JPH0237659Y2 - - Google Patents
Info
- Publication number
- JPH0237659Y2 JPH0237659Y2 JP1985007966U JP796685U JPH0237659Y2 JP H0237659 Y2 JPH0237659 Y2 JP H0237659Y2 JP 1985007966 U JP1985007966 U JP 1985007966U JP 796685 U JP796685 U JP 796685U JP H0237659 Y2 JPH0237659 Y2 JP H0237659Y2
- Authority
- JP
- Japan
- Prior art keywords
- rack shaft
- roller
- rack
- support
- disc spring
- 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
- 238000005096 rolling process Methods 0.000 claims description 46
- 230000002093 peripheral effect Effects 0.000 claims description 4
- 230000037431 insertion Effects 0.000 claims 1
- 238000003780 insertion Methods 0.000 claims 1
- 230000006866 deterioration Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 238000006073 displacement reaction Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 239000002184 metal Substances 0.000 description 2
- 238000010521 absorption reaction Methods 0.000 description 1
- 238000009957 hemming Methods 0.000 description 1
Landscapes
- Transmission Devices (AREA)
Description
【考案の詳細な説明】
（産業上の利用分野）
本考案は車両のラツクピニオンステアリングの
ラツク軸支持装置に関し、より詳細には、乗用車
等の操舵装置として使用されるラツクピニオン式
ステアリング装置において、荷重負担領域を調整
できかつ摩擦力を付加された転がり支持手段と所
定量以上のラツク軸の偏位を制限する制限手段と
によつてラツク軸を支持するラツク軸支持装置に
関するものである。[Detailed Description of the Invention] (Field of Industrial Application) The present invention relates to a rack shaft support device for rack and pinion steering of a vehicle, and more specifically, in a rack and pinion type steering device used as a steering device for a passenger car, etc. This invention relates to a rack shaft support device that supports a rack shaft by means of rolling support means that can adjust the load bearing area and that is applied with frictional force, and a limiting means that limits the displacement of the rack shaft by more than a predetermined amount.
（従来の技術）
車両のラツクピニオン式ステアリング装置は、
従来汎用されているボールスクリユウ式ステアリ
ング装置に比し、構造が簡単で、安価であり、ハ
ンドルの切れがよい等多くの利点を有することか
ら現在FF車を中心に広く用いられている。(Prior art) A rack and pinion steering device for a vehicle is
Compared to the ball screw type steering device that has been widely used in the past, it has many advantages such as a simpler structure, lower cost, and easier steering, so it is currently widely used mainly in front-wheel drive vehicles.
しかしながら、利用が広まるにつれ、そのラツ
ク軸支持装置に係る問題が認められるようになつ
た。 However, as its use has become more widespread, problems with the rack shaft support system have become apparent.
一般にラツクとピニオン間の噛み合いにがたが
発生するのを防止するため、ラツクにはピニオン
と対向する位置にラツク軸をピニオン方向へ押圧
して支持するラツク軸支持装置が設けられてお
り、このラツク軸支持装置では、滑り支持を利用
したものが一般的であるが、転がり支持を利用し
たものも研究されている。 Generally, in order to prevent play from occurring in the meshing between the rack and pinion, the rack is provided with a rack shaft support device at a position facing the pinion that presses and supports the rack shaft in the direction of the pinion. Generally, rack shaft support devices utilize sliding support, but devices that utilize rolling support are also being researched.
ラツク軸支持部材がピニオン側へばねによつて
押圧され、その当接面でラツク軸を滑り支持する
タイプのラツク軸支持装置では、常にラツク軸を
面支持している為裾切り時に大きな操舵力が必要
である。 In a rack shaft support device of the type where the rack shaft support member is pressed by a spring toward the pinion side and the rack shaft is slid and supported on the contact surface, the rack shaft is always surface supported, so there is a large steering force when hemming. is necessary.
一方、転がり部材の転動を利用してラツク軸を
転がり支持するタイプのラツク軸支持装置では、
転がり部材が路面からの激しい衝撃を受けるため
転動部を補強した構成とする必要があることに加
え、ラツク軸の支持が点支持又は線支持となる為
高速走行時に車輪の微小な首振り振動（シミーと
いう）が起きやすい等の問題点があつた。 On the other hand, in the type of rack shaft support device that uses the rolling motion of rolling members to support the rack shaft,
Since rolling members receive severe impacts from the road surface, it is necessary to have a reinforced structure for the rolling parts, and since the rack shaft is supported by point support or line support, minute vibrations of the wheel during high-speed driving are avoided. There were problems such as easy shimmy (shimmy).
更に、最近の研究によると、滑り支持と転がり
支持を併用する２相式ラツク軸支持装置も知られ
ている。 Furthermore, according to recent research, a two-phase rack shaft support device that uses both sliding support and rolling support is also known.
例えば、低荷重域では滑り支持を、特別な高荷
重域では更に転がり支持を加えて支持する２相式
ラツク軸支持装置も提案されているが、この場
合、常時は滑り支持であるが非常に高い荷重域で
は転がり支持を加えて支持するため操舵力は軽減
されず、過大負荷に対し転がり支持部を補強する
必要があるのでコンパクトな構成しにくいという
問題点がある。 For example, a two-phase rack shaft support device has been proposed that provides sliding support in low load ranges and additional rolling support in special high load ranges, but in this case, although the support is always sliding, the In a high load range, rolling support is added to support the steering force, so the steering force is not reduced, and the rolling support needs to be reinforced against excessive loads, making it difficult to achieve a compact structure.
また、低荷重域で転がり支持、高荷重域で滑り
支持を利用した２相式ラツク軸支持装置も提案さ
れているが、このラツク軸支持装置においては、
高速運転時の低荷重域では転がり支持によつての
みラツク軸を支持するようになつているので点支
持又は線支持となりシミーの吸収が不充分となり
易い。 In addition, a two-phase rack shaft support device that uses rolling support in the low load range and sliding support in the high load region has been proposed, but in this rack shaft support device,
In the low load range during high-speed operation, the rack shaft is supported only by rolling support, which results in point support or line support, which tends to result in insufficient absorption of shimmy.
本考案は、低荷重域で転がり支持手段、高荷重
域で所定量以上のラツク軸の偏位を制限する制限
手段を利用するラツク軸支持装置である。一般に
ラツク軸の支持を転がり化するだけでも操舵力の
軽減、高速走行時の安定性向上、滑り支持に比べ
て性能劣化が抑制される等の効果が期待される
が、本考案では更に、転がり支持手段に摩擦力を
付加することにより耐シミー性の向上、高速走行
の安定性を得ること、又、転がり支持手段に低荷
重域を負担させると共に制限手段を転がり支持手
段とは独立に設けることにより転がり支持手段を
コンパクトで簡単に構成にすることを目的とす
る。 The present invention is a rack shaft support device that utilizes a rolling support means in a low load region and a limiting means that limits displacement of the rack shaft by more than a predetermined amount in a high load region. In general, simply changing the support of the rack shaft to a rolling support is expected to reduce steering force, improve stability during high-speed driving, and suppress performance deterioration compared to sliding support. Improving shimmy resistance and achieving high-speed running stability by adding frictional force to the supporting means, and making the rolling supporting means bear the burden of a low load range, and providing a limiting means independently of the rolling supporting means. It is an object of the present invention to provide a compact and simple configuration of rolling support means.
（問題点を解決するための手段）
本考案では、前記ハウジング内に配設され、前
記ラツク軸のラツク歯が形成されたのとは反対側
の外周面に接触して前記ラツク軸を転がり支持す
る転がり部材を含む転がり支持手段１１と；該転
がり支持手段を所定の付勢力でピニオン側へ付勢
し、該所定の付勢力の大きさが調整可能とされた
付勢手段２２；前記転がり部材に圧接し、摩擦に
よつて前記ラツク軸の振動を吸収する振動吸収手
段２４，２６，３０と；前記ハウジング内に前記
転がり支持手段から軸方向に離れて配置され、前
記ラツク軸の挿通を許しつつ前記ラツク軸の所定
量以上の半径方向偏位を制限する制限手段３４
と；で構成して上記の目的を達成する。(Means for Solving the Problems) In the present invention, the rack is disposed in the housing and rolls and supports the rack shaft by contacting the outer peripheral surface of the rack shaft on the opposite side to where the rack teeth are formed. a rolling support means 11 including a rolling member; urging means 22 that urges the rolling support means toward the pinion with a predetermined urging force, and the magnitude of the predetermined urging force is adjustable; the rolling member; vibration absorbing means 24, 26, and 30 that are in pressure contact with the rack shaft and absorb vibrations of the rack shaft by friction; and vibration absorbing means 24, 26, and 30 that are arranged in the housing at a distance from the rolling support means in the axial direction and allow the rack shaft to pass therethrough; limiting means 34 for limiting the radial deviation of the rack shaft by more than a predetermined amount;
and ; to achieve the above purpose.
（実施例）
第１図はラツクピニオンステアリング全体の正
面図、第２図は第１図の線Ａ−Ａに沿つた横断面
図、第３図は第１図の縦断面の一部を表わす図で
ある。以下、これらの図にもとづいて本考案によ
る実施例を説明する。(Example) Figure 1 is a front view of the entire rack and pinion steering, Figure 2 is a cross-sectional view taken along line A-A in Figure 1, and Figure 3 is a part of the longitudinal cross-section of Figure 1. It is a diagram. Hereinafter, embodiments of the present invention will be described based on these figures.
ピニオン２は、その一端のみが図示されている
が、図示なき他端はステアリングシヤフト等に係
合され、ステアリングホイールからのトルクが伝
達される。ピニオン２の先端はハウジング１０内
でラツク軸４の歯と噛み合い、その歯部両端にお
いて、ハウジング１０内に配設された玉軸受６及
び８によつて回転自在に支承されている。ラツク
軸４はピニオン２に交差して延びており、ピニオ
ン２の回動に従い、ピニオン２に交差する方向に
直線運動する。ラツク軸４の直線運動は車両の左
右前輪に伝達され、両車両は左右に操舵されるこ
とになる。 Although only one end of the pinion 2 is illustrated, the other end (not illustrated) is engaged with a steering shaft or the like, and torque from the steering wheel is transmitted thereto. The tip of the pinion 2 meshes with the teeth of the rack shaft 4 within the housing 10, and is rotatably supported at both ends of the teeth by ball bearings 6 and 8 disposed within the housing 10. The rack shaft 4 extends across the pinion 2, and moves linearly in a direction crossing the pinion 2 as the pinion 2 rotates. The linear motion of the rack shaft 4 is transmitted to the left and right front wheels of the vehicle, and both vehicles are steered left and right.
ハウジング１０はピニオン２とラツク軸４の噛
み合い部を被い、ラツク軸４の歯部の背面側には
ピニオン２に対向して延びる凹所を有し、その内
部にラツク軸４の転がり支持手段１１を内包して
いる。 The housing 10 covers the meshing part between the pinion 2 and the rack shaft 4, has a recess on the back side of the teeth of the rack shaft 4 that extends opposite the pinion 2, and has a rolling support means for the rack shaft 4 inside. It contains 11.
転がり支持手段１１は以下のように構成されて
いる。 The rolling support means 11 is constructed as follows.
支持体２０が前述の凹所に密着して嵌合し、支
持体２０には、ピニオン２の長手方向軸と平行な
貫通孔と、こお貫通孔に垂直な空間部とが形成さ
れている。これら貫通孔と空間部とに、ローラ１
２、軸受１４、ピン１６からなる転がり部材が組
み込まれる。詳しく述べると、貫通孔によつてピ
ン１６が支承され、ローラ１２及び軸受１４は、
ラツク軸４の往復運動に応じてピン１６に対して
ローラ１２が回動自在となるように上述の空間部
に配置される。ローラ１２の外周面の縦断面形状
は勿論ラツク軸４の外周面の横断面形状とほぼ同
一になされており、後述する付勢手段によつてロ
ーラ１２がラツク軸４に対して押圧された時に両
者が密着するようになされている。 The support body 20 is closely fitted into the aforementioned recess, and the support body 20 is formed with a through hole parallel to the longitudinal axis of the pinion 2 and a space perpendicular to the through hole. . A roller 1 is inserted into these through holes and spaces.
2. A rolling member consisting of a bearing 14 and a pin 16 is incorporated. Specifically, the pin 16 is supported by the through hole, and the roller 12 and bearing 14 are
The roller 12 is arranged in the above-mentioned space so as to be rotatable relative to the pin 16 in accordance with the reciprocating movement of the rack shaft 4. The vertical cross-sectional shape of the outer circumferential surface of the roller 12 is, of course, made almost the same as the cross-sectional shape of the outer circumferential surface of the rack shaft 4, so that when the roller 12 is pressed against the rack shaft 4 by a biasing means to be described later. Both are made to be in close contact with each other.
本実施例では第２図に示すように支持体２０と
ローラ１２との間にスラストメタル軸受１８が介
挿されている。これは、ラツク軸４が第２図に於
る左右方向の力を受けた時にラツク軸４が左右方
向に移動してシミーを生ずるのを防ぐためのもの
であるが、スラストメタル軸受１８を介挿せずロ
ーラ１２を支持体２０で直接受けることにより、
支持体２０に上述の機能を果たさせることもでき
る。 In this embodiment, a thrust metal bearing 18 is inserted between the support body 20 and the roller 12, as shown in FIG. This is to prevent the rack shaft 4 from moving in the left-right direction and causing shimmy when the rack shaft 4 receives the force in the left-right direction shown in FIG. By directly receiving the roller 12 on the support 20 without inserting it,
The support 20 can also perform the functions described above.
ローラ１２のラツク軸４の反対側には、やはり
ローラ１２の外周面と密着する横断面形状を有す
るプランジヤー２６が配置されている。前記凹所
の下端部にはねじ溝を有する皿バネ支持体２８が
ハウジング１０の下部に形成されたねじ溝に螺合
し、皿バネ支持体２８と支持体２０との間に皿バ
ネ２２を装着することにより、支持体２０したが
つてローラ１２がラツク軸４に対して付勢押圧さ
れている。また皿バネ支持体２８の中央部に穿孔
されたねじ穴にはボルトよりなる皿バネ支持体３
０が螺合し、プランジヤー２６と皿バネ支持体３
０との間に皿バネ２４が装着され、これはプラン
ジヤー２６とローラ１２とを摩擦係合せしめると
共にプランジヤー２６を介してローラ１２をラツ
ク軸４に対して付勢押圧する。皿バネ支持体２８
及び皿バネ支持体３０にはそれぞれナツト３１及
びナツト３２が更に螺合しており、皿バネ支持体
２８及び３０を固定すると同時にその位置を調節
して皿バネ２２及び２４による付勢力を調節する
機能を果たしている。 On the opposite side of the roller 12 from the rack shaft 4, a plunger 26 is arranged, which also has a cross-sectional shape that is in close contact with the outer peripheral surface of the roller 12. A disc spring support 28 having a thread groove is screwed into a thread groove formed in the lower part of the housing 10 at the lower end of the recess, and the disc spring 22 is inserted between the disc spring support 28 and the support 20. By mounting, the support 20 and therefore the roller 12 are biased against the rack shaft 4. In addition, a screw hole drilled in the center of the disc spring support 28 has a bolt attached to the disc spring support 3.
0 are screwed together, and the plunger 26 and disc spring support 3
A disc spring 24 is installed between the rack shaft 4 and the rack shaft 4, and this frictionally engages the plunger 26 and the roller 12, and urges the roller 12 against the rack shaft 4 via the plunger 26. Disc spring support 28
Nuts 31 and 32 are further screwed into the disc spring supports 30 and 30, respectively, and fix the disc spring supports 28 and 30, and at the same time adjust their positions to adjust the biasing force exerted by the disc springs 22 and 24. fulfills its function.
皿バネ２２及び２４は、上述したようにローラ
１２を付勢してラツク軸４に圧接させる機能を有
するとともに、ピニオン２の回動を介してラツク
軸４に加えられた力に柔軟に対処するためローラ
１２が第２図に於て下方に移動することを許容す
る。この移動距離には皿バネ２２及び２４がつぶ
れた状態を限界とする上限がある。この上限の値
即ち皿バネ２２，２４がつぶれるまで、これらに
よつて確保されるクリアランスの長さをそれぞれ
δ1，δ2で表しておく。勿論δ1，δ2はナツト３１，
３２によつて調節可能であり、また皿バネ２２，
２４の付勢力及びδ1，δ2は、プランジヤー２６が
常にローラ１２を押圧してこれを摩擦係合するよ
うに調節されている。 The disc springs 22 and 24 have the function of urging the roller 12 to press against the rack shaft 4 as described above, and also flexibly deal with the force applied to the rack shaft 4 through the rotation of the pinion 2. This allows roller 12 to move downward in FIG. There is an upper limit to this moving distance, which is the limit when the disc springs 22 and 24 are collapsed. These upper limit values, that is, the lengths of the clearances secured by these disc springs 22 and 24 until they collapse, are expressed as δ 1 and δ 2, respectively. Of course, δ 1 and δ 2 are nuts 31,
32, and a disc spring 22,
The urging force of 24 and δ 1 , δ 2 are adjusted so that the plunger 26 always presses against the roller 12 and frictionally engages it.
第３図は第１図の縦断面の一部を表わす図であ
り、ラツク軸４の所定量以上の偏位を制限する制
限手段を示している。第３図によると、ラツク軸
４がローラ１２及びピニオン２と係合する場所と
は異なる位置に、ラツク軸４と同心でかつこれを
取り囲む環状の支持部材３４がハウジング１０の
内面に固定されている。支持部材３４とラツク軸
４との間のクリアランスδ3は、δ1，δ2より小さく
なるように形成されている。 FIG. 3 is a view showing a part of the longitudinal section of FIG. 1, and shows a limiting means for limiting the deviation of the rack shaft 4 by more than a predetermined amount. According to FIG. 3, an annular support member 34 concentric with and surrounding the rack shaft 4 is fixed to the inner surface of the housing 10 at a location different from where the rack shaft 4 engages the roller 12 and the pinion 2. There is. A clearance δ 3 between the support member 34 and the rack shaft 4 is formed to be smaller than δ 1 and δ 2 .
以上の構成によるラツクピニオンステアリング
の作動について説明する。 The operation of the rack and pinion steering with the above configuration will be explained.
運転者が任意の方向にハンドルを操舵すると、
そのトルクはステアリングシヤフトを介しピニオ
ン２へと伝達される。ピニオン２の回動によつ
て、これと噛み合うラツク軸４は噛み合いが離れ
る方向にローラ１２と支持体２０と共にわずかに
移動し、ラツク軸４とピニオン２とはトルク伝達
可能状態と成る。この移動距離が前述したクリア
ランスδ3より小いような一般走行や高速走行時で
はラツク軸４への比較的小さな負荷は転がり支持
手段１１及び皿バネ２４で付勢されたプランジヤ
ー２６によつて負担される。この場合、δ3は、
δ1，δ2より小さく設定されているが、プランジヤ
ー２６や支持体２０が皿バネ２４，２２が大きく
つぶされることはないのでラツク軸４が支持部材
３４に当接することはない。ラツク軸４をこのよ
うに転がり支持するだけでも耐シミー性能はかな
り向上するが、本考案ではプランジヤー２６がロ
ーラ１２と摩擦係合しているので、この時発生す
る摩擦力が転がり支持装置１１全体の剛性を更に
高めかつ振動を吸収するため、シミーを抑制し特
に高速走行時に於る操舵安定性が一層向上する。 When the driver turns the steering wheel in any direction,
The torque is transmitted to the pinion 2 via the steering shaft. As the pinion 2 rotates, the rack shaft 4 that engages with the pinion 2 moves slightly together with the roller 12 and the support body 20 in the direction in which the mesh is separated, and the rack shaft 4 and pinion 2 become in a state where torque can be transmitted. During normal running or high-speed running when this moving distance is smaller than the above-mentioned clearance δ 3 , a relatively small load on the rack shaft 4 is borne by the rolling support means 11 and the plunger 26 biased by the disc spring 24. be done. In this case, δ 3 is
Although set smaller than δ 1 and δ 2 , the rack shaft 4 does not come into contact with the support member 34 because the plunger 26 and the support member 20 do not cause the disk springs 24 and 22 to be greatly crushed. Simply supporting the rack shaft 4 by rolling in this manner can significantly improve the shimmy resistance, but in the present invention, the plunger 26 is frictionally engaged with the roller 12, so the friction force generated at this time is applied to the entire rolling support device 11. This further increases the rigidity and absorbs vibrations, suppressing shimmy and further improving steering stability, especially when driving at high speeds.
すえ切り時等において比較的高い負荷がラツク
軸４に加わると、ラツク軸４は皿バネ２２，２４
の付勢力に抗して支持部材３４に接するまで移動
する。この場合はそれ以上の負荷はすべて支持部
材３４を介してハウジング１０によつて負担され
る。 When a relatively high load is applied to the rack shaft 4 during stationary turning, the rack shaft 4 releases the disc springs 22 and 24.
It moves against the urging force of until it touches the support member 34. In this case, all further loads are borne by the housing 10 via the support member 34.
したがつて高負荷時、低負荷時のいずれに於て
もローラ１２の回転軸であるピン１６には、ナツ
ト３１，３２を介して調節されたδ1，δ2及びδ3に
よつて設定される所定荷重以上の負荷が加えられ
ることはなく、ピン１６が破損することはない。
このように、転がり支持手段に過大な負荷が加え
られることはないので、転がり支持手段を必要以
上に補強する必要はなく、又、従来の技術とは異
なり制限手段を転がり支持手段とは独立して設け
たので転がり支持手段を簡単でコンパクトな構成
とすることができる。 Therefore, under both high load and low load conditions, the pin 16, which is the axis of rotation of the roller 12, is set by δ 1 , δ 2 and δ 3 adjusted via the nuts 31 and 32. A load exceeding a predetermined load is not applied, and the pin 16 will not be damaged.
In this way, an excessive load is not applied to the rolling support means, so there is no need to reinforce the rolling support means more than necessary, and unlike conventional technology, the limiting means is independent of the rolling support means. The rolling support means can be provided with a simple and compact structure.
第４図は本考案の別の実施例を示す図である。
第２図の実施例と異なる点は、スラストメタル軸
受１８と支持体２０との間に皿バネ３６を介挿し
たことにある。この皿バネ３６はローラ１２を常
にピン１６の長手方向と平行な方向に付勢しかつ
ローラ１２との間に摩擦力を発生させるので、前
述したプランジヤー２６と同様に耐シミー性を向
上せしめるものである。したがつて特にプランジ
ヤー２６と皿バネ２４をなくして皿バネ３６のみ
によつてローラ１２を押圧しても、第２図の実施
例と同様の効果が期待される。 FIG. 4 is a diagram showing another embodiment of the present invention.
The difference from the embodiment shown in FIG. 2 is that a disc spring 36 is inserted between the thrust metal bearing 18 and the support 20. This disc spring 36 always urges the roller 12 in a direction parallel to the longitudinal direction of the pin 16 and generates a frictional force between it and the roller 12, so it improves shimmy resistance similarly to the plunger 26 described above. It is. Therefore, even if the plunger 26 and the disc spring 24 are eliminated and the roller 12 is pressed only by the disc spring 36, the same effect as in the embodiment shown in FIG. 2 can be expected.
尚、本考案による制限手段である支持部材３４
は、例えばスリーブのような滑り支持部材やベア
リング等の転がり支持部材で構成でき、更にこれ
らに付勢手段を付加したもので構成することもで
きる。 Note that the support member 34 which is the limiting means according to the present invention
can be composed of a sliding support member such as a sleeve, a rolling support member such as a bearing, and may also be constructed by adding a biasing means to these.
（発明の効果）
以上述べたように、本考案のラツクピニオンス
テアリングは、ラツクに常に接触しかつ摩擦力を
付加された転がり支持手段と所定荷重以上の高負
荷時にラツク荷重を負担しかつラツク軸の偏位を
制限する制限手段とからなる支持手段を有し、更
に転がり支持手段には調節可能な所定荷重以上の
負荷が加えられることのないよう構成されてい
る。したがつて、転がり支持手段には高負荷が加
わらないので操舵力は軽減されかつ性能の劣化が
抑えられ、又、上述の摩擦力による振動吸収によ
つて特に高速走行時の耐シミー性が向上する。更
に転がり支持手段と独立して制限手段を設けたの
で転がり支持手段をコンパクトで簡単な構成とす
ることができ、これはコストの低減にも寄与する
ことが期待できる。(Effects of the Invention) As described above, the rack and pinion steering of the present invention has a rolling support means that is always in contact with the rack and applies frictional force, and a rack and pinion steering device that bears the rack load when the load is higher than a predetermined load. The rolling support means is configured such that a load exceeding a predetermined adjustable load is not applied to the rolling support means. Therefore, a high load is not applied to the rolling support means, so the steering force is reduced and performance deterioration is suppressed, and shimmy resistance is improved especially when running at high speeds by absorbing vibrations due to the frictional force mentioned above. do. Furthermore, since the limiting means is provided independently of the rolling support means, the rolling support means can be made compact and simple in structure, which is expected to contribute to cost reduction.
第１図は本考案によるラツクピニオン式ステア
リングの全体図、第２図は第１図のＡ−Ａ横断面
図、第３図は第１図の縦断面の一部要素を表わす
図、第４図は第２図の別の実施例を表わす図であ
る。
主要部分の符号の説明、２……ピニオン、１０
……ハウジング、４……ラツク軸、｛１２，１４，
１６……転がり部材、２０……支持体｝転がり支
持手段、２２……付勢手段、２４，２６，３０…
…振動吸収手段、３４……制限手段。
Fig. 1 is an overall view of the rack and pinion type steering according to the present invention, Fig. 2 is a cross-sectional view taken along the line A-A in Fig. 1, Fig. 3 is a view showing some elements of the longitudinal section of Fig. 1, and Fig. 4 The figure shows another embodiment of FIG. 2. Explanation of symbols of main parts, 2...Pinion, 10
...Housing, 4...Rack shaft, {12,14,
16... Rolling member, 20... Support body} Rolling support means, 22... Urging means, 24, 26, 30...
...Vibration absorbing means, 34... Limiting means.
Claims (1)
に移動されるラツク軸がハウジング内に保持さ
れてなるラツクピニオン式ステアリングであつ
て、前記ラツク軸を支持するためのラツク軸支
持装置において、 前記ハウジング内に配設され、前記ラツク軸
のラツク歯が形成されたのとは反対側の外周面
に接触して前記ラツク軸を転がり支持する転が
り部材を含む転がり支持手段と、 該転がり支持手段を所定の付勢力でピニオン
側へ付勢し、該所定の付勢力の大きさが調整可
能とされた付勢手段と、 前記転がり部材に圧接し、摩擦によつて前記
ラツク軸の振動を吸収する振動吸収手段と、 前記ハウジング内に前記転がり支持手段から
軸方向に離れて配置され、前記ラツク軸の挿通
を許しつつ前記ラツク軸の所定量以上の半径方
向偏位を制限する制限手段と、 からなることを特徴とするラツク軸支持装置。 ２ 前記転がり支持手段は、ローラと、これを支
持する支持体とを含む実用新案登録請求の範囲
第１項に記載のラツク軸支持装置。 ３ 前記振動吸収手段は、前記ローラの前記ラツ
ク軸とは反対側の外周面に密着するプランジヤ
ーと、これを前記ローラに対して押圧する皿バ
ネとからなる実用新案登録請求の範囲第２項に
記載のラツク軸支持装置。 ４ 前記振動吸収手段は、前記ローラの前記ラツ
ク軸とは反対側の外周面に密着するプランジヤ
ーと、これを前記ローラに対して押圧する皿バ
ネと、前記ローラと前記支持体との間に介挿さ
れて前記ローラをその回動の軸方向に押圧する
皿バネとから成る実用新案登録請求の範囲第２
項に記載のラツク支持装置。 ５ 前記振動吸収手段は、前記ローラの前記ラツ
ク軸とは反対側の外周面に密着するプランジヤ
ーと、該プランジヤーを前記ローラに対して押
圧する皿バネと、前記ローラと前記支持体との
間に介挿されて前記ローラをその回動の軸方向
に押圧する皿バネとから成る実用新案登録請求
の範囲第２項に記載のラツク支持装置。[Claims for Utility Model Registration] 1. A rack and pinion type steering comprising a rotating pinion and a rack shaft that meshes with the rotating pinion and is moved in the axial direction, which is held in a housing, and a rack shaft for supporting the rack shaft. The support device includes a rolling support means disposed within the housing and including a rolling member that rolls and supports the rack shaft by contacting an outer circumferential surface of the rack shaft on the opposite side from where the rack teeth are formed; urging means that urges the rolling support means toward the pinion with a predetermined urging force, and the magnitude of the predetermined urging force is adjustable; a vibration absorbing means for absorbing vibrations of the rack shaft; and a vibration absorbing means disposed within the housing axially apart from the rolling support means, for restricting radial deviation of the rack shaft by more than a predetermined amount while allowing insertion of the rack shaft. A rack shaft support device comprising: a restriction means; and a rack shaft support device. 2. The rack shaft support device according to claim 1, wherein the rolling support means includes a roller and a support for supporting the roller. 3. The vibration absorbing means comprises a plunger that is in close contact with the outer peripheral surface of the roller opposite to the rack shaft, and a disc spring that presses the plunger against the roller. Rack shaft support device as described. 4. The vibration absorbing means includes a plunger that is in close contact with the outer peripheral surface of the roller opposite to the rack axis, a disc spring that presses the plunger against the roller, and a disc spring that is interposed between the roller and the support. and a disc spring inserted therein to press the roller in the axial direction of its rotation.
Rack support device as described in section. 5. The vibration absorbing means includes a plunger that is in close contact with the outer circumferential surface of the roller on the opposite side from the rack axis, a disc spring that presses the plunger against the roller, and between the roller and the support body. A rack support device according to claim 2, which is a registered utility model and comprises a disc spring that is inserted and presses the roller in the axial direction of its rotation.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1985007966U JPH0237659Y2 (en) | 1985-01-25 | 1985-01-25 |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1985007966U JPH0237659Y2 (en) | 1985-01-25 | 1985-01-25 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS61124471U JPS61124471U (en) | 1986-08-05 |
| JPH0237659Y2 true JPH0237659Y2 (en) | 1990-10-11 |
Family
ID=30486810
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1985007966U Expired JPH0237659Y2 (en) | 1985-01-25 | 1985-01-25 |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0237659Y2 (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH085899Y2 (en) * | 1988-10-27 | 1996-02-21 | 光洋精工株式会社 | Rack and pinion type steering device |
| JP2004034829A (en) | 2002-07-03 | 2004-02-05 | Nsk Ltd | Method for manufacturing steering device and rack spindle |
| JP2012254780A (en) | 2011-05-13 | 2012-12-27 | Nsk Ltd | Steering device |
| EP2730483B1 (en) | 2011-07-04 | 2018-01-10 | NSK Ltd. | Bearing affixation structure and steering gear unit using bearing affixation structure |
| JP5626162B2 (en) * | 2011-08-30 | 2014-11-19 | 日本精工株式会社 | Tapered snap ring fixing structure |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS59184060A (en) * | 1983-03-31 | 1984-10-19 | Tokai T R W Kk | Supporter for rack and pinion |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS54165933U (en) * | 1978-05-10 | 1979-11-21 |
-
1985
- 1985-01-25 JP JP1985007966U patent/JPH0237659Y2/ja not_active Expired
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS59184060A (en) * | 1983-03-31 | 1984-10-19 | Tokai T R W Kk | Supporter for rack and pinion |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS61124471U (en) | 1986-08-05 |
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