JPS6021547Y2 - Spider shaft bearing structure at universal joint - Google Patents
Spider shaft bearing structure at universal jointInfo
- Publication number
- JPS6021547Y2 JPS6021547Y2 JP1980131546U JP13154680U JPS6021547Y2 JP S6021547 Y2 JPS6021547 Y2 JP S6021547Y2 JP 1980131546 U JP1980131546 U JP 1980131546U JP 13154680 U JP13154680 U JP 13154680U JP S6021547 Y2 JPS6021547 Y2 JP S6021547Y2
- Authority
- JP
- Japan
- Prior art keywords
- shaft
- bearing
- universal joint
- spider shaft
- bearing structure
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
- F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
- F16D3/26—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected
- F16D3/38—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected with a single intermediate member with trunnions or bearings arranged on two axes perpendicular to one another
- F16D3/382—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected with a single intermediate member with trunnions or bearings arranged on two axes perpendicular to one another constructional details of other than the intermediate member
- F16D3/385—Bearing cup; Bearing construction; Bearing seal; Mounting of bearing on the intermediate member
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C21/00—Combinations of sliding-contact bearings with ball or roller bearings, for exclusively rotary movement
- F16C21/005—Combinations of sliding-contact bearings with ball or roller bearings, for exclusively rotary movement the external zone of a bearing with rolling members, e.g. needles, being cup-shaped, with or without a separate thrust-bearing disc or ring, e.g. for universal joints
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
- F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
- F16D3/26—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected
- F16D3/38—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected with a single intermediate member with trunnions or bearings arranged on two axes perpendicular to one another
- F16D3/40—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected with a single intermediate member with trunnions or bearings arranged on two axes perpendicular to one another with intermediate member provided with two pairs of outwardly-directed trunnions on intersecting axes
- F16D3/41—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected with a single intermediate member with trunnions or bearings arranged on two axes perpendicular to one another with intermediate member provided with two pairs of outwardly-directed trunnions on intersecting axes with ball or roller bearings
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Support Of The Bearing (AREA)
Description
【考案の詳細な説明】
本考案は、自動車用ステアリングシャフトあるいはステ
アリングリンケージにおけるユニバーサルジヨイント部
におけるスパイグー軸の軸受構造に関する。[Detailed Description of the Invention] The present invention relates to a bearing structure for a Spigoo shaft in a universal joint portion of an automobile steering shaft or steering linkage.
一般に、自動車用ステアリングシャフトにおけるユニバ
ーサルジヨイント部のスパイグー軸の軸受構造は、ヨー
クとベアリングアウター、及びスパイグー軸とベアリン
グインナーがそれぞれ圧入された構造となっている為、
これらの間のクリアランスは＋５０Ｌ１〜−３０Ｌ１と
バラツキが非常に大きい。Generally, the bearing structure of the Spigoo shaft in the universal joint part of an automobile steering shaft is such that the yoke and the bearing outer, and the Spigoo shaft and the bearing inner are press-fitted, respectively.
The clearance between these varies greatly from +50L1 to -30L1.
しかるに、このクリアランスのバラツキをおさえる為に
、ベアリング、スパイグー軸、ヨーク穴の加工精度を向
上させるようにしているがそれだけではおさえ切れず、
又選択嵌合実施しても、バラツキ幅は４帥程度あった。However, in order to suppress this variation in clearance, we are trying to improve the machining accuracy of the bearing, Spigoo shaft, and yoke hole, but this alone cannot suppress it.
Furthermore, even when selective fitting was carried out, the width of variation was about 4 wires.
この為、ラックピニオン型ステアリングギアボックス取
付車に装着されているインターミゾイエイトシャフトの
ゴム部の作用が悪く、十分にその機能が発揮されず、異
音の発生等があった。For this reason, the rubber part of the intermittent shaft installed in cars equipped with rack and pinion type steering gear boxes did not work well, and its function was not fully demonstrated, causing abnormal noises and the like.
これをさらに詳述するに、ラックピニオン型ステアリン
グギアにおいては、ラックバ−の路面からの外力による
左右の動きにピニオンが追従できず（ピニオンにはステ
アリングホイールまでの間に付属品がいくつかついてい
る為、慣性が大きく追従し切れない。To explain this in more detail, in rack and pinion type steering gears, the pinion cannot follow the left and right movement of the rack bar due to external forces from the road surface (the pinion has several accessories attached to it before it reaches the steering wheel). Therefore, the inertia is large and it cannot be followed.
）両者の歯の間に隙間が生じ、これら歯と歯が当接する
ことによって異音が発生する。) A gap is created between the two teeth, and when these teeth come into contact with each other, abnormal noise is generated.
そこでその対策として、第１図ａ、ｂに示すよう、イン
ターミゾイエイトシャフト１にゴムカップリング２を追
加してピニオンをステアリングホイール３に対し微少回
転できるように構成する。As a countermeasure, a rubber coupling 2 is added to the intermediary shaft 1 to allow the pinion to rotate slightly relative to the steering wheel 3, as shown in FIGS. 1a and 1b.
このように、インターミゾイエイトシャフト１のゴム特
性をマツチングさせると歯面干渉音は防止できる。In this way, by matching the rubber characteristics of the intermittent shaft 1, tooth surface interference noise can be prevented.
ただしユニバーサルジヨイント部４においてクリアラン
スが大きくいわゆるガタッキがあると、このゴムカップ
リング２のゴム２ａの特性が狂い、これが為、歯面干渉
音が発生することになる。However, if the universal joint portion 4 has a large clearance and there is so-called backlash, the characteristics of the rubber 2a of the rubber coupling 2 will be disturbed, resulting in tooth surface interference noise.
本考案は、このような欠点に鑑みなされたもので、ユニ
バーサルジヨイント部のガタッキを防止し、インターミ
ゾイエイトシャフトのゴムカップリングの作用で、歯面
干渉音を有効に防止しようトスルユニバーサルジョイン
ト部におけるスパイグー軸の軸受構造を提供することを
目的とする。The present invention was developed in view of these shortcomings, and aims to prevent rattling of the universal joint and effectively prevent tooth surface interference noise through the action of the rubber coupling of the intermittent shaft. The purpose of this invention is to provide a bearing structure for a Spigoo shaft.
この目的を遠戚する為に、スパイダー軸支持部に、該支
持部端面側に向って次第に細径となるテーパ部を設ける
と共に、このテーパ部に嵌合スル移動スペーサを弾性体
にて前記テーパ部面に押圧してその外径を拡張するよう
構成したものである。In order to achieve this objective, the spider shaft support part is provided with a tapered part whose diameter gradually becomes smaller toward the end face of the support part, and a spacer that is fitted through the tapered part is attached to the tapered part using an elastic body. It is configured so that it can be pressed against a surface to expand its outer diameter.
以下、図に示す実施例を用いて本考案を詳細に説明する
。Hereinafter, the present invention will be explained in detail using embodiments shown in the drawings.
第２図はステアリ−ングメインシャフト又はインターミ
ゾイエイトシャフトに採用されるユニバーサルジヨイン
ト部におけるスパイダー軸の軸受構造の拡大断面図であ
る。FIG. 2 is an enlarged cross-sectional view of the bearing structure of the spider shaft in the universal joint part employed in the steering main shaft or the intermittent shaft.
スパイダー軸５の支持部５ａの周囲に接してローラベア
リング６が回転可能な状態で装着されており、さらにこ
のローラベアリング６はケーシング７を介してヨーク８
の穴８ａ内に圧入された構造となっている。A roller bearing 6 is rotatably mounted in contact with the periphery of the support portion 5a of the spider shaft 5, and this roller bearing 6 is further connected to a yoke 8 via a casing 7.
It has a structure in which it is press-fitted into the hole 8a.
一方、前記スパイダー軸５の支持部５ａにおいて、その
端部は端面５ｂ側に向って次第に細径となるテーパ状に
形成されており、又このテーパ部５ｃには、該テーパ部
５ｃの軸方向に沿って移動可能なように移動スペーサ９
が嵌合されている。On the other hand, the end portion of the support portion 5a of the spider shaft 5 is formed into a tapered shape that gradually becomes smaller in diameter toward the end surface 5b side, and the tapered portion 5c is formed in the axial direction of the tapered portion 5c. The moving spacer 9 is movable along the
are fitted.
この移動スペーサ９は、その内周面９ａがテーパ部５ｃ
と同様、前記端面５ｂ側に向って次第に細径となるよう
にテーパ状に形成されており、前記スパイダー軸５のテ
ーパ部５Ｃに完全接触できるよう形成されている。This movable spacer 9 has an inner circumferential surface 9a with a tapered portion 5c.
Similarly, it is formed in a tapered shape so that the diameter becomes gradually smaller toward the end surface 5b side, and is formed so as to be able to completely contact the tapered portion 5C of the spider shaft 5.
又、前記移動スペーサ９にはその軸方向に対して斜め方
向にスリット（図示せず）が形成されており、これによ
って、移動スペーサ９は、スパイダー軸５のテーパ部５
ｃから半径方向への力を受けた時、その外径が数］Ｏｕ
大きくなるよう構成されている。Further, a slit (not shown) is formed in the movable spacer 9 in a diagonal direction with respect to the axial direction thereof, so that the movable spacer 9 can fit into the tapered portion 5 of the spider shaft 5.
When a force is applied in the radial direction from c, the outer diameter becomes number]Ou
It is designed to be large.
さらにこの移動スペーサ９の底面部９ｂと前記ケーシン
グ７の底面部７ａとの間には、移動スペーサ９を前記端
面５ｂ側と反対方向に押圧付勢してなる弾性体１０が介
装されており、この弾性体１０の押圧作用によって、前
記移動スペーサ９は、その外周面９Ｃ及び内周面９ａが
、前記ローラベアリング６の内周面６ａ及びスパイダー
軸５のテーパ部５Ｃに隙間なく接触するよう構成されて
いる。Furthermore, an elastic body 10 is interposed between the bottom surface 9b of the movable spacer 9 and the bottom surface 7a of the casing 7, and is formed by pressing the movable spacer 9 in a direction opposite to the end surface 5b. Due to the pressing action of the elastic body 10, the movable spacer 9 has its outer peripheral surface 9C and inner peripheral surface 9a in contact with the inner peripheral surface 6a of the roller bearing 6 and the tapered portion 5C of the spider shaft 5 without any gap. It is configured.
次に、本実施例軸受構造の作用について説明する。Next, the operation of the bearing structure of this embodiment will be explained.
通常、ローラベアリング６とスパイダー軸５の支持部５
ａとの間には、加工精度上５０ｕないし３０１３のクリ
アランスが生じるが、移動スペーサ９が弾性体１０の弾
性によって、端面５ｂと反対側、つまり矢印Ａ方向へ移
動させられると、この移動に伴なって移動スペーサ９の
外径が、スパイダー軸５のテーパ部５Ｃによって数１０
Ｌ］押し広げられることになるので、この移動スペーサ
９の外周面９ｃがローラベアリング６の内周面６ａに隙
間なく接触することになる。Usually, the roller bearing 6 and the support part 5 of the spider shaft 5
A clearance of 50u to 3013 mm is generated between the spacer 9 and Therefore, the outer diameter of the movable spacer 9 is reduced to several tens of degrees due to the tapered portion 5C of the spider shaft 5.
L] Since the movable spacer 9 is pushed out, the outer circumferential surface 9c of the movable spacer 9 comes into contact with the inner circumferential surface 6a of the roller bearing 6 without any gap.
この結果、前記ローラベアリング６とスパイダー軸５と
の間におけるクリアランスは完全に吸収されることにな
りユニバーサルジヨイント部における従来のようなガタ
ッキは確実に防止されることになる。As a result, the clearance between the roller bearing 6 and the spider shaft 5 is completely absorbed, and the backlash that occurs in the universal joint portion as in the prior art is reliably prevented.
又、ヨーク８に左右方向、つまり矢印Ｂ方向への力が加
わった場合においても、テーパはごくわずかしかついて
いない為、前記Ａ方向への動きに対して効率が極めて悪
く、従って、この場合において移動スペーサ９は動くこ
となく、クリアランス零を保つことになる。Furthermore, even when a force is applied to the yoke 8 in the left-right direction, that is, in the direction of arrow B, since the taper is only slight, the efficiency with respect to the movement in the direction A is extremely poor. The movable spacer 9 does not move and maintains zero clearance.
なお、第３図は移動スペーサ９を押圧する弾性体として
スプリング１１を使用したもので、該移動スペーサ９は
スプリング１１の上端部を保持できるよう二重筒形に形
成されている。In addition, in FIG. 3, a spring 11 is used as an elastic body to press the movable spacer 9, and the movable spacer 9 is formed into a double cylinder shape so as to be able to hold the upper end of the spring 11.
第３図においてその他の構成は、上述した実施例と同じ
であり、従って同一番号を付してその説明は省略する。The other configurations in FIG. 3 are the same as those in the above-described embodiment, so the same numbers are given and the explanation thereof will be omitted.
以上説明したように、本考案に係わるユニバーサルジヨ
イント部におけるスパイダー軸の軸受構造によれば、ス
パイダー軸支持部に、該支持部端面側に向って次第に細
径となるテーパ部を設けると共に、このテーパ部に嵌合
する移動スペーサを弾性体にて前記テーパ部面に押圧し
、これによって移動スペーサの外径を拡張して、ローラ
ベアリング内周面に密接するよう構成したので、前記ス
パイダー軸とローラベアリング間に加工上生じていたク
リアランスは完全に吸収されることになり、これによっ
てユニバーサルジヨイント部における従来のようなガタ
ッキは確実におさえることが可能となる。As explained above, according to the bearing structure of the spider shaft in the universal joint part according to the present invention, the spider shaft support part is provided with a tapered part whose diameter gradually becomes smaller toward the end face side of the support part. The movable spacer that fits into the tapered part is pressed against the taper part surface by an elastic body, thereby expanding the outer diameter of the movable spacer so that it comes into close contact with the inner circumferential surface of the roller bearing, so that the spider shaft and The clearance created between the roller bearings due to machining is completely absorbed, thereby making it possible to reliably suppress the backlash that occurs in the universal joint part as in the past.
従って、ギアボックスにおける歯面干渉音は確実に防止
されることになるという極めて優れた効果を有する。Therefore, tooth surface interference noise in the gearbox is reliably prevented, which is an extremely excellent effect.
第１図ａはステアリングメインシャフトの断面図、同図
すはａにおけるＢ−Ｂ線断面図、第２図はステアリング
メインシャフト又はインターミゾイエイトシャフトに採
用されるユニバーサルジヨイント部におけるスパイダー
軸の軸受構造の拡大断面図、第３図は本考案軸受構造の
他の変形例を示す拡大断面図である。
５・・・・・・スパイダー軸、５ａ・・・・・・支持部
、５ｂ・・・・・・端Ｌ ５ｃ・・・・・・テーバ部、
６・・・・・田−ラベアリング、８・・・・・・ヨーク
、８ａ・・・・・・穴、９・・・・・・移動スペーサ、
１０・・・・・・弾性体、
１・・・・・・スプリング。Figure 1a is a cross-sectional view of the steering main shaft, Figure 2 is a cross-sectional view taken along line B-B in figure a, and Figure 2 is a bearing of the spider shaft in the universal joint part adopted in the steering main shaft or intermittent shaft. FIG. 3 is an enlarged sectional view showing another modification of the bearing structure of the present invention. 5... Spider shaft, 5a... Support part, 5b... End L 5c... Taper part,
6...Tara bearing, 8...Yoke, 8a...Hole, 9...Movement spacer, 10...Elastic body, 1 ······spring.
Claims (1)
持部を装着して連結し、かつスパイグー軸の挿入先端部
には前記ベアリング内径より小径で先端に向って次第に
細径となるテーパ部を設け、該テーパ部とベアリングと
の間にはテーパ部に嵌着される移動スペーサと、該移動
スペーサをテーパ部拡径側に押圧移動させる弾性体を配
設したことを特徴とするユニバーサルジヨイント部にお
けるスパイグー軸の軸受構造。A spider shaft support part is installed and connected in a bearing installed in a yoke hole, and a tapered part is provided at the insertion tip of the spider shaft, the diameter of which is smaller than the inner diameter of the bearing and gradually becomes smaller toward the tip. A spike goo in a universal joint portion, characterized in that a movable spacer fitted into the taper portion and an elastic body that presses and moves the movable spacer toward the tapered portion expanding diameter side are disposed between the taper portion and the bearing. Shaft bearing structure.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1980131546U JPS6021547Y2 (en) | 1980-09-16 | 1980-09-16 | Spider shaft bearing structure at universal joint |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1980131546U JPS6021547Y2 (en) | 1980-09-16 | 1980-09-16 | Spider shaft bearing structure at universal joint |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5754735U JPS5754735U (en) | 1982-03-30 |
| JPS6021547Y2 true JPS6021547Y2 (en) | 1985-06-27 |
Family
ID=29491826
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1980131546U Expired JPS6021547Y2 (en) | 1980-09-16 | 1980-09-16 | Spider shaft bearing structure at universal joint |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS6021547Y2 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR102030486B1 (en) * | 2019-08-12 | 2019-10-10 | (주)한성테크 | A refractory mixing device capable of preventing deflection of a door |
-
1980
- 1980-09-16 JP JP1980131546U patent/JPS6021547Y2/en not_active Expired
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR102030486B1 (en) * | 2019-08-12 | 2019-10-10 | (주)한성테크 | A refractory mixing device capable of preventing deflection of a door |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS5754735U (en) | 1982-03-30 |
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