JP4940650B2 - Vehicle seat adjustment device - Google Patents

Vehicle seat adjustment device Download PDF

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JP4940650B2
JP4940650B2 JP2005368630A JP2005368630A JP4940650B2 JP 4940650 B2 JP4940650 B2 JP 4940650B2 JP 2005368630 A JP2005368630 A JP 2005368630A JP 2005368630 A JP2005368630 A JP 2005368630A JP 4940650 B2 JP4940650 B2 JP 4940650B2
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output shaft
force
input side
control member
clutch
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JP2007168600A (en
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幸史 山田
康敬 小島
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Aisin Corp
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Aisin Seiki Co Ltd
Aisin Corp
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  • Chairs Characterized By Structure (AREA)
  • Mechanical Operated Clutches (AREA)
  • Braking Arrangements (AREA)

Description

本発明は、シートクッションの高さを調整する車両用シート調整装置に係り、詳しくは車両用シート調整装置のクラッチ装置に関するものである。   The present invention relates to a vehicle seat adjustment device that adjusts the height of a seat cushion, and more particularly to a clutch device of a vehicle seat adjustment device.

従来、車両用シートには、シートクッションの高さを調整する車両用シート調整装置が設けられたものがある。このような車両用シート調整装置では、乗員がシート上に乗車した状態で、操作レバーの操作によりシートクッションの高さを調整可能となっている。   Conventionally, some vehicle seats are provided with a vehicle seat adjustment device that adjusts the height of the seat cushion. In such a vehicle seat adjustment device, the height of the seat cushion can be adjusted by operating the operation lever while the occupant is on the seat.

例えば、特許文献１に開示された車両用シート調整装置は、操作レバーによる正方向又は逆方向の入力トルクを入力することによってシートクッションの高さの調整を行うとともに、操作レバーを解放した状態でのシートクッションの位置を保持する第１クラッチ部及び第２クラッチ部を備えている。そして、操作レバーに操作力が入力されると、第１クラッチ部において操作レバーが取り付けられた外輪からローラを介して内輪に操作力が伝達され、第２クラッチ部において内輪から出力軸に操作力が伝達されることで、操作レバーの操作力は出力軸に伝達される。また、操作レバーの駆動操作以外のときは、第２クラッチ部が出力軸の回動を規制する。
特開２００２−５４６５８号公報（第１図） For example, in the vehicle seat adjustment device disclosed in Patent Document 1, the height of the seat cushion is adjusted by inputting the input torque in the forward direction or the reverse direction by the operation lever, and the operation lever is released. The first clutch portion and the second clutch portion that hold the position of the seat cushion are provided. When an operating force is input to the operating lever, the operating force is transmitted from the outer ring, to which the operating lever is attached in the first clutch portion, to the inner ring via a roller, and in the second clutch portion, the operating force is applied from the inner ring to the output shaft. Is transmitted, the operating force of the operating lever is transmitted to the output shaft. When the operation lever is not driven, the second clutch portion restricts the rotation of the output shaft.
Japanese Patent Laid-Open No. 2002-54658 (FIG. 1)

しかし、上記の車両用シート調整装置では、第１クラッチ部と第２クラッチ部ともに力の伝達方向が径方向内向きとなるように構成されているため、外輪を中立位置に戻すための戻しスプリングが軸方向に配置された両クラッチ部間に配置されている。このため、両クラッチ部は軸方向に離間して配置されており、第１クラッチ部から第２クラッチ部へ回転力を伝達する制御部材が軸方向に長くなる。このため、両クラッチ部間の力の伝達の際に制御部材に大きな捻り力が加わる。このため、制御部材は、大きな捻り力に耐えられるような強度が必要となる、例えば制御部材を径方向に厚くする必要があり、装置の大型化を招いていた。   However, in the above-described vehicle seat adjustment device, both the first clutch portion and the second clutch portion are configured such that the force transmission direction is radially inward, so that the return spring for returning the outer ring to the neutral position Is arranged between both clutch parts arranged in the axial direction. For this reason, both clutch parts are spaced apart from each other in the axial direction, and the control member that transmits the rotational force from the first clutch part to the second clutch part becomes longer in the axial direction. For this reason, a large twisting force is applied to the control member during transmission of the force between the two clutch portions. For this reason, the control member needs to be strong enough to withstand a large torsional force. For example, the control member needs to be thickened in the radial direction, leading to an increase in the size of the apparatus.

また、第１クラッチ部において外輪のカム面（内周面）がローラを介して径方向外側に向けて力を受けるため、その力により変形しないように外輪を肉厚とする必要があり、やはり装置の大型化を招くという問題があった。   Moreover, since the cam surface (inner peripheral surface) of the outer ring receives a force toward the radially outer side via the roller in the first clutch portion, it is necessary to make the outer ring thick so as not to be deformed by the force. There was a problem that the size of the apparatus was increased.

本発明は、こうした実情に鑑みてなされたものであり、その目的は、装置の小型化を図ることができる車両用シート調整装置を提供することにある。   The present invention has been made in view of such circumstances, and an object of the present invention is to provide a vehicle seat adjustment device capable of reducing the size of the device.

上記課題を解決するために、請求項１に記載の発明は、操作部材の操作に従って出力軸を回動させ、該出力軸の回動によりシートクッションを上下方向に移動させる車両用シート調整装置であって、前記操作部材が連結され前記出力軸に軸支された入力側部材と、前記入力側部材の径方向外側に配置された制御部材と、前記操作部材の駆動操作時には該操作部材の操作力を前記入力側部材から前記制御部材に伝達可能とし、前記操作部材の復帰時には前記入力側部材と前記制御部材との力の伝達を解除する第１クラッチ部と、前記操作部材の駆動操作時には該操作部材の操作力を前記制御部材から前記出力軸に伝達可能とし、前記操作部材の駆動操作以外のときに前記出力軸の回動を規制する第２クラッチ部と、前記制御部材の径方向外側に配置され、内周面で前記操作部材の駆動操作以外のときに前記出力軸の回動を規制する静止部材とを備え、前記制御部材の前記第１クラッチ部を収容した部分の半径を前記静止部材の内周面と同じとして該静止部材の内周面で前記制御部材を軸受けし、前記制御部材及び前記静止部材は、前記第１クラッチ部の径方向外側に、前記第１クラッチ部の径方向外側に向かう力を受けるべく径方向に延びた段差部をそれぞれ有することを要旨とする。 In order to solve the above-described problem, the invention according to claim 1 is a vehicle seat adjustment device that rotates an output shaft in accordance with an operation of an operation member and moves a seat cushion in the vertical direction by the rotation of the output shaft. An input side member connected to the operation member and pivotally supported by the output shaft; a control member disposed radially outside the input side member; and operating the operation member when the operation member is driven. A force can be transmitted from the input side member to the control member, and when the operation member is returned, a first clutch portion that releases transmission of force between the input side member and the control member; A second clutch portion that allows the operating force of the operating member to be transmitted from the control member to the output shaft, and restricts the rotation of the output shaft when the operating member is not driven; and the radial direction of the control member Outside And a stationary member for restricting the rotation of the output shaft at a time other than the drive operation of the operation member on the inner peripheral surface, and the radius of the portion of the control member containing the first clutch portion is stationary. The control member is supported by the inner peripheral surface of the stationary member in the same manner as the inner peripheral surface of the member, and the control member and the stationary member are arranged on the outer side in the radial direction of the first clutch portion. The gist of the invention is to have stepped portions extending in the radial direction so as to receive a force directed outward in the direction .

上記構成によれば、第１クラッチ部においては径方向内側から径方向外側に向けて力が伝達され、第２クラッチ部においては径方向外側から径方向内側に向けて力が伝達されるため、第１クラッチ部においても径方向外側から径方向内側に向けて力が伝達される場合と比較して、両クラッチ部の半径差が小さくなる。このため、操作力の伝達時に両クラッチ部間に生じる捻り力が低減されるため、捻り力を考慮した部材の補強は必要なく、装置の小型化を図ることができる。
また、制御部材が第１クラッチ部から受ける圧力を静止部材の内周面で受けることにより、制御部材の径方向の変形を抑制し、制御部材のみで前記圧力を受ける場合と比較して制御部材を薄肉化することが可能となる。
また、制御部材において第１クラッチ部の径方向外側に向かう力を受ける部位に径方向に延びた段差部が在るため、制御部材はその力を好適に受け止めることができる。また、静止部材において第１クラッチ部の径方向外側に向かう力を受ける部位に径方向に延びた段差部が在るため、静止部材はその力を好適に受け止めることができる。 According to the above configuration, the force is transmitted from the radially inner side to the radially outer side in the first clutch portion, and the force is transmitted from the radially outer side to the radially inner side in the second clutch portion. Also in the first clutch portion, the radial difference between both clutch portions is smaller than when force is transmitted from the radially outer side toward the radially inner side. For this reason, since the torsional force generated between the two clutch parts when the operating force is transmitted is reduced, the member need not be reinforced in consideration of the torsional force, and the apparatus can be downsized.
Further, by receiving the pressure received by the control member from the first clutch portion on the inner peripheral surface of the stationary member, the control member is prevented from being deformed in the radial direction, and compared with the case where the pressure is received only by the control member. Can be made thinner.
Moreover, since the step part extended in radial direction exists in the site | part which receives the force which goes to the radial direction outer side of a 1st clutch part in a control member, the control member can receive the force suitably. Moreover, since the step part extended in radial direction exists in the site | part which receives the force which goes to the radial direction outer side of a 1st clutch part in a stationary member, a stationary member can receive the force suitably.

請求項２に記載の発明は、操作部材の操作に従って出力軸を回動させ、該出力軸の回動によりシートクッションを上下方向に移動させる車両用シート調整装置であって、前記操作部材が連結され前記出力軸に軸支された入力側部材と、前記入力側部材の径方向外側に配置された制御部材と、前記操作部材の駆動操作時には該操作部材の操作力を前記入力側部材から前記制御部材に伝達可能とし、前記操作部材の復帰時には前記入力側部材と前記制御部材との力の伝達を解除する第１クラッチ部と、前記操作部材の駆動操作時には該操作部材の操作力を前記制御部材から前記出力軸に伝達可能とし、前記操作部材の駆動操作以外のときに前記出力軸の回動を規制する第２クラッチ部とを備え、前記第１クラッチ部は前記入力側部材のカム面と前記制御部材の内周面との間の力の伝達を可能とする第１回転体を備え、前記第２クラッチ部は前記制御部材の内周面と前記出力軸に連結された回動部材のカム面との間の力の伝達を可能とする第２回転体を備え、前記第１回転体の端部と前記第２回転体の端部とが、軸方向に同一又は重複するように配置されていることを要旨とする。 According to a second aspect of the present invention, there is provided a vehicle seat adjustment device that rotates an output shaft in accordance with an operation of an operation member and moves a seat cushion in a vertical direction by the rotation of the output shaft. And an input side member pivotally supported by the output shaft, a control member disposed radially outside the input side member, and an operating force of the operating member from the input side member when the operating member is driven. A first clutch portion that cancels transmission of force between the input side member and the control member when the operation member is returned; and an operation force of the operation member when the operation member is driven. A second clutch portion that is capable of transmitting from the control member to the output shaft and restricts the rotation of the output shaft when the operation member is not driven, and the first clutch portion is a cam of the input side member. Front and front A rotating member cam that includes a first rotating body that enables transmission of force between the inner peripheral surface of the control member and the second clutch portion is connected to the inner peripheral surface of the control member and the output shaft. A second rotating body capable of transmitting a force to the surface, and the end of the first rotating body and the end of the second rotating body are arranged so as to be the same or overlap in the axial direction. It is a summary.

上記構成によれば、第１クラッチ部においては径方向内側から径方向外側に向けて力が伝達され、第２クラッチ部においては径方向外側から径方向内側に向けて力が伝達されるため、第１クラッチ部においても径方向外側から径方向内側に向けて力が伝達される場合と比較して、両クラッチ部の半径差が小さくなる。このため、操作力の伝達時に両クラッチ部間に生じる捻り力が低減されるため、捻り力を考慮した部材の補強は必要なく、装置の小型化を図ることができる。
また、第１クラッチ部に設けられた第１回転体の端部と、第２クラッチ部に設けられた第２回転体の端部とが、軸方向に同一又は重複するように配置されることで、第１クラッチ部と第２クラッチ部とが近接配置される。このため、第１クラッチ部と第２クラッチ部との間に他の部材が配置される場合と比較して、操作部材の駆動操作時の第１クラッチ部と第２クラッチ部との間の操作力の伝達経路が短くなり、操作力の伝達効率が向上する。 According to the above configuration, the force is transmitted from the radially inner side to the radially outer side in the first clutch portion, and the force is transmitted from the radially outer side to the radially inner side in the second clutch portion. Also in the first clutch portion, the radial difference between both clutch portions is smaller than when force is transmitted from the radially outer side toward the radially inner side. For this reason, since the torsional force generated between the two clutch parts when the operating force is transmitted is reduced, the member need not be reinforced in consideration of the torsional force, and the apparatus can be downsized.
Also, the end of the first rotating body provided in the first clutch portion and the end of the second rotating body provided in the second clutch portion are arranged so as to be the same or overlap in the axial direction. Thus, the first clutch part and the second clutch part are arranged close to each other. For this reason, compared with the case where another member is arrange | positioned between a 1st clutch part and a 2nd clutch part, operation between the 1st clutch part and the 2nd clutch part at the time of drive operation of an operation member is carried out The force transmission path is shortened, and the transmission efficiency of operating force is improved.

請求項３に記載の発明は、請求項１又は２に記載の車両用シート調整装置において、前記入力側部材が解放されたときに該入力側部材を中立位置に復帰させる復帰手段を備え、前記復帰手段を軸方向に前記操作部材に近接した位置に配置したことを要旨とする。   According to a third aspect of the present invention, in the vehicle seat adjustment device according to the first or second aspect, the vehicle-side seat adjustment device further includes a return unit that returns the input-side member to a neutral position when the input-side member is released, The gist is that the return means is disposed at a position close to the operation member in the axial direction.

上記構成によれば、入力側部材を中立位置に復帰させる復帰手段が軸方向に操作部材に近接した位置に配置されているため、復帰手段の付勢力が入力側部材に効率よく伝達される。   According to the above configuration, since the return means for returning the input side member to the neutral position is disposed at a position close to the operation member in the axial direction, the urging force of the return means is efficiently transmitted to the input side member.

本発明の車両用シート調整装置によれば、装置の小型化を図ることができる。   According to the vehicle seat adjustment device of the present invention, the device can be miniaturized.

以下、本発明と具体化した一実施形態を図面に従って説明する。
図１及び図２に示す車両用シート１は、シートクッション１ａとシートクッション１ａの後端上面から斜め上側に延びるシートバック１ｂとを備え、車両のフロアに固定されたロアレール２ａ，２ｂ上に移動可能に支持される。シートクッション１ａの下側には、シートクッション１ａの座面の高さを調整する車両用シート調整装置３が設けられている。 DESCRIPTION OF EXEMPLARY EMBODIMENTS Hereinafter, an embodiment embodying the invention will be described with reference to the drawings.
The vehicle seat 1 shown in FIGS. 1 and 2 includes a seat cushion 1a and a seat back 1b extending obliquely upward from the upper surface of the rear end of the seat cushion 1a, and moves on lower rails 2a and 2b fixed to the vehicle floor. Supported as possible. A vehicle seat adjustment device 3 that adjusts the height of the seating surface of the seat cushion 1a is provided below the seat cushion 1a.

ロアレール２ａ，２ｂにはそれぞれアッパレール４ａ，４ｂが摺動可能に装着されている。アッパレール４ａ，４ｂには、シートクッション１ａのベースフレーム５ａ，５ｂが昇降可能に支持されている。   Upper rails 4a and 4b are slidably mounted on the lower rails 2a and 2b, respectively. Base frames 5a and 5b of the seat cushion 1a are supported on the upper rails 4a and 4b so as to be movable up and down.

即ち、アッパレール４ａの前後端部にリフタリンク６ａ，７ａの下端部が回動可能に支持され、そのリフタリンク６ａ，７ａの上端部がベースフレーム５ａの前後端部に回動可能に連結されている。同様に、アッパレール４ｂの前後端部にリフタリンク６ｂ，７ｂの下端部が回動可能に支持され、そのリフタリンク６ｂ，７ｂの上端部がベースフレーム５ｂの前後端部に回動可能に連結されている。また、リフタリンク７ａ，７ｂとベースフレーム５ａ，５ｂの連結部は筒状のトルクロッド８で連結されている。従って、ベースフレーム５ａ，５ｂは連動して昇降可能である。   That is, the lower end portions of the lifter links 6a and 7a are rotatably supported on the front and rear end portions of the upper rail 4a, and the upper end portions of the lifter links 6a and 7a are rotatably connected to the front and rear end portions of the base frame 5a. Yes. Similarly, the lower ends of the lifter links 6b and 7b are rotatably supported on the front and rear ends of the upper rail 4b, and the upper ends of the lifter links 6b and 7b are rotatably connected to the front and rear ends of the base frame 5b. ing. Further, the connecting portions of the lifter links 7 a and 7 b and the base frames 5 a and 5 b are connected by a cylindrical torque rod 8. Accordingly, the base frames 5a and 5b can be moved up and down in conjunction with each other.

ベースフレーム５ｂには車両用シート調整装置３を構成するクラッチ装置１１が取着され、そのクラッチ装置１１に操作部材としての操作レバー１２が取着され、クラッチ装置１１の出力軸にはピニオンギヤ１３が設けられている。そして、操作レバー１２の操作によりピニオンギヤ１３が回転される。クラッチ装置１１の後方において、ベースフレーム５ｂにはセクタギヤ１４の基端側下部が回動可能に支持され、そのセクタギヤ１４の先端部にはピニオンギヤ１３に噛み合う歯部１４ａが形成されている。そして、ピニオンギヤ１３の回転にともなってセクタギヤ１４が回動するようになっている。セクタギヤ１４の基端側上部と、リフタリンク７ｂの上端部は駆動リンク１５で連結されている。駆動リンク１５は、セクタギヤ１４及びリフタリンク７ｂに対しそれぞれ回動可能に連結されている。従って、セクタギヤ１４が回動されると、駆動リンク１５を介してリフタリンク７ｂが回動され、トルクロッド８を介してリフタリンク７ａが回動され、ベースフレーム５ａ，５ｂが連動して昇降される。   A clutch device 11 constituting the vehicle seat adjusting device 3 is attached to the base frame 5b, an operation lever 12 as an operation member is attached to the clutch device 11, and a pinion gear 13 is attached to the output shaft of the clutch device 11. Is provided. Then, the pinion gear 13 is rotated by the operation of the operation lever 12. At the rear of the clutch device 11, the base frame 5 b rotatably supports the lower portion of the base end side of the sector gear 14, and a tooth portion 14 a that meshes with the pinion gear 13 is formed at the distal end portion of the sector gear 14. The sector gear 14 rotates with the rotation of the pinion gear 13. The upper part of the base end side of the sector gear 14 and the upper end part of the lifter link 7 b are connected by a drive link 15. The drive link 15 is rotatably connected to the sector gear 14 and the lifter link 7b. Accordingly, when the sector gear 14 is rotated, the lifter link 7b is rotated via the drive link 15, the lifter link 7a is rotated via the torque rod 8, and the base frames 5a and 5b are moved up and down in conjunction with each other. The

次に、上記クラッチ装置１１の具体的構成を説明する。
図３及び図４に示すように、クラッチ装置１１は、略円筒状に形成された静止部材としてのケース２１を備え、該ケース２１は、図５に示すように、径方向外側に突出形成された複数の取付部２１ａにより、ベースフレーム５ｂに取付固定されている。また、ケース２１は、操作レバー１２側の小径部２１ｂと、反操作レバー１２側の大径部２１ｃとを備え、小径部２１ｂと大径部２１ｃとの間には径方向に延びた段差部２１ｄが形成されている。そして、ケース２１の内側には出力軸２２が配置され、該出力軸２２はベースフレーム５ｂに回転自在に支持されている。 Next, a specific configuration of the clutch device 11 will be described.
As shown in FIGS. 3 and 4, the clutch device 11 includes a case 21 as a stationary member formed in a substantially cylindrical shape, and the case 21 is formed to protrude radially outward as shown in FIG. 5. The plurality of attachment portions 21a are attached and fixed to the base frame 5b. The case 21 includes a small diameter portion 21b on the operation lever 12 side and a large diameter portion 21c on the counter operation lever 12 side, and a step portion extending in the radial direction between the small diameter portion 21b and the large diameter portion 21c. 21d is formed. An output shaft 22 is disposed inside the case 21, and the output shaft 22 is rotatably supported by the base frame 5b.

出力軸２２には、ベースフレーム５ｂの操作レバー１２側に回動部材としてのロータカム２３が一体形成され、ベースフレーム５ｂの反操作レバー１２側にピニオンギヤ１３が一体形成されている。ロータカム２３は、略６角形状に形成されて外周面がカム面２３ａとして構成され、各辺の中央位置に嵌着溝２３ｂがそれぞれ形成されている。なお、出力軸２２とロータカム２３、出力軸２２とピニオンギヤ１３とをそれぞれ別体にて形成し一体回転するように係合してもよい。   The output shaft 22 is integrally formed with a rotor cam 23 as a rotating member on the operation lever 12 side of the base frame 5b, and a pinion gear 13 is integrally formed on the non-operation lever 12 side of the base frame 5b. The rotor cam 23 is formed in a substantially hexagonal shape, the outer peripheral surface is configured as a cam surface 23a, and a fitting groove 23b is formed at the center position of each side. The output shaft 22 and the rotor cam 23, and the output shaft 22 and the pinion gear 13 may be formed separately and engaged so as to rotate integrally.

出力軸２２には、図１及び図２に示す操作レバー１２が取着された入力側部材２４が回転自在に支持されている。図４に示すように、入力側部材２４は、円筒状に形成され出力軸２２が挿通される内輪２５と、該内輪２５から径方向外側に向かって延びた板状のレバー係合部２６とを備えている。レバー係合部２６には、図６に示すように、操作レバー１２が嵌着される複数（図においては３個）の嵌着孔２６ａが周方向に沿って配列されている。これにより、入力側部材２４は、操作レバー１２とともに回動する。また、出力軸２２の先端部には、波型ばねや皿ばねからなる弾性体２７とワッシャ２８ａ，２８ｂとがネジ２９により取着され、該弾性体２７により入力側部材２４が軸方向に付勢されている。図７に示すように、内輪２５は、軸（図において表裏方向）が直交する断面において、内周が円状に形成され、外周が略５角形状に形成されており、該内輪２５の外周面がカム面２５ａを構成している。   An input side member 24 to which the operation lever 12 shown in FIGS. 1 and 2 is attached is rotatably supported on the output shaft 22. As shown in FIG. 4, the input side member 24 includes an inner ring 25 that is formed in a cylindrical shape and through which the output shaft 22 is inserted, and a plate-like lever engaging portion 26 that extends radially outward from the inner ring 25. It has. As shown in FIG. 6, a plurality (three in the figure) of fitting holes 26 a into which the operation lever 12 is fitted are arranged in the lever engaging portion 26 along the circumferential direction. As a result, the input side member 24 rotates together with the operation lever 12. Further, an elastic body 27 made of a wave spring or a disc spring and washers 28a, 28b are attached to the tip of the output shaft 22 by screws 29, and the input side member 24 is attached in the axial direction by the elastic body 27. It is energized. As shown in FIG. 7, the inner ring 25 has an inner circumference formed in a circular shape and an outer circumference formed in a substantially pentagonal shape in a cross section in which the axes (front and back directions in the figure) are orthogonal to each other. The surface constitutes the cam surface 25a.

また、図３及び図４に示すように、ケース２１の内側で入力側部材２４の径方向外側には、戻し部材３１と制御部材３２とが配置されている。戻し部材３１は内輪２５の径方向外側に遊嵌されている。戻し部材３１は、筒状部３１ａと、該筒状部３１ａから軸方向に沿って反操作レバー１２側に突出形成された複数の係合部３１ｂとを備えている。係合部３１ｂの数は、内輪２５の形状に対応し、本実施形態では５個設けられ、周方向に沿って等間隔に配置されている。   As shown in FIGS. 3 and 4, a return member 31 and a control member 32 are disposed inside the case 21 and outside the input side member 24 in the radial direction. The return member 31 is loosely fitted on the radially outer side of the inner ring 25. The return member 31 includes a cylindrical portion 31a and a plurality of engaging portions 31b that protrude from the cylindrical portion 31a toward the counter-operating lever 12 along the axial direction. The number of the engaging portions 31b corresponds to the shape of the inner ring 25, and in the present embodiment, five are provided and are arranged at equal intervals along the circumferential direction.

戻し部材３１の径方向外側には、制御部材３２が遊嵌されている。制御部材３２は、環状の外輪３２ａと、外輪３２ａから軸方向に沿って反操作レバー１２側に突出形成されるとともに周方向に沿って交互に配置された第１係合部３２ｂ及び第２係合部３２ｃとを備えている。外輪３２ａは、戻し部材３１の係合部３１ｂの径方向外側に配置されている。外輪３２ａの外周面の径は、ケース２１の小径部２１ｂの内周面の径と同一とされている。つまり、外輪３２ａの外周面は、小径部２１ｂの内周面２１ｇに圧接されている。第１係合部３２ｂは、ロータカム２３の嵌着溝２３ｂに所定のがたつきを有して嵌入されている。第２係合部３２ｃは、外輪３２ａから径方向外側に向かって延びた段差部３２ｄを備えたL字状に形成され、軸方向に沿って延びた部分が第１係合部３２ｂよりも径方向外側に配置されている。   A control member 32 is loosely fitted on the radially outer side of the return member 31. The control member 32 includes an annular outer ring 32a, first engaging portions 32b and second engagement members that are formed so as to protrude from the outer ring 32a toward the counter-operating lever 12 along the axial direction and are alternately disposed along the circumferential direction. And a joint portion 32c. The outer ring 32 a is disposed on the radially outer side of the engaging portion 31 b of the return member 31. The diameter of the outer peripheral surface of the outer ring 32 a is the same as the diameter of the inner peripheral surface of the small diameter portion 21 b of the case 21. That is, the outer peripheral surface of the outer ring 32a is in pressure contact with the inner peripheral surface 21g of the small diameter portion 21b. The first engaging portion 32b is fitted into the fitting groove 23b of the rotor cam 23 with a predetermined backlash. The second engaging portion 32c is formed in an L shape having a step portion 32d extending radially outward from the outer ring 32a, and a portion extending along the axial direction has a diameter larger than that of the first engaging portion 32b. It is arranged outside in the direction.

図４及び図７に示すように、内輪２５のカム面２５ａと制御部材３２の外輪３２ａの内周面と戻し部材３１とロータカム２３とにより囲まれるとともに、カム面２５ａに沿って配列され戻し部材３１の係合部３１ｂにより複数（５個）の空間が区画形成されている。各空間は、外輪３２ａの内周面が円筒状に形成され、内輪２５のカム面２５ａが多角形状に形成されているため、周方向両側に外輪３２ａの内周面とカム面２５ａとの距離が次第に狭くなる端部が形成されている。図７に示すように、各空間にはそれぞれ２個の第１回転体としての第１ローラ３３が収容され、各空間に収容された２個の第１ローラ３３間には、第１ガタ止めバネ３４が挿入配置されている。図３に示すように、第１ガタ止めバネ３４は、各第１ローラ３３間に配置されたバネ部３４ａと、複数のバネ部３４ａを連結する連結部３４ｂとから構成されている。バネ部３４ａは、周方向両側にそれぞれ配設された第１ローラ３３と、同配設された方向に向かって付勢する。従って、各バネ部３４ａは、外周面が略多角形状に形成された内輪２５の頂点側、即ち内輪２５のカム面２５ａと該カム面２５ａと径方向に対向する制御部材３２の外輪３２ａ内周面とにより形成された略楔状空間の狭い空間となる端部の方向へ第１ローラ３３をそれぞれ付勢する。   As shown in FIGS. 4 and 7, the return member is surrounded by the cam surface 25a of the inner ring 25, the inner peripheral surface of the outer ring 32a of the control member 32, the return member 31 and the rotor cam 23, and arranged along the cam surface 25a. A plurality of (five) spaces are defined by 31 engaging portions 31b. In each space, since the inner peripheral surface of the outer ring 32a is formed in a cylindrical shape and the cam surface 25a of the inner ring 25 is formed in a polygonal shape, the distance between the inner peripheral surface of the outer ring 32a and the cam surface 25a on both sides in the circumferential direction. Is formed with an end portion that becomes gradually narrower. As shown in FIG. 7, each space contains two first rollers 33 as first rotating bodies, and a first backlash stop is provided between the two first rollers 33 housed in each space. A spring 34 is inserted and arranged. As shown in FIG. 3, the first backlash spring 34 includes a spring part 34a disposed between the first rollers 33 and a connecting part 34b that connects the plurality of spring parts 34a. The spring part 34a is urged toward the first roller 33 disposed on both sides in the circumferential direction and in the disposed direction. Accordingly, each spring portion 34a has an inner periphery of the outer ring 32a of the control member 32 that is radially opposed to the cam surface 25a of the inner ring 25 and the cam surface 25a of the inner ring 25. The first roller 33 is urged in the direction of the end portion that becomes a narrow space of a substantially wedge-shaped space formed by the surface.

上記のように構成されることで、図３及び図７に示すように、入力側部材２４（内輪２４）、戻し部材３１、第１ローラ３３、第１ガタ止めバネ３４、制御部材３２（外輪３２ａ）により第１クラッチ部４１が構成されている。なお、ケース２１の前記段差部２１ｄ及び制御部材３２の前記段差部３２ｄは、第１クラッチ部４１の径方向外側に配置されている。   3 and FIG. 7, the input side member 24 (inner ring 24), the return member 31, the first roller 33, the first backlash spring 34, and the control member 32 (outer ring) are configured as described above. 32a) constitutes the first clutch part 41. The step portion 21 d of the case 21 and the step portion 32 d of the control member 32 are disposed on the radially outer side of the first clutch portion 41.

図４及び図５に示すように、ロータカム２３のカム面２３ａとケース２１の内周面２１eとベースフレーム５ｂとにより囲まれるとともに、カム面２３ａに沿って配列され制御部材３２の第２係合部３２ｃにより複数（６個）の空間が区画形成される。各空間は、ロータカム２３のカム面２３ａが多角形状に形成され、ケース２１の内周面２１ｅが円筒状に形成されているため、周方向両側に内周面２１ｅとカム面２３ａとの距離が次第に狭くなる端部が形成されている。各空間にはそれぞれ２個の第２回転体としての第２ローラ３５が収容されている。本実施の形態では、前記第１ローラ３３の端部と第２ローラ３５の端部とが軸方向に重複するように配置されている。   4 and 5, the second engagement of the control member 32 is surrounded by the cam surface 23a of the rotor cam 23, the inner peripheral surface 21e of the case 21 and the base frame 5b, and is arranged along the cam surface 23a. A plurality (six) spaces are partitioned by the portion 32c. In each space, the cam surface 23a of the rotor cam 23 is formed in a polygonal shape, and the inner peripheral surface 21e of the case 21 is formed in a cylindrical shape, so that the distance between the inner peripheral surface 21e and the cam surface 23a is on both sides in the circumferential direction. A gradually narrowing end is formed. Each space accommodates two second rollers 35 as two second rotating bodies. In the present embodiment, the end of the first roller 33 and the end of the second roller 35 are arranged so as to overlap in the axial direction.

図５に示すように、各空間に収容された２個の第２ローラ３５間には、第２ガタ止めバネ３６が挿入配置されている。図３に示すように、第２ガタ止めバネ３６は、各第２ローラ３５間に配置されたバネ部３６ａと、複数のバネ部３６ａを連結する連結部３６ｂとから構成されている。各バネ部３６ａは、外周面が略多角形状に形成されたロータカム２３の頂点側、即ちロータカム２３のカム面２３ａと該カム面２３ａと径方向に対向するケース２１の内周面とにより形成された略楔状空間の狭い空間となる端部の方向へ第２ローラ３５をそれぞれ付勢する。   As shown in FIG. 5, a second backlash spring 36 is inserted between the two second rollers 35 housed in each space. As shown in FIG. 3, the second backlash spring 36 includes a spring portion 36a disposed between the second rollers 35 and a connecting portion 36b that connects the plurality of spring portions 36a. Each spring portion 36a is formed by the apex side of the rotor cam 23 whose outer peripheral surface is formed in a substantially polygonal shape, that is, the cam surface 23a of the rotor cam 23 and the inner peripheral surface of the case 21 that is radially opposed to the cam surface 23a. The second rollers 35 are urged in the direction of the end portion that becomes a narrow space of the substantially wedge-shaped space.

上記のように構成されることで、図３及び図６に示すように、制御部材３２（第１係合部３２ｂ及び第２係合部３２ｃ）、ロータカム２３、第２ローラ３５、第２ガタ止めバネ３６、ケース２１により第２クラッチ部４２が構成されている。本実施の形態では、第１クラッチ部４１と第２クラッチ部４２とが軸方向に近接配置されている。   With the above configuration, as shown in FIGS. 3 and 6, the control member 32 (the first engagement portion 32 b and the second engagement portion 32 c), the rotor cam 23, the second roller 35, and the second backlash. A second clutch portion 42 is configured by the stop spring 36 and the case 21. In the present embodiment, the first clutch portion 41 and the second clutch portion 42 are disposed close to each other in the axial direction.

また、図３に示すように、ケース２１と入力側部材２４と戻し部材３１には、それぞれフック部２１ｆ，２４ａ，３１ｃが径方向に重なるように形成されている。図８に示すように、各フック部２１ｆ，２４ａ，３１ｃは、復帰手段としての戻しバネ３７，３８と係合し該戻しバネ３７，３８の弾性力により径方向に重なる位置に回動されるように付勢されることで、入力側部材２４と戻し部材３１とをケース２１のフック部２１ｆに応じた中立位置に戻すために設けられている。本実施形態では、戻しバネ３７，３８は軸方向に操作レバー１２に近接して配置されている。   As shown in FIG. 3, hooks 21 f, 24 a, and 31 c are formed on the case 21, the input side member 24, and the return member 31 so as to overlap in the radial direction, respectively. As shown in FIG. 8, the hook portions 21f, 24a, 31c are engaged with return springs 37, 38 as return means, and are rotated to positions overlapping in the radial direction by the elastic force of the return springs 37, 38. By being biased in this manner, the input side member 24 and the return member 31 are provided to return to the neutral position corresponding to the hook portion 21f of the case 21. In the present embodiment, the return springs 37 and 38 are disposed close to the operation lever 12 in the axial direction.

また、図４に示すように、ベースフレーム５ｂはクラッチ装置１１を支持する位置に補助フレーム１６が取着されている。この補助フレーム１６はその基端部がベースフレーム５ｂに例えばボルト等で固定され、先端部はベースフレーム５ｂに対し所定間隔を隔てて平行となるよう延設されている。   As shown in FIG. 4, the base frame 5 b has an auxiliary frame 16 attached at a position where the clutch device 11 is supported. The auxiliary frame 16 has a base end portion fixed to the base frame 5b with, for example, a bolt, and a distal end portion extending in parallel to the base frame 5b with a predetermined interval.

補助フレーム１６には貫通孔が形成されて第１の軸受部１７が形成され、ベースフレーム５ｂには第１の軸受部１７と中心線が重なるように貫通孔が形成されて第２の軸受部１８が形成されている。第２の軸受部１８の径は、第１の軸受部１７の径より大きい径で形成されている。   A through hole is formed in the auxiliary frame 16 to form a first bearing portion 17, and a through hole is formed in the base frame 5 b so that the center line overlaps with the first bearing portion 17, and a second bearing portion is formed. 18 is formed. The diameter of the second bearing portion 18 is larger than the diameter of the first bearing portion 17.

出力軸２２はその中間部が第２の軸受部１８に回転可能に支持され、先端部が第１の軸受部１７に回転可能に支持されている。また、補助フレーム１６とベースフレーム５ｂとの間で、ピニオンギヤ１３にセクタギヤ１４の歯部１４ａが噛み合わされている。   The output shaft 22 has an intermediate portion rotatably supported by the second bearing portion 18 and a distal end portion rotatably supported by the first bearing portion 17. Further, the tooth portion 14a of the sector gear 14 is meshed with the pinion gear 13 between the auxiliary frame 16 and the base frame 5b.

図４に示すように、ピニオンギヤ１３の側方において、出力軸２２の先端部側面には、互いに平行な２つの平面部２２ａが形成されている。出力軸２２の先端部周囲にスパイラルスプリング３９が配設され、図９に示すようにそのスパイラルスプリング３９の内周側端部３９ａは略平行に対向するように形成されている。スパイラルスプリング３９の内周側端部３９ａ内側に平面部２２ａが当接するように出力軸２２の先端部が嵌入され、スパイラルスプリング３９の外周側端部３９ｂが補助フレーム１６とベースフレーム５ｂとの間に支持される掛止軸４０に係合されている。従って、スパイラルスプリング３９の付勢力はベースフレーム５ｂを支点として出力軸２２に所要の回転トルクを付与し、そのトルクはベースフレーム５ａ，５ｂを上昇させる方向に作用する。   As shown in FIG. 4, on the side of the pinion gear 13, two plane portions 22 a that are parallel to each other are formed on the side surface of the distal end portion of the output shaft 22. A spiral spring 39 is disposed around the distal end portion of the output shaft 22, and the inner peripheral side end portion 39a of the spiral spring 39 is formed so as to face substantially parallel as shown in FIG. The tip end portion of the output shaft 22 is fitted so that the flat surface portion 22a is in contact with the inner peripheral end portion 39a of the spiral spring 39, and the outer peripheral end portion 39b of the spiral spring 39 is between the auxiliary frame 16 and the base frame 5b. It is engaged with the latching shaft 40 supported by. Accordingly, the urging force of the spiral spring 39 applies a required rotational torque to the output shaft 22 with the base frame 5b as a fulcrum, and the torque acts in a direction to raise the base frames 5a and 5b.

次に、上記のようなクラッチ装置１１を備えた車両用シート調整装置の動作を説明する。
図４に示すように、ユーザが操作レバー１２をシート上昇方向に回動させると、操作レバー１２が取着された入力側部材２４が一体的に回動する。この入力側部材２４の回動により、図７に示す内輪２５が例えば時計方向に回動し、内輪２５のカム面２５ａと制御部材３２の外輪３２ａとの間に配設された第１ローラ３３が楔隙間に係合する（噛み込む）。これにより、内輪２５の回動が制御部材に伝達される。このように、第１クラッチ部４１においては、操作レバー１２の駆動操作時には操作レバー１２の操作力を入力側部材２４から制御部材３２に伝達可能である。 Next, the operation of the vehicle seat adjustment apparatus including the clutch device 11 as described above will be described.
As shown in FIG. 4, when the user rotates the operation lever 12 in the seat raising direction, the input side member 24 to which the operation lever 12 is attached rotates integrally. By the rotation of the input side member 24, the inner ring 25 shown in FIG. 7 rotates, for example, in the clockwise direction, and the first roller 33 disposed between the cam surface 25a of the inner ring 25 and the outer ring 32a of the control member 32. Engages (bits into) the wedge gap. Thereby, the rotation of the inner ring 25 is transmitted to the control member. As described above, in the first clutch portion 41, the operating force of the operation lever 12 can be transmitted from the input side member 24 to the control member 32 when the operation lever 12 is driven.

制御部材３２が回動すると、図５に示す制御部材３２の第１係合部３２ｂがロータカム２３の嵌着溝２３ｂ側面と係合し、ロータカム２３が図において時計方向に回動する。この時、ロータカム２３のカム面２３ａとケース２１の内周面２１ｅとの間に配設された第２ローラ３５は、第２係合部３２ｃによりロータカム２３の回動方向に押されて移動するため、楔隙間に係合しない（噛み込まない）。つまり、出力軸２２は操作レバー１２の操作に従って回動する。このように、第２クラッチ部４２においては、操作レバー１２の駆動操作時には操作レバー１２の操作力を制御部材３２から出力軸２２に伝達可能である。これにより、出力軸２２のピニオンギヤ１３と歯合するセクタギヤ１４が回転される。セクタギヤ１４の回動に基づいて、駆動リンク１５を介してリフタリンク７ａ，７ｂが回動され、ベースフレーム５ａ，５ｂが上昇する。従って、シートクッション１ａが上昇する。このとき、スパイラルスプリング３９の付勢力が出力軸２２の回転を助勢する方向に作用するため、操作レバー１２の操作力が軽減される。   When the control member 32 rotates, the first engaging portion 32b of the control member 32 shown in FIG. 5 engages with the side surface of the fitting groove 23b of the rotor cam 23, and the rotor cam 23 rotates clockwise in the drawing. At this time, the second roller 35 disposed between the cam surface 23a of the rotor cam 23 and the inner peripheral surface 21e of the case 21 is pushed and moved in the rotational direction of the rotor cam 23 by the second engagement portion 32c. Therefore, it does not engage (do not bite) the wedge gap. That is, the output shaft 22 rotates according to the operation of the operation lever 12. As described above, in the second clutch portion 42, the operating force of the operating lever 12 can be transmitted from the control member 32 to the output shaft 22 when the operating lever 12 is driven. Thereby, the sector gear 14 which meshes with the pinion gear 13 of the output shaft 22 is rotated. Based on the rotation of the sector gear 14, the lifter links 7a and 7b are rotated via the drive link 15, and the base frames 5a and 5b are raised. Accordingly, the seat cushion 1a is raised. At this time, since the urging force of the spiral spring 39 acts in the direction of assisting the rotation of the output shaft 22, the operating force of the operating lever 12 is reduced.

操作レバー１２を解放すると、車両用シート１の重量及び乗員の体重による負荷によって、図５において、出力軸２２が反時計方向に回動する。この時、出力軸２２とロータカム２３とが一体回動し、このロータカム２３の回動により、上記と同様に、ロータカム２３のカム面２３ａとケース２１の内周面２１ｅとの間に配設された第２ローラ３５が楔隙間に係合する（噛み込む）。ケース２１はベースフレーム５ｂに固定されているため、出力軸２２の回動が阻止される。つまり、第２クラッチ部４２においては、操作レバー１２の駆動操作以外のときは出力軸２２の回動を規制する。   When the operation lever 12 is released, the output shaft 22 rotates counterclockwise in FIG. 5 due to the load due to the weight of the vehicle seat 1 and the weight of the passenger. At this time, the output shaft 22 and the rotor cam 23 are integrally rotated, and the rotor cam 23 is rotated between the cam surface 23a of the rotor cam 23 and the inner peripheral surface 21e of the case 21 as described above. The second roller 35 engages (bits into) the wedge gap. Since the case 21 is fixed to the base frame 5b, the rotation of the output shaft 22 is prevented. That is, in the second clutch portion 42, the rotation of the output shaft 22 is restricted when the operation lever 12 is not driven.

上記操作レバー１２の解放により、戻し部材３１と入力側部材２４とは戻しバネ３７，３８により中立位置まで回動する。この時、第１ローラ３３は、戻し部材３１の係合部３１ｂによって戻し部材３１及び入力側部材２４の回動方向と同方向に移動し、噛み込まないため、中立方向への回動は規制されない。つまり、第１クラッチ部４１においては操作レバー１２の復帰時には入力側部材２４と制御部材３２との力の伝達を解除する。   When the operation lever 12 is released, the return member 31 and the input side member 24 are rotated to the neutral position by the return springs 37 and 38. At this time, the first roller 33 moves in the same direction as the rotation direction of the return member 31 and the input side member 24 by the engaging portion 31b of the return member 31 and does not bite, so that the rotation in the neutral direction is restricted. Not. That is, in the first clutch portion 41, the transmission of force between the input side member 24 and the control member 32 is released when the operation lever 12 is returned.

クラッチ装置１１は、シート上昇方向に回動させた操作レバー１２を中立位置へ回動する場合も、上記の操作レバー１２を解放したときと同様に動作するため、該操作レバー１２の回動が規制されない。なお、操作レバー１２をシート下降方向に回動した場合、回動方向は異なるが上記と同様に動作するため、説明を省略する。   The clutch device 11 operates in the same manner as when the operation lever 12 is released when the operation lever 12 rotated in the seat raising direction is rotated to the neutral position. Not regulated. When the operation lever 12 is rotated in the seat lowering direction, the rotation direction is different, but the operation is the same as described above, and thus the description thereof is omitted.

本実施形態の構成によれば、以下に記載の効果を得ることができる。
（１）第１クラッチ部４１においては径方向内側から径方向外側に向けて力が伝達され、第２クラッチ部４２においては径方向外側から径方向内側に向けて力が伝達されるため、第１クラッチ部においても径方向外側から径方向内側に向けて力が伝達される場合と比較して、第１クラッチ部４１と第２クラッチ部４２との半径差が小さくなる。このため、操作力の伝達時に第１クラッチ部４１と第２クラッチ部４２と間に生じる捻り力が低減されるため、捻り力を考慮した制御部材３２の補強は必要なく、装置の小型化を図ることができる。 According to the configuration of the present embodiment, the following effects can be obtained.
(1) Since the force is transmitted from the radially inner side to the radially outer side in the first clutch part 41, and the force is transmitted from the radially outer side to the radially inner side in the second clutch part 41, The radial difference between the first clutch portion 41 and the second clutch portion 42 is smaller in the one clutch portion than in the case where force is transmitted from the radially outer side toward the radially inner side. For this reason, since the twisting force generated between the first clutch part 41 and the second clutch part 42 during transmission of the operating force is reduced, it is not necessary to reinforce the control member 32 in consideration of the twisting force, and the device can be downsized. You can plan.

（２）上記特許文献１記載の如く制御部材を入力側部材の径方向内側に配置すると、制御部材を、第１クラッチ部のローラの内側からそのローラの外側に位置する第２クラッチ部のローラまで延びる形状にせざるを得なくなるため、軸方向において制御部材が両ローラ間に介在することとなり、両ローラを軸方向に近づけて配置することができなくなる。これに対し、本実施形態の構成によれば、制御部材３２を入力側部材２４の径方向外側に配置しているので、第１クラッチ部４１の第１ローラ３３と第２クラッチ部４２の第２ローラ３５との間に制御部材３２を介在させない構成とできる。即ち、第１ローラ３３の端部と第２ローラ３５の端部とが重複するように配置することで、第１ローラ３３と第２ローラ３５とを軸方向に近接して配置することを容易に実現できる。   (2) When the control member is disposed on the radially inner side of the input side member as described in Patent Document 1, the control member is a roller of the second clutch portion located outside the roller from the inside of the roller of the first clutch portion. Therefore, the control member is interposed between the rollers in the axial direction, and the rollers cannot be arranged close to the axial direction. On the other hand, according to the configuration of the present embodiment, since the control member 32 is arranged on the radially outer side of the input side member 24, the first roller 33 of the first clutch portion 41 and the second clutch portion 42 of the second clutch portion 42 are arranged. The control member 32 may not be interposed between the two rollers 35. That is, by arranging the end of the first roller 33 and the end of the second roller 35 so as to overlap, it is easy to arrange the first roller 33 and the second roller 35 close to each other in the axial direction. Can be realized.

そして、このように第１クラッチ部４１の第１ローラ３３と第２クラッチ部の第２ローラ３５とを軸方向に近接して配置することで、第１クラッチ部４１と第２クラッチ部４２との間に他の部材が配置される場合と比較して、操作レバー１２の駆動操作時の第１クラッチ部４１と第２クラッチ部４２と間の操作力の伝達経路が短くなり、操作力の伝達効率が向上する。   In this way, by arranging the first roller 33 of the first clutch portion 41 and the second roller 35 of the second clutch portion close to each other in the axial direction, the first clutch portion 41, the second clutch portion 42, Compared with the case where another member is disposed between the first clutch portion 41 and the second clutch portion 42 during the driving operation of the operation lever 12, the transmission path of the operation force between the first clutch portion 41 and the second clutch portion 42 is shortened. Transmission efficiency is improved.

（３）入力側部材２４を中立位置に復帰させる戻しバネ３７，３８が軸方向に操作レバー１２に近接した位置に配置されているため、戻しバネ３７，３８の付勢力を入力側部材２４に伝達する第１クラッチ部４１とは軸方向に離間した位置となる。このため、戻しバネ３７，３８の付勢力が入力側部材２４に効率よく伝達される。   (3) Since the return springs 37 and 38 for returning the input side member 24 to the neutral position are disposed at positions close to the operation lever 12 in the axial direction, the urging force of the return springs 37 and 38 is applied to the input side member 24. The first clutch portion 41 to be transmitted is at a position separated in the axial direction. For this reason, the urging force of the return springs 37 and 38 is efficiently transmitted to the input side member 24.

（４）制御部材３２において第１クラッチ部４１の径方向外側に向かう力を受ける部位に径方向に延びた段差部３２ｄが在るため、制御部材はその力を好適に受け止めることができる。   (4) Since the step portion 32d extending in the radial direction is present at the portion of the control member 32 that receives the force toward the radially outer side of the first clutch portion 41, the control member can suitably receive the force.

（５）制御部材３２が第１クラッチ部４１から受ける圧力をケース２１の内周面２１ｇで受けることにより、制御部材３２の径方向の変形を抑制し、制御部材３２のみで前記圧力を受ける場合と比較して制御部材を薄肉化することが可能となる。   (5) When the pressure received by the control member 32 from the first clutch portion 41 is received by the inner peripheral surface 21g of the case 21, the radial deformation of the control member 32 is suppressed, and the pressure is received only by the control member 32. In comparison with the control member, the thickness of the control member can be reduced.

（６）ケース２１において第１クラッチ部４１の径方向外側に向かう力を受ける部位に径方向に延びた段差部２１ｄが在るため、ケース２１はその力を好適に受け止めることができる。   (6) Since the step portion 21d extending in the radial direction is present at the portion of the case 21 that receives the force toward the radially outer side of the first clutch portion 41, the case 21 can suitably receive the force.

なお、本実施形態は上記構成に限らず、以下の態様に変更してもよい。
・上記実施形態では、第１クラッチ部４１の第１ローラ３３の端部と第２クラッチ部４２の第２ローラ３５の端部とが軸方向に重複するように配置されているが、第１ローラ３３の端面と第２ローラ３５の端面とが軸方向に同一位置となるように配置してもよい。 Note that the present embodiment is not limited to the above configuration, and may be modified to the following modes.
In the above embodiment, the end portion of the first roller 33 of the first clutch portion 41 and the end portion of the second roller 35 of the second clutch portion 42 are arranged so as to overlap in the axial direction. You may arrange | position so that the end surface of the roller 33 and the end surface of the 2nd roller 35 may become the same position in an axial direction.

・上記実施形態では、クラッチ装置１１のケース２１をベースフレーム５ｂに直接取り付け固定したが、出力軸２２を支持するベースを設け、該ベースにケース２１を固定してクラッチ装置１１をユニット化してもよい。   In the above embodiment, the case 21 of the clutch device 11 is directly attached and fixed to the base frame 5b. However, even if the base for supporting the output shaft 22 is provided and the case 21 is fixed to the base, the clutch device 11 is unitized. Good.

・上記実施形態では、スパイラルスプリング３９によりシートクッション１ａを上昇させるように付勢したが、トーションバー等の他の弾性体により付勢するようにしてもよい。   In the above-described embodiment, the seat cushion 1a is urged by the spiral spring 39, but may be urged by another elastic body such as a torsion bar.

車両用シートの斜視図。The perspective view of a vehicle seat. 車両用シート調整装置の斜視図。The perspective view of the vehicle seat adjustment apparatus. クラッチ装置の分解斜視図。The disassembled perspective view of a clutch apparatus. クラッチ装置の断面図。Sectional drawing of a clutch apparatus. 図４のＡ−Ａ線断面図。AA line sectional view of Drawing 4. 入力側部材の説明図。Explanatory drawing of an input side member. 図４のＢ−Ｂ線断面図。BB sectional drawing of FIG. 戻しバネの説明図。Explanatory drawing of a return spring. スパイラルスプリングの正面図。The front view of a spiral spring.

符号の説明Explanation of symbols

１ａ…シートクッション、３…車両用シート調整装置、１２…操作レバー（操作部材）、２１…ケース（静止部材）、２１ｄ…段差部、２１ｅ…内周面、２３…ロータカム（回動部材）、２３ａ…カム面、２４…入力側部材、２２…出力軸、２５ａ…カム面、３２…制御部材、３２ｄ…段差部、３３…第１ローラ（第１回転体）、３５…第２ローラ（第２回転体）、３７，３８…戻しバネ（復帰手段）、４１…第１クラッチ部、４２…第２クラッチ部。   DESCRIPTION OF SYMBOLS 1a ... Seat cushion, 3 ... Vehicle seat adjustment apparatus, 12 ... Operation lever (operation member), 21 ... Case (stationary member), 21d ... Step part, 21e ... Inner peripheral surface, 23 ... Rotor cam (rotating member), 23a ... cam surface, 24 ... input side member, 22 ... output shaft, 25a ... cam surface, 32 ... control member, 32d ... step portion, 33 ... first roller (first rotating body), 35 ... second roller (first) 2 rotation bodies), 37, 38 ... return spring (return means), 41 ... first clutch portion, 42 ... second clutch portion.

Claims (3)

操作部材の操作に従って出力軸を回動させ、該出力軸の回動によりシートクッションを上下方向に移動させる車両用シート調整装置であって、
前記操作部材が連結され前記出力軸に軸支された入力側部材と、
前記入力側部材の径方向外側に配置された制御部材と、
前記操作部材の駆動操作時には該操作部材の操作力を前記入力側部材から前記制御部材に伝達可能とし、前記操作部材の復帰時には前記入力側部材と前記制御部材との力の伝達を解除する第１クラッチ部と、
前記操作部材の駆動操作時には該操作部材の操作力を前記制御部材から前記出力軸に伝達可能とし、前記操作部材の駆動操作以外のときに前記出力軸の回動を規制する第２クラッチ部と、
前記制御部材の径方向外側に配置され、内周面で前記操作部材の駆動操作以外のときに前記出力軸の回動を規制する静止部材とを備え、
前記制御部材の前記第１クラッチ部を収容した部分の半径を前記静止部材の内周面と同じとして該静止部材の内周面で前記制御部材を軸受けし、
前記制御部材及び前記静止部材は、前記第１クラッチ部の径方向外側に、前記第１クラッチ部の径方向外側に向かう力を受けるべく径方向に延びた段差部をそれぞれ有する
ことを特徴とする車両用シート調整装置。 A vehicle seat adjustment device that rotates an output shaft according to an operation of an operation member and moves a seat cushion in the vertical direction by rotation of the output shaft,
An input side member connected to the operation member and supported by the output shaft;
A control member disposed radially outside the input side member;
When the operation member is driven, the operation force of the operation member can be transmitted from the input side member to the control member, and when the operation member is returned, the force transmission between the input side member and the control member is released. 1 clutch part,
A second clutch portion that allows the operating force of the operating member to be transmitted from the control member to the output shaft during a driving operation of the operating member, and restricts the rotation of the output shaft during a time other than the driving operation of the operating member; ,
A stationary member that is disposed on the radially outer side of the control member and restricts the rotation of the output shaft at a time other than the drive operation of the operation member on the inner peripheral surface;
Bearing the control member on the inner peripheral surface of the stationary member with the radius of the portion of the control member containing the first clutch portion being the same as the inner peripheral surface of the stationary member;
The control member and the stationary member each have a step portion extending in the radial direction so as to receive a force toward the radially outer side of the first clutch portion on the radially outer side of the first clutch portion. Vehicle seat adjustment device. 操作部材の操作に従って出力軸を回動させ、該出力軸の回動によりシートクッションを上下方向に移動させる車両用シート調整装置であって、
前記操作部材が連結され前記出力軸に軸支された入力側部材と、
前記入力側部材の径方向外側に配置された制御部材と、
前記操作部材の駆動操作時には該操作部材の操作力を前記入力側部材から前記制御部材に伝達可能とし、前記操作部材の復帰時には前記入力側部材と前記制御部材との力の伝達を解除する第１クラッチ部と、
前記操作部材の駆動操作時には該操作部材の操作力を前記制御部材から前記出力軸に伝達可能とし、前記操作部材の駆動操作以外のときに前記出力軸の回動を規制する第２クラッチ部とを備え、
前記第１クラッチ部は前記入力側部材のカム面と前記制御部材の内周面との間の力の伝達を可能とする第１回転体を備え、
前記第２クラッチ部は前記制御部材の内周面と前記出力軸に連結された回動部材のカム面との間の力の伝達を可能とする第２回転体を備え、
前記第１回転体の端部と前記第２回転体の端部とが、軸方向に同一又は重複するように配置されている
ことを特徴とする車両用シート調整装置。 A vehicle seat adjustment device that rotates an output shaft according to an operation of an operation member and moves a seat cushion in the vertical direction by rotation of the output shaft,
An input side member connected to the operation member and supported by the output shaft;
A control member disposed radially outside the input side member;
When the operation member is driven, the operation force of the operation member can be transmitted from the input side member to the control member, and when the operation member is returned, the force transmission between the input side member and the control member is released. 1 clutch part,
A second clutch portion that allows the operating force of the operating member to be transmitted from the control member to the output shaft during a driving operation of the operating member, and restricts the rotation of the output shaft during a time other than the driving operation of the operating member; With
The first clutch portion includes a first rotating body that enables transmission of force between a cam surface of the input side member and an inner peripheral surface of the control member,
The second clutch portion includes a second rotating body that enables transmission of force between an inner peripheral surface of the control member and a cam surface of a rotating member connected to the output shaft,
Wherein an end portion of the first rotating body and the end portion of the second rotating body, car dual seat adjustment mechanism characterized in that it is arranged to the same or overlapping in the axial direction. 前記入力側部材が解放されたときに該入力側部材を中立位置に復帰させる復帰手段を備え、前記復帰手段を軸方向に前記操作部材に近接した位置に配置したことを特徴とする請求項１又は２に記載の車両用シート調整装置。   2. A return means for returning the input side member to a neutral position when the input side member is released, wherein the return means is disposed at a position close to the operation member in the axial direction. Or the vehicle seat adjustment device according to 2;
JP2005368630A 2005-12-21 2005-12-21 Vehicle seat adjustment device Expired - Fee Related JP4940650B2 (en)

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