JPH0752421Y2 - Rolling bearing support sleeve - Google Patents
Rolling bearing support sleeveInfo
- Publication number
- JPH0752421Y2 JPH0752421Y2 JP1989055253U JP5525389U JPH0752421Y2 JP H0752421 Y2 JPH0752421 Y2 JP H0752421Y2 JP 1989055253 U JP1989055253 U JP 1989055253U JP 5525389 U JP5525389 U JP 5525389U JP H0752421 Y2 JPH0752421 Y2 JP H0752421Y2
- Authority
- JP
- Japan
- Prior art keywords
- peripheral surface
- outer peripheral
- core material
- rolling bearing
- sleeve
- 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
- Support Of The Bearing (AREA)
Description
【考案の詳細な説明】 （産業上の利用分野） この考案に係る転がり軸受支持用スリーブは、例えばコ
ンプレッサを構成するアルミニウム合金製のハウジング
に、コンプレッサを構成するロータの回転軸の端部を、
回転自在に支承する場合に利用する。DETAILED DESCRIPTION OF THE INVENTION (Industrial field of use) A rolling bearing support sleeve according to the present invention includes, for example, an aluminum alloy housing forming a compressor, and an end portion of a rotary shaft of a rotor forming the compressor.
It is used when it is rotatably supported.
（従来の技術） 例えば、自動車用空調機を構成するコンプレッサとし
て、ベーン型等、各種構造のコンプレッサを使用する。
この様な空調機用コンプレッサ等、ハウジングの内側で
回転する回転軸を有する機器の場合、この回転軸の端部
をハウジングに対して、回転自在に支承する必要があ
る。(Prior Art) For example, a vane type compressor having various structures is used as a compressor constituting an automobile air conditioner.
In the case of a device having a rotating shaft that rotates inside the housing, such as an air conditioner compressor, it is necessary to rotatably support the end of the rotating shaft with respect to the housing.
この為従来から、第８図に示した様な構造を有する支持
部により、回転軸１の端部をハウジング２の壁面３に対
し、回転自在に支承していた。この支持部は、ハウジン
グ２の壁面３に形成した、円筒状の受凹部４（図示の様
な有底円筒状の他、単なる円筒状の場合もある。）に、
内周面に内方軌道７を有する円筒状の外輪５を内嵌固定
し、この外輪５内周面の内方軌道７と上記回転軸１の端
部外周面との間に、例えば複数の転動体６、６（ころ）
を設ける事で構成されている。Therefore, conventionally, the end portion of the rotary shaft 1 is rotatably supported on the wall surface 3 of the housing 2 by the support portion having the structure shown in FIG. The support portion is formed in a cylindrical receiving recess 4 (which may be a simple cylindrical shape in addition to the bottomed cylindrical shape shown in the drawing) formed on the wall surface 3 of the housing 2.
A cylindrical outer ring 5 having an inner raceway 7 on its inner peripheral surface is fitted and fixed inside, and between the inner raceway 7 on the inner peripheral surface of the outer race 5 and the outer peripheral surface of the end of the rotary shaft 1, for example, a plurality of Rolling elements 6, 6 (rollers)
It is configured by providing.
回転軸１端部の支持部を上述の様に構成する事で、この
回転軸１は、複数の転動体６、６の転動に基づいて軽い
力で回転自在となり、上記回転軸１を設けたコンプレッ
サ等の機器の運転が円滑に行なわれる様になる。By configuring the support portion at the end of the rotary shaft 1 as described above, the rotary shaft 1 becomes rotatable with a light force based on the rolling of the plurality of rolling elements 6, 6, and the rotary shaft 1 is provided. Also, equipment such as compressors can be operated smoothly.
（考案が解決しようとする課題） ところで、上述の様に構成され作用する、従来の支持部
の場合、次に述べる様な不都合を生じる。即ち、近年、
コンプレッサ等、各種機器の軽量化を図る為、これら機
器のハウジングをアルミニウム合金により造る場合が多
くなっている。この様に、ハウジングをアルミニウム合
金により造る場合でも、大きな剛性及び耐摩耗性を要求
される回転軸１、並びに転がり軸受を構成する外輪５、
転動体６、６は、鋼製のままである。(Problems to be Solved by the Invention) By the way, in the case of the conventional supporting portion configured and functioning as described above, the following inconvenience occurs. That is, in recent years
In order to reduce the weight of various devices such as compressors, the housings of these devices are often made of aluminum alloy. As described above, even when the housing is made of aluminum alloy, the rotating shaft 1 and the outer ring 5 constituting the rolling bearing, which are required to have high rigidity and wear resistance,
The rolling elements 6, 6 remain made of steel.
鋼とアルミニウム合金との熱膨張率を比較した場合、ア
ルミニウム合金の熱膨張率が鋼の熱膨張率よりも相当に
大きい。この為、上記コンプレッサ等の機器の温度が上
昇した場合には、ハウジング２の熱膨張量と外輪５の熱
膨張量との間に、大きな差が生じてしまう。When the thermal expansion coefficients of steel and aluminum alloy are compared, the thermal expansion coefficient of aluminum alloy is considerably larger than that of steel. Therefore, when the temperature of equipment such as the compressor rises, a large difference occurs between the thermal expansion amount of the housing 2 and the thermal expansion amount of the outer ring 5.
この様に、温度上昇に基づき、ハウジング２の熱膨張量
と外輪５の熱膨張量との間に、大きな差が生じた場合、
ハウジング２に形成した受凹部４の内周面と外輪５の外
周面との間に隙間が形成されてしまう。この様に受凹部
４の内周面と外輪５の外周面との間に隙間が生じた場
合、外輪５が受凹部４の内側でがたつき、回転軸１がそ
の回転に伴なってハウジング２に対し、上記隙間の幅に
相当する分だけの偏心運動をする。In this way, when a large difference occurs between the thermal expansion amount of the housing 2 and the thermal expansion amount of the outer ring 5 due to the temperature increase,
A gap is formed between the inner peripheral surface of the receiving recess 4 formed in the housing 2 and the outer peripheral surface of the outer ring 5. When a gap is formed between the inner peripheral surface of the receiving recess 4 and the outer peripheral surface of the outer ring 5 in this way, the outer ring 5 rattles inside the receiving recess 4, and the rotary shaft 1 rotates as the housing moves. With respect to 2, the eccentric motion corresponding to the width of the gap is performed.
回転軸１がこの様な偏心運動をした場合、受凹部４の内
周面と外輪５の外周面との衝突音に基づいて発生する騒
音により、この回転軸１を設けたコンプレッサ等の機器
の運転音が大きくなる。しかも、コンプレッサ等を構成
するロータリーとシリンダ室内周面との間に隙間が生じ
る等により、コンプレッサ等の機器の性能が低下する原
因ともなる。When the rotary shaft 1 makes such an eccentric motion, noise generated based on a collision sound between the inner peripheral surface of the receiving recess 4 and the outer peripheral surface of the outer ring 5 causes a noise in a device such as a compressor provided with the rotary shaft 1. The driving noise is loud. Moreover, a gap between the rotary forming the compressor or the like and the circumferential surface of the cylinder chamber may cause a decrease in the performance of equipment such as the compressor.
この様な不都合を解消する為従来から、特公昭36−2255
号公報、同39−21584号公報、同40−13082号公報、実公
昭44−22006号公報、同57−53873号公報、実開昭56−13
1024号公報、同62−62023号公報等に示されている様
に、板ばね、合成樹脂、板ばねとゴムとの組み合わせ体
等により造られた円環状のスリーブを、ハウジングと転
がり軸受の外輪との間に装着する技術が知られている。In order to eliminate such inconvenience, the Japanese Patent Publication No. 36-2255
No. 39, No. 21584, No. 40-13082, No. 44-22006, No. 57-53873, No. 56-13
As disclosed in Japanese Patent No. 1024, No. 62-62023, etc., an annular sleeve made of a leaf spring, a synthetic resin, a combination of a leaf spring and rubber, or the like is used as an outer ring of a housing and a rolling bearing. There is a known technique for mounting between and.
ところが、上述の様な従来から知られたスリーブの場
合、圧縮方向の荷重に対する剛性が十分でなかったり、
或は熱膨張に伴なう隙間幅の変動に対する追従性が悪い
等、必ずしも満足出来る性能を得る事が出来なかった。However, in the case of the conventionally known sleeve as described above, the rigidity against the load in the compression direction is not sufficient,
Or, it was not always possible to obtain satisfactory performance, such as poor followability to variations in the gap width due to thermal expansion.
実公昭57−61220号公報には、ピンによりハウジングに
対する外輪の回転（クリープ）を防止する技術が記載さ
れているが、ハウジングに対して外輪が偏心する事の防
止は出来ない。Japanese Utility Model Publication No. 57-61220 discloses a technique for preventing rotation (creep) of an outer ring with respect to a housing by a pin, but it cannot prevent eccentricity of the outer ring with respect to the housing.
本考案の転がり軸受支持用スリーブは、上述の様な不都
合を何れも解消するものである。The rolling bearing support sleeve of the present invention eliminates any of the inconveniences described above.
（課題を解決する為の手段） 本考案の転がり軸受支持用スリーブは、金属板製で全体
を筒状に造られた芯材と、この芯材の外周面に形成され
た凹溝部分に積層された合成樹脂製のスペーサ部とから
成る。このうちの芯材は、軸方向に亙る断面形状を屈曲
させる事により、外周面に上記凹溝を設けている。又、
この芯材の軸と直角方向の断面形状は円形である。又、
この芯材は、上記凹溝から外れた部分に付与された半径
方向の弾力に基づき、周面を抑え付けられない自由状態
に於いて半径方向の厚さ寸法を大きくする。そして、常
温時に上記芯材の周面を抑え付けた状態で、この芯材の
一部外周面と上記スペーサ部の一部外周面とが単一の外
周面を構成する。(Means for Solving the Problems) The rolling bearing support sleeve of the present invention is made of a metal plate and is laminated on a core material formed entirely in a tubular shape and a groove portion formed on the outer peripheral surface of the core material. And a spacer part made of synthetic resin. Of these core materials, the groove is provided on the outer peripheral surface by bending the cross-sectional shape in the axial direction. or,
The cross-sectional shape of the core material in the direction perpendicular to the axis is circular. or,
This core material increases the radial thickness dimension in a free state where the peripheral surface cannot be restrained, based on the radial elastic force applied to the portion deviated from the groove. Then, in a state where the peripheral surface of the core material is held down at room temperature, the partial outer peripheral surface of the core material and the partial outer peripheral surface of the spacer portion constitute a single outer peripheral surface.
（作用） 上述の様に本考案の転がり軸受支持用スリーブは、弾性
を有する金属製の芯材と、熱膨張率の大きな合成樹脂製
の円筒状のスペーサ部とにより造られている。この為、
温度上昇に伴なって鋼製の外輪の外周面とアルミニウム
合金製のハウジングの内周面との間の隙間寸法が大きく
なった場合でも、この隙間を塞ぎ、外輪の内側に支持さ
れた回転軸ががたつくのを防止する。(Operation) As described above, the rolling bearing supporting sleeve of the present invention is made of the elastic metal core material and the synthetic resin cylindrical spacer portion having a large thermal expansion coefficient. Therefore,
Even if the gap between the outer peripheral surface of the steel outer ring and the inner peripheral surface of the aluminum alloy housing increases with increasing temperature, this gap is closed and the rotating shaft supported inside the outer ring Prevent rattling.
特に本考案の場合、屈曲した断面形状を有する金属製の
芯材と、この芯材の外周面に積層された合成樹脂製のス
ペーサ部との共同作用により、上記がたつき防止作用
と、回転軸の直角方向に加わる荷重を支承する作用とが
確実になる。Particularly in the case of the present invention, the above-mentioned rattling prevention action and rotation can be achieved by the joint action of the metal core material having a bent cross-sectional shape and the synthetic resin spacer portion laminated on the outer peripheral surface of the core material. This ensures the function of supporting the load applied in the direction perpendicular to the shaft.
（実施例） 第１〜４図は本考案の第一実施例を示している。第１図
は転がり軸受支持用スリーブを示す半部断面図、第２図
はこのスリーブを組み付けたスリーブ付転がり軸受の断
面図、第３図はこのスリーブ付転がり軸受により構成さ
れた回転軸支持装置の部分断面図、第４図は、温度上昇
時に於けるスリーブの変形状態を示す部分断面図であ
る。(Embodiment) FIGS. 1 to 4 show a first embodiment of the present invention. FIG. 1 is a half sectional view showing a rolling bearing supporting sleeve, FIG. 2 is a sectional view of a rolling bearing with a sleeve in which the sleeve is assembled, and FIG. 3 is a rotary shaft supporting device constituted by the rolling bearing with the sleeve. FIG. 4 is a partial cross-sectional view showing a deformed state of the sleeve when the temperature rises.
本考案の転がり軸受支持用スリーブ８は、金属ばね板製
の芯材９と、この芯材９の外周面に、射出成形によって
積層された合成樹脂製のスペーサ部10とから構成されて
いる。尚、第１〜２図では転がり軸受支持用スリーブ８
の外周面を抑え付けていないが、芯材９の断面形状は、
この芯材９の外周面を抑え付け、この芯材９の外周面と
スペーサ部10の外周面とが単一の外周面を構成した状態
で描いている。実際に上記転がり軸受支持用スリーブ８
の外周面を抑え付けていない状態では、上記芯材９は、
その両端部の直径が大きくなる方向に僅かに傾斜する。The rolling bearing supporting sleeve 8 of the present invention comprises a core material 9 made of a metal spring plate and a spacer portion 10 made of synthetic resin laminated on the outer peripheral surface of the core material 9 by injection molding. Incidentally, in FIGS. 1 and 2, the rolling bearing support sleeve 8 is shown.
Although the outer peripheral surface of is not suppressed, the cross-sectional shape of the core material 9 is
The outer peripheral surface of the core material 9 is suppressed, and the outer peripheral surface of the core material 9 and the outer peripheral surface of the spacer portion 10 are drawn as a single outer peripheral surface. Actually, the sleeve 8 for supporting the rolling bearing
In the state where the outer peripheral surface of is not held down, the core material 9 is
It slightly inclines in the direction in which the diameter of both ends increases.
上記芯材９は、軸方向（図１〜４の左右方向）に亙る断
面形状を屈曲させる事により、外周面に凹溝11を設けて
いる。又、この芯材９の軸と直角方向の断面形状は円形
である。上記凹溝11の底部には、円周方向に亙って、複
数の透孔12、12を穿設している。又、上記芯材９は、上
記凹溝11から外れた部分に付与された半径方向（図１〜
４の上下方向）の弾力に基づき、周面を抑え付けられな
い自由状態に於いて半径方向の厚さ寸法を大きくする。The core material 9 has a groove 11 formed in the outer peripheral surface by bending the cross-sectional shape in the axial direction (the left-right direction in FIGS. 1 to 4). The cross-sectional shape of the core material 9 in the direction perpendicular to the axis is circular. A plurality of through holes 12, 12 are formed in the bottom of the groove 11 in the circumferential direction. Further, the core material 9 is provided in the radial direction (FIGS.
4 in the vertical direction), the thickness in the radial direction is increased in the free state where the peripheral surface cannot be held down.
即ち、ばね鋼板等の金属ばね板により造られた芯材９
は、透孔12、12の形状を除き、全体が保持器の如き絞り
加工された形状とされている。そして、幅方向中央に存
在し、上記凹溝11の底面を構成する内周側平坦部13と、
幅方向両端部に存在する外周側平坦部14、14とを、傾斜
部15、15で互いに連続させている。That is, the core material 9 made of a metal spring plate such as a spring steel plate
Except for the shape of the through holes 12 and 12, the whole has a drawn shape such as a cage. Then, at the center in the width direction, and the inner peripheral side flat portion 13 forming the bottom surface of the concave groove 11,
The outer peripheral side flat portions 14, 14 existing at both ends in the width direction are connected to each other by the inclined portions 15, 15.
尚、転がり軸受支持用スリーブ８の外周面を抑え付けて
いない未装着状態で上記各外周側平坦部14、14は、その
両端部の直径が大きくなる方向に傾斜している。但し、
この傾斜は僅かであり、自由状態でもこれら各外周側平
坦部14、14の形状はほぼ円筒状である。それぞれが円形
に形成された上記各透孔12、12は、上記内周側平坦部13
の中央部に、円周方向に亙り等間隔で設けている。The outer peripheral flat portions 14 and 14 are inclined in a direction in which the diameters of both end portions become large in a state where the outer peripheral surface of the rolling bearing supporting sleeve 8 is not attached and not held. However,
This inclination is slight, and even in the free state, the outer peripheral side flat portions 14, 14 are substantially cylindrical in shape. The through holes 12, 12 each formed in a circular shape are the inner peripheral side flat portion 13
Are provided at equal intervals in the circumferential direction in the central portion of.
上述の様な形状を有する金属ばね板製の芯材９の外周面
に形成された凹溝11には、合成樹脂製のスペーサ部10
が、射出成形によって積層されている。このスペーサ部
10の内周面に、成形時の流出によって形成された凸部16
は、上記透孔12、12と結合している。実際の場合には、
芯材９を合成樹脂の成形用型の内側にセットした状態で
スペーサ部10の射出成形を行ない、芯材９とスペーサ部
10とを一体的に結合する。In the concave groove 11 formed on the outer peripheral surface of the core material 9 made of a metal spring plate having the above-described shape, the spacer portion 10 made of synthetic resin is provided.
Are laminated by injection molding. This spacer part
On the inner peripheral surface of 10, the convex portion 16 formed by the outflow at the time of molding
Are connected to the through holes 12, 12. In the actual case,
The spacer portion 10 is injection-molded with the core material 9 set inside the molding die made of synthetic resin.
10 and united together.
上述の様なスペーサ部10を構成する合成樹脂の膨張係数
α10は、ハウジング２（第３〜４図、第８図）を構成す
るアルミニウム合金の膨張係数α2や、芯材９を構成す
る金属ばね板材の膨張係数α9、更には転がり軸受の外
輪５を構成する軸受鋼の膨張係数α5よりも大きくして
いる（α10＞α2＞α9≧α5）。そして、合成樹脂によ
りスペーサ部10を成形する際には、成形用の型内にセッ
トした芯材９の厚さ寸法（第１〜４図の上下方向の寸
法）を弾性的に少し縮め、第１図に示す様に、芯材９の
内周側平坦部13と外周側平坦部14、14とを互いに平行に
しておく。この様に、芯材９を上述の様に弾性的に圧縮
した状態で合成樹脂製のスペーサ部10を成形する結果、
常温時に上記芯材９の外周面を抑え付けた状態では、こ
の芯材９の外周側平坦部14、14の外周面とスペーサ部10
の外周面とが単一の外周面17を構成する。The expansion coefficient α 10 of the synthetic resin forming the spacer portion 10 as described above forms the expansion coefficient α 2 of the aluminum alloy forming the housing 2 (FIGS. 3 to 4 and FIG. 8) and the core material 9. The expansion coefficient α 9 of the metal spring plate material is further set to be larger than the expansion coefficient α 5 of the bearing steel constituting the outer ring 5 of the rolling bearing (α 10 > α 2 > α 9 ≧ α 5 ). When the spacer portion 10 is molded with synthetic resin, the thickness dimension of the core material 9 set in the molding die (vertical dimension in FIGS. 1 to 4) is elastically slightly shortened. As shown in FIG. 1, the inner peripheral side flat portion 13 and the outer peripheral side flat portions 14, 14 of the core material 9 are set parallel to each other. Thus, as a result of molding the synthetic resin spacer portion 10 with the core material 9 elastically compressed as described above,
When the outer peripheral surface of the core material 9 is held down at room temperature, the outer peripheral surfaces of the outer peripheral side flat portions 14, 14 of the core material 9 and the spacer portion 10 are kept.
And the outer peripheral surface of the first outer peripheral surface 17 form a single outer peripheral surface 17.
上述の様に構成された、本考案の転がり軸受支持用スリ
ーブ８は、第２図に示す様に、転がり軸受18を構成する
外輪19に外嵌固定して、スリーブ付転がり軸受20を構成
する。尚、上記外輪19の内周面には内方軌道21を形成し
ており、外輪19の内側に配置され、保持器22によって保
持された複数の転動体23、23（ころ）を上記内方軌道21
と転接させる事により、転がり軸受18としている。As shown in FIG. 2, the rolling bearing supporting sleeve 8 of the present invention constructed as described above is externally fitted and fixed to the outer ring 19 of the rolling bearing 18 to form the rolling bearing with sleeve 20. . An inner raceway 21 is formed on the inner peripheral surface of the outer ring 19, and a plurality of rolling elements 23, 23 (rollers) arranged inside the outer ring 19 and held by a cage 22 are formed on the inner side. Orbit 21
The rolling bearing 18 is formed by rolling contact with.
更に、上述の様に構成されたスリーブ付転がり軸受20
は、第３図に示す様に、アルミニウム合金等、鋼に比べ
て大きな熱膨張率を有する材質により造られたハウジン
グ２に形成した、円筒状の受凹部４に内嵌固定する。こ
の際、上記外周側平坦部14、14の外径を弾性的に縮めつ
つ、上記スリーブ付転がり軸受20を上記受凹部４に内嵌
する。内嵌した状態で、これら外周側平坦部14、14の外
周面と上記スペーサ部10の外周面とが、上記単一の外周
面17を構成する。Further, the rolling bearing with sleeve 20 configured as described above
As shown in FIG. 3, is internally fitted and fixed in a cylindrical receiving recess 4 formed in a housing 2 made of a material having a greater coefficient of thermal expansion than steel such as aluminum alloy. At this time, the rolling bearing 20 with the sleeve is fitted in the receiving recess 4 while elastically reducing the outer diameters of the outer peripheral side flat portions 14, 14. The outer peripheral surfaces of the outer peripheral side flat portions 14, 14 and the outer peripheral surface of the spacer portion 10 constitute the single outer peripheral surface 17 in a state of being fitted therein.
そして、転がり軸受18を構成する転動体23の内側に回転
軸１の端部を挿入する事により、この回転軸１の支持装
置を構成している。この様に組み立てた状態で上記スリ
ーブ８は、転がり軸受18を構成する外輪19の外周面と、
ハウジング２の受凹部４の内周面との間で、厚さ方向
（図面の上下方向）に亙り強く押圧された状態となる。Then, by inserting the end portion of the rotary shaft 1 inside the rolling element 23 constituting the rolling bearing 18, a support device for the rotary shaft 1 is constructed. In the assembled state as described above, the sleeve 8 is provided with the outer peripheral surface of the outer ring 19 which constitutes the rolling bearing 18,
The inner peripheral surface of the receiving recess 4 of the housing 2 is strongly pressed in the thickness direction (vertical direction in the drawing).
上述の様に回転軸１の支持部に組み付けられる、本考案
の転がり軸受支持用スリーブ８は、スリーブ８が弾性を
有する金属ばね板製の芯材９と、熱膨張率の大きな合成
樹脂製のスペーサ部10とにより造られている。この為、
温度上昇に伴なって鋼製の外輪19の外周面とアルミニウ
ム合金製のハウジング２に形成された受凹部４の内周面
との間の隙間寸法が大きくなった場合でも、上記スリー
ブ８の厚さ寸法が大きくなる事によってこの隙間を塞
ぐ。そして、外輪19の内側に支持された回転軸１が、が
たつくのを防止する。The rolling bearing support sleeve 8 of the present invention, which is assembled to the support portion of the rotary shaft 1 as described above, is made of a metal spring plate core 9 having elasticity and a synthetic resin having a large coefficient of thermal expansion. It is made of the spacer portion 10. Therefore,
Even if the clearance between the outer peripheral surface of the outer ring 19 made of steel and the inner peripheral surface of the receiving recess 4 formed in the housing 2 made of aluminum alloy increases as the temperature rises, the thickness of the sleeve 8 is increased. By increasing the size, this gap is closed. Then, the rotating shaft 1 supported inside the outer ring 19 is prevented from rattling.
即ち、転がり軸受支持用スリーブ８を構成するスペーサ
部10は、ハウジング２を構成するアルミニウム合金より
も大きな熱膨張率を有する合成樹脂により造られてい
る。この為、回転軸支持装置の温度が上昇した場合で
も、このスリーブ８の外周面と上記受凹部４の内周面と
の間に隙間が生じる事はない。That is, the spacer portion 10 forming the rolling bearing supporting sleeve 8 is made of a synthetic resin having a thermal expansion coefficient higher than that of the aluminum alloy forming the housing 2. Therefore, even if the temperature of the rotary shaft support device rises, no gap is created between the outer peripheral surface of the sleeve 8 and the inner peripheral surface of the receiving recess 4.
本考案の転がり軸受支持用スリーブ８の温度が上昇した
場合には、合成樹脂製のスペーサ部10と金属ばね板製の
芯材９とが、上記スペーサ部10の熱膨張によって、第４
図に誇張して示す様に変形する。即ち、膨張係数の大き
な合成樹脂製のスペーサ部10の厚さ寸法が大きくなる事
に伴って、上記各外周側平坦部14、14の外周面と上記受
凹部４の内周面との間に微小な隙間が形成される傾向と
なる。これに対して、上記各外周側平坦部14、14が、そ
れぞれの外端部（スペーサ部10から遠い側の端部）が直
径方向外方に弾性変位する。この結果、上記スペーサ部
10と芯材９とが、外輪19の外周面と受凹部４の内周面と
の間で、互いに並列に突っ張る。この為、上記外輪19の
支持は確実なものとなる。When the temperature of the rolling bearing supporting sleeve 8 of the present invention rises, the spacer portion 10 made of synthetic resin and the core material 9 made of a metal spring plate are heated by the thermal expansion of the spacer portion 10
It is transformed as shown exaggerated in the figure. That is, as the thickness of the spacer portion 10 made of synthetic resin having a large expansion coefficient increases, the space between the outer peripheral surface of each outer peripheral flat portion 14 and the inner peripheral surface of the receiving recess 4 is increased. A minute gap tends to be formed. On the other hand, the outer peripheral side flat portions 14, 14 are elastically displaced outward in the diametrical direction at the outer end portions (end portions on the side far from the spacer portion 10). As a result, the spacer part
10 and the core material 9 are stretched in parallel with each other between the outer peripheral surface of the outer ring 19 and the inner peripheral surface of the receiving recess 4. Therefore, the outer ring 19 is reliably supported.
尚、支持部の温度上昇が少なく、合成樹脂製のスペーサ
部10の熱膨張量が未だ少ない場合には、芯材９の弾性に
よって、外輪19が受凹部４の内側でしっかりと支持され
る。When the temperature rise of the supporting portion is small and the thermal expansion amount of the spacer portion 10 made of synthetic resin is still small, the outer ring 19 is firmly supported inside the receiving recess 4 by the elasticity of the core material 9.
又、回転軸１と直角方向に加わる荷重に就いては、合成
樹脂製のスペーサ部10と金属ばね板製の芯材９との双方
が、これを受ける。この為、スリーブ８は十分に大きな
負荷荷重も受ける事が出来、回転軸１の直角方向に加わ
る荷重により、この回転軸１ががたついたり、或はスリ
ーブ８がへたる事はない。Further, with respect to the load applied in the direction perpendicular to the rotary shaft 1, both the spacer portion 10 made of synthetic resin and the core material 9 made of metal spring plate receive this. Therefore, the sleeve 8 can also receive a sufficiently large load, and the load applied in the direction perpendicular to the rotary shaft 1 does not cause the rotary shaft 1 to rattle or the sleeve 8 to sag.
尚、本考案の転がり軸受支持用スリーブ８を構成する金
属ばね板製の芯材９の断面形状は、第１〜４図の様な形
状に限定されず、他にも第５〜７図に示す様な断面形状
を採用する事が出来る。The cross-sectional shape of the core material 9 made of a metal spring plate that constitutes the rolling bearing supporting sleeve 8 of the present invention is not limited to the shapes shown in FIGS. The cross-sectional shape shown can be adopted.
このうち、先ず、第５図に示した第二実施例の断面形状
は、内周側平坦部13、13を２箇所、外周側平坦部14、14
を３箇所、両平坦部13、14同士を結ぶ傾斜部15、15を４
箇所、それぞれ設けたもの、第６図に示した第三実施例
は、上記第二実施例の断面形状の内外周を変換したもの
である。Among them, first, the cross-sectional shape of the second embodiment shown in FIG. 5 has two flat portions 13 and 13 on the inner peripheral side and flat portions 14 and 14 on the outer peripheral side.
At three locations, and four inclined sections 15 and 15 connecting the flat sections 13 and 14 to each other.
The points, the respective parts, and the third embodiment shown in FIG. 6 are obtained by converting the inner and outer circumferences of the cross-sectional shape of the second embodiment.
又、第７図に示した第四実施例の断面形状は、円弧部2
4、24を２箇所に、平坦部25、25を３箇所に、それぞれ
設け、上記円弧部24、24の外周側部分を合成樹脂製のス
ペーサ部10、10を設ける為の凹溝11、11としたものであ
る。In addition, the sectional shape of the fourth embodiment shown in FIG.
4, 4 are provided at 2 places, flat portions 25, 25 are provided at 3 places, respectively, and the outer peripheral portions of the arc portions 24, 24 are recessed grooves 11, 11 for providing the synthetic resin spacer portions 10, 10. It is what
但し、何れの実施例の場合も、芯材９の外周面を抑え付
けた状態では、この芯材９の外周面とスペーサ部10の外
周面とが、単一の外周面17を構成する。この芯材９とス
ペーサ部10とから成るスリーブ８を外輪19の外周面と受
凹部４の内周面との間に押し込んだ場合には、合成樹脂
製のスペーサ部10だけでなく、金属ばね板製の芯材９
も、上記受凹部４の内周面に接触する。However, in any of the embodiments, when the outer peripheral surface of the core material 9 is held down, the outer peripheral surface of the core material 9 and the outer peripheral surface of the spacer portion 10 form a single outer peripheral surface 17. When the sleeve 8 including the core material 9 and the spacer portion 10 is pushed between the outer peripheral surface of the outer ring 19 and the inner peripheral surface of the receiving recess 4, not only the spacer portion 10 made of synthetic resin but also the metal spring. Board core 9
Also comes into contact with the inner peripheral surface of the receiving recess 4.
尚、本考案の転がり軸受支持用スリーブ８を組み込んだ
スリーブ付転がり軸受20、或はスリーブ付転がり軸受20
を組み付けた回転支持装置を構成する場合、スペーサ部
10の射出成形時に、転がり軸受18の外輪19とスリーブ８
（更には受凹部４）とを一体に結合する事も出来る。In addition, a rolling bearing with a sleeve 20 or a rolling bearing with a sleeve 20 incorporating the sleeve 8 for supporting the rolling bearing of the present invention.
When constructing the rotation support device with the
Outer ring 19 of rolling bearing 18 and sleeve 8 during injection molding of 10.
(Furthermore, the receiving recess 4) can be integrally connected.
又、芯材９の一部に、半径方向の内方及び外方に向けて
折り曲げた係止片を設け、この係止片を外輪19及びハウ
ジング２に設けた凹部に係合させる事で、ハウジング２
に対するスリーブ８及び外輪19の回動防止を、確実に図
る事も出来る。Further, a locking piece bent inward and outward in the radial direction is provided on a part of the core material 9, and the locking piece is engaged with a recess provided in the outer ring 19 and the housing 2, Housing 2
It is possible to surely prevent the sleeve 8 and the outer ring 19 from rotating with respect to.
（考案の効果） 本考案の転がり軸受支持用スリーブは、以上に述べた通
り構成され作用する為、鋼等により造られた、転がり軸
受を構成する部材と、アルミニウム合金等により造られ
た、ハウジングを構成する部材との熱膨張量の差に基づ
き、転がり軸受の外周面とハウジングの内周面との間に
存在する隙間が大きくなった場合でも、上記ハウジング
内で転がり軸受ががたつく事を確実に防止出来る。(Effect of the Invention) Since the rolling bearing supporting sleeve of the present invention is configured and operates as described above, the rolling bearing supporting member made of steel or the like and the housing made of aluminum alloy or the like are used. Due to the difference in the amount of thermal expansion with the members that make up the roller, even if the gap between the outer peripheral surface of the rolling bearing and the inner peripheral surface of the housing becomes large, it is possible to ensure that the rolling bearing rattles inside the housing. Can be prevented.
この結果、アルミニウム合金製のハウジングを有するコ
ンプレッサ等の機器の運転音の低減を図れるだけでな
く、温度上昇に基づき、この様な機器の性能が低下する
事の防止も図る事が出来る。As a result, not only can the operating noise of a device such as a compressor having a housing made of aluminum alloy be reduced, but it is also possible to prevent the performance of such a device from deteriorating due to a rise in temperature.
第１〜４図は本考案の第一実施例を示しており、第１図
は転がり軸受支持用スリーブを示す半部断面図、第２図
はこのスリーブを組み付けたスリーブ付転がり軸受の断
面図、第３図はこのスリーブ付転がり軸受により構成さ
れた回転軸支持装置の部分断面図、第４図は、温度上昇
時に於けるスリーブの変形状態を示す部分断面図、第５
〜７図は、本考案の転がり軸受支持用スリーブの第二〜
四実施例を示す、それぞれ第１図と同様の断面図、第８
図は従来の回転軸支持部の１例を示す断面図である。 1:回転軸、2:ハウジング、3:壁面、4:受凹部、5:外輪、
6:転動体、7:内方軌道、8:転がり軸受支持用スリーブ、
9:芯材、10:スペーサ部、11:凹溝、12:透孔、13:内周側
平坦部、14:外周側平坦部、15:傾斜部、16:凸部、17:外
周面、18:転がり軸受、19:外輪、20:スリーブ付転がり
軸受、21:内方軌道、22:保持器、23:転動体、24:円弧
部、25:平坦部。1 to 4 show a first embodiment of the present invention. FIG. 1 is a half sectional view showing a sleeve for supporting a rolling bearing, and FIG. 2 is a sectional view of a rolling bearing with a sleeve in which this sleeve is assembled. FIG. 3 is a partial cross-sectional view of a rotary shaft support device constituted by this rolling bearing with sleeve, and FIG. 4 is a partial cross-sectional view showing a deformed state of the sleeve at the time of temperature rise.
~ Fig. 7 is a second view of the rolling bearing supporting sleeve of the present invention ~
Sectional views similar to FIG. 1 and FIG.
FIG. 1 is a sectional view showing an example of a conventional rotary shaft support portion. 1: rotating shaft, 2: housing, 3: wall surface, 4: receiving recess, 5: outer ring,
6: Rolling element, 7: Inner raceway, 8: Rolling bearing support sleeve,
9: core material, 10: spacer portion, 11: concave groove, 12: through hole, 13: inner peripheral side flat portion, 14: outer peripheral side flat portion, 15: inclined portion, 16: convex portion, 17: outer peripheral surface, 18: rolling bearing, 19: outer ring, 20: rolling bearing with sleeve, 21: inner race, 22: cage, 23: rolling element, 24: arc portion, 25: flat portion.
Claims (2)
この芯材の外周面に形成された凹溝部分に積層された合
成樹脂製のスペーサ部とから成り、このうちの芯材は、
軸方向に亙る断面形状を屈曲させる事により外周面に上
記凹溝を設けており、この芯材の軸と直角方向の断面形
状は円形であり、この芯材は、上記凹溝から外れた部分
に付与された半径方向の弾力に基づき、周面を抑え付け
られない自由状態に於いて半径方向の厚さ寸法を大きく
するものであり、常温時に上記芯材の周面を抑え付けた
状態で、この芯材の一部外周面と上記スペーサ部の一部
外周面とが単一の外周面を構成する転がり軸受支持用ス
リーブ。1. A core material made of a metal plate and made entirely into a tubular shape,
The core material is composed of a synthetic resin spacer portion laminated on the concave groove portion formed on the outer peripheral surface of the core material.
The concave groove is provided on the outer peripheral surface by bending the cross-sectional shape in the axial direction, and the cross-sectional shape of the core material in the direction perpendicular to the axis is circular, and the core material is a portion separated from the concave groove. Based on the elastic force in the radial direction applied to the, the thickness of the radial direction is increased in the free state where the circumferential surface cannot be held down. A rolling bearing supporting sleeve in which a part of the outer peripheral surface of the core member and a part of the outer peripheral surface of the spacer portion form a single outer peripheral surface.
孔を有し、合成樹脂製のスペーサ部の内周面の一部が、
この透孔と結合している、請求項１に記載の転がり軸受
支持用スリーブ。2. A core material made of metal has a plurality of through holes in the circumferential direction, and a part of an inner peripheral surface of a spacer portion made of synthetic resin,
The rolling bearing supporting sleeve according to claim 1, which is connected to the through hole.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1989055253U JPH0752421Y2 (en) | 1989-05-16 | 1989-05-16 | Rolling bearing support sleeve |
| US07/515,937 US5062721A (en) | 1989-04-28 | 1990-04-27 | Rolling bearing with sleeve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1989055253U JPH0752421Y2 (en) | 1989-05-16 | 1989-05-16 | Rolling bearing support sleeve |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH02146213U JPH02146213U (en) | 1990-12-12 |
| JPH0752421Y2 true JPH0752421Y2 (en) | 1995-11-29 |
Family
ID=31578036
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1989055253U Expired - Lifetime JPH0752421Y2 (en) | 1989-04-28 | 1989-05-16 | Rolling bearing support sleeve |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0752421Y2 (en) |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS4422006Y1 (en) * | 1965-07-05 | 1969-09-18 |
-
1989
- 1989-05-16 JP JP1989055253U patent/JPH0752421Y2/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| JPH02146213U (en) | 1990-12-12 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| JPH026264Y2 (en) | ||
| US7610671B2 (en) | Method for assembling an electric motor using a slip fit tolerance ring | |
| JPH0599223A (en) | Antifriction bearing | |
| JPH1082428A (en) | Creep prevention device of rolling bearing | |
| JPS63158316A (en) | Thrust bearing | |
| US5758978A (en) | Thrust ball bearing | |
| JPH0752421Y2 (en) | Rolling bearing support sleeve | |
| US3529874A (en) | Bearing structure | |
| JP2743458B2 (en) | Rolling shaft support device with rolling bearing support sleeve, sleeved rolling bearing and sleeved rolling bearing | |
| US6310415B1 (en) | Bearing structures for a motor rotor | |
| US2812987A (en) | Bearing mounting structures | |
| JP4004115B2 (en) | Supercharger and supercharger assembly method | |
| JPH10339323A (en) | Slide bearing and motor | |
| JP2000120670A (en) | Rolling bearing | |
| JP4864341B2 (en) | Electric actuator | |
| JPH064090Y2 (en) | Rolling bearing support sleeve | |
| JP3737860B2 (en) | Thrust ball bearing | |
| MXPA06002027A (en) | Limited swivel self-aligning bearing assembly. | |
| JP3342750B2 (en) | Sealing device for rolling bearings | |
| JPH10153217A (en) | Synthetic resin holder for cylindrical roller bearing | |
| JP3731246B2 (en) | Manufacturing method of bearing | |
| JP2003134719A (en) | Electric motor | |
| JP3632358B2 (en) | Friction roller type transmission assembly method | |
| JP7222329B2 (en) | bearing device | |
| JPH0725849Y2 (en) | Spindle head spindle support device |