrical member 50, and the meshing portion 26 a enters the inner peripheral side from the outer peripheral side of the cylindrical member 50 through the interference preventing hole 56, and the meshing portion 26 a becomes the cylindrical member 50. The parking gear 25, that is, the output shaft 14 is locked so as not to rotate by meshing with the parking gear 25 disposed on the inner peripheral side of the parking gear 25.
図７は、パーキングカム２８との干渉防止用の孔５８の形状を説明する説明図である。なお、図７（ａ）に実施例におけるパーキングカム２８との干渉防止用の孔５８の形状を示し、図７（ｂ）に比較例におけるパーキングカム２８との干渉防止用の孔１５８の形状を示す。実施例の干渉防止用の孔５８は、図７（ａ）に示すように、第１の開口部５８ａと第１の開口部５８ａよりも段差部５２から離れた第２の開口部５８ｂとが軸方向（図中上下方向）に沿って連続して一つの孔をなし、軸方向に対して線対称（左右方向対称）の２段の段付き形状に形成されている。この干渉防止用の孔５８では、第１の開口部５８ａは周方向（図中左右方向）の幅がパーキングカム２８が入り込む幅に合わせて形成されており、第２の開口部５８ｂは周方向の幅が第１の開口部５８ａよりも広く設定されている。また、干渉防止用の孔５８では、軸方向の幅が円筒部材５０の移動範囲でパーキングカム２８が干渉しない幅に設定されており、第２の開口部５８ｂは軸方向の幅が第１の開口部５８ａよりも広く設定されている。また、干渉防止用の孔５８は、第１の開口部５８ａでは周方向側（図中左右端側）の開口縁と軸方向側（図中下端側）の開口縁とが共に直線状に形成され両開口縁がＲが比較的小さな円弧（図中領域Ｘ）をもって繋がれており、第２の開口部５８ｂでは周方向側（図中左右方向側）の開口縁がＲが比較的大きな円弧状（図中領域Ｙ）に形成されると共に軸方向側（図中上端側）の開口縁が直線状に形成されている。一方、比較例の干渉防止用の孔１５８は、図７（ｂ）に示すように、第１の開口部１５８ａは周方向（図中左右方向）の幅がパーキングカムが入り込む幅に合わせて形成されており、第２の開口部１５８ｂは第１の開口部１５８ａの周方向の幅を底面として段差部１５２から軸方向に離れるほど幅が狭くなる台形形状に形成されている。また、比較例の干渉防止用の孔１５８は、第１の開口部１５８ａでは周方向側の開口縁と軸方向側の開口縁とが共に直線状に形成され両開口縁が実施例の対応する箇所の領域Ｘに比してＲが大きな円弧（図中領域Ｚ）をもって繋がれている。 FIG. 7 is an explanatory diagram for explaining the shape of the hole 58 for preventing interference with the parking cam 28. 7A shows the shape of the hole 58 for preventing interference with the parking cam 28 in the embodiment, and FIG. 7B shows the shape of the hole 158 for preventing interference with the parking cam 28 in the comparative example. Show. As shown in FIG. 7A, the interference preventing hole 58 of the embodiment includes a first opening 58a and a second opening 58b that is farther from the step portion 52 than the first opening 58a. One hole is formed continuously along the axial direction (vertical direction in the figure), and is formed in a two-step step shape that is line-symmetric (laterally symmetric) with respect to the axial direction. In the interference preventing hole 58, the first opening 58a has a width in the circumferential direction (left-right direction in the figure) that matches the width into which the parking cam 28 enters, and the second opening 58b has a circumferential direction. Is set wider than the first opening 58a. Further, in the interference preventing hole 58, the axial width is set such that the parking cam 28 does not interfere with the movement range of the cylindrical member 50, and the second opening 58b has the first axial width. It is set wider than the opening 58a. Further, in the first opening 58a, the interference preventing hole 58 is formed such that the opening edge on the circumferential direction side (left and right end side in the figure) and the opening edge on the axial direction side (lower end side in the figure) are both linear. Both opening edges are connected by a circular arc having a relatively small R (region X in the figure), and the opening edge on the circumferential direction side (left and right direction side in the figure) is a circle having a relatively large R in the second opening 58b. It is formed in an arc shape (region Y in the figure) and the opening edge on the axial direction side (upper end side in the figure) is formed linearly. On the other hand, as shown in FIG. 7B, the interference prevention hole 158 of the comparative example is formed so that the first opening 158a has a width in the circumferential direction (left-right direction in the figure) that fits into the parking cam. The second opening 158b is formed in a trapezoidal shape having a width in the circumferential direction of the first opening 158a as a bottom surface and narrowing as the distance from the stepped portion 152 in the axial direction decreases. Further, the interference preventing hole 158 of the comparative example is such that both the opening edge on the circumferential side and the opening edge on the axial direction side are linearly formed in the first opening 158a, and both opening edges correspond to the embodiment. R is connected with a circular arc (region Z in the figure) where R is larger than the region X.
こうして形成された実施例の円筒部材５０は、段差部５２が第１のピストン４１からの押圧を受ける受圧部となるため、円筒部材５０に形成された３つの干渉防止用の孔５４，５６，５８のうち最も段差部５２の近くまで開口領域が広がる干渉防止用の孔５８に応力が集中し易い。実施例では、干渉防止用の孔５８を、第１の開口部５８ａと第１の開口部５８ａよりも段差部５２から離れた第２の開口部５８ｂとが軸方向に沿って連続して一つの孔をなすよう段付き形状とし、第２の開口部５８ｂを周方向の幅が第１の開口部５８ａよりも広くなると共に周方向側の開口縁がＲが領域Ｘよりも大きな円弧状（領域Ｙ）となるよう形成するから、第１の開口部５８ａの領域Ｘに作用する応力を第２の開口部５８ｂの領域Ｙにも分散することができる。従って、円筒部材５０が第１のピストン４１による押圧を受けるものとしても、応力が一部の箇所に集中することがないから、その耐久性を向上させることができる。一方、比較例では、円筒部材１５０の段差部１５２を押圧力が受けると、第１の開口部１５８ａの最弱部分である領域Ｚに応力が集中するため、変形や破損のおそれが生じる。 Since the cylindrical member 50 of the embodiment formed in this way is a pressure receiving portion where the step portion 52 receives the pressure from the first piston 41, the three interference preventing holes 54, 56, The stress is likely to concentrate in the interference preventing hole 58 in which the opening region extends to the vicinity of the stepped portion 52 most of the 58. In the embodiment, the interference preventing hole 58 is formed such that the first opening 58a and the second opening 58b farther from the stepped portion 52 than the first opening 58a are continuously arranged along the axial direction. The second opening 58b has an arcuate shape in which the circumferential width of the second opening 58b is wider than that of the first opening 58a and the circumferential edge of the opening R is larger than the region X. Since the region Y) is formed, the stress acting on the region X of the first opening 58a can be distributed to the region Y of the second opening 58b. Therefore, even if the cylindrical member 50 is pressed by the first piston 41, the stress does not concentrate on a part of the portion, so that the durability can be improved. On the other hand, in the comparative example, when a pressing force is applied to the stepped portion 152 of the cylindrical member 150, the stress concentrates on the region Z that is the weakest portion of the first opening 158a, which may cause deformation or breakage.
以上説明した実施例のピストン部材２０によれば、円筒部材５０を押圧部として第１のピストン４１から円筒部材５０を介して多板のブレーキ３０を軸方向に沿って押圧するものにおいて、円筒部材５０の側面に形成されパーキングカム２８の一部が円筒部材５０の外周側から内周側に入り込む干渉防止用の孔５８を、第１の開口部５８ａと第１の開口部５８ａよりも段差部５２から離れた第２の開口部５８ｂとが軸方向に沿って連続して一つの孔をなすよう段付き形状とし、第２の開口部５８ｂを周方向の幅が第１の開口部５８ａよりも広くなると共に周方向側の開口縁が円弧状となるよう形成するから、第１の開口部５８ａの開口縁（図７中の領域Ｘ）に作用する応力を第２の開口部５８ｂの円弧状の開口縁（図７中の領域Ｙ）にも分散することができる。この結果、円筒部材５０が第１のピストン４１による押圧を受けるものとしても、応力が一部の箇所に集中することがないから、耐久性をより向上させることができる。 According to the piston member 20 of the embodiment described above, the cylindrical member 50 is used as the pressing portion to press the multi-plate brake 30 along the axial direction from the first piston 41 via the cylindrical member 50. 50, a part of the parking cam 28 into which the part of the parking cam 28 enters the inner peripheral side from the outer peripheral side of the cylindrical member 50 is provided with a stepped portion than the first opening 58a and the first opening 58a. The second opening 58b away from the second opening 58b is stepped so as to continuously form one hole along the axial direction, and the second opening 58b has a circumferential width larger than that of the first opening 58a. Since the opening edge on the circumferential side is formed in an arc shape, the stress acting on the opening edge (region X in FIG. 7) of the first opening 58a is applied to the circle of the second opening 58b. Dispersed to arc-shaped opening edge (region Y in FIG. 7) Rukoto can. As a result, even if the cylindrical member 50 is pressed by the first piston 41, the stress does not concentrate at a part of the portion, so that the durability can be further improved.
実施例では、干渉防止用の孔５８における孔形状を軸方向に対して線対称に形成するものとしたが、これに限定されるものではなく、非対称に形成するものとしてもよい。 In the embodiment, the hole shape in the interference preventing hole 58 is formed symmetrically with respect to the axial direction. However, the present invention is not limited to this, and the hole shape may be formed asymmetrically.
実施例では、干渉防止用の孔５８における第２の開口部５８ｂを軸方向の幅が第１の開口部５８ａよりも広くなるよう形成するものとしたが、両開口部５８ａ，５８ｂで軸方向の幅を略同一とするものとしてもよいし、第２の開口部５８ｂを軸方向の幅が第１の開口部５８ａよりも狭くなるよう形成するものとしてもよい。 In the embodiment, the second opening 58b in the interference preventing hole 58 is formed so that the axial width is wider than that of the first opening 58a. However, both the openings 58a and 58b are axially formed. The second openings 58b may be formed so that the width in the axial direction is narrower than that of the first openings 58a.
実施例では、干渉防止用の孔５８における第２の開口部５８ｂを周方向側の開口縁が円弧状となるよう形成するものとしたが、これに限定されるものではなく、隅部で円弧が形成されていれば直線状に形成するものとしても差し支えない。 In the embodiment, the second opening 58b in the interference preventing hole 58 is formed so that the opening edge on the circumferential side has an arc shape. However, the present invention is not limited to this. If it is formed, it may be formed linearly.
実施例では、干渉防止用の孔５８の形状を、第１の開口部５８ａと第２の開口部５８ｂとからなる２段の段付き形状に形成するものとしたが、周方向の幅が段差部５２から離れるに従って広くなる３つ以上の開口部により３段以上の段付き形状に形成するものとしてもよい。 In the embodiment, the shape of the interference preventing hole 58 is formed in a two-stepped shape including the first opening 58a and the second opening 58b, but the width in the circumferential direction is a step. It is good also as what is formed in the stepped shape of 3 steps | paragraphs or more by the 3 or more opening part which becomes wide as it leaves | separates from the part 52. FIG.
実施例では、パーキングカム２８の干渉防止用の孔５８の形状を、第１の開口部５８ａと第２の開口部５８ｂとからなる２段の段付き形状に形成するものとしたが、車速センサの干渉防止用の孔５４の形状を応力を分散させるための上述した段付き形状に形成するものとしてもよいし、パーキングポール２６の干渉防止用の孔５６の形状を上述した段付き形状に形成するものとしてもよい。 In the embodiment, the shape of the interference preventing hole 58 of the parking cam 28 is formed in a two-stepped shape including the first opening 58a and the second opening 58b. The interference prevention hole 54 may be formed in the above-described stepped shape for dispersing stress, and the interference prevention hole 56 of the parking pole 26 is formed in the above-described stepped shape. It is good also as what to do.
実施例では、車両に搭載された自動変速機が備えるクラッチやブレーキをピストンにより押圧する油圧アクチュエータに適用して説明するものとしたが、これに限られず、油圧を受けて軸方向に移動して摩擦係合要素を押圧するものであれば、如何なるものに適用するものとしてもよい。 In the embodiment, the description is made by applying the clutch or brake included in the automatic transmission mounted on the vehicle to the hydraulic actuator that presses the piston. However, the present invention is not limited to this, and receives the hydraulic pressure and moves in the axial direction. As long as it presses the frictional engagement element, it may be applied to anything.
ここで、実施例の主要な要素と課題を解決するための手段の欄に記載した発明の主要な要素との対応関係について説明する。実施例では、第１のピストン４１と第２のピストン４２と中間部材４３と円筒部材５０とが「ピストン部材」に相当し、円筒部材５０が「押圧部」に相当し、干渉防止用の孔５８が「干渉防止用の孔」に相当し、第１の開口部５８ａが「第１の開口部」に相当し、第２の開口部５８ｂが「第２の開口部」に相当する。なお、実施例の主要な要素と課題を解決するための手段の欄に記載した発明の主要な要素との対応関係は、実施例が課題を解決するための手段の欄に記載した発明を実施するための最良の形態を具体的に説明するための一例であることから、課題を解決するための手段の欄に記載した発明の要素を限定するものではない。即ち、課題を解決するための手段の欄に記載した発明についての解釈はその欄の記載に基づいて行なわれるべきものであり、実施例は課題を解決するための手段の欄に記載した発明の具体的な一例に過ぎないものである。 Here, the correspondence between the main elements of the embodiment and the main elements of the invention described in the column of means for solving the problems will be described. In the embodiment, the first piston 41, the second piston 42, the intermediate member 43, and the cylindrical member 50 correspond to a “piston member”, the cylindrical member 50 corresponds to a “pressing portion”, and a hole for preventing interference. 58 corresponds to the “interference prevention hole”, the first opening 58a corresponds to the “first opening”, and the second opening 58b corresponds to the “second opening”. The correspondence between the main elements of the embodiment and the main elements of the invention described in the column of means for solving the problem is the same as that of the embodiment described in the column of means for solving the problem. It is an example for specifically explaining the best mode for doing so, and does not limit the elements of the invention described in the column of means for solving the problem. That is, the interpretation of the invention described in the column of means for solving the problems should be made based on the description of the column, and the examples are those of the invention described in the column of means for solving the problems. It is only a specific example.
以上、本発明を実施するための最良の形態について実施例を用いて説明したが、本発明はこうした実施例に何等限定されるものではなく、本発明の要旨を逸脱しない範囲内において、種々なる形態で実施し得ることは勿論である。 The best mode for carrying out the present invention has been described with reference to the embodiments. However, the present invention is not limited to these embodiments, and various modifications can be made without departing from the gist of the present invention. Of course, it can be implemented in the form.
本発明は、ピストン部材の製造産業などに利用可能である。 The present invention can be used in the manufacturing industry of piston members.
１０ 自動変速機、１２ ケース、１２ａ スプライン溝、１４ 出力軸、２０ 遊星歯車機構、２１ サンギヤ、２２ リングギヤ、２２ａ スプライン溝、２３ ピニオンギヤ、２４ キャリア、２５ パーキングギヤ、２６ パーキングポール、２８ パーキングカム、３０ ブレーキ、３１ 摩擦板、３２ セパレータ、３３ アウターレース、３４ スナップリング、３５ プレッシャープレート、４０ 油圧アクチュエータ、４１ 第１のピストン、４２ 第２のピストン、４３ 中間部材、４４ 支持プレート、４５ リターンスプリング、５０ 円筒部材、５２ 段差部、５４，５６，５８ 干渉防止用の孔、５８ａ 第１の開口部、５８ｂ 第２の開口部、１５０ 円筒部材、１５２ 段差部、１５８ａ 第１の開口部、１５８ｂ 第２の開口部。 10 automatic transmission, 12 case, 12a spline groove, 14 output shaft, 20 planetary gear mechanism, 21 sun gear, 22 ring gear, 22a spline groove, 23 pinion gear, 24 carrier, 25 parking gear, 26 parking pole, 28 parking cam, 30 Brake, 31 Friction plate, 32 Separator, 33 Outer race, 34 Snap ring, 35 Pressure plate, 40 Hydraulic actuator, 41 1st piston, 42 2nd piston, 43 Intermediate member, 44 Support plate, 45 Return spring, 50 Cylindrical member, 52 stepped portion, 54, 56, 58 Interference prevention hole, 58a first opening, 58b second opening, 150 cylindrical member, 152 stepped portion, 158a first opening, 158b second Opening
Claims (6)
前記押圧部は、他の部材との干渉防止用の孔を側面に有する円筒状に形成され、
前記干渉防止用の孔は、前記押圧部の周方向の幅が前記他の部材を挿通可能に設定された第１の開口部と、前記押圧部の周方向の幅が前記第１の開口部よりも広く且つ該第１の開口部よりも前記押圧部の受圧部から離れた第２の開口部とが軸方向に沿って連続して一つの孔をなすよう段付き形状に形成されてなる
ことを特徴とするピストン部材。 A piston member that has a pressing portion that receives hydraulic pressure and moves in the axial direction to press the friction engagement element,
The pressing part is formed in a cylindrical shape having holes for preventing interference with other members on the side surface,
The interference preventing hole includes a first opening in which a circumferential width of the pressing portion is set to be able to pass through the other member, and a circumferential width of the pressing portion is the first opening. The second opening that is wider than the first opening and away from the pressure receiving portion of the pressing portion is formed in a stepped shape so as to continuously form one hole along the axial direction. A piston member characterized by that.
前記第１の開口部は、開口縁の少なくとも一部が円弧状に形成され、
前記第２の開口部は、前記第１の開口部よりも円弧の径が大きくなるよう形成されてなる
ピストン部材。 The piston member according to claim 2,
In the first opening, at least a part of the opening edge is formed in an arc shape,
The piston member, wherein the second opening is formed to have a larger arc diameter than the first opening.
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| JP2011075703A JP5413395B2 (en) | 2011-03-30 | 2011-03-30 | Piston member |
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| JP2011075703A JP5413395B2 (en) | 2011-03-30 | 2011-03-30 | Piston member |
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| JP5413395B2 true JP5413395B2 (en) | 2014-02-12 |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS60249732A (en) * | 1984-05-23 | 1985-12-10 | Toyota Motor Corp | Servo device for friction engaging apparatus |
| JP4449178B2 (en) * | 2000-07-04 | 2010-04-14 | アイシン・エィ・ダブリュ株式会社 | Hydraulic servo piston |
| JP4843405B2 (en) * | 2006-08-02 | 2011-12-21 | 光洋シーリングテクノ株式会社 | Sealing device |
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