JP4357385B2

JP4357385B2 - Electric brake device

Info

Publication number: JP4357385B2
Application number: JP2004232049A
Authority: JP
Inventors: 山本　　憲
Original assignee: NTN Corp
Current assignee: NTN Corp
Priority date: 2004-08-09
Filing date: 2004-08-09
Publication date: 2009-11-04
Anticipated expiration: 2024-08-09
Also published as: JP2006046614A

Abstract

<P>PROBLEM TO BE SOLVED: To provide an electric brake device with a parking brake operating function and an abrasion compensating function of a brake member without impairing compact design assigned to the electric brake device. <P>SOLUTION: Rotation is transmitted to a rotor 6 as a cylindrical rotating member rotated forward by the rotational driving force of an electric motor, and allowing a screw shaft 9 as a linear moving member to be advanced by a ball screw mechanism from a driving shaft 17 driven by the operation of the parking brake through an output shaft 19 connected by an one-way clutch 18, further the rotor 6 is also rotated forward by the operation of the parking brake, and a brake pad 3 is pressed to a disk rotor 2 by the advancing motion of the screw shaft 9, thus the operating function of the parking brake can be assembled without impairing the compact design. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

本発明は、電動モータの回転駆動力を直線駆動力に変換して、ブレーキ部材を被制動部材に押圧する電動式ブレーキ装置に関する。 The present invention relates to an electric brake device that converts a rotational driving force of an electric motor into a linear driving force and presses a brake member against a member to be braked.

車両用ブレーキ装置としては油圧式のものが多く採用されてきたが、近年、ＡＢＳ(Antilock Brake System)等の高度なブレーキ制御の導入に伴い、これらの制御を複雑な油圧回路なしに行うことができ、コンパクトに設計できる電動式ブレーキ装置が注目されている。電動式ブレーキ装置は、ブレーキペダルの踏み込み信号等で電動モータを作動させ、電動モータの回転駆動力を直線駆動力に変換する駆動力変換機構によって直動部材に直線駆動力を伝達し、直動部材の直線運動でブレーキ部材を被制動部材に押圧するものである。 Although many hydraulic brake devices have been adopted as a vehicle brake device, in recent years, with the introduction of advanced brake control such as ABS (Antilock Brake System), these controls can be performed without complicated hydraulic circuits. Electric brake devices that can be designed compactly are drawing attention. The electric brake device operates the electric motor in response to a brake pedal depression signal, etc., and transmits the linear driving force to the linear motion member by a driving force conversion mechanism that converts the rotational driving force of the electric motor into a linear driving force. The brake member is pressed against the member to be braked by the linear motion of the member.

このような電動式ブレーキ装置は、車両のばね下に取り付けられるので、コンパクトで軽量な設計が可能なことが望まれる。このような設計を可能とするために、電動式ブレーキ装置の駆動力変換機構には、電動モータで回転駆動される回転体に直動部材を螺合したねじ機構が多く採用され、ねじ機構としては摩擦抵抗が小さく駆動力の変換ロスが少ないボールねじ機構が多く用いられている（例えば、特許文献１、２参照）。電動式ブレーキ装置には、電気的制御が不能となったときのバックアップ機能を兼ねて、駐車ブレーキの作動機能を組み込むことも望まれている（例えば、特許文献３参照）。 Since such an electric brake device is attached under the spring of a vehicle, it is desired that a compact and lightweight design is possible. In order to make such a design possible, a screw mechanism in which a linear member is screwed to a rotating body that is rotationally driven by an electric motor is often used as a driving force conversion mechanism of an electric brake device. In many cases, a ball screw mechanism having a small frictional resistance and a small conversion loss of driving force is used (see, for example, Patent Documents 1 and 2). It is also desired to incorporate an operation function of a parking brake in the electric brake device that also serves as a backup function when electrical control becomes impossible (see, for example, Patent Document 3).

これらの電動式ブレーキ装置では、ブレーキ部材の摩耗に伴って直動部材によるブレーキ部材の押圧位置が前方へ移動するように変化する。このため、ブレーキ効きの応答性を確保するためには、このブレーキ部材の摩耗に伴う押圧位置の変化に応じて、直動部材の待機位置を前方へ徐々に変化させる必要がある。 In these electric brake devices, as the brake member wears, the pressing position of the brake member by the linear motion member changes so as to move forward. For this reason, in order to ensure the responsiveness of the brake effect, it is necessary to gradually change the standby position of the linear motion member forward in accordance with the change of the pressing position accompanying the wear of the brake member.

特許文献１に記載されたものでは、制動時に電動モータを正回転させてブレーキ部材押圧側へ前進させた直動部材としてのボールねじのねじ軸を、制動解除時に電動モータを逆回転させてブレーキ部材から後退させたのち、再び電動モータを正回転させてねじ軸を待機位置に戻すようにしているが、ブレーキ部材の摩耗を補償するように待機位置を変化させることはしていない。 According to the technique described in Patent Document 1, the screw shaft of a ball screw as a linear motion member that is rotated forward by an electric motor during braking and advanced toward the brake member pressing side is reversely rotated when the brake is released. After retracting from the member, the electric motor is rotated forward again to return the screw shaft to the standby position, but the standby position is not changed to compensate for the wear of the brake member.

また、特許文献２に記載されたものは、駆動力変換機構と直動部材としてのピストンの間に調整ねじを設け、この調整ねじと電動モータのロータとの間に、ロータの所定範囲を越える回転変位のみを伝達するリミッタと一方向クラッチとを設け、ロータの制動時の回転変位が所定範囲を越えたとき、ロータの制動解除時の逆回転変位を一方向クラッチを介して調整ねじに伝達して、ピストンを被制動部材であるディスクロータ側へ前進させ、ブレーキ部材であるブレーキパッドの摩耗を補償するようにしている。 In addition, in Patent Document 2, an adjustment screw is provided between the driving force conversion mechanism and the piston as the linear motion member, and the predetermined range of the rotor is exceeded between the adjustment screw and the rotor of the electric motor. A limiter that transmits only rotational displacement and a one-way clutch are provided, and when the rotational displacement during braking of the rotor exceeds a predetermined range, the reverse rotational displacement when the rotor is released is transmitted to the adjustment screw via the one-way clutch. Thus, the piston is advanced toward the disk rotor that is the member to be braked to compensate for wear of the brake pad that is the brake member.

特開２００２−２１３５０５号公報（第２−４頁、第１−２図）JP 2002-213505 A (page 2-4, FIG. 1-2) 特開２０００−２８３１９５号公報（第２−５頁、第１−４図）JP 2000-283195 A (page 2-5, Fig. 1-4) 実用新案登録公報第２５４６３４８号（第２−４頁、第１図）Utility Model Registration Gazette No. 2546348 (page 2-4, Fig. 1)

特許文献１に記載の電動式ブレーキ装置でブレーキ部材の摩耗を補償するためには、ブレーキ部材の摩耗量を検出し、制動解除後に再び電動モータを正回転させてねじ軸を待機位置に戻すときに、検出したブレーキ部材の摩耗量に応じて待機位置を変化させればよいが、別途のセンサや余分の制御アルゴリズムを必要とし、装置が複雑なものとなる。 In order to compensate for the wear of the brake member with the electric brake device described in Patent Document 1, the amount of wear of the brake member is detected, and after the brake is released, the electric motor is rotated forward again to return the screw shaft to the standby position. In addition, the standby position may be changed according to the detected amount of wear of the brake member, but a separate sensor and an extra control algorithm are required, and the apparatus becomes complicated.

一方、特許文献２に記載されたものは、別途のセンサや制御アルゴリズムを必要とせずに、ブレーキパッドの摩耗を補償することができるが、その構成が複雑で部品点数も多いので、電動式ブレーキ装置に課せられるコンパクトで軽量な設計が難しく、かつ、製造コストも高価なものとなる問題がある。 On the other hand, the one described in Patent Document 2 can compensate for brake pad wear without requiring a separate sensor or control algorithm, but its configuration is complicated and the number of parts is large. There is a problem that a compact and lightweight design imposed on the apparatus is difficult and the manufacturing cost is high.

また、特許文献１および２に記載されたものは、いずれも制動解除時に電動モータを逆回転させる必要があるので、制動解除のタイミングが遅れ、運転者に違和感を与える問題もある。さらに、電気的制御が不能となったときのバックアップ機能を兼ねる駐車ブレーキの作動機能も組み込まれていない。 In addition, both of those described in Patent Documents 1 and 2 have a problem that the timing of releasing the brake is delayed and the driver feels uncomfortable because it is necessary to reversely rotate the electric motor when releasing the brake. Furthermore, a parking brake operating function that also serves as a backup function when electrical control becomes impossible is not incorporated.

そこで、本発明の課題は、電動式ブレーキ装置に課せられたコンパクトな設計を損なうことなく、駐車ブレーキの作動機能とブレーキ部材の摩耗補償機能を組み込むことである。 Accordingly, an object of the present invention is to incorporate a parking brake operation function and a brake member wear compensation function without impairing the compact design imposed on the electric brake device.

上記の課題を解決するために、本発明は、電動モータの回転駆動力を直線駆動力に変換する駆動力変換機構を備え、この駆動力変換機構によって直線駆動力を伝達される直動部材の前進運動で、ブレーキ部材を被制動部材に押圧する電動式ブレーキ装置において、前記駆動力変換機構を、前記電動モータの回転駆動力によって正回転する筒状回転部材の内径側に設けたねじ機構で前記直動部材を前進運動させるものとし、駐車ブレーキの操作によって駆動される駆動シャフトの回転を前記筒状回転部材に伝達する駐車ブレーキ伝達機構を設け、前記駐車ブレーキの操作によっても前記筒状回転部材を正回転させ、前記直動部材の前進運動で前記ブレーキ部材を被制動部材に押圧する構成を採用した。 In order to solve the above-described problems, the present invention includes a driving force conversion mechanism that converts a rotational driving force of an electric motor into a linear driving force, and a linear motion member to which the linear driving force is transmitted by the driving force conversion mechanism. In the electric brake device that presses the brake member against the member to be braked by forward movement, the driving force conversion mechanism is a screw mechanism provided on the inner diameter side of the cylindrical rotating member that rotates forward by the rotational driving force of the electric motor. The linear motion member is moved forward, and a parking brake transmission mechanism is provided for transmitting the rotation of the drive shaft driven by the operation of the parking brake to the cylindrical rotation member, and the cylindrical rotation is also performed by the operation of the parking brake. A configuration is adopted in which the member is rotated forward and the brake member is pressed against the member to be braked by the forward movement of the linear motion member.

すなわち、電動モータの回転駆動力によって正回転し、ねじ機構で直動部材を前進運動させる筒状回転部材に、駐車ブレーキの操作によって駆動される駆動シャフトの回転を伝達する駐車ブレーキ伝達機構を設け、駐車ブレーキの操作によっても筒状回転部材を正回転させ、直動部材の前進運動でブレーキ部材を被制動部材に押圧することにより、コンパクトな設計を損なうことなく、駐車ブレーキの作動機能を組み込むことができるようにした。 In other words, a parking brake transmission mechanism that transmits the rotation of the drive shaft driven by the operation of the parking brake is provided on the cylindrical rotating member that rotates forward by the rotational driving force of the electric motor and moves the linear motion member forward by the screw mechanism. Incorporating the parking brake operation function without compromising the compact design by rotating the cylindrical rotating member forward by the parking brake operation and pressing the brake member against the braked member by the forward movement of the linear motion member I was able to do that.

前記駐車ブレーキ伝達機構を、前記駐車ブレーキの操作によって駆動される駆動シャフトに、一方向クラッチを介して前記筒状回転部材に正回転を伝達する出力シャフトを連結したものとすることにより、よりコンパクトな設計とすることができる。 The parking brake transmission mechanism is more compact by connecting an output shaft that transmits normal rotation to the cylindrical rotating member via a one-way clutch to a drive shaft that is driven by operation of the parking brake. Design.

前記直動部材の前進運動でブレーキ部材を押圧するように正回転させた筒状回転部材を、所定の回転角だけ逆回転させて、前記ブレーキ部材を押圧した位置から所定の距離だけ自動的に後退待機させる自動待機機構を設けることにより、ブレーキ部材が摩耗しても制動後の直動部材を常にブレーキ部材の押圧位置近くに後退待機させ、コンパクトな設計を損なうことなく、ブレーキ部材の摩耗補償機能を組み込むことができる。 The cylindrical rotating member rotated forward so as to press the brake member by the forward movement of the linear motion member is reversely rotated by a predetermined rotation angle, and automatically a predetermined distance from the position where the brake member is pressed. By providing an automatic standby mechanism that makes the brake stand by, even if the brake member wears, the linear motion member after braking always keeps moving backward and close to the pressing position of the brake member, so that the wear of the brake member is compensated without compromising the compact design. Functions can be incorporated.

前記駐車ブレーキ伝達機構と前記自動待機機構とを合体させてユニット化することにより、よりコンパクトな設計とすることができる。 By combining the parking brake transmission mechanism and the automatic standby mechanism into a unit, a more compact design can be achieved.

前記合体させたユニットとしては、前記駐車ブレーキ伝達機構を、前記駐車ブレーキの操作によって駆動される駆動シャフトに、一方向クラッチを介して前記筒状回転部材に正回転を伝達する出力シャフトを連結したものとし、前記自動待機機構を、前記正回転させた筒状回転部材を前記出力シャフトとの間に配したねじりコイルばねで逆回転方向へ付勢したものとし、前記出力シャフトと筒状回転部材とに、これらの正逆両方向への相対回転を所定の回転角だけ許容して互いに係合し合う係合部を設けて、前記駐車ブレーキの操作によって前記筒状回転部材に正回転を伝達した出力シャフトを、逆方向へ戻し回転する手段を設けたものを採用することができる。 As the united unit, the parking brake transmission mechanism is connected to a drive shaft that is driven by the operation of the parking brake, and an output shaft that transmits normal rotation to the cylindrical rotating member via a one-way clutch. The automatic standby mechanism is biased in the reverse rotation direction by a torsion coil spring in which the forwardly rotated cylindrical rotating member is disposed between the output shaft and the output shaft and the cylindrical rotating member. In addition, an engaging portion that allows the relative rotation in both the forward and reverse directions by a predetermined rotation angle to engage with each other is provided, and the forward rotation is transmitted to the cylindrical rotating member by the operation of the parking brake. A device provided with means for rotating the output shaft back in the reverse direction can be employed.

前記正逆両方向への相対回転を所定の回転角だけ許容して互いに係合し合う係合部は、前記筒状回転部材の内径側に前記出力シャフトを挿入し、この出力シャフトの外径側と前記筒状回転部材の内径側とに軸方向位置を合致させて設けた、互いに回転方向で係合し合う突起とすることができる。 An engaging portion that engages with each other while allowing relative rotation in both the forward and reverse directions by a predetermined rotation angle inserts the output shaft on the inner diameter side of the cylindrical rotating member, and the outer diameter side of the output shaft. And a projection that is provided on the inner diameter side of the cylindrical rotating member so as to match the axial position and engage with each other in the rotational direction.

前記出力シャフトを逆方向へ戻し回転する手段は、前記駆動シャフトと出力シャフトとの間に摩擦部材を介在させ、前記駐車ブレーキの操作後に戻し回転される駆動シャフトによって、前記ねじりコイルばねの回転付勢力よりも大きな前記摩擦部材の摩擦力で、前記出力シャフトを連れ戻し回転するものとすることができる。 The means for rotating the output shaft back in the reverse direction includes a friction member interposed between the drive shaft and the output shaft, and the torsion coil spring is rotated by the drive shaft rotated back after the parking brake is operated. The output shaft can be rotated back with the friction force of the friction member larger than the force.

前記直動部材を前進運動させるねじ機構はボールねじ機構とするのが好適である。 The screw mechanism for moving the linear motion member forward is preferably a ball screw mechanism.

本発明の電動式ブレーキ装置は、電動モータの回転駆動力によって正回転し、ねじ機構で直動部材を前進運動させる筒状回転部材に、駐車ブレーキの操作によって駆動される駆動シャフトの回転を伝達する駐車ブレーキ伝達機構を設け、駐車ブレーキの操作によっても筒状回転部材を正回転させ、直動部材の前進運動でブレーキ部材を被制動部材に押圧するようにしたので、コンパクトな設計を損なうことなく、駐車ブレーキの作動機能を組み込むことができる。 The electric brake device of the present invention rotates forward by the rotational driving force of the electric motor, and transmits the rotation of the drive shaft driven by the operation of the parking brake to the cylindrical rotating member that moves the linear motion member forward by the screw mechanism. Since the parking brake transmission mechanism is provided and the cylindrical rotating member is rotated forward by the operation of the parking brake and the brake member is pressed against the member to be braked by the forward movement of the linear motion member, the compact design is impaired. In addition, the parking brake operating function can be incorporated.

前記駐車ブレーキ伝達機構を、駐車ブレーキの操作によって駆動される駆動シャフトに、一方向クラッチを介して筒状回転部材に正回転を伝達する出力シャフトを連結したものとすることにより、よりコンパクトな設計とすることができる。 A more compact design by connecting the parking brake transmission mechanism to a drive shaft driven by the operation of the parking brake and an output shaft that transmits normal rotation to the cylindrical rotating member via a one-way clutch. It can be.

前記直動部材の前進運動でブレーキ部材を押圧するように正回転させた筒状回転部材を、所定の回転角だけ逆回転させて、ブレーキ部材を押圧した位置から所定の距離だけ自動的に後退待機させる自動待機機構を設けることにより、ブレーキ部材が摩耗しても制動後の直動部材を常にブレーキ部材の押圧位置近くに後退待機させ、コンパクトな設計を損なうことなく、ブレーキ部材の摩耗補償機能を組み込むことができる。 The cylindrical rotating member rotated forward so as to press the brake member by the forward movement of the linear motion member is reversely rotated by a predetermined rotation angle, and automatically retracted by a predetermined distance from the position where the brake member is pressed. By providing an automatic standby mechanism that waits, even if the brake member wears, the braked member's wear compensation function always keeps the linear motion member after braking backward and close to the brake member's pressing position, without compromising the compact design. Can be incorporated.

前記駐車ブレーキ伝達機構と自動待機機構とを合体させてユニット化することにより、よりコンパクトな設計とすることができる。 A more compact design can be achieved by uniting the parking brake transmission mechanism and the automatic standby mechanism.

以下、図面に基づき、本発明の実施形態を説明する。この電動式ブレーキ装置は、図１および図２に示すように、キャリパ１の内部で被制動部材としてのディスクロータ２の両側に、ブレーキ部材としてのブレーキパッド３を対向配置したディスクブレーキであり、キャリパ１と一体に形成したケーシング４の内径面に、電動モータのステータ５が固定されるとともに、筒状回転部材としてのロータ６が軸受７で回転自在に支持されている。ロータ６の軸方向前端側には、駆動力変換機構であるねじ機構としてのボールねじ機構のナット８が内嵌されて、直動部材としてのねじ軸９がボール１０を介してナット８に螺合され、ねじ軸９の前端側に別体の押圧部材１１が取り付けられて、ボルト１２で結合されたねじ軸９と押圧部材１１が回り止めキー１３で回り止めされている。ねじ軸９はロータ６が正回転したときに前進運動し、押圧部材１１でブレーキパッド３をディスクロータ２に押圧する。なお、ケーシング４の前端側は、キャリパ１と押圧部材１１間に取り付けられたブーツ１４でシールされ、ケーシング４の後端側には蓋１５が取り付けられている。 Hereinafter, embodiments of the present invention will be described with reference to the drawings. As shown in FIGS. 1 and 2, this electric brake device is a disc brake in which brake pads 3 as brake members are disposed opposite to both sides of a disc rotor 2 as a braked member inside the caliper 1. A stator 5 of an electric motor is fixed to an inner diameter surface of a casing 4 formed integrally with the caliper 1, and a rotor 6 as a cylindrical rotating member is rotatably supported by a bearing 7. A nut 8 of a ball screw mechanism as a screw mechanism that is a driving force conversion mechanism is fitted inside the front end side of the rotor 6 in the axial direction, and a screw shaft 9 as a linear motion member is screwed onto the nut 8 via a ball 10. The separate pressing member 11 is attached to the front end side of the screw shaft 9, and the screw shaft 9 and the pressing member 11 coupled by the bolt 12 are prevented from rotating by the rotation-preventing key 13. The screw shaft 9 moves forward when the rotor 6 rotates forward, and presses the brake pad 3 against the disc rotor 2 by the pressing member 11. The front end side of the casing 4 is sealed with a boot 14 attached between the caliper 1 and the pressing member 11, and a lid 15 is attached to the rear end side of the casing 4.

前記ケーシング４の後端側からは、駐車ブレーキ用レバー１６で回転駆動される駆動シャフト１７が、蓋１５を通してロータ６と同軸上に挿入され、駆動シャフト１７の先端側拡径部１７ａの外径面に、ころ１８ａを係合子とする一方向クラッチ１８を介して、ロータ６に正回転を伝達する駐車ブレーキ伝達機構の出力シャフト１９が、その後端側拡径部１９ａの内径面で連結されている。したがって、駐車ブレーキの操作によって、駆動シャフト１７の正回転が一方向クラッチ１８を介して出力シャフト１９からロータ６に伝達され、ねじ軸９が前進運動して押圧部材１１でブレーキパッド３をディスクロータ２に押圧する。 From the rear end side of the casing 4, a drive shaft 17 that is rotationally driven by the parking brake lever 16 is inserted coaxially with the rotor 6 through the lid 15, and the outer diameter of the tip-side enlarged diameter portion 17 a of the drive shaft 17. An output shaft 19 of a parking brake transmission mechanism that transmits a normal rotation to the rotor 6 is connected to an inner diameter surface of the rear end side enlarged diameter portion 19a via a one-way clutch 18 having a roller 18a as an engaging member. Yes. Accordingly, the forward rotation of the drive shaft 17 is transmitted from the output shaft 19 to the rotor 6 through the one-way clutch 18 by the operation of the parking brake, the screw shaft 9 moves forward, and the brake member 3 is moved to the disc rotor by the pressing member 11. Press 2

前記出力シャフト１９の後端側には、駆動シャフト１７からの抜け止め用のストッパリング２０が取り付けられ、ストッパリング２０とロータ６との間には、後述する自動待機機構として、電動ブレーキや駐車ブレーキの作動で正回転させたロータ６を所定の回転角だけ逆回転させるためのねじりコイルばね２１が取り付けられている。 A stopper ring 20 for preventing the output shaft 19 from coming off from the drive shaft 17 is attached to the rear end side of the output shaft 19, and an electric brake or parking is provided between the stopper ring 20 and the rotor 6 as an automatic standby mechanism described later. A torsion coil spring 21 is attached to reversely rotate the rotor 6 rotated forward by the operation of the brake by a predetermined rotation angle.

前記駐車ブレーキ用レバー１６は、駆動シャフト１７のセレーション１７ｃが切られた後端部を抱くアーム部が両側からボルト２２で締め付けられて取り付けられており、駐車ブレーキの操作端に接続されたワイヤ２３で、駆動シャフト１７を正回転する方向に回動され、駐車ブレーキ操作後には、ねじりコイルばね２４で戻し回動されて、ケーシング４に取り付けられたストッパピン２５で戻し位置を規制されるようになっている。 The parking brake lever 16 is attached with an arm portion holding a rear end portion of the drive shaft 17 where the serration 17c is cut and tightened with bolts 22 from both sides, and a wire 23 connected to the operation end of the parking brake. Thus, the drive shaft 17 is rotated in the forward rotation direction, and after the parking brake operation, the drive shaft 17 is rotated back by the torsion coil spring 24 and the return position is regulated by the stopper pin 25 attached to the casing 4. It has become.

前記出力シャフト１９の先端側縮径部１９ｂはロータ６の後端側に挿入され、図３（ａ）に示すように、挿入された縮径部１９ｂの外径側とロータ６の内径側とに軸方向位置を合致させて、互いに係合し合う突起２６ａ、２６ｂがそれぞれ１８０°の位相で設けられており、出力シャフト１９からロータ６に正回転が伝達されるとともに、両者の正逆両方向への相対回転が約半回転だけ許容されるようになっている。なお、ロータ６の内径側の突起２６ｂは、ロータ６に内嵌されて溝２７に回り止めされた環状部材２８に形成されている。 The front-end-side reduced diameter portion 19b of the output shaft 19 is inserted into the rear end side of the rotor 6, and as shown in FIG. 3A, the outer diameter side of the inserted reduced diameter portion 19b and the inner diameter side of the rotor 6 Protrusions 26a and 26b that are in axial alignment with each other and are engaged with each other are provided at a phase of 180 °, and forward rotation is transmitted from the output shaft 19 to the rotor 6, and both forward and reverse directions. Relative rotation to is allowed only about half a turn. The protrusion 26 b on the inner diameter side of the rotor 6 is formed on an annular member 28 that is fitted in the rotor 6 and is prevented from rotating in the groove 27.

図１に示したように、前記駆動シャフト１７の拡径部１７ａの内径側には、圧縮コイルばね２９で前方に付勢された摩擦板押さえ３０が設けられ、摩擦板押さえ３０の前端側に設けられたフランジ３０ａと、出力シャフト１９の拡径部１９ａの内側段差部との間に摩擦板３１ａが挟持されている。図４（ａ）、（ｂ）に示すように、駆動シャフト１７の拡径部１７ａの前端面には、１８０°の位相で２つの切欠き部１７ｂが設けられ、図５（ａ）、（ｂ）に示すように、摩擦板押さえ３０のフランジ３０ａの先端には、同じく１８０°の位相で２つの突出部３０ｂが設けられており、摩擦板押さえ３０は突出部３０ｂと切欠き部１７ｂの係合で、駆動シャフト１７に回り止めされている。 As shown in FIG. 1, a friction plate presser 30 urged forward by a compression coil spring 29 is provided on the inner diameter side of the enlarged diameter portion 17 a of the drive shaft 17. A friction plate 31 a is sandwiched between the provided flange 30 a and an inner stepped portion of the enlarged diameter portion 19 a of the output shaft 19. As shown in FIGS. 4A and 4B, the front end surface of the enlarged diameter portion 17a of the drive shaft 17 is provided with two notches 17b with a phase of 180 °. As shown in b), two protrusions 30b are similarly provided at the tip of the flange 30a of the friction plate press 30 with a phase of 180 °, and the friction plate press 30 has a protrusion 30b and a notch 17b. The engagement prevents the drive shaft 17 from rotating.

また、前記出力シャフト１９に取り付けられたストッパリング２０と、駆動シャフト１７の拡径部１７ａの外側段差部との間にも摩擦板３１ｂが挟持されている。これらの摩擦部材としての摩擦板３１ａ、３１ｂによる駆動シャフト１７と出力シャフト１９間の摩擦力は、前記ロータ６を所定の回転角だけ逆回転させるねじりコイルばね２１の回転付勢力よりも大きく設定されている。 A friction plate 31b is also sandwiched between the stopper ring 20 attached to the output shaft 19 and the outer stepped portion of the enlarged diameter portion 17a of the drive shaft 17. The frictional force between the drive shaft 17 and the output shaft 19 by the friction plates 31a and 31b as the friction members is set to be larger than the rotational biasing force of the torsion coil spring 21 that reversely rotates the rotor 6 by a predetermined rotation angle. ing.

以下に、電動ブレーキまたは駐車ブレーキの作動で正回転させたロータ６を所定の回転角だけ逆回転させ、直動部材としてのねじ軸９を、押圧部材１１でブレーキパッド３をディスクロータ２に押圧した押圧位置から、所定の距離だけ自動的に後退待機させる自動待機機構を、図３に基づいて説明する。なお、図３の各図は、時計回りが正回転、反時計回りが逆回転であり、実線の矢印はロータ６の回転方向を、破線の矢印はねじりコイルばね２１の回転付勢方向を示す。 Below, the rotor 6 rotated forward by the operation of the electric brake or the parking brake is reversely rotated by a predetermined rotation angle, and the screw shaft 9 as the linear motion member is pressed against the disc rotor 2 by the pressing member 11. An automatic standby mechanism for automatically retracting and waiting for a predetermined distance from the pressed position will be described with reference to FIG. In each drawing of FIG. 3, clockwise rotation is normal rotation and counterclockwise rotation is reverse rotation, the solid arrow indicates the rotation direction of the rotor 6, and the broken arrow indicates the rotation biasing direction of the torsion coil spring 21. .

まず、電動ブレーキの作動で電動モータの回転駆動力によってロータ６を正回転させた場合は、図３（ａ）に示すように、正回転するロータ６の突起２６ｂが出力シャフト１９の突起２６ａを後方から押圧する。このとき、一方向クラッチ１８は係合解除状態となり、かつ、電動モータの回転駆動力は各摩擦板３１ａ、３１ｂの摩擦力よりも十分に大きいので、出力シャフト１９は正回転するロータ６と共回りする。 First, when the rotor 6 is rotated forward by the rotational driving force of the electric motor by the operation of the electric brake, as shown in FIG. 3A, the protrusion 26b of the rotor 6 rotating in the forward direction is replaced with the protrusion 26a of the output shaft 19. Press from behind. At this time, the one-way clutch 18 is disengaged and the rotational driving force of the electric motor is sufficiently larger than the frictional force of the friction plates 31a and 31b. Turn around.

こののち、電動ブレーキを解除して電動モータの回転駆動力がなくなると、ロータ６はねじりコイルばね２１の回転付勢力で逆回転し、図３（ｂ）に示すように、約半回転してロータ６の突起２６ｂが出力シャフト１９の突起２６ａに係合すると、一方向クラッチ１８が係合状態となって、ロータ６の逆回転が停止する。したがって、このロータ６の約半回転分の逆回転によって、ねじ軸９がブレーキパッド３の押圧位置から所定の距離だけ自動的に後退する。 After that, when the electric brake is released and the rotational driving force of the electric motor disappears, the rotor 6 rotates in reverse by the rotational biasing force of the torsion coil spring 21, and as shown in FIG. When the protrusion 26b of the rotor 6 is engaged with the protrusion 26a of the output shaft 19, the one-way clutch 18 is engaged, and the reverse rotation of the rotor 6 is stopped. Therefore, the screw shaft 9 is automatically retracted from the pressing position of the brake pad 3 by a predetermined distance by reverse rotation of the rotor 6 by about half a rotation.

つぎに、駐車ブレーキの作動で駆動シャフト１７の回転駆動力によってロータ６を正回転させた場合は、図３（ｃ）に示すように、一方向クラッチ１８が係合状態となって回転する出力シャフト１９の突起２６ａがロータ６の突起２６ｂを後方から押圧してロータ６を正回転させる。 Next, when the rotor 6 is rotated forward by the rotational driving force of the drive shaft 17 by the operation of the parking brake, as shown in FIG. 3C, the one-way clutch 18 is engaged and rotated. The protrusion 26a of the shaft 19 presses the protrusion 26b of the rotor 6 from the rear to rotate the rotor 6 forward.

こののち、駐車ブレーキを解除して駐車ブレーキ用レバー１６がねじりコイルばね２４で戻し回動され、駆動シャフト１７が逆回転されると、図３（ｄ）に示すように、一方向クラッチ１８は係合解除状態となるが、出力シャフト１９は、ねじりコイルばね２１の回転付勢力に打ち勝つ各摩擦板３１ａ、３１ｂの摩擦力によって、駆動シャフト１７と一緒に所定の回転角だけ逆回転する。したがって、この出力シャフト１９の逆回転でその突起２６ａがロータ６の突起２６ｂから後方に逃げ、ロータ６もねじりコイルばね２１の回転付勢力で所定の回転角だけ逆回転して、ねじ軸９がブレーキパッド３の押圧位置から所定の距離だけ自動的に後退する。 After that, when the parking brake is released and the parking brake lever 16 is rotated back by the torsion coil spring 24 and the drive shaft 17 is rotated in the reverse direction, as shown in FIG. In the disengaged state, the output shaft 19 rotates backward by a predetermined rotation angle together with the drive shaft 17 by the frictional force of each friction plate 31a, 31b that overcomes the rotational biasing force of the torsion coil spring 21. Therefore, when the output shaft 19 rotates in reverse, the projection 26a escapes backward from the projection 26b of the rotor 6, and the rotor 6 also rotates in reverse by a predetermined rotation angle by the rotational biasing force of the torsion coil spring 21, so that the screw shaft 9 rotates. The brake pad 3 is automatically retracted by a predetermined distance from the pressed position of the brake pad 3.

以上のように、電動ブレーキと駐車ブレーキのいずれを解除したときも、ロータ６はねじりコイルばね２１の回転付勢力で所定の回転角だけ逆回転して、直動部材としてのねじ軸９をブレーキパッド３の押圧位置から所定の距離だけ自動的に後退させるので、この電動ブレーキ装置は、ブレーキパッド３の摩耗によって押圧位置が変化しても、ねじ軸９を常に押圧位置の近くに待機させることができる摩耗補償機能を有する。 As described above, when either the electric brake or the parking brake is released, the rotor 6 reversely rotates by a predetermined rotation angle by the rotational biasing force of the torsion coil spring 21 to brake the screw shaft 9 as the linear motion member. Since the electric brake device is automatically retracted by a predetermined distance from the pressing position of the pad 3, even if the pressing position is changed due to wear of the brake pad 3, the electric brake device always makes the screw shaft 9 stand by near the pressing position. Wear compensation function.

前記ブレーキパッド３が摩耗したときは、駐車ブレーキ用レバー１６を取り外して電動モータを逆回転することにより、ねじ軸９を元の位置に戻して、摩耗したブレーキパッド３を簡単に交換することができる。 When the brake pad 3 is worn, it is possible to easily replace the worn brake pad 3 by removing the parking brake lever 16 and rotating the electric motor in reverse to return the screw shaft 9 to its original position. it can.

上述した実施形態では、出力シャフト１９からロータ６へ正回転を伝達し、両者の正逆両方向への相対回転を所定の回転角だけ許容して互いに係合し合う係合部を、出力シャフト１９の外径側とロータ６の内径側とに１８０°の位相で２つずつ設けた突起２６ａ、２６ｂとしたが、これらの突起２６ａ、２６ｂは１つずつ以上あればよく、任意の位相で設けることができる。また、この係合部は必ずしも出力シャフト１９の外径側とロータ６の内径側に設ける必要はなく、例えば、両者の対向する端面に設けることもできる。 In the above-described embodiment, the output shaft 19 includes an engaging portion that transmits forward rotation from the output shaft 19 to the rotor 6 and engages with each other while allowing relative rotation in both forward and reverse directions by a predetermined rotation angle. The projections 26a and 26b are provided in two at a phase of 180 ° on the outer diameter side of the rotor 6 and the inner diameter side of the rotor 6, but one or more of these projections 26a and 26b may be provided and provided in an arbitrary phase. be able to. In addition, the engaging portion is not necessarily provided on the outer diameter side of the output shaft 19 and the inner diameter side of the rotor 6, and can be provided, for example, on the end surfaces facing each other.

電動式ブレーキ装置の実施形態を示す縦断面図A longitudinal sectional view showing an embodiment of an electric brake device 図１の側面図Side view of FIG. ａ、ｂ、ｃ、ｄは、それぞれ電動ブレーキと駐車ブレーキの作動と解除の際の作用を説明する図１のIII−III線に沿った模式的断面図a, b, c, and d are schematic cross-sectional views along the line III-III in FIG. 1 for explaining the operation when the electric brake and parking brake are operated and released, respectively. ａは図1の駆動シャフトの切欠き縦断面図、ｂはａの側面図a is a longitudinal sectional view of the drive shaft of FIG. 1, and b is a side view of a. ａは図１の摩擦板押さえの縦断面図、ｂはａの側面図a is a longitudinal sectional view of the friction plate press of FIG. 1, b is a side view of a

符号の説明Explanation of symbols

１キャリパ
２ディスクロータ
３ブレーキパッド
４ケーシング
５ステータ
６ロータ
７軸受
８ナット
９ねじ軸
１０ボール
１１押圧部材
１２ボルト
１３回り止めキー
１４ブーツ
１５蓋
１６レバー
１７駆動シャフト
１７ａ拡径部
１７ｂ切欠き部
１７ｃセレーション
１８一方向クラッチ
１８ａころ
１９出力シャフト
１９ａ拡径部
１９ｂ縮径部
２０ストッパリング
２１ねじりコイルばね
２２ボルト
２３ワイヤ
２４ねじりコイルばね
２５ストッパピン
２６ａ、２６ｂ突起
２７溝
２８環状部材
２９圧縮コイルばね
３０摩擦板押さえ
３０ａフランジ
３０ｂ突出部
３１ａ、３１ｂ摩擦板 DESCRIPTION OF SYMBOLS 1 Caliper 2 Disc rotor 3 Brake pad 4 Casing 5 Stator 6 Rotor 7 Bearing 8 Nut 9 Screw shaft 10 Ball 11 Pressing member 12 Bolt 13 Non-rotating key 14 Boot 15 Lid 16 Lever 17 Drive shaft 17a Expanded portion 17b Notched portion 17c Serration 18 One-way clutch 18a Roller 19 Output shaft 19a Expanded portion 19b Reduced portion 20 Stopper ring 21 Torsion coil spring 22 Bolt 23 Wire 24 Torsion coil spring 25 Stopper pins 26a and 26b Protrusion 27 Groove 28 Annular member 29 Compression coil spring 30 Friction plate presser 30a Flange 30b Protruding part 31a, 31b Friction plate

Claims

電動モータの回転駆動力を直線駆動力に変換する駆動力変換機構を備え、この駆動力変換機構によって直線駆動力を伝達される直動部材の前進運動で、ブレーキ部材を被制動部材に押圧する電動式ブレーキ装置において、前記駆動力変換機構を、前記電動モータの回転駆動力によって正回転する筒状回転部材の内径側に設けたねじ機構で前記直動部材を前進運動させるものとし、駐車ブレーキの操作によって駆動される駆動シャフトの回転を前記筒状回転部材に伝達する駐車ブレーキ伝達機構を設け、前記駐車ブレーキの操作によっても前記筒状回転部材を正回転させ、前記直動部材の前進運動で前記ブレーキ部材を被制動部材に押圧するようにし、前記駐車ブレーキ伝達機構を、前記駐車ブレーキの操作によって駆動される駆動シャフトに、一方向クラッチを介して前記筒状回転部材に正回転を伝達する出力シャフトを連結したものとしたことを特徴とする電動式ブレーキ装置。 A driving force conversion mechanism that converts the rotational driving force of the electric motor into a linear driving force is provided, and the brake member is pressed against the member to be braked by the forward movement of the linear motion member to which the linear driving force is transmitted by the driving force conversion mechanism. In the electric brake device, the driving force conversion mechanism is configured to move the linear motion member forward by a screw mechanism provided on an inner diameter side of a cylindrical rotating member that is rotated forward by the rotational driving force of the electric motor. A parking brake transmission mechanism that transmits the rotation of the drive shaft driven by the operation to the cylindrical rotating member, and the cylindrical rotating member is rotated forward by the operation of the parking brake, so that the linear motion member moves forward. in so as to press the brake member to the braked member, the parking brake transmission mechanism, the drive shaft driven by the operation of the parking brake Electric brake apparatus according to claim through the one-way clutch that was obtained by connecting the output shaft for transmitting the forward rotation to the cylindrical rotary member.

前記直動部材の前進運動でブレーキ部材を押圧するように正回転させた筒状回転部材を、所定の回転角だけ逆回転させて、前記ブレーキ部材を押圧した位置から所定の距離だけ自動的に後退待機させる自動待機機構を設けた請求項１に記載の電動式ブレーキ装置。 The cylindrical rotating member rotated forward so as to press the brake member by the forward movement of the linear motion member is reversely rotated by a predetermined rotation angle, and automatically a predetermined distance from the position where the brake member is pressed. The electric brake device according to claim 1 , further comprising an automatic standby mechanism for performing backward standby.

前記駐車ブレーキ伝達機構と前記自動待機機構とを合体させてユニット化した請求項２に記載の電動式ブレーキ装置。 The electric brake device according to claim 2 , wherein the parking brake transmission mechanism and the automatic standby mechanism are combined into a unit.

前記合体させたユニットが、前記駐車ブレーキ伝達機構を、前記駐車ブレーキの操作によって駆動される駆動シャフトに、一方向クラッチを介して前記筒状回転部材に正回転を伝達する出力シャフトを連結したものとし、前記自動待機機構を、前記正回転させた筒状回転部材を前記出力シャフトとの間に配したねじりコイルばねで逆回転方向へ付勢したものとし、前記出力シャフトと筒状回転部材とに、これらの正逆両方向への相対回転を所定の回転角だけ許容して互いに係合し合う係合部を設けて、前記駐車ブレーキの操作によって前記筒状回転部材に正回転を伝達した出力シャフトを、逆方向へ戻し回転する手段を設けたものである請求項３に記載の電動式ブレーキ装置。 The combined unit is a unit in which the parking brake transmission mechanism is connected to a drive shaft that is driven by the operation of the parking brake and an output shaft that transmits normal rotation to the cylindrical rotating member via a one-way clutch. And the automatic standby mechanism is urged in the reverse rotation direction by a torsion coil spring arranged between the output rotating shaft and the cylindrical rotating member rotated forward, and the output shaft, the cylindrical rotating member, In addition, an engaging portion that allows the relative rotation in both the forward and reverse directions by a predetermined rotation angle to be engaged with each other is provided, and the forward rotation is transmitted to the cylindrical rotating member by the operation of the parking brake. 4. The electric brake device according to claim 3 , wherein means for rotating the shaft back in the reverse direction is provided.

前記正逆両方向への相対回転を所定の回転角だけ許容して互いに係合し合う係合部を、前記筒状回転部材の内径側に前記出力シャフトを挿入し、この出力シャフトの外径側と前記筒状回転部材の内径側とに軸方向位置を合致させて設けた、互いに回転方向で係合し合う突起とした請求項４に記載の電動式ブレーキ装置。 The output shaft is inserted into the inner diameter side of the cylindrical rotating member with the engaging portion engaging with each other while allowing relative rotation in both the forward and reverse directions by a predetermined rotation angle, and the outer diameter side of the output shaft. 5. The electric brake device according to claim 4 , wherein the protrusions are provided so as to be axially aligned with each other on the inner diameter side of the cylindrical rotating member and engage with each other in the rotational direction.

前記出力シャフトを逆方向へ戻し回転する手段を、前記駆動シャフトと出力シャフトとの間に摩擦部材を介在させ、前記駐車ブレーキの操作後に戻し回転される駆動シャフトによって、前記ねじりコイルばねの回転付勢力よりも大きな前記摩擦部材の摩擦力で、前記出力シャフトを連れ戻し回転するものとした請求項４または５に記載の電動式ブレーキ装置。 The means for rotating the output shaft in the reverse direction is provided with a rotation of the torsion coil spring by the drive shaft that is rotated back after the parking brake is operated by interposing a friction member between the drive shaft and the output shaft. The electric brake device according to claim 4 or 5 , wherein the output shaft is rotated back by a frictional force of the friction member larger than a force.

前記直動部材を前進運動させるねじ機構をボールねじ機構とした請求項１乃至６のいずれかに記載の電動式ブレーキ装置。 The electric brake device according to any one of claims 1 to 6 , wherein a screw mechanism that moves the linear motion member forward is a ball screw mechanism.