JP2816408B2 - Power steering device - Google Patents
Power steering deviceInfo
- Publication number
- JP2816408B2 JP2816408B2 JP7798690A JP7798690A JP2816408B2 JP 2816408 B2 JP2816408 B2 JP 2816408B2 JP 7798690 A JP7798690 A JP 7798690A JP 7798690 A JP7798690 A JP 7798690A JP 2816408 B2 JP2816408 B2 JP 2816408B2
- Authority
- JP
- Japan
- Prior art keywords
- transmission shaft
- steering
- shaft
- electromagnetic clutch
- output shaft
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
Links
Landscapes
- Power Steering Mechanism (AREA)
Description
【発明の詳細な説明】 〔産業上の利用分野〕 本発明は電動モータを操舵補助力の発生源とする電動
式の動力舵取装置に関し、更に詳述すれば、前記モータ
から舵取機構への伝動系の中途にクラッチを設けてなる
動力舵取装置に関する。Description: BACKGROUND OF THE INVENTION The present invention relates to an electric power steering apparatus using an electric motor as a source of a steering assist force, and more specifically, from an electric motor to a steering mechanism. The present invention relates to a power steering device provided with a clutch in the middle of a transmission system.
近年、操舵補助力の発生源として電動モータを用いる
電動式の動力舵取装置が実用化されている。これは、舵
取機構の中途に配された操舵補助用のモータを操舵トル
クの検出結果に基づいて駆動し、該モータの回転力にて
舵取機構の動作を補助することにより、舵取りのための
舵輪操作に要する労力負担を軽減するものである。2. Description of the Related Art In recent years, an electric power steering apparatus using an electric motor as a source of a steering assist force has been put to practical use. This is because the steering assist motor arranged in the middle of the steering mechanism is driven based on the detection result of the steering torque, and the operation of the steering mechanism is assisted by the rotational force of the motor, so that steering is performed. It is intended to reduce the labor burden required for steering operation of the vehicle.
この電動式の動力舵取装置は、操舵補助力の発生源と
して油圧アクチュエータを用いる油圧式の動力舵取装置
と比較した場合、前記モータの回転制御により特性変更
を容易に行い得ることから、車速の高低,操舵の頻度
等、走行状態に対応する適正な特性の実現が可能である
という利点を有している反面、操舵補助のための十分な
回転力を発生でき、しかも小型のモータが得難いこと、
モータの回転部分の慣性が舵取り動作に影響を及ぼすこ
と等の難点がある。そこで従来から、モータの出力軸と
舵取機構への伝動軸との間に適宜の減速装置を配し、該
減速装置の増力作用により前者の難点の解消が図られて
おり、また、モータの出力軸と舵取機構へ連なる伝動軸
との間に電磁クラッチを配し、この電磁クラッチの動作
により、前記両軸を所要時にのみ係合せしめる構成とし
て、後者の難点の解消が図られている。この電磁クラッ
チは、前記出力軸及び前記伝動軸の夫々と連動回転する
摩擦板と、出力軸側の摩擦板の背部に固設された駆動コ
イルと、伝動軸側の摩擦板の背部に配されたアーマチュ
ア部とを備えてなり、駆動コイルの励磁に伴うアーマチ
ュア部の動作により、前記摩擦板を相互に押付けて両軸
を係合する一方、駆動コイルの消磁に伴うアーマチュア
部の動作により、前記押付けを解除して両軸間の係合を
遮断するものであり、従来、一方の摩擦板及びこれの保
持体を同軸的に嵌着してなる前記出力軸と、他方の摩擦
板を一体化させた前記アーマチュア部を同軸的に嵌着し
てなる前記伝動軸とを、同軸上にて各別に支承し、夫々
の前記装着側端部を適宜の間隙を隔てて突き合わせて構
成されている。また前記減速装置としては、モータの出
力軸及び舵取機構への伝動軸と同軸的に構成でき、小型
化が容易なことから、遊星歯車減速装置又は遊星ローラ
減速装置が用いられており、これは前記電磁クラッチの
一側に並設されている。When compared with a hydraulic power steering device that uses a hydraulic actuator as a source of steering assist force, the electric power steering device can easily change the characteristics by controlling the rotation of the motor. It has the advantage of being able to realize appropriate characteristics corresponding to the driving conditions, such as the level of steering and the frequency of steering, but can generate sufficient rotational force for steering assistance, and it is difficult to obtain a small motor. thing,
There are difficulties such as that the inertia of the rotating part of the motor affects the steering operation. Therefore, conventionally, an appropriate reduction gear has been arranged between the output shaft of the motor and the transmission shaft to the steering mechanism, and the former difficulty has been solved by the boosting action of the reduction gear. An electromagnetic clutch is arranged between the output shaft and the transmission shaft connected to the steering mechanism, and the operation of the electromagnetic clutch causes the two shafts to be engaged only when necessary, thereby solving the latter difficulty. . The electromagnetic clutch is arranged on a friction plate that rotates in conjunction with each of the output shaft and the transmission shaft, a drive coil fixed to the back of the friction plate on the output shaft side, and a back of the friction plate on the transmission shaft side. The armature part is operated by the excitation of the drive coil, and the friction plates are pressed against each other to engage the two shafts, while the operation of the armature part caused by the demagnetization of the drive coil is performed by the operation of the armature part. This is to release the pressing to interrupt the engagement between the two shafts. Conventionally, the output shaft formed by coaxially fitting one friction plate and its holding body and the other friction plate are integrated. The power transmission shaft formed by coaxially fitting the armature portion thus mounted is separately supported coaxially, and the respective mounting-side ends are abutted with an appropriate gap therebetween. As the reduction gear, a planetary gear reduction gear or a planetary roller reduction gear is used because it can be configured coaxially with an output shaft of a motor and a transmission shaft to a steering mechanism, and can be easily miniaturized. Are arranged side by side on one side of the electromagnetic clutch.
ところが、このように構成された従来の動力舵取装置
においては、電磁クラッチの両摩擦板間に所定の初期間
隙を確保するためには、両軸の支承部、及び両軸と保持
体又はアーマチュア部との嵌合部に極めて高精度の加工
が要求される。またアーマチュア部及び保持体が片持ち
支持状態にあって、これらに保持された摩擦板の傾倒が
避けられず、両摩擦板間に周方向に均一な初期間隙を確
保するためには、組立て時に繁雑なギャップ調整作業が
要求されて、組立てに多大の時間を要するという難点が
ある。更に、加工及び組立てに十分な注意を払ったとし
ても、初期間隙の設定不良を完全に防止することはかな
り困難であり、初期間隙が過大であった場合、係合時に
摩擦板間に滑りが生じて舵取機構への伝動が阻害され、
逆に初期間隙が過小であった場合、遮断時に摩擦板間の
摺接に伴う耳障りな異音が発生する等の動作上の不都合
が生じていた。However, in the conventional power steering apparatus configured as described above, in order to secure a predetermined initial gap between the friction plates of the electromagnetic clutch, the support portions of both shafts, and both shafts and the holding body or the armature are required. Very high precision processing is required for the fitting part with the part. Also, since the armature and the holder are in a cantilevered support state, the tilting of the friction plates held by them is unavoidable, and to ensure a uniform initial gap in the circumferential direction between both friction plates, There is a problem that a complicated gap adjustment operation is required and a large amount of time is required for assembly. Furthermore, even if sufficient attention is paid to machining and assembly, it is quite difficult to completely prevent the initial gap from being set incorrectly.If the initial gap is too large, slippage occurs between the friction plates during engagement. And transmission to the steering mechanism is obstructed,
Conversely, if the initial gap is too small, there is an inconvenience in operation, such as generation of an unpleasant noise due to sliding contact between the friction plates at the time of interruption.
またモータの出力軸と舵取機構への伝動軸との間に前
述した如き減速装置が構成されている場合、該減速装置
の動作時に、これの転動部位に塗布された潤滑剤(グリ
ース)が電磁クラッチ側に飛散し、該電磁クラッチの両
摩擦板に付着して、両摩擦板の押付けにより行われる電
磁クラッチの係合動作が阻害されるという難点が生じて
いた。In the case where the above-described speed reducer is configured between the output shaft of the motor and the transmission shaft to the steering mechanism, a lubricant (grease) applied to a rolling portion of the speed reducer when the speed reducer operates. Has scattered to the electromagnetic clutch side, adhered to both friction plates of the electromagnetic clutch, and the engaging operation of the electromagnetic clutch performed by pressing both friction plates has been disadvantageously hindered.
本発明は斯かる事情に鑑みてなされたものであり、操
舵補助用のモータと舵取機構への伝動軸との間に構成さ
れる電磁クラッチの加工及び組立てに際しての煩わしさ
を解消し、しかも該電磁クラッチの摩擦板間に所定の初
期間隙を確実に実現できると共に、前記モータと伝動軸
との間に構成された減速装置から前記電磁クラッチへの
潤滑剤の飛散を有効に阻止でき、電磁クラッチの係合動
作に支障を来すことのない動力舵取装置を提供すること
を目的とする。The present invention has been made in view of such circumstances, and eliminates the inconvenience in processing and assembling an electromagnetic clutch configured between a steering assist motor and a transmission shaft to a steering mechanism. A predetermined initial gap can be reliably realized between the friction plates of the electromagnetic clutch, and the scattering of the lubricant from the speed reducer formed between the motor and the transmission shaft to the electromagnetic clutch can be effectively prevented. An object of the present invention is to provide a power steering device that does not hinder the engagement operation of a clutch.
本発明に係る動力舵取装置は、操舵トルクの検出結果
に基づいて駆動される操舵補助用モータの出力軸と、舵
取機構への伝動軸との間に、その駆動コイルの励磁,消
磁に伴うアーマチュア部の動作により前記両軸を係断す
る電磁クラッチを備えた動力舵取装置において、前記出
力軸と前記伝動軸との間に両持ち支持され、前記アーマ
チュア部を支承する中間伝動軸、該中間伝動軸を軸長方
向に付勢して、前記出力軸側の支持部位に押付ける付勢
手段とを具備することを特徴とし、更に前記中間伝動軸
上に構成された減速装置と前記電磁クラッチとの間に、
両者を前記中間伝動軸の貫通部分を残して遮蔽する遮蔽
部材を具備することを特徴とする。A power steering device according to the present invention is configured to excite and demagnetize a drive coil between an output shaft of a steering assist motor driven based on a detection result of a steering torque and a transmission shaft to a steering mechanism. In a power steering apparatus provided with an electromagnetic clutch for engaging the two shafts by the operation of the accompanying armature portion, an intermediate transmission shaft supported at both ends between the output shaft and the transmission shaft to support the armature portion, A biasing means for biasing the intermediate transmission shaft in the axial direction and pressing the support portion on the output shaft side is provided, further comprising a reduction device configured on the intermediate transmission shaft and Between the electromagnetic clutch,
It is characterized in that it comprises a shielding member for shielding both of them while leaving the penetrating portion of the intermediate transmission shaft.
本発明においては、出力軸と伝動軸との間に両持ち支
持された中間伝動軸を設け、該軸にアーマチュア部を支
承させて、該アーマチュア部の傾倒を防止し、またこの
中間伝動軸を前記付勢手段により出力軸側に押付け、出
力軸と中間伝動軸及びこれに支承されたアーマチュア部
との間に生じる軸長方向の移動を拘束して、出力軸とア
ーマチュア部とに夫々取付けられた摩擦板間に周方向に
略均一な所定の初期間隙を実現する。また、前記出力軸
の回転を減速して前記伝動軸に伝達する減速装置を前記
中間伝動軸上に構成し、この減速装置と前記電磁クラッ
チとの間に遮蔽部材を設け、減速装置から飛散する潤滑
剤の電磁クラッチへの到達をこの遮蔽部材にて確実に阻
止して、潤滑剤の付着に伴う電磁クラッチの動作不良を
解消する。In the present invention, an intermediate transmission shaft that is supported at both ends is provided between the output shaft and the transmission shaft, and the armature portion is supported on the shaft to prevent the armature portion from tilting. The urging means presses against the output shaft side, restrains movement in the axial direction generated between the output shaft and the intermediate transmission shaft and the armature portion supported by the output shaft, and is attached to the output shaft and the armature portion, respectively. A substantially uniform predetermined initial gap is realized in the circumferential direction between the friction plates. In addition, a reduction gear for reducing the rotation of the output shaft and transmitting the rotation to the transmission shaft is formed on the intermediate transmission shaft, and a shielding member is provided between the reduction gear and the electromagnetic clutch to scatter from the reduction gear. The shielding member reliably prevents the lubricant from reaching the electromagnetic clutch, and eliminates the malfunction of the electromagnetic clutch due to the adhesion of the lubricant.
以下本発明をその実施例を示す図面に基づいて詳述す
る。第1図は本発明に係る動力舵取装置の要部を示す縦
断面図である。Hereinafter, the present invention will be described in detail with reference to the drawings showing the embodiments. FIG. 1 is a longitudinal sectional view showing a main part of a power steering apparatus according to the present invention.
図において、1は上部軸であり、また2は下部軸であ
って、これらはトーションバー3を介して同軸上に連結
され、筒形をなす共通のハウジング4内に回動自在に支
承してある。上部軸1の上端は、図示しない舵輪に連結
されており、また下部軸2は、図示の如く、下端部近傍
の外周に形成されたピニオン2aをこれに交叉するラック
軸5に噛合させ、該ラック軸5の軸長方向への摺動に応
じて舵取りがなされるラック・ピニオン式の舵取機構を
構成している。従って、舵輪に操作トルクが加えられた
場合、上部軸1はこれに伴って回動しようとする一方、
下部軸2の回動は舵取機構に加わる抵抗により拘束され
ているから、トーションバー3に前記操作トルクの大き
さ及び方向に対応する捩れが生じ、上部軸1と下部軸2
との連結部にこの捩れに相当する相対角変位が生じる。
図中6は、舵輪に加わる操舵トルクをこれに伴って生じ
る前記相対角変位として検出すべく、上部軸1と下部軸
2の連結部に構成されたトルクセンサである。In the drawing, reference numeral 1 denotes an upper shaft, and 2 denotes a lower shaft, which are coaxially connected via a torsion bar 3 and rotatably supported in a common housing 4 having a cylindrical shape. is there. The upper end of the upper shaft 1 is connected to a steering wheel (not shown), and the lower shaft 2 engages a pinion 2a formed on the outer periphery near the lower end with a rack shaft 5 intersecting the pinion 2a as shown in the figure. A rack-and-pinion type steering mechanism is provided in which steering is performed according to sliding of the rack shaft 5 in the axial direction. Therefore, when an operating torque is applied to the steering wheel, the upper shaft 1 tries to rotate accordingly,
Since the rotation of the lower shaft 2 is restricted by the resistance applied to the steering mechanism, the torsion bar 3 is twisted corresponding to the magnitude and direction of the operation torque, and the upper shaft 1 and the lower shaft 2 are rotated.
A relative angular displacement corresponding to this torsion is generated at the connection portion with the.
In the figure, reference numeral 6 denotes a torque sensor provided at a connecting portion between the upper shaft 1 and the lower shaft 2 in order to detect a steering torque applied to the steering wheel as the relative angular displacement generated therewith.
さて下部軸2の中途部外周には、大傘歯車7aが歯面を
上向きとして嵌着してあり、この嵌着位置近傍におい
て、前記ハウジング4には、円筒形をなす固定ハウジン
グ40が外方に延設してある。この固定ハウジング40の開
口端には、操舵補助力の発生源であるモータ11、該モー
タ11の出力を係断する電磁クラッチ12、及びモータ11の
出力を増力する遊星歯車減速装置13を同心上に並設して
なる補助力発生部10が嵌着されている。該補助力発生部
10の出力軸である伝動軸14は、固定ハウジング40内を経
てハウジング4中に延設されており、この延設端に嵌着
された小傘歯車7bが前記大傘歯車7aに噛合させてある。
これにより、前記モータ11の出力は、電磁クラッチ12及
び遊星歯車減速装置13を経て伝動軸14に取出され、次い
で小傘歯車7b及びこれに噛合する大傘歯車7aを介して下
部軸2に伝達され、更にピニオン2aとラック軸5との噛
合により該ラック軸5の軸長方向の摺動に変換されて舵
取りがなされる。モータ11は、前記トルクセンサ6によ
る操舵トルクの検出結果に基づいて駆動され、舵輪に加
わる操舵トルクの方向に、該操舵トルクの大きさに対応
する力を発生するようになしてあり、この力が前述した
如くラック軸5に伝達されて、舵取りのための舵輪操作
に要する力がモータ11の発生力にて補助されるのであ
る。A large bevel gear 7a is fitted on the outer periphery of the middle part of the lower shaft 2 with the tooth surface facing upward. In the vicinity of the fitted position, a fixed housing 40 having a cylindrical shape is outwardly mounted on the housing 4. It has been extended to. At the open end of the fixed housing 40, a motor 11, which is a source of the steering assist force, an electromagnetic clutch 12 for engaging and disengaging the output of the motor 11, and a planetary gear reduction device 13 for increasing the output of the motor 11 are concentrically mounted. An auxiliary force generating unit 10 arranged side by side is fitted. The auxiliary force generator
The transmission shaft 14, which is the output shaft of 10, extends into the housing 4 through the inside of the fixed housing 40, and the small bevel gear 7b fitted to the extended end meshes with the large bevel gear 7a. is there.
Thereby, the output of the motor 11 is taken out to the transmission shaft 14 via the electromagnetic clutch 12 and the planetary gear reduction device 13, and then transmitted to the lower shaft 2 via the small bevel gear 7b and the large bevel gear 7a meshing therewith. Further, the engagement between the pinion 2a and the rack shaft 5 is converted into sliding in the axial direction of the rack shaft 5 to perform steering. The motor 11 is driven based on the detection result of the steering torque by the torque sensor 6, and generates a force corresponding to the magnitude of the steering torque in the direction of the steering torque applied to the steering wheel. Is transmitted to the rack shaft 5 as described above, and the force required for steering operation for steering is assisted by the generated force of the motor 11.
なお前記ハウジング4内には、傘歯車7a,7bの噛合部
とトクルセンサ6との間を隔絶する態様にて、薄肉,浅
底のカップ状をなす遮蔽部材8が、図示の如く装着され
ている。この遮蔽部材8は、傘歯車7a,7bの噛合部に封
入される潤滑用のグリースの飛散を防ぎ、該噛合部にお
ける良好な潤滑状態を維持する一方、前記グリースのト
ルクセンサ6の構成部位への侵入を阻止し、該グリース
の付着に伴う操舵トルクの誤検出を防止すべく機能す
る。In the housing 4, a thin, shallow cup-shaped shielding member 8 is mounted as shown in the figure so as to separate the meshing portion of the bevel gears 7a, 7b from the torque sensor 6. . The shielding member 8 prevents the grease for lubrication sealed in the meshing portion of the bevel gears 7a and 7b from scattering and maintains a good lubricating state in the meshing portion, and at the same time, to the components of the torque sensor 6 of the grease. And prevents the steering torque from being erroneously detected due to the adhesion of the grease.
さて本発明に係る動力舵取装置においては、補助力発
生部10の内部構成に特徴がある。第2図は補助力発生部
10の拡大断面図である。Now, the power steering apparatus according to the present invention is characterized by the internal configuration of the auxiliary force generation unit 10. Figure 2 shows the auxiliary force generator
It is an expanded sectional view of 10.
図中10aは、補助力発生部10全体を囲繞するハウジン
グであり、操舵補助用のモータ11の出力軸11aと前述し
た如く舵取機構に連なる伝動軸14とは、夫々の先端を軸
長方向に所定長離隔させた態様にて、前記ハウジング10
a内に同軸的に支承されており、出力軸11aから伝動軸14
への伝動系は、両軸11a,14間において、モータ11側(図
の右側)に構成された電磁クラッチ12と、伝動軸14側
(図の左側)に構成された遊星歯車減速装置13とからな
る。In the figure, reference numeral 10a denotes a housing that surrounds the entire assisting force generating unit 10, and the output shaft 11a of the steering assist motor 11 and the transmission shaft 14 that is connected to the steering mechanism as described above have their respective ends in the axial direction. At a predetermined distance from the housing 10
a is coaxially supported in the transmission shaft 14a from the output shaft 11a.
The transmission system includes an electromagnetic clutch 12 arranged on the motor 11 side (right side in the figure) and a planetary gear reduction device 13 arranged on the transmission shaft 14 side (left side in the figure) between the two shafts 11a and 14. Consists of
モータ11の出力軸11aには、後述する如く電磁クラッ
チ12の一部をなす厚肉円板形の保持体20が、また伝動軸
14には、後述する如く遊星歯車減速装置13の一部をなす
厚肉円板形のキャリア30が、夫々と同軸をなしてスプラ
イン結合されている。保持体20及びキャリア30は、互い
に対向する側の軸心位置に所定深さの円孔を夫々有して
おり、保持体20の円孔には、玉軸受20aが内嵌固定さ
れ、キャリア30の円孔には玉軸受30aが軸長方向への摺
動自在に内嵌されている。本発明の特徴たる中間伝動軸
15は、その両端を前記玉軸受20a,30aに支承させ、出力
軸11aと伝動軸14との間に両持ち支持されている。キャ
リア30に形成された前記円孔の内部には、該円孔内に面
する伝動軸14の端面と玉軸受30aの外輪とに両側を接触
させた態様にて、付勢手段たるウェーブワッシャ16が介
装されており、中間伝動軸15は、玉軸受30aを介してこ
のウェーブワッシャ16により、出力軸11a側に向けて付
勢されている。The output shaft 11a of the motor 11 is provided with a thick disk-shaped holding member 20, which forms a part of the electromagnetic clutch 12, as will be described later.
A thick disk-shaped carrier 30 which forms a part of the planetary gear reduction device 13 is spline-coupled to each other coaxially with each other as described later. The holding body 20 and the carrier 30 each have a circular hole with a predetermined depth at the axial center position on the side facing each other, and a ball bearing 20a is internally fitted and fixed in the circular hole of the holding body 20. A ball bearing 30a is fitted in the circular hole so as to be slidable in the axial direction. Intermediate transmission shaft that is a feature of the present invention
15 has both ends supported by the ball bearings 20a, 30a, and is supported at both ends between the output shaft 11a and the transmission shaft 14. The inside of the circular hole formed in the carrier 30 has a wave washer 16 serving as urging means in a state in which both ends are in contact with the end face of the transmission shaft 14 facing the circular hole and the outer ring of the ball bearing 30a. The intermediate transmission shaft 15 is urged toward the output shaft 11a by the wave washer 16 via a ball bearing 30a.
中間伝動軸15の伝動軸14側の外周には、遊星歯車減速
装置13のサンギヤ31が形成されており、また出力軸11a
側の外周には、電磁クラッチ12のアーマチュア部22が嵌
着されている。アーマチュア部22は、中間伝動軸15に外
嵌された円筒形をなすボス部22a、該ボス部22aに一端を
固定され半径方向外向きに延設された薄肉の可動板22
b、及び該可動板22bの出力軸11a側の面に固着された摩
擦板22cとを備えてなる。ボス部22aは、前記サンギヤ31
形成部における肩面と玉軸受20aの内輪とに両端を挾持
されており、前記肩面との接触部を介して作用する前記
ウェーブワッシャ16の付勢力により、玉軸受20aの内輪
面に押付けられている。On the outer periphery of the intermediate transmission shaft 15 on the transmission shaft 14 side, a sun gear 31 of the planetary gear reduction device 13 is formed, and the output shaft 11a
The armature portion 22 of the electromagnetic clutch 12 is fitted on the outer periphery on the side. The armature portion 22 has a cylindrical boss portion 22a externally fitted to the intermediate transmission shaft 15, a thin movable plate 22 having one end fixed to the boss portion 22a and extending radially outward.
b, and a friction plate 22c fixed to the surface of the movable plate 22b on the output shaft 11a side. The boss portion 22a is provided with the sun gear 31.
Both ends are sandwiched between the shoulder surface in the forming portion and the inner ring of the ball bearing 20a, and are pressed against the inner ring surface of the ball bearing 20a by the urging force of the wave washer 16 acting through the contact portion with the shoulder surface. ing.
前記ハウジング10aには、モータ11の出力軸11a先端と
軸長方向に略整合する位置に駆動コイル21が内嵌固定さ
れており、この駆動コイル21は、前記保持体20のモータ
11側の面に全周に亘って形成された凹部内に配され、該
凹部の底面に微小な間隙を隔てて対向している。また保
持体20の他面には摩擦板20cが固着され、これは、前記
アーマチュア部22の摩擦板22cと半径方向に整合され、
軸長方向に所定の間隙を隔てて対向させてある。A drive coil 21 is fixedly fitted in the housing 10a at a position substantially aligned with the tip of the output shaft 11a of the motor 11 in the axial direction, and the drive coil 21 is a motor of the holder 20.
It is arranged in a recess formed over the entire circumference on the surface on the 11 side, and faces the bottom of the recess with a small gap. Further, a friction plate 20c is fixed to the other surface of the holding body 20, which is radially aligned with the friction plate 22c of the armature portion 22,
They face each other with a predetermined gap in the axial direction.
電磁クラッチ12は、以上の如く構成された保持体20、
駆動コイル21及びアーマチュア部22からなり、駆動コイ
ル21が消磁されている場合、保持体20のみが出力軸11a
と連動回転し、また駆動コイル21が励磁されている場
合、保持体20を経てアーマチュア部22近傍に形成される
磁界の作用により、該アーマチュア部22の摩擦板22cが
可動板22bと共に保持体20側に引きつけられて両摩擦板2
0c,22cが摺接し、出力軸11aの出力は、保持体20及びア
ーマチュア部22を経て中間伝動軸15に伝達される。The electromagnetic clutch 12 includes a holding body 20 configured as described above,
When the drive coil 21 is demagnetized, only the holder 20 is connected to the output shaft 11a.
When the driving coil 21 is excited, the friction plate 22c of the armature portion 22 is moved together with the movable plate 22b by the action of a magnetic field formed near the armature portion 22 via the holding member 20. Attracted to the side and both friction plates 2
The output of the output shaft 11a is transmitted to the intermediate transmission shaft 15 via the holding body 20 and the armature section 22.
一方遊星歯車減速装置13は、中間伝動軸15外周に形成
された前記サンギヤ31と、ゴム材を内張りしてなる固定
環10bを介してハウジング10aに内嵌固定され、内側に歯
面を有するリングギヤ33と、前記キャリア30に枢支され
た複数のプラネタリギヤ32,32…とを備えてなる。サン
ギヤ31とリングギヤ33とは軸長方向に略整合しており、
プラネタリギヤ32,32…は、サンギヤ31とリングギヤ33
との間に形成された環状空間内において、両ギヤ31,32
夫々に噛合させてある。プラネタリギヤ32,32…は、伝
動軸14と連動回転するキャリア30と共に公転し、またこ
の公転軸と平行をなす各別の枢支軸廻りに自転するか
ら、電磁クラッチ12の係合により中間伝動軸15に伝達さ
れた回転力は、サンギヤ31を介してプラネタリギヤ32,3
2…に伝達され、これらの公転軸、即ち伝動軸14に所定
の減速を伴って出力され、舵取機構へ前述の如く伝達さ
れる。On the other hand, the planetary gear reduction device 13 is a ring gear having a sun gear 31 formed on the outer periphery of the intermediate transmission shaft 15 and a housing 10a which is internally fitted and fixed through a fixed ring 10b lined with a rubber material, and having a tooth surface inside. 33, and a plurality of planetary gears 32, 32,... Pivotally supported by the carrier 30. The sun gear 31 and the ring gear 33 are substantially aligned in the axial direction,
The planetary gears 32, 32 ... are the sun gear 31 and the ring gear 33
In the annular space formed between the two gears 31, 32
Each is meshed. The planetary gears 32, 32 ... revolve with the carrier 30 which rotates in conjunction with the transmission shaft 14, and rotate around respective pivot shafts parallel to the revolving shaft. The torque transmitted to 15 is transmitted through planetary gears 32, 3 via sun gear 31.
Are output to these revolving shafts, that is, the transmission shaft 14 with a predetermined deceleration, and transmitted to the steering mechanism as described above.
さて電磁クラッチ12による前述の如き係断が確実に行
われるためには、前記摩擦板20c,22c間の摺接前の間隙
(初期間隙)が、周方向全域に亘って適正に保たれてい
ることが重要である。本発明に係る動力舵取装置におい
ては、前述した如く、出力軸11aと伝動軸14との間に両
持ち支持された中間伝動軸15にアーマチュア部22が嵌着
されており、出力軸11aに固着された保持体20に対して
の該アーマチュア部22の傾倒はわずかであり、前記初期
間隙の周方向の均一性が、組立て時における繁雑な調整
作業を必要とせず極めて良好に保たれる。またアーマチ
ュア部22を支承する中間伝動軸15は、ウェーブワッシャ
16の付勢力により出力軸11a側に付勢されており、アー
マチュア部22及びこれの摩擦板22cは、前記保持体20及
びこれに固着された摩擦板20cに対し、中間伝動軸15の
前記サンギヤ31形成部における肩面と玉軸受20aの内輪
との間にそのボス部22aの両端面を挾持されて位置決め
される。従って前記初期間隙の大きさは、保持板20及び
アーマチュア部22の加工精度を高めることにより、組立
時における調整作業を必要とせず容易に適正化し得る。
即ち本発明に係る動力舵取装置においては、電磁クラッ
チ12の組立てに際し、摩擦板20a,22a間の初期間隙の繁
雑な調整作業を行う必要がなく、確実な係断動作が保証
される。Now, in order to reliably perform the above-described engagement by the electromagnetic clutch 12, the gap (initial gap) between the friction plates 20c and 22c before sliding contact is appropriately maintained over the entire circumferential direction. This is very important. In the power steering device according to the present invention, as described above, the armature portion 22 is fitted to the intermediate transmission shaft 15 supported at both ends between the output shaft 11a and the transmission shaft 14, and the output shaft 11a The inclination of the armature portion 22 with respect to the fixed holding body 20 is slight, and the uniformity of the initial gap in the circumferential direction can be maintained extremely well without requiring a complicated adjustment operation at the time of assembly. The intermediate transmission shaft 15 that supports the armature part 22 has a wave washer.
The armature portion 22 and its friction plate 22c are urged toward the output shaft 11a by the urging force of 16, and the sun gear of the intermediate transmission shaft 15 is moved relative to the holder 20 and the friction plate 20c fixed thereto. Both end surfaces of the boss portion 22a are sandwiched and positioned between the shoulder surface at the formation portion 31 and the inner ring of the ball bearing 20a. Therefore, the size of the initial gap can be easily adjusted without the need for adjustment work at the time of assembly by increasing the processing accuracy of the holding plate 20 and the armature portion 22.
That is, in the power steering apparatus according to the present invention, when assembling the electromagnetic clutch 12, there is no need to perform complicated adjustment work of the initial gap between the friction plates 20a and 22a, and a reliable engagement operation is guaranteed.
また遊星歯車減速装置13には、サンギヤ31及びリング
ギヤ33とプラネタリギヤ32,32…との噛合部における潤
滑作用をなさしめるべくグリースが充填されており、こ
のグリースが電磁クラッチ12側に飛散して摩擦板20c,22
cの摺接面に付着した場合、電磁クラッチ12による係合
動作が阻害される。本発明に係る動力舵取装置において
は、遊星歯車減速装置13と電磁クラッチ12との間に遮蔽
部材9を設け、電磁クラッチ12の構成部分への飛散グリ
ースの侵入を阻止している。第2図に示す遮蔽部材9
は、前記固定環10bの一側端面とハウジング10aの内側肩
面との間に挾持固定された薄肉円板状の部材であり、該
遮蔽部材9の内周縁は、中間伝動軸15に外嵌された前記
ボス部22aの外周にわずかな間隙を隔てて対向させてあ
る。即ち、遊星歯車減速装置13の構成部分と電磁クラッ
チ12の構成部分とは、中間伝動軸15の貫通に必要なわず
かな部分を除き、遮蔽部材9にて略完全に遮蔽されてい
る。従って、遊星歯車減速装置13にて生じるグリースの
飛散は遮蔽部材9にて確実に阻止され、飛散グリースの
侵入により生じる電磁クラッチ12の係合動作不良を未然
に回避できる。またこの遮蔽部材9の設置により、遊星
歯車減速装置13においては、前記飛散に伴う経時的なグ
リース不足が軽減され、遊星歯車減速装置13の正常な伝
動動作が長期間に亘って保証されるという付加的な効果
も得られる。Further, the planetary gear reduction device 13 is filled with grease to perform a lubricating action at a meshing portion between the sun gear 31 and the ring gear 33 and the planetary gears 32, 32, and the grease is scattered toward the electromagnetic clutch 12 to cause friction. Board 20c, 22
When it adheres to the sliding surface of c, the engagement operation by the electromagnetic clutch 12 is hindered. In the power steering device according to the present invention, the shielding member 9 is provided between the planetary gear reduction device 13 and the electromagnetic clutch 12 to prevent the scattered grease from entering the components of the electromagnetic clutch 12. Shielding member 9 shown in FIG.
Is a thin disk-shaped member sandwiched and fixed between one side end surface of the fixed ring 10b and the inner shoulder surface of the housing 10a. The inner peripheral edge of the shielding member 9 is fitted around the intermediate transmission shaft 15 outside. The boss 22a is opposed to the outer periphery of the boss 22a with a slight gap. That is, the components of the planetary gear reduction device 13 and the components of the electromagnetic clutch 12 are almost completely shielded by the shielding member 9 except for a small portion necessary for the intermediate transmission shaft 15 to penetrate. Therefore, the scattering of the grease generated in the planetary gear reduction device 13 is reliably prevented by the shielding member 9, and it is possible to prevent a defective engagement operation of the electromagnetic clutch 12 caused by the intrusion of the scattered grease. In addition, by providing the shielding member 9, in the planetary gear reduction device 13, a shortage of grease due to the scattering is reduced over time, and normal transmission operation of the planetary gear reduction device 13 is guaranteed for a long period of time. Additional effects can also be obtained.
第3図は本発明の他の実施例を示す補助力発生部10の
拡大断面図である。FIG. 3 is an enlarged sectional view of an auxiliary force generating section 10 showing another embodiment of the present invention.
本図に示す補助力発生部10においては、第1図におけ
る遊星歯車減速装置13に換えて遊星ローラ減速装置17が
設けてある。この遊星ローラ減速装置17は、中間伝動軸
15の中途部を大径化して形成された大陽軸51とハウジン
グ10aに内嵌固定された固定環53との間に、両者夫々に
転接する複数の遊星ローラ52,52…を配し、これらを伝
動軸14の端部にスプライン結合された前記キャリア30に
回動自在に枢支してなる。そして、電磁クラッチ12の係
合により中間伝動軸15に取出されるモータ11の駆動力
は、該中間伝動軸15の中途に形成された太陽軸51を介し
て遊星ローラ52,52…に伝達され、これらの公転軸、即
ち伝動軸14に所定の減速を伴って伝達される。固定環53
は、中抜き円板形のスペーサ板54,55にて両側を挾持さ
れて前記ハウジング10a内に固定してある。スペーサ板5
4,55の内周は、固定環53内周よりも内側にまで達してお
り、これらのスペーサ板54,55は、前記遊星ローラ52,52
…に生じる軸長方向の移動を拘束して、該遊星ローラ5
2,52…と固定環53との軸長方向の整合性を維持する作用
をなしている。本実施例においては、前記スペーサ板5
4,55の内、電磁クラッチ12側に位置するスペーサ板54を
アーマチュア部22のボス部22aの外周近傍にまで延長し
て、電磁クラッチ12と遊星ローラ減速装置17との間を遮
蔽する遮蔽部材として利用している。即ち、補助力発生
部10のハウジング10a内において、遊星ローラ減速装置1
7の構成部分と電磁クラッチ12の構成部分とは、中間伝
動軸15の貫通、具体的には前記ボス部22aの貫通に必要
なわずかな部分を除いて、遮蔽部材としても機能する前
記スペーサ板54にて遮蔽されている。従って、遊星ロー
ラ減速装置17の動作に応じて生じる潤滑用グリースの飛
散は、スペーサ板54により確実に阻止され、電磁クラッ
チ12の係合動作不良が未然に回避されると共に、遊星ロ
ーラ減速装置17における経時的なグリース不足が解消さ
れて、該遊星ローラ減速装置17による正常な伝動動作が
長期間に亘って保証される。In the assisting force generator 10 shown in this figure, a planetary roller speed reducer 17 is provided instead of the planetary gear speed reducer 13 in FIG. This planetary roller reduction device 17 has an intermediate transmission shaft.
A plurality of planetary rollers 52, 52, which are respectively in rolling contact with each other, are arranged between a sunshaft 51 formed by increasing the diameter of the middle part of 15 and a fixed ring 53 fixedly fitted in the housing 10a, These are rotatably supported by the carrier 30 spline-coupled to the end of the transmission shaft 14. The driving force of the motor 11, which is taken out to the intermediate transmission shaft 15 by the engagement of the electromagnetic clutch 12, is transmitted to the planetary rollers 52, 52 via a sun shaft 51 formed in the middle of the intermediate transmission shaft 15. The power is transmitted to these revolving shafts, that is, the transmission shaft 14 with a predetermined speed reduction. Fixed ring 53
Are fixed in the housing 10a by being sandwiched between both sides by hollow disc-shaped spacer plates 54 and 55. Spacer plate 5
The inner circumference of 4,55 reaches the inside of the inner circumference of the fixed ring 53, and these spacer plates 54,55 are attached to the planetary rollers 52,52.
The movement of the planetary roller 5 in
.. And the fixed ring 53 are maintained in the axial direction. In this embodiment, the spacer plate 5
4, 55, a shielding member that extends between the electromagnetic clutch 12 and the planetary roller reduction device 17 by extending the spacer plate 54 located on the electromagnetic clutch 12 side to near the outer periphery of the boss portion 22a of the armature portion 22. We use as. That is, in the housing 10a of the auxiliary force generation unit 10, the planetary roller reduction device 1
7 and the electromagnetic clutch 12 are formed by the spacer plate which also functions as a shielding member, except for a small portion necessary for the penetration of the intermediate transmission shaft 15, specifically, for the penetration of the boss portion 22a. Shielded at 54. Therefore, the scattering of the lubricating grease generated in accordance with the operation of the planetary roller reduction device 17 is reliably prevented by the spacer plate 54, so that the engagement operation failure of the electromagnetic clutch 12 is prevented beforehand, and the planetary roller reduction device 17 is prevented. The shortage of grease over time is eliminated, and the normal transmission operation by the planetary roller reduction device 17 is guaranteed for a long period of time.
また本実施例における電磁クラッチ12は、アーマチュ
ア部22の構成において第1図に示す電磁クラッチ12と若
干異なる。即ちアーマチュア部22は、中間伝動軸15に外
嵌されたボス部22aの外側に、前記スペーサ板54と略平
行をなす態様にて円板形の保持板22dを固設し、該保持
板22dの前記保持体20側の面に薄肉の可動板22bを、更に
この可動板22bの保持体20側の面に摩擦板22cを、夫々周
方向複数個所において鋲着した構成となっている。そし
て駆動コイル21の励磁により保持体20を経てアーマチュ
ア部22近傍に磁界が生じると、摩擦板22cは、その鋲着
点を中心とする可動板22bの撓み変形を伴って保持体20
側に引きつけられ、摩擦板20cに摺接して、出力軸11aと
中間伝動軸15とが係合される。前記保持板22dは、スペ
ーサ部54との間に半径方向外向きに延びる細幅の間隙を
形成し、スペーサ板54の内周縁とボス部22aとの間から
漏洩するグリースが前記摩擦板20c,22cの摺接部位へ到
達することを妨害する作用をなす。The electromagnetic clutch 12 in this embodiment is slightly different from the electromagnetic clutch 12 shown in FIG. That is, the armature portion 22 is provided with a disk-shaped holding plate 22d fixed to the outside of the boss portion 22a externally fitted to the intermediate transmission shaft 15 so as to be substantially parallel to the spacer plate 54. A thin movable plate 22b is attached to the surface of the holding member 20 side, and a friction plate 22c is attached to the surface of the movable plate 22b facing the holding member 20 at a plurality of circumferential positions. Then, when a magnetic field is generated in the vicinity of the armature section 22 through the holder 20 by the excitation of the drive coil 21, the friction plate 22c is deformed by the movable plate 22b around the point where the tack is attached, and the friction plate 22c is deformed.
The output shaft 11a and the intermediate transmission shaft 15 are engaged with each other while sliding on the friction plate 20c. The holding plate 22d forms a narrow gap extending radially outward with the spacer portion 54, and grease leaking from between the inner peripheral edge of the spacer plate 54 and the boss portion 22a is formed on the friction plate 20c, It has the effect of preventing it from reaching the sliding contact area of 22c.
なおこれらの実施例においては、操舵補助用のモータ
11の出力が、ラック・ピニオン式舵取機構のピニオンに
連なる下部軸2の中途に伝達される構成について説明し
たが、モータ11の出力は前記舵取機構中の他の部分に伝
達されるようにしてもよく、またラック・ピニオン式以
外の形式の舵取機構においても本発明の適用は可能であ
る。In these embodiments, the steering assist motor is
Although the configuration in which the output of the motor 11 is transmitted to the middle of the lower shaft 2 connected to the pinion of the rack and pinion type steering mechanism has been described, the output of the motor 11 may be transmitted to other parts in the steering mechanism. Alternatively, the present invention can be applied to a steering mechanism other than the rack and pinion type.
また中間伝動軸15の付勢手段は、実施例中に示すウェ
ーブワッシャ16に限るものではなく、コイルばね、皿ば
ね等の他の付勢手段であってもよいことは言うまでもな
い。Further, the urging means of the intermediate transmission shaft 15 is not limited to the wave washer 16 shown in the embodiment, and it goes without saying that other urging means such as a coil spring and a disc spring may be used.
以上詳述した如く本発明に係る動力舵取装置において
は、操舵補助用のモータの出力軸と舵取機構へ連なる出
力軸との間に両持ち支持された中間伝動軸を設け、該軸
に電磁クラッチのアーマチュア部を支承させてあるか
ら、該アーマチュア部の傾倒をわずかに保つことがで
き、また、この中間伝動軸が付勢手段により出力軸側に
押付けられているから、該中間伝動軸及びこれに支承さ
れたアーマチュア部が出力軸に対して正しく位置決めさ
れ、アーマチュア部側及び出力軸側に夫々取付けられた
摩擦板間に周方向に略均一な所定の初期間隙を容易に実
現でき、初期間隙の不良に起因する動作上の不都合の発
生を未然に防止し得ると共に、前記中間伝動軸上に構成
された減速装置と前記電磁クラッチとの間に設けた遮蔽
部材により、前記減速装置の潤滑剤が電磁クラッチの構
成部分への侵入が確実に阻止されるから、潤滑剤の付着
に起因する電磁クラッチの動作不良が発生する虞もな
く、操舵補助用のモータから舵取機構への操舵補助力の
伝達を確実になし得る等、本発明は優れた効果を奏す
る。As described in detail above, in the power steering device according to the present invention, an intermediate transmission shaft supported at both ends is provided between the output shaft of the steering assist motor and the output shaft connected to the steering mechanism. Since the armature portion of the electromagnetic clutch is supported, the inclination of the armature portion can be kept slightly, and since the intermediate transmission shaft is pressed against the output shaft side by the biasing means, the intermediate transmission shaft is And the armature part supported thereby is correctly positioned with respect to the output shaft, and it is possible to easily realize a predetermined circumferentially uniform initial gap between the friction plates respectively attached to the armature part side and the output shaft side, It is possible to prevent the occurrence of operational inconvenience due to the failure of the initial gap beforehand, and the shielding member provided between the reduction gear provided on the intermediate transmission shaft and the electromagnetic clutch is used to reduce the speed reduction gear. Is reliably prevented from entering the components of the electromagnetic clutch, there is no risk of malfunction of the electromagnetic clutch due to the adhesion of the lubricant, and the motor from the steering assist to the steering mechanism is not The present invention has excellent effects, such as reliable transmission of steering assist force.
第1図は本発明に係る動力舵取装置の要部を示す縦断面
図、第2図は補助力発生部の拡大断面図、第3図は本発
明の他の実施例を示す補助力発生部の拡大断面図であ
る。 1……上部軸、2……下部軸、3……トーションバー、
6……トルクセンサ、9……遮蔽部材、10……補助力発
生部、11……モータ、11a……出力軸、12……電磁クラ
ッチ、13……遊星歯車減速装置、14……伝動軸、15……
中間伝動軸、16……ウェーブワッシャ、17……遊星ロー
ラ減速装置、20……保持体、21……駆動コイル、22……
アーマチュア部、20c,22c……摩擦板、54,55……スペー
サ板FIG. 1 is a longitudinal sectional view showing a main part of a power steering apparatus according to the present invention, FIG. 2 is an enlarged sectional view of an auxiliary force generating section, and FIG. 3 is an auxiliary force generating apparatus showing another embodiment of the present invention. It is an expanded sectional view of a part. 1 ... upper shaft, 2 ... lower shaft, 3 ... torsion bar,
6 Torque sensor 9, Shielding member 10, Auxiliary force generating unit, 11 Motor, 11a Output shaft, 12 Electromagnetic clutch, 13 Planetary gear reduction device, 14 Transmission shaft , 15 ……
Intermediate transmission shaft, 16 Wave washer, 17 Planetary roller reduction gear, 20 Holder, 21 Drive coil, 22
Armature part, 20c, 22c …… Friction plate, 54,55 …… Spacer plate
Claims (2)
る操舵補助用モータの出力軸と、舵取機構への伝動軸と
の間に、その駆動コイルの励磁,消磁に伴うアーマチュ
ア部の動作により前記両軸を係断する電磁クラッチを備
えた動力舵取装置において、 前記出力軸と前記伝動軸との間に両持ち支持され、前記
アーマチュア部を支承する中間伝動軸と、 該中間伝動軸を軸長方向に付勢して、前記出力軸側の支
持部位に押付ける付勢手段と を具備することを特徴とする動力舵取装置。An operation of an armature section between an output shaft of a steering assist motor driven based on a detection result of a steering torque and a transmission shaft to a steering mechanism in response to excitation and demagnetization of a drive coil thereof. A power steering device provided with an electromagnetic clutch for disengaging the two shafts, an intermediate transmission shaft supported at both ends between the output shaft and the transmission shaft and supporting the armature portion; And a biasing means for biasing the shaft in the axial direction and pressing it against the supporting portion on the output shaft side.
前記電磁クラッチとの間に、両者を前記中間伝動軸の貫
通部分を残して遮蔽する遮蔽部材を具備する請求項1記
載の動力舵取装置。2. The motive power according to claim 1, further comprising a shielding member between the speed reducer formed on the intermediate transmission shaft and the electromagnetic clutch, which shields both of them, leaving a penetrating portion of the intermediate transmission shaft. Steering gear.
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP7798690A JP2816408B2 (en) | 1989-08-04 | 1990-03-26 | Power steering device |
EP90114746A EP0411600B1 (en) | 1989-08-04 | 1990-08-01 | Power steering apparatus |
US07/561,539 US5145021A (en) | 1989-08-04 | 1990-08-01 | Power steering apparatus |
DE69016120T DE69016120T2 (en) | 1989-08-04 | 1990-08-01 | Power steering. |
KR1019900011981A KR940002082B1 (en) | 1989-08-04 | 1990-08-04 | Power steering apparatus |
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP1-203240 | 1989-08-04 | ||
JP20324089 | 1989-08-04 | ||
JP7798690A JP2816408B2 (en) | 1989-08-04 | 1990-03-26 | Power steering device |
Publications (2)
Publication Number | Publication Date |
---|---|
JPH03164370A JPH03164370A (en) | 1991-07-16 |
JP2816408B2 true JP2816408B2 (en) | 1998-10-27 |
Family
ID=26419045
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP7798690A Expired - Lifetime JP2816408B2 (en) | 1989-08-04 | 1990-03-26 | Power steering device |
Country Status (1)
Country | Link |
---|---|
JP (1) | JP2816408B2 (en) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2010111164A2 (en) * | 2009-03-27 | 2010-09-30 | Borgwarner Inc. | Motor with torsional isolation means |
-
1990
- 1990-03-26 JP JP7798690A patent/JP2816408B2/en not_active Expired - Lifetime
Also Published As
Publication number | Publication date |
---|---|
JPH03164370A (en) | 1991-07-16 |
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