JPS6033704B2 - force transmission device - Google Patents
force transmission deviceInfo
- Publication number
- JPS6033704B2 JPS6033704B2 JP53029173A JP2917378A JPS6033704B2 JP S6033704 B2 JPS6033704 B2 JP S6033704B2 JP 53029173 A JP53029173 A JP 53029173A JP 2917378 A JP2917378 A JP 2917378A JP S6033704 B2 JPS6033704 B2 JP S6033704B2
- Authority
- JP
- Japan
- Prior art keywords
- drive member
- rack teeth
- pinion
- cam track
- rack
- 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
Links
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
- B62D—MOTOR VEHICLES; TRAILERS
- B62D3/00—Steering gears
- B62D3/02—Steering gears mechanical
- B62D3/12—Steering gears mechanical of rack-and-pinion type
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transportation (AREA)
- Mechanical Engineering (AREA)
- Transmission Devices (AREA)
- Power Steering Mechanism (AREA)
Description
【発明の詳細な説明】
本発明は力伝達装置に係り、特に、自動車のかじ取輪の
向き変える可変比かじ取装置として好適な力伝達装置に
関する。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a force transmission device, and more particularly to a force transmission device suitable as a variable ratio steering device for changing the direction of a steering wheel of an automobile.
周知の可変比かじ取装置はフレデリック・ジョン・アダ
ムズ（ＦｒｅｄｅｒｊｃｋＪｏｈｎＡｄａｍｓ）及びラ
ルフ・マルコルム・レーマン（ＲａｌｐｈＭａｌｃｏｌ
ｍ比ｈｍａｎ）両氏によって１９７母王１月９日に出願
された“ラックピニオン組立体（Ｒａｃｋ ＡｎｄＰ手
ｎｉｏｎ 松ｓｅｍｂｌｉｅｓ）’’と題する米国特許
第４２４０３０６号明細書に記載されている。Well known variable ratio steering systems are those of Frederick John Adams and Ralph Malcolm Lehman.
No. 4,240,306, entitled "Rack and Pinion Assemblies," filed on January 9, 1977 by Messrs. M. and H.M.
同米国特許明細書に記載されているかじ取装置は、榛状
のラック上のら族状歯とかみ合う歯を持つピニオンを有
し、この棒状のラックは、ピニオンを回転することによ
りハウジングに対して相対的に長手方向に移動させられ
るようになっている。カム軌道が棒状のラック上に配置
されており、ハウジングに連結された従節に係合してい
る。棒状のラックが長手方向に移動すると、カム軌道と
従節とは、互に協力してこの棒状のラックを回転する。
棒状のラックがこのように回転すると、ラックの歯とピ
ニオンの歯とは棒状のラックの藤線方向移動の速度を変
えるように相互に作用する。前述の米国特許明細書に記
載されているかじ取装置は同装置の構造及び作動はほぼ
満足であるが、＝，長期にわたる使用によって棒状のラ
ックの両端の玉継手が摩耗する欠点がある。The steering device described in that patent has a pinion with teeth that mesh with the spiral teeth on the rod-like rack, and the rod-like rack is moved against the housing by rotating the pinion. and can be moved relative to each other in the longitudinal direction. A cam track is disposed on the rod-like rack and engages a follower connected to the housing. As the rod-like rack moves longitudinally, the cam track and the follower cooperate with each other to rotate the rod-like rack.
When the rod-like rack rotates in this manner, the teeth of the rack and the teeth of the pinion interact to change the speed of movement of the rod-like rack in the ratchet direction. Although the steering device described in the above-mentioned U.S. patent specification is generally satisfactory in structure and operation, it has the disadvantage that the ball joints at both ends of the rod-like rack wear out after long-term use.
玉継手のこの摩耗は棒状のラックの回転に起因するとこ
ろが少くない。更に、前述の米国特許明細書に記載され
ているかじ取装置のカム軌道はラック歯と軸線方向に隔
てられている。This wear on the ball joint is largely due to the rotation of the rod-like rack. Furthermore, the cam track of the steering system described in the aforementioned US patent is axially spaced from the rack teeth.
従って、棒状のラックは少くともラック歯の列の長さの
２倍の長さを有していなければならない。この比較的長
いラックは小形の自動車には不適当である。その上、ラ
ック歯から軸線方向に隔てられたところにカム軌道を設
けると、ラックがカム従節によって回転される時にこの
ラックにねじり及び曲げの双方の力が加えられる。本発
明の目的は前述の欠点を除去し、小型でしかも信頼性の
高い力伝達装置を得ることである。Therefore, the rod-like rack must have a length that is at least twice the length of the row of rack teeth. This relatively long rack is unsuitable for small motor vehicles. Additionally, having the cam track axially spaced from the rack teeth subjects the rack to both torsional and bending forces as it is rotated by the cam follower. The object of the invention is to eliminate the above-mentioned drawbacks and to obtain a compact and reliable force transmission device.
本発明による力伝達装置は、ハウジングと、少くとも一
部がこのハウジング内に位置されて軸線方向の運動が可
能になった力伝達部材と、この力伝達部材に回転可能に
設けられたスリーブ状の駆動部材と、この駆動部材と力
伝達部材との並進運動を行いしかも力伝達部材に対する
駆動部材の回転運動を可能にするように両者を結合する
結合部材と、駆動部材に設けられたラック歯の列と、駆
動部材と力伝達部材との並進運動を可能にするように前
記ラック歯の列とかみ合い係合する回転可能なピニオン
と、ラック歯の列がピニオンと係合するように駆動部材
を支持するためにこの駆動部材に滑動可能に係合する支
持部材と、駆動部材に設けられたカム軌道と、駆動部材
の並進運動中にこのカム軌道に係合して駆動部材の回転
運動を制御するためにハウジングに取付けられたカム従
節とを有し、ラック歯は、駆動部材の回転運動中にピニ
オンとの係合を維持するに必要な程度に駆動部材の周囲
の一部のみに延在しており、更に、ラック歯の列と並列
になった駆動部村のラック歯が形成されていない部分は
駆動部材の並進運動並びに回転運動中に前記支持部村が
係合する滑り面を形成しており、これによって力伝達装
置を小型化すると同時に摩耗や損傷を少くして信頼性を
向上している。次に、添付図面を参照して本発明の好適
実施例を説明する。第１図に示された本発明による可変
比かじ取装置１０は、自動車の一方のかじ取車輪に連結
されたタィロッド１２と、他方のかじ取車輪に連結され
た他のタィロッド１４とを有する。A force transmitting device according to the present invention includes a housing, a force transmitting member at least partially located within the housing and capable of axial movement, and a sleeve-like member rotatably mounted on the force transmitting member. a driving member; a coupling member coupling the driving member and the force transmitting member to perform translational movement and to enable rotational movement of the driving member relative to the force transmitting member; and rack teeth provided on the driving member. a rotatable pinion in mating engagement with the row of rack teeth to permit translational movement between the drive member and the force transmitting member; and a drive member such that the row of rack teeth engages the pinion. a support member slidably engaged with the drive member to support the drive member, a cam track provided on the drive member, and a support member that engages the cam track during translational movement of the drive member to direct rotational movement of the drive member; and a cam follower mounted to the housing for control, the rack teeth extending only a portion of the circumference of the drive member to the extent necessary to maintain engagement with the pinion during rotational movement of the drive member. The portion of the drive section which extends and is parallel to the row of rack teeth and is not provided with rack teeth is a sliding surface with which the support section engages during translational and rotational movement of the drive member. This reduces the size of the force transmission device, reduces wear and damage, and improves reliability. Next, preferred embodiments of the present invention will be described with reference to the accompanying drawings. A variable ratio steering system 10 according to the invention shown in FIG. 1 has a tie rod 12 connected to one steering wheel of a motor vehicle and another tie rod 14 connected to the other steering wheel.
両タィロッド１２，１４はハウジング２４を貫通する力
伝達部材即ち榛１６の両端と１対の玉継手１８，２０に
よって夫々連結されており、棒１６をハウジング２４に
関して相対的に軸線方向に動かすことによって自動車の
かじ取車輪の向きを変えるようになつている。棒１６に
はスリーブ状の駆動部村２８が軸受組立体３０および針
軸受組立体３４を介して棒１６と同心に織装されている
。Both tie rods 12, 14 are connected by a pair of ball and socket joints 18, 20, respectively, to opposite ends of a force transmitting member or shank 16 passing through the housing 24, so that by moving the rod 16 axially relative to the housing 24, It is designed to change the direction of the steering wheels of a car. A sleeve-like drive village 28 is woven into the rod 16 concentrically with the rod 16 via a bearing assembly 30 and a needle bearing assembly 34.
この軸受組立体３０は、駆動部材２８の棒１６上におけ
る回転運動を可能にはするが、駆動部材２８の榛１６に
関する長手方向の相対的な運動を阻止して、駆動部材２
８が軸線方向に動かされたときには棒１６もこの駆動部
材２８と共に鞄線方向に並進運動をするようになつてい
る。スリーブ状の駆動部材２８の円筒形の外周面の一部
に、中心軸線４６に対して斜めに形成されたらせん状の
ラック歯４０の列３８が図示するように長手方向に形成
されており、ピニオン４２のはす歯と噛合している。The bearing assembly 30 allows rotational movement of the drive member 28 on the rod 16 but prevents relative longitudinal movement of the drive member 28 with respect to the shank 16, so that the drive member 28
8 is moved in the axial direction, the rod 16 also moves in translation along with the drive member 28 in the bag line direction. A row 38 of spiral rack teeth 40 formed obliquely with respect to the central axis 46 is formed in the longitudinal direction on a part of the cylindrical outer peripheral surface of the sleeve-shaped drive member 28, as shown in the figure. It meshes with the helical teeth of the pinion 42.
かくして、かじ取ハンドル（図示せず）の回転によって
ピニオン４２が回転されると、駆動部材２８が軸線方向
に動かされ、これと共に樺１６が軸線方向に動かされて
自動車のかじ取車輪の向きを変えるようになっている。
駆動部材２８の円筒状の外周面には、ラック歯４０の列
３８に沿ってカム軌道５０が形成されており、ハウジン
グ４２のピニオン４２に整合した位置に固定された従節
５２がこのカム軌道５０‘こ係合している。カム軌道５
０は駆動部材２８の長さを最少にするためラック歯４０
の列３８の長さとほぼ同じ長さを有する。Thus, when the pinion 42 is rotated by rotation of the steering wheel (not shown), the drive member 28 is moved axially, and with it the birch 16 is moved axially to orient the steering wheels of the vehicle. It is supposed to change.
A cam track 50 is formed on the cylindrical outer peripheral surface of the drive member 28 along the row 38 of rack teeth 40, and a follower 52 fixed in alignment with the pinion 42 of the housing 42 follows this cam track. 50' is engaged. Cam trajectory 5
0 is the rack tooth 40 in order to minimize the length of the drive member 28.
It has approximately the same length as the column 38 of.
そして、軸線方向に延在するまつすぐな中央部６２と、
その両端において互に反対の方向に蟹曲した２個の端部
５４，５８とを有し、駆動部材２８の軸線方向の運動中
に従節５２がこの轡曲した端部５４，５８に係合すると
この駆動部材２８は中心軸線４６を中心として回転され
るようになっている。駆動部村２８の外周面に形成され
たラック歯４０は、駆動部材２８のこの回転運動中にお
けるピニオン４２とラック歯４０との係合を維持するに
必要な程度に駆動部材２８の一部に形成されている。and a straight central portion 62 extending in the axial direction;
It has two end portions 54, 58 bent in opposite directions at its opposite ends, with the follower 52 engaging the bent ends 54, 58 during axial movement of the drive member 28. When assembled, the drive member 28 is rotated about the central axis 46. The rack teeth 40 formed on the outer peripheral surface of the drive member 28 are formed on a portion of the drive member 28 to the extent necessary to maintain engagement between the pinion 42 and the rack teeth 40 during this rotational movement of the drive member 28. It is formed.
図示実施例では、ラック歯４０の列３８は前述の如くカ
ム軌道５０とほぼ同じ長さを有し、しかもその両端部は
カム軌道５０の端部５４，５８ほぼ同じような形状で轡
曲している。In the illustrated embodiment, the row 38 of rack teeth 40 has substantially the same length as the cam track 50, as described above, and its ends are curved in substantially the same manner as the ends 54, 58 of the cam track 50. ing.
即ち、ラック歯４０の列３８の長手方向に延在する側綾
部分６６は、カム軌道５０の中央部６２に隣接するまつ
すぐな部分と、轡曲した端部５４，５８に隣接してこれ
と同様にわん曲した端部とを有し、全体的にはカム軌道
５０と平行になっている。従って、ラック歯４０の列３
８は駆動部材２８の周囲の約１４０ｏの範囲内に形成す
ることができる。駆動部材２８は第１図および第２図に
示す支持部村即ち支持ヨーク７０‘こよって支持されて
いる。このヨーク７川まハウジング２４に設けられてお
り、偏向ばね７２によって駆動部材２８に連続的に加圧
されており、これによって駆動部材２８とピニオン４２
との噛合を確実にしている。そして、このヨーク７０が
接触する駆動部材２８の円周面はラック歯４０やカム軌
道５０等が形成されていない滑らかな滑り面を形成して
おり、駆動部材２８の回転並びに車由線方向運動を容易
にしている。この支持ヨーク７川ま、駆動部材２８に加
えられるねじり荷重や曲げモーメントを最少にするため
に、ピニオン４２がラック歯４０の列３８に噛合する位
置の丁度反対側の位置において駆動部材２８に係合する
ことができる。次に、かじ取装置１０の作動を説明する
。That is, the longitudinally extending side twill portions 66 of the row 38 of rack teeth 40 have a straight portion adjacent the central portion 62 of the cam track 50 and a straight portion adjacent the curved ends 54, 58. and similarly curved ends, and are generally parallel to the cam track 50. Therefore, row 3 of rack teeth 40
8 may be formed within about 140 degrees around the drive member 28. The drive member 28 is supported by a support yoke 70' shown in FIGS. 1 and 2. This yoke 7 is provided in the housing 24 and is continuously pressurized against the drive member 28 by a deflection spring 72, whereby the drive member 28 and pinion 42 are
This ensures a good fit. The circumferential surface of the drive member 28 that the yoke 70 comes into contact with forms a smooth sliding surface on which no rack teeth 40, cam tracks 50, etc. are formed. is facilitated. This support yoke 7 engages the drive member 28 at a position just opposite the position where the pinion 42 meshes with the row 38 of rack teeth 40 in order to minimize torsional loads and bending moments applied to the drive member 28. can be matched. Next, the operation of the steering device 10 will be explained.
かじ取ハンドル（図示せず）によってピニオン４２が回
転されると、これに噛合するラック歯４０‘こよってス
リーブ状の駆動部材２８が轍線方向に移動する。When the pinion 42 is rotated by a steering handle (not shown), the sleeve-like drive member 28 is moved in the direction of the rut line by the engaging rack teeth 40'.
棒１６は軸受組立体３０１こよって駆動部材２８との相
対的な藤線運動が阻止されているので、榛１６は駆動部
材２８と一体に軸線方向の並進を行い、これによってタ
ィロツド１２，１４を動かしてかじ取車輪（図示せず）
の方向を変えることができる。自動車の駐車中や低速運
転中にかじ取車輪の向きを変えようとすると非常に大き
な労力が必要であるが、図示のかじ取装置１０ではスリ
ーブ状の駆動部材２８を回転することによってかじ取比
を変化して、かじ敬操作に要する労力を減じている。Since the rod 16 is prevented from moving relative to the drive member 28 by the bearing assembly 301, the bar 16 axially translates integrally with the drive member 28, thereby causing the tie rods 12, 14 to move. Moving steering wheels (not shown)
can change the direction of Changing the direction of the steering wheel while the car is parked or driving at low speed requires a great deal of effort, but in the illustrated steering device 10, the steering ratio is changed by rotating the sleeve-shaped drive member 28. This reduces the effort required for key operation.
即ち、ピニオン４２が回転されたとき、従節５２がカム
軌道５０にまつすぐな中央部６２に係合している間は駆
動部材２８は回転せず、軸線方向の運動のみをする。That is, when the pinion 42 is rotated, while the follower 52 engages the central portion 62 straight into the cam track 50, the drive member 28 does not rotate, but only moves axially.
然しながら、駆動部材２８のこの軸線方向の運動が続行
されて従節５２が、カム軌道５０の馨曲した端部５４，
５８のいづれかに係合すると、駆動部材２８の軸線方向
の運動に従ってこの駆動部村２８はあたかもねじのよう
に中心軸線４６の周りを回転し始める。However, this axial movement of drive member 28 continues to cause follower 52 to move toward curved end 54 of cam track 50,
58, the axial movement of the drive member 28 causes the drive village 28 to begin to rotate about the central axis 46 like a screw.
このように、駆動部材２８がその軸線方向の運動中に回
転をすると、らせん状のラック歯４０とピニオン４２の
はす歯との間には相対的な滑りが発生し、この滑り作用
によって駆動部材２８は従節５２及びハウジング２４に
関して相対的に軸線方向に移動される。Thus, when the drive member 28 rotates during its axial movement, a relative slip occurs between the helical rack teeth 40 and the helical teeth of the pinion 42, and this sliding action causes the drive member to rotate. Member 28 is axially moved relative to follower 52 and housing 24.
カム軌道５０の端部５４，５８と従節６２とによる駆動
部材２８のこの軸線方向の運動の向きは、ピニオン４２
のはす歯と駆動部材２８のラック歯４０とによる駆動部
材２８の鼠線方向の運動の向きとは反対であり、これに
よってかじ取比が増大されることになる。例えば、第２
図においてピニオン４２が反時計廻りの方向に回転され
ると駆動部材２８および棒１６は右向きに移動する。The direction of this axial movement of drive member 28 by ends 54, 58 of cam track 50 and follower 62 is determined by pinion 42.
The direction of the inguinal movement of the drive member 28 due to the helical teeth and the rack teeth 40 of the drive member 28 is opposite, thereby increasing the steering ratio. For example, the second
In the figure, when pinion 42 is rotated counterclockwise, drive member 28 and rod 16 move to the right.
そして、従節５２がカム軌道５０の下向きに轡曲した端
部５４に係合すると、駆動部村２８はカム軌道５０を持
ち上げる方向、即ち第３図において時計回りの方向に回
転される。駆動部村２８上のラック歯４０は中心軸線４
６に対して斜になっているので、この駆動部材２８が回
転すると、ラック歯４０の側面はピニオン４２のはす歯
の側面に対して滑り作用艮０ちカム作用をする。When the follower 52 engages the downwardly curved end 54 of the cam track 50, the drive village 28 is rotated in a direction that lifts the cam track 50, ie, in a clockwise direction in FIG. The rack teeth 40 on the drive village 28 are aligned with the center axis 4
6, when this drive member 28 rotates, the side surfaces of the rack teeth 40 slide or cam against the side surfaces of the helical teeth of the pinion 42.
このカム作用によって駆動部村２８は第２図において左
向きに移動される。その結果、駆動部材２８および棒１
６の右向きの運動の速度が減されるので、少し、労力で
大きな抵抗に打勝って駐車中や低速運転中におけるかじ
取りを容易に行うことができる。これと同様に、ピニオ
ン４２が第２図において時計廻り方向に回転されると駆
動部材２８および棒１６が左向きに移動される。This cam action causes the drive section 28 to move to the left in FIG. As a result, drive member 28 and rod 1
Since the speed of the rightward movement of the vehicle 6 is reduced, it is possible to easily steer the vehicle while parking or driving at low speeds by overcoming a large amount of resistance with little effort. Similarly, when pinion 42 is rotated clockwise in FIG. 2, drive member 28 and rod 16 are moved to the left.
このように駆動部材２８が左方に移動すると、従節５２
がカム軌道５０の上向きに轡曲した端部５８に係合して
駆動部材２８を第３図において反時計回りの方向に回転
する。その結果、斜になったラック歯４０とピニオン４
２のはす歯との間に相対的な滑り作用が発生し、駆動部
材２８と棒１６とは第２図において右向きに移動される
。かくして、ピニオン４２による駆動部材２８の左向き
の運動速度が減少されてかじ取に要する労力を減少する
ことができる。以上の如く、本発明によるかじ取装置貝
０ち力伝達装置ではピニオン４２が、穣１６即ち力伝達
部材に回転可能に設けられたスリーブ状の駆動部材２８
に直接係合することによってこの力伝達部村を動かすよ
うになっており、両者の間には何等追加の歯車等が不必
要である。When the drive member 28 moves to the left in this way, the follower 52
engages the upwardly curved end 58 of cam track 50 to rotate drive member 28 in a counterclockwise direction in FIG. As a result, the rack teeth 40 and pinion 4 are oblique.
A relative sliding action occurs between the helical teeth of 2 and the drive member 28 and the rod 16 are moved to the right in FIG. Thus, the speed of leftward movement of the drive member 28 by the pinion 42 is reduced and the effort required for steering can be reduced. As described above, in the steering force transmission device according to the present invention, the pinion 42 is connected to the sleeve-shaped drive member 28 rotatably provided on the shaft 16, that is, the force transmission member.
The force transmitting part is moved by directly engaging with the part, and there is no need for any additional gears or the like between the two parts.
そして、ピニオン４２に噛合するラック歯４０の列３８
は、駆動部材２８の回転運動中にピニオン４２との係合
を維持するに必要な程度にこの駆動部材２８の周囲の一
部にのみ形成されている。従って、ラック歯４０やカム
軌道５０等が形成されていない滑らかな残朱の部分を支
持部材７０のための滑り面として使用することが可能で
あり、これによってかじ取装置１０を極めて小形なもの
とすることができる効果を有する。そして力を伝達する
棒１６は回転をしないのでこの榛１６に連結された継手
の摩耗を最少にすることもできる。以上、本発明を自動
車の可変比かじ取装置として説明したけれども、図示実
施例に限定されることなく、他の装置、例えば工作機械
の往復動滑り台をベッドに関して動かすための装置等に
も実施可能である。and a row 38 of rack teeth 40 meshing with the pinion 42.
are formed only around a portion of the periphery of drive member 28 to the extent necessary to maintain engagement with pinion 42 during rotational movement of drive member 28. Therefore, it is possible to use the smooth remaining red portion where the rack teeth 40, cam track 50, etc. are not formed as a sliding surface for the support member 70, and thereby the steering device 10 can be made extremely small. It has an effect that can be Since the force transmitting rod 16 does not rotate, wear of the joint connected to the rod 16 can be minimized. Although the present invention has been described above as a variable ratio steering device for an automobile, it is not limited to the illustrated embodiment and can be implemented in other devices, such as a device for moving a reciprocating slide of a machine tool relative to a bed. It is.
第１図は本発明の好適実施例を示す可変比かじ取装置の
部分断面図、第２図は第１図に示されたかじ取装置の要
部の部分断面図、第３図は第２図の線３一３にける断面
図である。
１２，１４……タィロッド、１６……棒、２４・…・・
ハウジング、２８・・・・・・駆動部村、３０……軸受
組立体、３８・・・・・・ラック歯の列、４０・・・・
・・ラック歯、４２…・・・ピニオン、５０・・・・・
・カム軌道、５２……従節、７０・・・・・・支持ヨー
ク。
ＦＩＧ．ｌＦＩＧ．２
ＦＩＧ．３FIG. 1 is a partial cross-sectional view of a variable ratio steering device showing a preferred embodiment of the present invention, FIG. 2 is a partial cross-sectional view of essential parts of the steering device shown in FIG. 1, and FIG. FIG. 3 is a cross-sectional view taken along line 3--3 in the figure. 12, 14...Tie-rod, 16...Bar, 24...
Housing, 28... Drive unit village, 30... Bearing assembly, 38... Row of rack teeth, 40...
...Rack tooth, 42...Pinion, 50...
- Cam orbit, 52... follower, 70... support yoke. FIG. lFIG. 2 FIG. 3
Claims (1)
、ハウジング２４と、少くとも一部が該ハウジング内に
位置されて軸線方向の運動が可能になつた力伝達部材１
６と、該力伝達部材１６に回転可能に設けられたスリー
ブ状の駆動部材２８と、前記駆動部材２８と力伝達部材
１６との並進運動を行いしかも力伝達部材１６に対する
駆動部材２８の回転運動を可能にするように両者を結合
する結合部材３０と、前記駆動部材２８に設けられたラ
ツク歯の列３８と、前記駆動部材２８と力伝達部材１６
との並進運動を可能にするように前記ラツク歯の列３８
とかみ合い係合する回転可能なピニオン４２と、前記ラ
ツク歯の列３８がピニオン４２と係合するように前記駆
動部材２８を支持するために該駆動部材２８に滑動可能
に係合する支持部材７０と、前記駆動部材２８に設けら
れたカム軌道５０と、駆動部材２８の並進運動中に前記
カム軌道５０に係合して駆動部材２８の回転運動を制御
するために前記ハウジング２４に取付けられたカム従節
５２とを有し、前記ラツク歯は、前記駆動部材２８の回
転運動中にピニオン４２との係合を維持するに必要な程
度に駆動部材２８の周囲の一部のみに延在しており、
前記ラツク歯の列３８と並列になつた前記駆動部材２８
のラツク歯が形成されていない部分は該駆動部材２８の
並進運動並びに回転運動中に前記支持部材７０が係合す
る滑り面を形成している力伝達装置。1. A force transmitting device used for transmitting forces, comprising a housing 24 and a force transmitting member 1 at least partially located within the housing to allow axial movement.
6, a sleeve-shaped drive member 28 rotatably provided on the force transmission member 16, and a drive member 28 that performs translational movement between the drive member 28 and the force transmission member 16, and rotational movement of the drive member 28 with respect to the force transmission member 16. a coupling member 30 for coupling the two together in a manner that enables
said row of rack teeth 38 to permit translational movement with
a rotatable pinion 42 in meshing engagement and a support member 70 slidably engaged with the drive member 28 to support the drive member 28 such that the row of rack teeth 38 engages the pinion 42; a cam track 50 provided on the drive member 28; and a cam track 50 attached to the housing 24 for engaging the cam track 50 during translational movement of the drive member 28 to control rotational movement of the drive member 28. a cam follower 52, the rack teeth extending only a portion of the circumference of the drive member 28 to the extent necessary to maintain engagement with the pinion 42 during rotational movement of the drive member 28; and
the drive member 28 in parallel with the row of rack teeth 38;
The portion of the force transmitting device in which the rack teeth are not formed forms a sliding surface with which the support member 70 engages during the translational and rotational movements of the drive member 28.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| GB10867/77A GB1546339A (en) | 1977-03-15 | 1977-03-15 | Gear assemblies |
| GB10867/77 | 1977-03-15 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS53133835A JPS53133835A (en) | 1978-11-22 |
| JPS6033704B2 true JPS6033704B2 (en) | 1985-08-05 |
Family
ID=9975781
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP53029173A Expired JPS6033704B2 (en) | 1977-03-15 | 1978-03-14 | force transmission device |
Country Status (20)
| Country | Link |
|---|---|
| JP (1) | JPS6033704B2 (en) |
| AR (1) | AR213757A1 (en) |
| AU (1) | AU516614B2 (en) |
| BE (1) | BE864870A (en) |
| BR (1) | BR7801547A (en) |
| CA (1) | CA1096755A (en) |
| DD (1) | DD134134A5 (en) |
| DE (1) | DE2809221C2 (en) |
| DK (1) | DK117878A (en) |
| ES (1) | ES467816A1 (en) |
| FR (1) | FR2384172A1 (en) |
| GB (1) | GB1546339A (en) |
| IT (1) | IT1107114B (en) |
| LU (1) | LU79225A1 (en) |
| NL (1) | NL7802851A (en) |
| PL (1) | PL205328A1 (en) |
| SE (1) | SE443754B (en) |
| SU (1) | SU888808A3 (en) |
| YU (1) | YU61578A (en) |
| ZA (1) | ZA781395B (en) |
Families Citing this family (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5497928A (en) * | 1978-01-17 | 1979-08-02 | Nippon Seiko Kk | Automotive steering device |
| JPS589034B2 (en) * | 1978-04-24 | 1983-02-18 | 東海テイ−ア−ルダブリユ−株式会社 | Rack and pinion steering system |
| GB2036240B (en) * | 1978-11-27 | 1982-12-15 | Cam Gears Ltd | Variable ratio rack and pinion gear |
| DE2965951D1 (en) * | 1978-12-07 | 1983-08-25 | Cam Gears Ltd | Steering gear and method of assembling such gear |
| JPS5590224A (en) * | 1978-12-27 | 1980-07-08 | Tokai T R W Kk | Rack pinion steering gear and gear cutting method of its rack |
| US4263817A (en) * | 1979-07-02 | 1981-04-28 | The Bendix Corporation | Support member for rack and pinion assembly |
| JPS5948262A (en) * | 1982-09-09 | 1984-03-19 | Tokai T R W Kk | Rack-and-pinion gear |
| JP2006168559A (en) * | 2004-12-16 | 2006-06-29 | Ogasawara Precision Engineering:Kk | Vehicular variable steering device |
| JP2010058599A (en) * | 2008-09-02 | 2010-03-18 | Jtekt Corp | Rack shaft support device and vehicular steering device |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB609356A (en) * | 1946-03-12 | 1948-09-29 | Frederick Osgood Hickling | Improvements in or relating to cam mechanisms for steering gears and other purposes |
| AU462162B2 (en) * | 1970-08-17 | 1975-05-30 | Bishop, A.E. | Variable ratio steering mechanism for automotive vehicles |
| ZA722759B (en) * | 1971-05-14 | 1973-04-25 | Bendix Westinghouse Ltd | Vehicle steering mechanism |
| US3753375A (en) * | 1971-11-29 | 1973-08-21 | Trw Inc | Rack and pinion steering gear |
| FR2180157A5 (en) * | 1972-04-10 | 1973-11-23 | Gemmer France |
-
1977
- 1977-03-15 GB GB10867/77A patent/GB1546339A/en not_active Expired
-
1978
- 1978-03-03 DE DE2809221A patent/DE2809221C2/en not_active Expired
- 1978-03-09 ZA ZA00781395A patent/ZA781395B/en unknown
- 1978-03-13 DD DD78204141A patent/DD134134A5/en unknown
- 1978-03-13 ES ES467816A patent/ES467816A1/en not_active Expired
- 1978-03-14 LU LU79225A patent/LU79225A1/en unknown
- 1978-03-14 CA CA299,038A patent/CA1096755A/en not_active Expired
- 1978-03-14 JP JP53029173A patent/JPS6033704B2/en not_active Expired
- 1978-03-14 BE BE185815A patent/BE864870A/en unknown
- 1978-03-14 BR BR7801547A patent/BR7801547A/en unknown
- 1978-03-14 IT IT67551/78A patent/IT1107114B/en active
- 1978-03-15 FR FR7807491A patent/FR2384172A1/en active Granted
- 1978-03-15 NL NL7802851A patent/NL7802851A/en not_active Application Discontinuation
- 1978-03-15 AR AR271433A patent/AR213757A1/en active
- 1978-03-15 SE SE7803022A patent/SE443754B/en unknown
- 1978-03-15 YU YU00615/78A patent/YU61578A/en unknown
- 1978-03-15 DK DK117878A patent/DK117878A/en unknown
- 1978-03-15 AU AU34169/78A patent/AU516614B2/en not_active Expired
- 1978-03-15 SU SU782599105A patent/SU888808A3/en active
- 1978-03-15 PL PL20532878A patent/PL205328A1/en unknown
Also Published As
| Publication number | Publication date |
|---|---|
| IT7867551A0 (en) | 1978-03-14 |
| ES467816A1 (en) | 1978-11-01 |
| CA1096755A (en) | 1981-03-03 |
| GB1546339A (en) | 1979-05-23 |
| AU3416978A (en) | 1979-12-13 |
| IT1107114B (en) | 1985-11-18 |
| ZA781395B (en) | 1979-02-28 |
| BR7801547A (en) | 1978-10-03 |
| NL7802851A (en) | 1978-09-19 |
| JPS53133835A (en) | 1978-11-22 |
| DE2809221C2 (en) | 1982-04-01 |
| BE864870A (en) | 1978-07-03 |
| SE7803022L (en) | 1978-09-16 |
| AR213757A1 (en) | 1979-03-15 |
| FR2384172A1 (en) | 1978-10-13 |
| YU61578A (en) | 1983-01-21 |
| DE2809221A1 (en) | 1978-09-28 |
| FR2384172B1 (en) | 1984-10-19 |
| AU516614B2 (en) | 1981-06-11 |
| LU79225A1 (en) | 1978-06-28 |
| DK117878A (en) | 1978-09-16 |
| SE443754B (en) | 1986-03-10 |
| PL205328A1 (en) | 1979-02-12 |
| DD134134A5 (en) | 1979-02-07 |
| SU888808A3 (en) | 1981-12-07 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US4694925A (en) | Steering apparatus | |
| US7413051B2 (en) | Electric power steering apparatus | |
| US4221137A (en) | Ball nut type steering gear | |
| JPH07257406A (en) | Vehicular steering device with variable rudder angle ratio | |
| JPS6033704B2 (en) | force transmission device | |
| JPH11263232A (en) | Vehicle steering device | |
| US6374693B1 (en) | Variable steering ratio steering system | |
| EP0279034A1 (en) | Center take-off electric rack and pinion steering gear | |
| JP4133412B2 (en) | Electric power steering device | |
| JPS59106370A (en) | Steering device for car | |
| DE3713496C2 (en) | ||
| US4270397A (en) | Rotatable sleeve rack | |
| JP5892369B2 (en) | Rear wheel steering device | |
| JP3233716B2 (en) | Automotive steering system | |
| US4240306A (en) | Rack and pinion assemblies | |
| US3153948A (en) | Vehicular steering mechanism | |
| US4217793A (en) | Rack and pinion type steering gear | |
| JPS58110372A (en) | Rack pinion type steering unit | |
| DE4437941A1 (en) | Position sensor for determining rotational settings of 2 parts moving relative to each other | |
| JP3638370B2 (en) | Integral type power steering system | |
| JPH03136975A (en) | Rear-wheel steering device of front-and-rear-wheel steering vehicle | |
| US6397970B1 (en) | Steering system | |
| JPH0620710Y2 (en) | Rear wheel steering system for front and rear wheel steering vehicles | |
| JPH0236786Y2 (en) | ||
| US4984815A (en) | Steering device for a motor vehicle with four steered wheels |