JP6109121B2 - Electric disc brake device - Google Patents

Electric disc brake device Download PDF

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JP6109121B2
JP6109121B2 JP2014160412A JP2014160412A JP6109121B2 JP 6109121 B2 JP6109121 B2 JP 6109121B2 JP 2014160412 A JP2014160412 A JP 2014160412A JP 2014160412 A JP2014160412 A JP 2014160412A JP 6109121 B2 JP6109121 B2 JP 6109121B2
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planetary roller
seat plate
pressure receiving
driven member
pressure
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JP2014206286A (en
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雅章 江口
雅章 江口
村松　誠
誠 村松
山崎　達也
達也 山崎
安井　誠
誠 安井
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NTN Corp
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Description

この発明は、電動式ディスクブレーキ装置に関する。   The present invention relates to an electric disc brake device.

電動式ディスクブレーキ装置のブレーキパッドを直線駆動する電動式直動アクチュエータにおいては、電動モータのロータ軸の回転運動を運動変換機構によって軸方向に移動自在に支持された被駆動部材の直線運動に変換するようにしている。 In an electric linear actuator that linearly drives a brake pad of an electric disc brake device, the rotational motion of the rotor shaft of the electric motor is converted into a linear motion of a driven member that is supported so as to be axially movable by a motion conversion mechanism. Like to do.

電動式直動アクチュエータに採用された運動変換機構として、ボールねじ機構やボールランプ機構が知られているが、これらの運動変換機構においては、ある程度の増力機能を有するものの、電動式ディスクブレーキ装置等で必要とされるような大きな増力機能を確保することができない。   Ball screw mechanisms and ball ramp mechanisms are known as motion conversion mechanisms employed in electric linear actuators. Although these motion conversion mechanisms have a certain degree of boosting function, electric disk brake devices, etc. It is not possible to secure a large boosting function as required by the company.

そこで、上記のような運動変換機構を採用した電動式直動アクチュエータにおいては、遊星歯車機構等の減速機構を別途組込んで駆動力の増大を図るようにしており、上記減速機構を組込む分、構成が複雑となり、電動式直動アクチュエータが大型化するという問題があった。   Therefore, in the electric linear motion actuator adopting the motion conversion mechanism as described above, a reduction mechanism such as a planetary gear mechanism is separately incorporated so as to increase the driving force. There is a problem in that the configuration is complicated and the electric linear actuator is increased in size.

そのような問題点を解決するため、本件出願人は、減速機構を組込むことなく大きな増力機能を確保することができ、直動ストロークが比較的小さい電動式ディスクブレーキ装置への採用に好適な電動式直動アクチュエータを特許文献１および特許文献２において既に提案している。   In order to solve such problems, the applicant of the present application can secure a large boosting function without incorporating a speed reduction mechanism, and is suitable for use in an electric disc brake device having a relatively small linear motion stroke. Patent Literature 1 and Patent Literature 2 have already proposed a linear actuator.

ここで、上記特許文献１および２に記載された電動式直動アクチュエータにおいては、電動モータによって回転駆動される回転軸と軸方向に移動自在に支持された外輪部材との間に遊星ローラを組込み、上記回転軸の回転により、その回転軸との摩擦接触によって遊星ローラを自転させつつ公転させ、その遊星ローラの外径面に形成された螺旋溝または円周溝と外輪部材の内径面に設けられた螺旋突条との噛み合いによって外輪部材を軸方向に直線移動させるようにしている。   Here, in the electric linear actuators described in Patent Documents 1 and 2, a planetary roller is incorporated between a rotating shaft that is rotationally driven by an electric motor and an outer ring member that is movably supported in the axial direction. Rotating the rotating shaft causes the planetary roller to revolve while rotating by frictional contact with the rotating shaft, and is provided on the inner surface of the outer ring member and the spiral groove or circumferential groove formed on the outer surface of the planetary roller. The outer ring member is linearly moved in the axial direction by meshing with the formed spiral protrusion.

また、上記特許文献１および２に記載された電動式直動アクチュエータにおいては、遊星ローラとその遊星ローラを回転自在に支持するキャリアのインナ側ディスク間にスラスト軸受を組込み、そのスラスト軸受によって外輪部材から遊星ローラに負荷される軸方向の押し込み荷重を受けて、遊星ローラの回転の円滑化を図るようにしている。   In the electric linear actuators described in Patent Documents 1 and 2, a thrust bearing is incorporated between the planetary roller and the inner disk of the carrier that rotatably supports the planetary roller, and the outer ring member is formed by the thrust bearing. The rotation of the planetary roller is made smooth by receiving an axial indentation load applied to the planetary roller.

特開２０１０−６５７７７号公報JP 2010-65777 A 特開２０１０−９０９５９号公報JP 2010-90959 A

ところで、特許文献１および２に記載された電動式直動アクチュエータにおいては、直線駆動される被駆動部材としての外輪部材から遊星ローラに負荷される軸方向荷重は、遊星ローラの外径面に形成された螺旋溝または円周溝と外輪部材の内径面に設けられた螺旋突条の係合部に入力されるため、その遊星ローラのインナ側端面に形成された軸受軌道面へ負荷される軸方向荷重は偏荷重となり、スラスト軸受はその偏荷重を受けることになる。 By the way, in the electric linear actuator described in Patent Documents 1 and 2, the axial load applied to the planetary roller from the outer ring member as the driven member that is linearly driven is formed on the outer diameter surface of the planetary roller. The shaft is loaded on the bearing raceway surface formed on the inner side end surface of the planetary roller, because it is input to the engagement portion of the spiral groove or circumferential groove formed on the inner ring surface of the outer ring member. The directional load becomes an unbalanced load, and the thrust bearing receives the unbalanced load.

このため、受圧部としてのスラスト軸受においては、軸方向荷重が入力される入力部位と同一の位相に位置する転動体に大きな軸方向荷重が負荷され、その転動体から周方向にずれるにしたがって転動体に負荷される荷重が次第に小さくなって、スラスト軸受の面圧分布が周方向で不均一となり、転動体や軌道輪が偏摩耗する可能性がある。 For this reason, in the thrust bearing as the pressure receiving portion, a large axial load is applied to the rolling element located at the same phase as the input portion to which the axial load is input, and the rolling element is rotated as it deviates in the circumferential direction. There is a possibility that the load applied to the moving body becomes gradually smaller, the surface pressure distribution of the thrust bearing becomes non-uniform in the circumferential direction, and the rolling elements and the races are unevenly worn.

この発明の課題は、軸方向荷重を受ける受圧部の周方向の面圧分布の均一化を図ることである。 An object of the present invention is to make uniform the surface pressure distribution in the circumferential direction of a pressure receiving portion that receives an axial load .

上記の課題を解決するため、この発明においては、ハウジングと、そのハウジングに支持された電動モータと、前記ハウジング内に組み込まれた軸方向に移動可能な被駆動部材と、前記電動モータのロータ軸の回転運動を前記被駆動部材の軸方向への直線運動に変換する運動変換機構とを有し、前記ハウジングに一体に設けられたキャリパボディ内にブレーキディスクの外周の一部を配置し、そのブレーキディスクの両側に固定ブレーキパッドと可動ブレーキパッドとを設け、前記可動ブレーキパッドを前記被駆動部材でブレーキディスクに押し付けて制動力を付与し、可動ブレーキパッドからの軸方向荷重を受圧部で受けるようした電動式ディスクブレーキ装置において、前記可動ブレーキパッドから前記受圧部に至る軸方向荷重の負荷系路に、前記受圧部での周方向の面圧分布の均一化を図る調心機構を設けた構成を採用したのである。 To solve the above problem, our Itewa to the present invention, a housing, an electric motor supported on the housing, and a driven member axially movable incorporated in the housing of the electric motor A motion conversion mechanism for converting the rotational motion of the rotor shaft into a linear motion in the axial direction of the driven member, and a part of the outer periphery of the brake disk is disposed in a caliper body provided integrally with the housing. A fixed brake pad and a movable brake pad are provided on both sides of the brake disk, the movable brake pad is pressed against the brake disk by the driven member to apply a braking force, and an axial load from the movable brake pad is received by the pressure receiving portion. In the electric disc brake device that is received by the load system of the axial load from the movable brake pad to the pressure receiving portion To, than is adopted the configuration in which the aligning mechanism uniformed in the circumferential direction of the surface pressure distribution in the pressure receiving portion.

上記の構成からなる電動式ディスクブレーキ装置において、電動モータを駆動すると、運動変換機構の作動により被駆動部材が軸方向に直線移動し、可動ブレーキパッドがブレーキディスクに押し付けられてブレーキディスクに制動力が付与される。In the electric disc brake device having the above-described configuration, when the electric motor is driven, the driven member is linearly moved in the axial direction by the operation of the motion conversion mechanism, and the movable brake pad is pressed against the brake disc to apply the braking force to the brake disc. Is granted.

上記のような制動力の付与時、可動ブレーキパッドから受圧部に軸方向荷重が負荷される。その軸方向荷重が偏荷重であると、調心機構が作動し、受圧部での周方向の面圧分布の均一化が図られる。When the braking force is applied as described above, an axial load is applied from the movable brake pad to the pressure receiving portion. When the axial load is an eccentric load, the aligning mechanism operates and the surface pressure distribution in the circumferential direction at the pressure receiving portion is made uniform.

この発明においては、上記のように、ブレーキディスクに対する制動力の付与時、可動ブレーキパッドからの軸方向荷重が偏荷重であると調心機構が作動するため、受圧部での周方向の面圧分布の均一化を図り、耐久性の低下を抑制することができる。 Contact Itewa to the present invention, as described above, when applying the braking force to the brake disk, since the aligning mechanism axial load is a load polarized from the movable brake pad is activated, the circumferential direction of the pressure-receiving portion It is possible to make the surface pressure distribution uniform and suppress a decrease in durability.

この発明に係る電動式ディスクブレーキ装置に採用される電動式直動アクチュエータの縦断面図 Longitudinal cross-sectional view of the electric linear motion actuator which is employed in the electric disc brake apparatus according to the present invention 図１の一部を拡大して示す断面図Sectional drawing which expands and shows a part of FIG. 図２のIII−III線に沿った断面図Sectional view along line III-III in FIG. 図２の一部を拡大して示す断面図Sectional drawing which expands and shows a part of FIG. (ａ)および(ｂ)は、凹面が形成された座板の各例を示す断面図(a) And (b) is sectional drawing which shows each example of the seat plate in which the concave surface was formed 電動式直動アクチュエータの他の例を示す縦断面図Longitudinal sectional view showing another example of a conductive Doshiki linear actuator 電動式直動アクチュエータのさらに他の例を示す縦断面図Vertical sectional view showing still another example of the electrostatic Doshiki linear actuator 電動式直動アクチュエータのさらに他の例を示す縦断面図Vertical sectional view showing still another example of the electrostatic Doshiki linear actuator 電動式直動アクチュエータのさらに他の例を示す縦断面図Vertical sectional view showing still another example of the electrostatic Doshiki linear actuator 電動式直動アクチュエータのさらに他の例を示す縦断面図Vertical sectional view showing still another example of the electrostatic Doshiki linear actuator 電動式直動アクチュエータのさらに他の例を示す縦断面図Vertical sectional view showing still another example of the electrostatic Doshiki linear actuator 電動式直動アクチュエータのさらに他の例を示す縦断面図Vertical sectional view showing still another example of the electrostatic Doshiki linear actuator 電動式直動アクチュエータのさらに他の例を示す縦断面図Vertical sectional view showing still another example of the electrostatic Doshiki linear actuator (ｃ)は、座板の他の例を示す正面図、(ｄ)は、(ｃ)の縦断面図(c) is a front view showing another example of the seat plate, (d) is a longitudinal sectional view of (c). (ｅ)は、座板の他の例を示す正面図、(ｆ)は、(ｅ)の縦断面図(e) is a front view showing another example of a seat plate, (f) is a longitudinal sectional view of (e). (ｇ)、(ｈ)は、座板の他の例を示す断面図(g), (h) is a sectional view showing another example of a seat plate 電動式直動アクチュエータのさらに他の例を示す縦断面図Vertical sectional view showing still another example of the electrostatic Doshiki linear actuator 電動式直動アクチュエータのさらに他の例を示す縦断面図Vertical sectional view showing still another example of the electrostatic Doshiki linear actuator 電動式直動アクチュエータのさらに他の例を示す縦断面図Vertical sectional view showing still another example of the electrostatic Doshiki linear actuator 電動式直動アクチュエータのさらに他の例を示す縦断面図Vertical sectional view showing still another example of the electrostatic Doshiki linear actuator この発明に係る電動式ディスクブレーキ装置の実施の形態を示す縦断面図A longitudinal sectional view showing an embodiment of an electric disc brake device according to the present invention

以下、この発明の実施の形態を図面に基づいて説明する。図１乃至図３は、この発明に係る電動式直動アクチュエータＡの第１の実施の形態を示す。図１に示すように、ハウジング１は、円筒状をなし、その一端には径方向外方に張り出すベースプレート２が設けられ、そのベースプレート２の外側面はハウジング１の一端部にボルト止めされたカバー３によって覆われている。   Hereinafter, embodiments of the present invention will be described with reference to the drawings. 1 to 3 show a first embodiment of an electric linear actuator A according to the present invention. As shown in FIG. 1, the housing 1 has a cylindrical shape, and a base plate 2 projecting radially outward is provided at one end thereof, and an outer surface of the base plate 2 is bolted to one end of the housing 1. Covered by the cover 3.

ハウジング１の内部には外輪部材５が組込まれている。外輪部材５は回り止めされ、かつ、ハウジング１の内径面に沿って軸方向に移動自在とされ、その内径面には、図２に示すように、断面Ｖ字形の螺旋突条６が設けられている。   An outer ring member 5 is incorporated in the housing 1. The outer ring member 5 is prevented from rotating and is movable in the axial direction along the inner diameter surface of the housing 1, and a spiral protrusion 6 having a V-shaped cross section is provided on the inner diameter surface as shown in FIG. ing.

図１に示すように、ハウジング１内には、外輪部材５の軸方向一端側に軸受部材７が組込まれている。軸受部材７は円盤状をなし、その中央部にはボス部７ａが設けられている。軸受部材７は、ハウジング１の内径面に取付けた止め輪８によってカバー３側に移動するのが防止されている。   As shown in FIG. 1, a bearing member 7 is incorporated in the housing 1 on one end side in the axial direction of the outer ring member 5. The bearing member 7 has a disk shape, and a boss portion 7a is provided at the center thereof. The bearing member 7 is prevented from moving toward the cover 3 by a retaining ring 8 attached to the inner diameter surface of the housing 1.

軸受部材７のボス部７ａ内には一対の転がり軸受９が軸方向に間隔をおいて組込まれ、その転がり軸受９によって外輪部材５の軸心上に配置された回転軸１０が回転自在に支持されている。   A pair of rolling bearings 9 is incorporated in the boss portion 7a of the bearing member 7 with an interval in the axial direction, and the rotating shaft 10 disposed on the axis of the outer ring member 5 is rotatably supported by the rolling bearing 9. Has been.

ハウジング１のベースプレート２には電動モータ１１が支持され、その電動モータ１１のロータ軸１２の回転は、カバー３内に組込まれたギヤ減速機構１３によって回転軸１０に伝達されるようになっている。   An electric motor 11 is supported on the base plate 2 of the housing 1, and the rotation of the rotor shaft 12 of the electric motor 11 is transmitted to the rotating shaft 10 by a gear reduction mechanism 13 incorporated in the cover 3. .

外輪部材５の内側には回転軸１０を中心にして回転可能なキャリア１４が組込まれている。図２および図３に示すように、キャリア１４は、軸方向で対向する一対のディスク１４ａ、１４ｂを有し、一方のディスク１４ｂに設けられた複数の間隔調整用柱部１５によって一対のディスク１４ａ、１４ｂの対向間隔が一定に保持されている。   A carrier 14 that is rotatable about the rotation shaft 10 is incorporated inside the outer ring member 5. As shown in FIG. 2 and FIG. 3, the carrier 14 has a pair of discs 14a and 14b facing each other in the axial direction, and a pair of discs 14a is provided by a plurality of interval adjusting column portions 15 provided on one disc 14b. , 14b is kept constant.

キャリア１４は、一対のディスク１４ａ、１４ｂの内径面に組み込まれたすべり軸受１６により回転軸１０を中心にして回転自在に、かつ、軸方向にスライド自在に支持され、上記回転軸１０の軸端部に取付けられた止め輪１７により回転軸１０の軸端から抜け出るのが防止されている。   The carrier 14 is supported by a slide bearing 16 incorporated in the inner surface of the pair of disks 14a and 14b so as to be rotatable about the rotary shaft 10 and slidable in the axial direction. The retaining ring 17 attached to the portion prevents the rotating shaft 10 from coming off the shaft end.

キャリア１４における一対のディスク１４ａ、１４ｂのそれぞれには、軸方向で対向する一対の軸挿入孔１８が周方向に間隔をおいて形成され、その対向一対の軸挿入孔１８のそれぞれ内部にローラ軸１９の軸端部が挿入されており、それぞれのローラ軸１９に対向一対の軸受２０が嵌合され、その軸受２０によって遊星ローラ２１が回転自在に支持されている。   Each of the pair of disks 14a and 14b in the carrier 14 is formed with a pair of axial insertion holes 18 opposed in the axial direction at intervals in the circumferential direction, and a roller shaft is formed inside each of the opposed pair of shaft insertion holes 18. 19 shaft end portions are inserted, and a pair of opposed bearings 20 are fitted to the respective roller shafts 19, and planetary rollers 21 are rotatably supported by the bearings 20.

ここで、一対のディスク１４ａ、１４ｂに形成された軸挿入孔１８は径方向に長い長孔とされており、ローラ軸１９はその長孔の両端に当接する範囲において移動自在とされ、それぞれのローラ軸１９の軸端部を包み込むようにかけ渡された径方向に弾性変形可能な弾性リング２２によりローラ軸１９が内向きに付勢されて、遊星ローラ２１が回転軸１０の外径面に押し付けられている。このため、回転軸１０が回転すると、その回転軸１０の外径面に対する摩擦接触によって遊星ローラ２１が回転するようになっている。   Here, the shaft insertion holes 18 formed in the pair of disks 14a and 14b are elongated holes that are long in the radial direction, and the roller shaft 19 is movable within a range where both ends of the elongated holes are in contact with each other. The roller shaft 19 is urged inward by an elastic ring 22 that is elastically deformable in the radial direction and is wrapped so as to wrap around the end portion of the roller shaft 19, so that the planetary roller 21 is pressed against the outer diameter surface of the rotating shaft 10. It has been. For this reason, when the rotating shaft 10 rotates, the planetary roller 21 rotates by frictional contact with the outer diameter surface of the rotating shaft 10.

遊星ローラ２１の外径面には、外輪部材５に設けられた螺旋突条６のピッチと同一のピッチで螺旋溝２３が形成され、その螺旋溝２３に螺旋突条６が係合している。なお、螺旋溝２３に代えて、複数の円周溝を螺旋突条６のピッチと同一のピッチで形成してもよい。   A spiral groove 23 is formed on the outer diameter surface of the planetary roller 21 at the same pitch as that of the spiral protrusion 6 provided on the outer ring member 5, and the spiral protrusion 6 is engaged with the spiral groove 23. . Instead of the spiral groove 23, a plurality of circumferential grooves may be formed at the same pitch as the pitch of the spiral ridge 6.

キャリア１４の一対のディスク１４ａ、１４ｂのうち、軸受部材７側に位置するインナ側ディスク１４ａと遊星ローラ２１間には、遊星ローラ２１側より順に、スラスト軸受２４、加圧座板２５および受圧座板２６が組み込まれている。   Among the pair of disks 14a and 14b of the carrier 14, between the inner disk 14a located on the bearing member 7 side and the planetary roller 21, the thrust bearing 24, the pressure seat plate 25, and the pressure receiving seat plate are sequentially arranged from the planetary roller 21 side. 26 is incorporated.

図４に示すように、スラスト軸受２４は、軌道輪２４ａと、その軌道輪２４ａと遊星ローラ２１の対向面に沿って転動可能な複数の転動体２４ｂと、その転動体２４ｂを保持する保持器２４ｃからなっている。   As shown in FIG. 4, the thrust bearing 24 holds a raceway ring 24 a, a plurality of rolling elements 24 b that can roll along the facing surfaces of the raceway ring 24 a and the planetary roller 21, and a holder that holds the rolling element 24 b. 24 c.

加圧座板２５と受圧座板２６の対向面には調心座２７が形成されている。調心座２７は、加圧座板２５に形成された凸形球面２７ａと受圧座板２６に形成されてその凸形球面２７ａを接触案内する凹面２７ｂとからなっている。凹面２７ｂは、図５(ａ)に示すように、凹形球面であってもよく、図５(ｂ)に示すように、テーパ面であってもよい。   An aligning seat 27 is formed on the opposing surface of the pressure seat plate 25 and the pressure receiving seat plate 26. The aligning seat 27 includes a convex spherical surface 27a formed on the pressure seat plate 25 and a concave surface 27b formed on the pressure receiving seat plate 26 to contact and guide the convex spherical surface 27a. The concave surface 27b may be a concave spherical surface as shown in FIG. 5 (a), or may be a tapered surface as shown in FIG. 5 (b).

加圧座板２５および受圧座板２６のそれぞれ中心部にはローラ軸１９が挿通される軸挿入孔２５ａ、２６ａが形成され、受圧座板２６に形成された軸挿入孔２６ａとローラ軸１９との間には隙間２８がある。   Shaft insertion holes 25 a and 26 a through which the roller shaft 19 is inserted are formed at the center of each of the pressure seat plate 25 and the pressure receiving seat plate 26, and the shaft insertion hole 26 a formed in the pressure receiving seat plate 26 and the roller shaft 19. There is a gap 28 between them.

一方、加圧座板２５に形成された軸挿入孔２５ａの内径はローラ軸１９の外径とほぼ同径とされ、前記隙間２８の範囲内において加圧座板２５は傾動自在とされている。   On the other hand, the inner diameter of the shaft insertion hole 25 a formed in the pressure seat plate 25 is substantially the same as the outer diameter of the roller shaft 19, and the pressure seat plate 25 is tiltable within the gap 28.

図２に示すように、キャリア１４におけるインナ側ディスク１４ａと軸受部材７の対向面間には、環状のサポート部材３０と、スラスト軸受３１とが組み込まれ、上記スラスト軸受３１はキャリア１４およびサポート部材３０に負荷される軸方向のスラスト荷重を受けるようになっている。   As shown in FIG. 2, an annular support member 30 and a thrust bearing 31 are incorporated between opposing surfaces of the inner disk 14 a and the bearing member 7 in the carrier 14, and the thrust bearing 31 includes the carrier 14 and the support member. The axial thrust load applied to 30 is received.

サポート部材３０にはインナ側ディスク１４ａと対向する面に環状溝３２が形成され、その環状溝３２内に前述の弾性リング２２が収容されている。   An annular groove 32 is formed on the support member 30 on the surface facing the inner disk 14 a, and the aforementioned elastic ring 22 is accommodated in the annular groove 32.

外輪部材５のハウジング１の端部開口から外部に位置する他端の開口はシールカバー３３の取付けにより閉塞されて内部に異物が侵入するのが防止されている。一方、ハウジング１の他端開口は、その他端部と外輪部材５の他端部間に取付けられたブーツ３４により閉塞されて内部に異物が侵入するのが防止されている。   The opening at the other end located outside the end opening of the housing 1 of the outer ring member 5 is closed by the attachment of the seal cover 33 to prevent foreign matter from entering the inside. On the other hand, the other end opening of the housing 1 is blocked by a boot 34 attached between the other end and the other end of the outer ring member 5 to prevent foreign matter from entering the inside.

第１の実施の形態で示す電動式直動アクチュエータＡは上記の構造からなり、図２１は、その電動式直動アクチュエータＡを採用した電動式ディスクブレーキ装置Ｂを示す。この電動式ディスクブレーキ装置においては、電動式直動アクチュエータにおけるハウジング１の他端部にキャリパボディ部４０を一体に設け、そのキャリパボディ部４０内に外周部の一部が配置されたブレーキディスク４１の両側に固定ブレーキパッド４２と可動ブレーキパッド４３を設け、その可動ブレーキパッド４３を外輪部材５の他端部に連結一体化している。   The electric linear actuator A shown in the first embodiment has the above structure, and FIG. 21 shows an electric disc brake device B that employs the electric linear actuator A. In this electric disc brake device, a caliper body portion 40 is integrally provided at the other end portion of the housing 1 in the electric linear motion actuator, and a brake disc 41 in which a part of the outer peripheral portion is disposed in the caliper body portion 40. A fixed brake pad 42 and a movable brake pad 43 are provided on both sides of the outer ring member 5, and the movable brake pad 43 is connected and integrated with the other end of the outer ring member 5.

図２１に示すような電動式ディスクブレーキ装置Ｂへの電動式直動アクチュエータＡの使用状態において、図１に示す電動モータ１１の駆動により回転軸１０が回転すると、遊星ローラ２１が回転軸１０との摩擦接触により自転しつつ公転する。   When the electric linear actuator A is used for the electric disc brake device B as shown in FIG. 21, when the rotating shaft 10 is rotated by driving the electric motor 11 shown in FIG. Revolves while rotating by frictional contact.

この時、遊星ローラ２１の外径面には螺旋溝２３が形成され、その螺旋溝２３に外輪部材５の内径面に設けられた螺旋突条６が係合しているため、遊星ローラ２１の自転および公転により外輪部材５が軸方向に移動し、可動ブレーキパッド４３がブレーキディスク４１に押し付けられ、ブレーキディスク４１に制動力が付与される。   At this time, a spiral groove 23 is formed on the outer diameter surface of the planetary roller 21, and the spiral protrusion 6 provided on the inner diameter surface of the outer ring member 5 is engaged with the spiral groove 23. The outer ring member 5 moves in the axial direction by rotation and revolution, and the movable brake pad 43 is pressed against the brake disc 41, and a braking force is applied to the brake disc 41.

上記のような制動力の付与時、外輪部材５から遊星ローラ２１に軸方向荷重が負荷される。その軸方向荷重の入力部位は、外輪部材５の内径面に設けられた螺旋突条６と遊星ローラ２１の外径面に形成された螺旋溝２３の係合部であるため、遊星ローラ２１には偏荷重が負荷されることになる。   When the braking force is applied as described above, an axial load is applied from the outer ring member 5 to the planetary roller 21. The input portion of the axial load is an engaging portion of the spiral protrusion 6 provided on the inner diameter surface of the outer ring member 5 and the spiral groove 23 formed on the outer diameter surface of the planetary roller 21. An unbalanced load is applied.

このとき、遊星ローラ２１とキャリア１４のインナ側ディスク１４ａ間には加圧座板２５と受圧座板２６が組み込まれ、その両座板２５、２６の対向面に調心座２７が設けられているため、上記のように、遊星ローラ２１に偏荷重が負荷されると、加圧座板２５の凸形球面２７ａが受圧座板２６の凹面２７ｂに接触案内される状態で加圧座板２５が傾動し、凸形球面２７ａと凹面２７ｂの接触部で周方向の面圧分布の均一化が図られることになる。   At this time, a pressure seat plate 25 and a pressure-receiving seat plate 26 are incorporated between the planetary roller 21 and the inner disk 14 a of the carrier 14, and a centering seat 27 is provided on the opposing surface of the both seat plates 25, 26. Therefore, as described above, when an eccentric load is applied to the planetary roller 21, the pressure seat 25 is tilted in a state where the convex spherical surface 27 a of the pressure seat 25 is brought into contact with the concave surface 27 b of the pressure receiving seat 26. Thus, the surface pressure distribution in the circumferential direction is made uniform at the contact portion between the convex spherical surface 27a and the concave surface 27b.

このため、受圧部としてのスラスト軸受２４には、周方向の全体にわたって同じ大きさの軸方向荷重が負荷されることになり、軌道輪２４ａや転動体２４ｂが偏摩耗するという不都合の発生はなく、スラスト軸受２４の耐久性の低下が抑制される。 For this reason, the axial bearing of the same magnitude | size will be loaded to the thrust bearing 24 as a pressure receiving part over the whole circumferential direction, and there will be no inconvenience that the track ring 24a and the rolling element 24b are worn unevenly. Further, a decrease in the durability of the thrust bearing 24 is suppressed.

図６は、この発明に係る電動式直動アクチュエータの第２の実施の形態を示す。この実施の形態では、遊星ローラ２１とスラスト軸受２４間に加圧座板２５と受圧座板２６とを組み込んでいる点で第１の実施の形態と相違する。このため、第１の実施の形態と同一の部品には同一の符号を付して説明を省略する。   FIG. 6 shows a second embodiment of the electric linear actuator according to the present invention. This embodiment is different from the first embodiment in that a pressure seat plate 25 and a pressure receiving seat plate 26 are incorporated between the planetary roller 21 and the thrust bearing 24. For this reason, the same components as those in the first embodiment are denoted by the same reference numerals and description thereof is omitted.

図６では、加圧座板２５に凸形球面２７ａを設け、受圧座板２６に凹面２７ｂを設けたが、図７に示す第３の実施の形態のように、加圧座板２５に凹面２７ｂを設け、受圧座板２６に凸形球面２７ａを形成するようにしてもよい。   In FIG. 6, the convex spherical surface 27a is provided on the pressure seat plate 25 and the concave surface 27b is provided on the pressure receiving seat plate 26. However, the concave surface 27b is provided on the pressure seat plate 25 as in the third embodiment shown in FIG. A convex spherical surface 27 a may be formed on the pressure receiving seat plate 26.

図６に示す第２の実施の形態および図７に示す第３の実施の形態において、受圧座板２６にスラスト軸受２４の転動体２４ｂの転動を案内する軌道面を形成して、軌道輪２４ａを省略してもよい。   In the second embodiment shown in FIG. 6 and the third embodiment shown in FIG. 7, a raceway surface that guides the rolling of the rolling elements 24 b of the thrust bearing 24 is formed on the pressure receiving seat plate 26, thereby 24a may be omitted.

図８は、この発明に係る電動式直動アクチュエータの第４の実施の形態を示す。この実施の形態では、加圧座板２５に凹形球面からなる凹面２７ｂを設け、受圧座板２６には凸形球面２７ａを設けた点で第１の実施の形態と相違する。このため、第１の実施の形態と同一の部品には同一の符号を付して説明を省略する。   FIG. 8 shows a fourth embodiment of the electric linear actuator according to the present invention. This embodiment is different from the first embodiment in that a concave surface 27b made of a concave spherical surface is provided on the pressure seat plate 25, and a convex spherical surface 27a is provided on the pressure receiving seat plate 26. For this reason, the same components as those in the first embodiment are denoted by the same reference numerals and description thereof is omitted.

第２乃至第４のいずれの実施の形態に示す電動式直動アクチュエータにおいても、外輪部材５から遊星ローラ２１に負荷される偏荷重により加圧座板２５が傾動し、その傾動による調心作用によってスラスト軸受２４の周方向の面圧分布の均一化が図られる。   In the electric linear actuator shown in any of the second to fourth embodiments, the pressure seat plate 25 is tilted by the biased load applied to the planetary roller 21 from the outer ring member 5, and by the aligning action by the tilting. The surface pressure distribution in the circumferential direction of the thrust bearing 24 is made uniform.

なお、図８において、凹面２７ｂが形成された加圧座板２５にスラスト軸受２４の転動体２４ｂを案内する軌道面を設けることにより、同図に示す軌道輪２４ａを省略することができる。   In FIG. 8, the raceway 24a shown in the figure can be omitted by providing a raceway surface for guiding the rolling element 24b of the thrust bearing 24 on the pressure seat plate 25 having the concave surface 27b.

図９は、この発明に係る電動式直動アクチュエータの第５の実施の形態を示す。この実施の形態では、スラスト軸受２４の軌道輪２４ａとキャリア１４のインナ側ディスク１４ａ間に受圧座板２６を組込み、上記軌道輪２４ａに凸形球面２７ａを設け、受圧座板２６には凹形球面からなる凹面２７ｂを形成して、その凹面２７ｂと凸形球面２７ａとで調心座２７を形成している。   FIG. 9 shows a fifth embodiment of the electric linear actuator according to the present invention. In this embodiment, a pressure receiving seat plate 26 is assembled between the raceway ring 24a of the thrust bearing 24 and the inner disk 14a of the carrier 14, and the raceway ring 24a is provided with a convex spherical surface 27a, and the pressure receiving seat plate 26 has a concave shape. A concave surface 27b made of a spherical surface is formed, and the aligning seat 27 is formed by the concave surface 27b and the convex spherical surface 27a.

上記のように、軌道輪２４ａと受圧座板２６との対向面に調心座２７を形成することにより、図２に示す加圧座板２５を省略することができるため、部品点数の低減によって、組立ての容易化と電動式直動アクチュエータの軸方向長さのコンパクト化を図ることができる。   As described above, by forming the aligning seat 27 on the facing surface of the raceway ring 24a and the pressure receiving seat plate 26, the pressurizing seat plate 25 shown in FIG. 2 can be omitted. The assembly can be facilitated and the axial length of the electric linear actuator can be made compact.

図１０は、この発明に係る電動式直動アクチュエータの第６の実施の形態を示す。この実施の形態では、スラスト軸受２４とキャリア１４のインナ側ディスク１４ａとの間に加圧座板２５を組込み、その加圧座板２５に凹形球面からなる凹面２７ｂを形成し、上記インナ側ディスク１４ａには加圧座板２５と対向する位置に凸形球面２７ａを設けて、その凸形球面２７ａと凹面２７ｂとで調心座２７を形成している。   FIG. 10 shows a sixth embodiment of the electric linear actuator according to the present invention. In this embodiment, a pressure seat plate 25 is assembled between the thrust bearing 24 and the inner side disk 14a of the carrier 14, and a concave surface 27b made of a concave spherical surface is formed on the pressure seat plate 25, and the inner side disk 14a. The convex spherical surface 27a is provided at a position facing the pressure seat plate 25, and the convex spherical surface 27a and the concave surface 27b form the aligning seat 27.

上記のように、加圧座板２５とキャリア１４のインナ側ディスク１４ａとの対向面に調心座２７を形成することにより、図８に示す受圧座板２６を省略することができるため、部品点数の低減によって組立ての容易化と電動式直動アクチュエータの軸方向長さのコンパクト化を図ることができる。   As described above, the pressure receiving seat plate 26 shown in FIG. 8 can be omitted by forming the aligning seat 27 on the opposing surface of the pressure seat plate 25 and the inner disk 14a of the carrier 14, so that the number of parts is reduced. As a result of this reduction, the assembly can be facilitated and the axial length of the electric linear actuator can be made compact.

図１０では、加圧座板２５に凹面２７ｂを形成し、インナ側ディスク１４ａに凸形球面２７ａを設けたが、図１１に示す第７の実施の形態のように、加圧座板２５に凸形球面２７ａを設け、インナ側ディスク１４ａに凹面２７ｂを形成してもよい。   In FIG. 10, the concave surface 27b is formed on the pressure seat plate 25 and the convex spherical surface 27a is provided on the inner disk 14a. However, the convex shape is formed on the pressure seat plate 25 as in the seventh embodiment shown in FIG. A spherical surface 27a may be provided, and a concave surface 27b may be formed on the inner disk 14a.

図１０および図１１に示す実施の形態において、加圧座板２５にスラスト軸受２４の転動体２４ｂの転動を案内する軌道面を設けることにより、図１０および図１１のそれぞれに示す軌道輪２４ａを省略することができる。   In the embodiment shown in FIGS. 10 and 11, by providing a raceway surface for guiding the rolling of the rolling element 24b of the thrust bearing 24 on the pressure seat plate 25, the raceway ring 24a shown in each of FIGS. Can be omitted.

図１２は、この発明に係る電動式直動アクチュエータの第８の実施の形態を示す。この実施の形態では、遊星ローラ２１とスラスト軸受２４間に受圧座板２６を組込み、その受圧座板２６の遊星ローラ２１と対向する面に凹形球面からなる凹面２７ｂを形成し、遊星ローラ２１には受圧座板２６と対向する面に凸形球面２７ａを形成して、その凸形球面２７ａと凹面２７ｂとで調心座２７を形成している。   FIG. 12 shows an eighth embodiment of the electric linear actuator according to the present invention. In this embodiment, a pressure receiving seat plate 26 is incorporated between the planetary roller 21 and the thrust bearing 24, and a concave surface 27 b made of a concave spherical surface is formed on the surface of the pressure receiving seat plate 26 facing the planetary roller 21. The convex spherical surface 27a is formed on the surface facing the pressure receiving seat plate 26, and the aligning seat 27 is formed by the convex spherical surface 27a and the concave surface 27b.

上記のように、遊星ローラ２１と受圧座板２６の対向面間に調心座２７を設けることにより、図６に示す加圧座板２５を省略することができるため、部品点数の低減によって組立ての容易化と電動式直動アクチュエータの軸方向長さのコンパクト化を図ることができる。   As described above, by providing the aligning seat 27 between the opposed surfaces of the planetary roller 21 and the pressure receiving seat plate 26, the pressurizing seat plate 25 shown in FIG. 6 can be omitted. Simplification and reduction in the axial length of the electric linear actuator can be achieved.

図１２に示す第８の実施の形態では、遊星ローラ２１に凸形球面２７ａを形成し、受圧座板２６に凹面２７ｂを設けたが、図１３に示す第９の実施の形態のように、遊星ローラ２１に凹面２７ｂを設け、受圧座板２６に凸形球面２７ａを形成してもよい。この場合、受圧座板２６にスラスト軸受２４の転動体２４ｂの転動を案内する軌道面を設けることにより、同図に示す軌道輪２４ａを省略することができる。   In the eighth embodiment shown in FIG. 12, the convex spherical surface 27a is formed on the planetary roller 21, and the concave surface 27b is provided on the pressure receiving seat plate 26. However, as in the ninth embodiment shown in FIG. The planetary roller 21 may be provided with a concave surface 27b, and the pressure receiving seat plate 26 may be formed with a convex spherical surface 27a. In this case, by providing the pressure receiving seat plate 26 with a raceway surface that guides the rolling of the rolling elements 24b of the thrust bearing 24, the raceway ring 24a shown in the figure can be omitted.

図５(ａ)に示す受圧座板２６のように、凹面２７ｂが凹形球面からなる場合において、その凹形球面からなる凹面２７ｂの曲率半径を図４に示す凸形球面２７ａの曲率半径と同一値以上とすることにより、受圧座板２６の軸方向厚さを薄くすることができ、電動式直動アクチュエータの軸方向長さのコンパクト化を図ることができる。   When the concave surface 27b is formed of a concave spherical surface as in the pressure receiving seat plate 26 shown in FIG. 5A, the radius of curvature of the concave surface 27b made of the concave spherical surface is set to the curvature radius of the convex spherical surface 27a shown in FIG. By setting it to the same value or more, the axial thickness of the pressure receiving seat plate 26 can be reduced, and the axial length of the electric linear actuator can be made compact.

また、図５(ｂ)に示す受圧座板２６のように、凹面２７ｂがテーパ面からなる場合に、そのテーパ面からなる凹面２７ｂのテーパ角θを鈍角とすることで、上記と同様に、受圧座板２６の軸方向厚さを薄くすることができ、電動式直動アクチュエータの軸方向長さのコンパクト化を図ることができる。   Further, as in the pressure receiving seat plate 26 shown in FIG. 5B, when the concave surface 27b is a tapered surface, the taper angle θ of the concave surface 27b made of the tapered surface is made obtuse, similarly to the above. The axial thickness of the pressure receiving seat plate 26 can be reduced, and the axial length of the electric linear actuator can be reduced.

図１４(ｃ)、(ｄ)は、調心座２７を形成する凸形球面２７ａに放射状の溝３５を設けた例を示す。また、図１５(ｅ)、(ｆ)は、調心座２７を形成する凹面２７ｂに螺旋状の溝３５を設けた例を示す。上記のように、調心座２７を形成する凸形球面２７ａや凹面２７ｂに溝３５を設けると、その溝３５で潤滑油やグリースといった油脂からなる潤滑剤を保持することができるため、凸形球面２７ａと凹面２７ｂの接触部における摺動性の向上を図ることができ、摩耗や焼付きの防止に効果を挙げることができる。   14C and 14D show an example in which a radial groove 35 is provided on a convex spherical surface 27a that forms the aligning seat 27. FIG. FIGS. 15E and 15F show an example in which a spiral groove 35 is provided on the concave surface 27 b forming the aligning seat 27. As described above, when the groove 35 is provided in the convex spherical surface 27a and the concave surface 27b forming the aligning seat 27, the groove 35 can hold a lubricant made of oil and fat such as lubricating oil or grease. The slidability at the contact portion between the spherical surface 27a and the concave surface 27b can be improved, and an effect can be obtained in preventing wear and seizure.

なお、溝３５に代えて、図１６(ｇ)、(ｈ)に示すように、調心座２７を形成する凸形球面２７ａや凹面２７ｂに各々が独立した無数の微細な凹部３６をランダムに形成し、その凹部３６で油脂を保持するようにしてもよい。また、凸形球面２７ａや凹面２７ｂに固体潤滑被膜を形成して、凸形球面２７ａと凹面２７ｂの接触部を潤滑するようにしてもよい。   Instead of the grooves 35, as shown in FIGS. 16 (g) and 16 (h), innumerable fine recesses 36 that are independent of each other on the convex spherical surface 27a and the concave surface 27b forming the aligning seat 27 are randomly formed. It is also possible to form and hold the fats and oils in the recesses 36. Alternatively, a solid lubricating film may be formed on the convex spherical surface 27a or the concave surface 27b to lubricate the contact portion between the convex spherical surface 27a and the concave surface 27b.

図１７は、この発明に係る電動式直動アクチュエータの第１０の実施の形態を示す。この実施の形態では、遊星ローラ２１とスラスト軸受２４との間に凸形球面２７ａを有する加圧座板２５と凹形球面からなる凹面２７ｂを有する受圧座板２６とが組込まれ、その加圧座板２５に形成された軸部２５ｂが遊星ローラ２１の端面に形成された軸挿入孔２１ａ内に圧入されて遊星ローラ２１とともに加圧座板２５が回転するようになっている。   FIG. 17 shows a tenth embodiment of the electric linear actuator according to the present invention. In this embodiment, a pressure seat plate 25 having a convex spherical surface 27a and a pressure receiving seat plate 26 having a concave surface 27b made of a concave spherical surface are incorporated between the planetary roller 21 and the thrust bearing 24, and the pressure seat plate. The shaft portion 25 b formed in the shaft 25 is press-fitted into a shaft insertion hole 21 a formed in the end face of the planetary roller 21, so that the pressure seat plate 25 rotates together with the planetary roller 21.

また、受圧座板２６に形成された軸部２６ｂがスラスト軸受２４およびキャリア１４のインナ側ディスク１４ａによって回転自在に支持されている。   Further, a shaft portion 26 b formed on the pressure receiving seat plate 26 is rotatably supported by the thrust bearing 24 and the inner disk 14 a of the carrier 14.

さらに、インナ側ディスク１４ａと軸受部材７のボス部７ａ間にはばねホルダ５１が組み込まれ、そのばねホルダ５１の凹部５２内に組み込まれた弾性部材５０はキャリア１４を外方に向けて付勢し、アウタ側ディスク１４ｂのテーパ孔１４ｃが回転軸１０の軸端部に形成されたテーパ面１０ａに押し付けられている。   Further, a spring holder 51 is incorporated between the inner disk 14a and the boss 7a of the bearing member 7, and the elastic member 50 incorporated in the recess 52 of the spring holder 51 urges the carrier 14 outward. The tapered hole 14c of the outer disk 14b is pressed against the tapered surface 10a formed at the shaft end of the rotating shaft 10.

ここで、凹面２７ｂの曲率半径は凸形球面２７ａの曲率半径よりもわずかに大きくされている。また、ばねホルダ５１と軸受部材７間にはスラスト軸受３１と間座５３とが組み込まれている。   Here, the radius of curvature of the concave surface 27b is slightly larger than the radius of curvature of the convex spherical surface 27a. A thrust bearing 31 and a spacer 53 are incorporated between the spring holder 51 and the bearing member 7.

上記の実施の形態では、図１に示すローラ軸１９を不要としている。その実施の形態で示す電動式直動アクチュエータにおいては、外輪部材５から遊星ローラ２１に偏荷重が負荷されると、凹面２７ｂの曲率半径が凸形球面２７ａの曲率半径より大きいため、その荷重は受圧座板２６の凹面２７ｂの曲率中心に一旦集中し、同軸上に配置されたスラスト軸受２４には、この集中荷重が各転動体２４ｂおよびその転動体２４ｂを案内する軌道輪２４ａに均等に分散されて負荷されることになる。   In the above embodiment, the roller shaft 19 shown in FIG. 1 is unnecessary. In the electric linear actuator shown in the embodiment, when an eccentric load is applied from the outer ring member 5 to the planetary roller 21, the radius of curvature of the concave surface 27b is larger than the radius of curvature of the convex spherical surface 27a. In the thrust bearing 24 once concentrated on the center of curvature of the concave surface 27b of the pressure receiving seat plate 26, this concentrated load is evenly distributed to each rolling element 24b and the raceway ring 24a guiding the rolling element 24b. Will be loaded.

第１０の実施の形態では、凹面２７ｂの曲率半径は凸形球面２７ａの曲率半径よりもわずかに大きくしているが、同一の大きさであってもよい。この場合、凸形球面２７ａと凹面２７ｂの球面接触によって転動体２４ｂおよび軌道輪２４ａに均等な荷重が負荷されるようになる。   In the tenth embodiment, the radius of curvature of the concave surface 27b is slightly larger than the radius of curvature of the convex spherical surface 27a, but may be the same size. In this case, an equal load is applied to the rolling element 24b and the raceway ring 24a by the spherical contact between the convex spherical surface 27a and the concave surface 27b.

第１０の実施の形態では、軸部２５ｂを有する加圧座板２５に凸形球面２７ａを形成し、軸部２６ｂを有する受圧座板２６に凹面２７ｂを設けたが、図１８に示す第１１の実施の形態のように、加圧座板２５に凹面２７ｂを設け、受圧座板２６に凸形球面２７ａを形成してもよい。   In the tenth embodiment, the convex spherical surface 27a is formed on the pressure seat plate 25 having the shaft portion 25b, and the concave surface 27b is provided on the pressure receiving seat plate 26 having the shaft portion 26b. However, the eleventh embodiment shown in FIG. As in the embodiment, the pressurizing seat plate 25 may be provided with the concave surface 27b, and the pressure receiving seat plate 26 may be formed with the convex spherical surface 27a.

また、第１０の実施の形態では、遊星ローラ２１に加圧座板２５を取付け、その加圧座板２５に凸形球面２７ａを形成したが、図１９に示す第１２の実施の形態のように、遊星ローラ２１の端面に凸形球面２７を直接形成して、加圧座板２５を省略してもよい。   Further, in the tenth embodiment, the pressure seat plate 25 is attached to the planetary roller 21 and the convex spherical surface 27a is formed on the pressure seat plate 25. However, as in the twelfth embodiment shown in FIG. The convex spherical surface 27 may be formed directly on the end surface of the planetary roller 21 and the pressure seat plate 25 may be omitted.

さらに、第１０の実施の形態では、遊星ローラ２１とスラスト軸受２４間に加圧座板２５を組込み、その加圧座板２５に形成された凸形球面２７ａを受圧座板２６に形成された凹面２７ｂに接触させるようにしたが、図２０に示す第１３の実施の形態のように、スラスト軸受２４とキャリア１４のインナ側ディスク１４ａ間に加圧座板２５を組込み、その加圧座板２５に形成された凸形球面２７ａをインナ側ディスク１４ａに形成された凹形球面からなる凹面２７ｂに接触させるようにしてもよい。   Furthermore, in the tenth embodiment, a pressure seat plate 25 is incorporated between the planetary roller 21 and the thrust bearing 24, and a convex spherical surface 27a formed on the pressure seat plate 25 is formed into a concave surface 27b formed on the pressure receiving seat plate 26. The pressure seat plate 25 is assembled between the thrust bearing 24 and the inner disk 14a of the carrier 14 and is formed on the pressure seat plate 25 as in the thirteenth embodiment shown in FIG. The convex spherical surface 27a may be brought into contact with a concave surface 27b formed of a concave spherical surface formed on the inner disk 14a.

なお、図２０に示す第１３の実施の形態では、加圧座板２５に設けられた軸部２５ｂを遊星ローラ２１によって回転自在に支持している。   In the thirteenth embodiment shown in FIG. 20, the shaft portion 25 b provided on the pressure seat plate 25 is rotatably supported by the planetary roller 21.

第１の実施の形態乃至第９の実施の形態においては、凸形球面２７ａが形成された加圧座板２５等の部材や凹形球面等の凹面２７ｂが形成された受圧座板２６等の部材を入手の容易な加工性の良好な鉄鋼材料や焼結材料で形成している。この場合、必要に応じて、熱処理やめっき処理という表面処理を施して強度、摺動性、耐摩耗性を向上させ、寿命の延長や信頼性の向上を図るようにしてもよい。   In the first embodiment to the ninth embodiment, a member such as a pressure seat plate 25 formed with a convex spherical surface 27a or a member such as a pressure receiving seat plate 26 formed with a concave surface 27b such as a concave spherical surface. It is made of steel materials and sintered materials that are easily available and have good workability. In this case, if necessary, surface treatment such as heat treatment or plating treatment may be performed to improve strength, slidability, and wear resistance, thereby extending life and improving reliability.

１ ハウジング
５ 外輪部材（被駆動部材）
１１ 電動モータ
２４ スラスト軸受（受圧部）
２５ 加圧座板（調心機構）
２６ 受圧座板（調心機構）
２７ 調心座（調心機構）
４０ キャリパボディ
４１ ブレーキディスク
４２ 固定ブレーキパッド
４３ 可動ブレーキパッド 1 Housing 5 Outer ring member (driven member)
11 Electric motor 24 Thrust bearing (pressure receiving part)
25 Pressure seat (alignment mechanism)
26 Pressure-receiving seat plate (alignment mechanism)
27 aligning seat (alignment mechanism)
40 caliper body 41 brake disc 42 fixed brake pad 43 movable brake pad

Claims (1)

ハウジングと、
前記ハウジングに支持された電動モータと、
前記ハウジング内に組み込まれた軸方向に移動可能な被駆動部材と、
前記電動モータのロータ軸の回転運動を前記被駆動部材の軸方向への直線運動に変換す
る運動変換機構と、を有し、
前記運動変換機構は、
前記電動モータによって回転駆動される回転軸と、
前記回転軸の外径面と前記被駆動部材の内径面間に組み込まれた遊星ローラと、
前記遊星ローラを前記回転軸を中心にして回転自在に支持するキャリアと、を備え、
前記回転軸の回転により、その回転軸との摩擦接触で前記遊星ローラを自転および公転させることで前記被駆動部材を軸方向に直線移動するものであり、
前記ハウジングに一体に設けられたキャリパボディ内にブレーキディスクの外周の一部
を配置し、そのブレーキディスクの両側に固定ブレーキパッドと可動ブレーキパッドとを
設け、前記可動ブレーキパッドを前記被駆動部材でブレーキディスクに押し付けて制動力
を付与し、可動ブレーキパッドからの軸方向荷重を、前記運動変換機構の遊星ローラとキャリアのインナ側ディスクとの間に組み込まれたスラスト軸受からなる受圧部で受けるようした電動式ディスクブレーキ装置において、
前記可動ブレーキパッドから前記被駆動部材および前記運動変換機構の遊星ローラを介して前記受圧部に負荷される偏荷重を伴なう軸方向荷重の、前記受圧部での周方向の面圧分布の均一化を図る調心機構を、前記被駆動部材の内側であって、前記遊星ローラと前記受圧部との間、または前記受圧部と前記キャリアのインナ側ディスクとの間に設けたことを特徴とする電動式ディスクブレーキ装置。
A housing;
An electric motor supported by the housing;
An axially movable driven member incorporated in the housing;
A motion conversion mechanism that converts the rotational motion of the rotor shaft of the electric motor into a linear motion in the axial direction of the driven member;
The motion conversion mechanism is
A rotating shaft that is rotationally driven by the electric motor;
A planetary roller incorporated between an outer diameter surface of the rotating shaft and an inner diameter surface of the driven member;
A carrier that rotatably supports the planetary roller about the rotation axis;
The driven member is linearly moved in the axial direction by rotating and revolving the planetary roller by frictional contact with the rotating shaft by the rotation of the rotating shaft,
A part of the outer periphery of the brake disc is disposed in a caliper body provided integrally with the housing, a fixed brake pad and a movable brake pad are provided on both sides of the brake disc, and the movable brake pad is attached to the driven member. A braking force is applied by pressing against the brake disc so that the axial load from the movable brake pad is received by a pressure receiving portion comprising a thrust bearing built in between the planetary roller of the motion conversion mechanism and the inner disc of the carrier. In the electric disc brake device
The distribution of the surface pressure distribution in the circumferential direction at the pressure receiving portion of the axial load accompanied by the uneven load applied to the pressure receiving portion from the movable brake pad via the driven member and the planetary roller of the motion conversion mechanism . the aim aligning mechanism homogenization, the an inner driven member, characterized in that provided between the between the planetary roller and the pressure receiving portion or the inner side disk of the carrier and the pressure receiving portion, Electric disc brake device.
JP2014160412A 2014-08-06 2014-08-06 Electric disc brake device Expired - Fee Related JP6109121B2 (en)

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