JP2002250345A - Cage for rolling bearing for turbocharger and rotary support device for turbocharger - Google Patents

Cage for rolling bearing for turbocharger and rotary support device for turbocharger

Info

Publication number
JP2002250345A
JP2002250345A JP2001046610A JP2001046610A JP2002250345A JP 2002250345 A JP2002250345 A JP 2002250345A JP 2001046610 A JP2001046610 A JP 2001046610A JP 2001046610 A JP2001046610 A JP 2001046610A JP 2002250345 A JP2002250345 A JP 2002250345A
Authority
JP
Japan
Prior art keywords
turbocharger
peripheral surface
cage
retainer
bearing
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.)
Pending
Application number
JP2001046610A
Other languages
Japanese (ja)
Inventor
Kenji Yakura
健二 矢倉
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
NSK Ltd
Original Assignee
NSK Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by NSK Ltd filed Critical NSK Ltd
Priority to JP2001046610A priority Critical patent/JP2002250345A/en
Publication of JP2002250345A publication Critical patent/JP2002250345A/en
Pending legal-status Critical Current

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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/38—Ball cages
    • 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
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/16—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls
    • F16C19/163—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls with angular contact
    • 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
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/54—Systems consisting of a plurality of bearings with rolling friction
    • F16C19/546—Systems with spaced apart rolling bearings including at least one angular contact bearing
    • F16C19/547—Systems with spaced apart rolling bearings including at least one angular contact bearing with two angular contact rolling bearings
    • F16C19/548—Systems with spaced apart rolling bearings including at least one angular contact bearing with two angular contact rolling bearings in O-arrangement
    • 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
    • F16C2360/00—Engines or pumps
    • F16C2360/23—Gas turbine engines
    • F16C2360/24—Turbochargers

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Supercharger (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

PROBLEM TO BE SOLVED: To prevent the reduction of durability of a rolling bearing, namely, a turbocharger, due to a burr on the outer peripheral face of a cage formed accompanied with injection molding. SOLUTION: A groove 25 recessed inward in the radial direction from the outer peripheral face of an intermediate part in the axial direction of the cage 14b is provided over the whole periphery of the outer peripheral face. Moreover, the burr formed at end fringes of abutting faces of molds in a cavity when the injection molding is performed exists on the bottom face of the groove 25. When the depth of the groove 25 is h and the thickness in the radial direction of the cage 14b is H, h/H is 0.01 to 0.4. As a result, the strength of the cage 14b can be ensured, and it is possible to prevent lubricating oil fed into a ball bearing not to satisfactorily spread to parts to be lubricated, due to the burr.

Description

【発明の詳細な説明】DETAILED DESCRIPTION OF THE INVENTION

【０００１】[0001]

【発明の属する技術分野】本発明のターボチャージャ用
転がり軸受の保持器とターボチャージャ用回転支持装置
は、例えば自動車用エンジンの出力を向上させる為のタ
ーボチャージャの回転支持部を構成する転がり軸受（主
として玉軸受）の改良に関する。特に本発明は、この転
がり軸受の潤滑性能の向上を図り、優れた耐久性を有す
るターボチャージャ用回転支持装置を実現するものであ
る。BACKGROUND OF THE INVENTION A cage for a turbocharger rolling bearing and a turbocharger rotary support device according to the present invention are, for example, a rolling bearing (a rotary support portion constituting a rotary support portion of a turbocharger for improving the output of an automobile engine). (Mainly ball bearings). In particular, the present invention aims to improve the lubricating performance of the rolling bearing and realize a rotation supporting device for a turbocharger having excellent durability.

【０００２】[0002]

【従来の技術】エンジンの出力を排気量を変えずに増大
させる為、エンジンに送り込む空気を排気のエネルギに
より圧縮するターボチャージャが、広く使用されてい
る。このターボチャージャは、排気のエネルギを、排気
通路の途中に設けたタービンにより回収し、このタービ
ンをその端部に固定した回転軸により、給気通路の途中
に設けたコンプレッサのインペラを回転させる。このイ
ンペラは、エンジンの運転に伴って数万乃至は十数万mi
n-1 （r.p.m.）の速度で回転し、上記給気通路を通じて
エンジンに送り込まれる空気を圧縮する。2. Description of the Related Art In order to increase the output of an engine without changing the displacement, a turbocharger for compressing air sent to the engine by the energy of the exhaust is widely used. This turbocharger collects the energy of exhaust gas by a turbine provided in the middle of the exhaust passage, and rotates an impeller of a compressor provided in the middle of the air supply passage by a rotating shaft fixed to an end of the turbine. This impeller can be tens of thousands or hundreds of thousands of mi with the operation of the engine.
It rotates at a speed of n -1 (rpm) and compresses the air sent to the engine through the air supply passage.

【０００３】図３〜４は、この様なターボチャージャの
１例を示している。このターボチャージャは、排気流路
１を流通する排気により、回転軸２の一端（図３の左
端）に固定したタービン３を回転させる。この回転軸２
の回転は、この回転軸２の他端（図３の右端）に固定し
たインペラ４に伝わり、このインペラ４が給気流路５内
で回転する。この結果、この給気流路５の上流端開口か
ら吸引された空気が圧縮されて、ガソリン、軽油等の燃
料と共にエンジンのシリンダ室内に送り込まれる。この
様なターボチャージャの回転軸２は、数万〜十数万min
-1 もの高速で回転し、しかも、エンジンの運転状況に
応じてその回転速度が頻繁に変化する。従って、上記回
転軸２は、軸受ハウジング６に対し、小さな回転抵抗で
支持する必要がある。FIGS. 3 and 4 show an example of such a turbocharger. The turbocharger rotates the turbine 3 fixed to one end (the left end in FIG. 3) of the rotating shaft 2 by exhaust gas flowing through the exhaust passage 1. This rotating shaft 2
Is transmitted to the impeller 4 fixed to the other end (the right end in FIG. 3) of the rotating shaft 2, and the impeller 4 rotates in the air supply flow path 5. As a result, the air sucked from the upstream end opening of the air supply passage 5 is compressed and sent into the cylinder chamber of the engine together with fuel such as gasoline or light oil. The rotation axis 2 of such a turbocharger is tens of thousands to several hundred thousand minutes.
It rotates at a high speed of -1 , and its rotation speed changes frequently depending on the operating conditions of the engine. Therefore, the rotating shaft 2 needs to be supported by the bearing housing 6 with a small rotation resistance.

【０００４】この為に従来から、上記軸受ハウジング６
の内側に上記回転軸２を、請求項に記載した転がり軸受
に相当する第一、第二の玉軸受７、８により、回転自在
に支持している。これら第一、第二の玉軸受７、８は、
図５に示す様なアンギュラ型玉軸受であって、これら第
一、第二の玉軸受７、８の構成は、基本的には同じであ
る。但し、これら両玉軸受７、８のうち、高温の排気が
流通する排気流路１に近く、温度上昇が著しい第一の玉
軸受７の潤滑条件は、低温の空気が流通する給気流路５
に近く、温度上昇がそれ程著しくはない、第二の玉軸受
８に比べて厳しい。For this reason, conventionally, the bearing housing 6
The rotating shaft 2 is rotatably supported by the first and second ball bearings 7 and 8 corresponding to the rolling bearing described in the claims. These first and second ball bearings 7, 8
This is an angular type ball bearing as shown in FIG. 5, and the configuration of the first and second ball bearings 7, 8 is basically the same. However, of these two ball bearings 7, 8, the lubrication condition of the first ball bearing 7, which is close to the exhaust passage 1 through which high-temperature exhaust flows and whose temperature rises remarkably, is determined by the air supply passage 5 through which low-temperature air flows.
, And the temperature rise is not so significant, which is more severe than that of the second ball bearing 8.

【０００５】この様な第一、第二の玉軸受７、８は、内
周面に外輪軌道９を有する外輪１０と、外周面に内輪軌
道１１を有する内輪１２と、これら外輪軌道９と内輪軌
道１１との間に転動自在に設けられた、それぞれが請求
項に記載した転動体に相当する、複数個の玉１３、１３
とを備える。又、これら各玉１３、１３は、円環状の保
持器１４に設けた複数のポケット１５内に、それぞれ１
個ずつ転動自在に保持している。又、図示の例の場合に
は、上記内輪１２を、片側の肩部をなくした、所謂カウ
ンタボアとしている。又、上記保持器１４の外周面を、
上記外輪１０の内周面に近接対向させる事により、この
保持器１４の直径方向位置をこの外輪１０により規制す
る、外輪案内としている。The first and second ball bearings 7 and 8 have an outer race 10 having an outer race 9 on an inner peripheral surface, an inner race 12 having an inner race 11 on an outer peripheral surface, and the outer race 9 and the inner race. A plurality of balls 13, 13 each rotatably provided between the track 11 and each corresponding to a rolling element described in the claims.
And Each of these balls 13, 13 is placed in a plurality of pockets 15 provided in an annular retainer 14, respectively.
It is held so that it can roll freely one by one. In the illustrated example, the inner ring 12 has a so-called counter bore in which one shoulder is not provided. Further, the outer peripheral surface of the cage 14 is
An outer ring guide is provided in which the diametrical position of the retainer 14 is regulated by the outer ring 10 by being opposed to the inner peripheral surface of the outer ring 10.

【０００６】この様な第一、第二の玉軸受７、８のうち
の第一の玉軸受７は、上記外輪１０を、前記軸受ハウジ
ング６の一端部（図３〜４の左端部）に内嵌すると共
に、上記内輪１２を上記回転軸２の一端部に外嵌固定す
る事により、この回転軸２の一端部を上記軸受ハウジン
グ６に対し、回転自在に支持している。一方、上記第二
の玉軸受８は、外輪１０を軸受ハウジング６の他端部
（図３〜４の右端部）に内嵌すると共に、内輪１２を上
記回転軸２の他端部に外嵌固定する事により、この回転
軸２の他端部を上記軸受ハウジング６に対し、回転自在
に支持している。又、上記第一、第二の玉軸受７、８を
構成する１対の外輪１０、１０には、圧縮ばね１６によ
り互いに離れる方向の弾力を付与している。即ち、これ
ら両外輪１０、１０の互いに対向する端面にそれぞれ押
圧環１７、１７を突き合わせ、これら両押圧環１７、１
７同士の間に上記圧縮ばね１６を挟持している。従っ
て、上記第一、第二の玉軸受７、８は、互いに接触角の
方向を逆にした状態｛背面組み合せ（ＤＢ）型｝で組み
込まれている。The first ball bearing 7 of the first and second ball bearings 7 and 8 has the outer ring 10 attached to one end of the bearing housing 6 (the left end in FIGS. 3 and 4). The inner ring 12 is fitted inside and the outer ring 12 is fixed to the one end of the rotary shaft 2 so that one end of the rotary shaft 2 is rotatably supported by the bearing housing 6. On the other hand, in the second ball bearing 8, the outer ring 10 is internally fitted to the other end of the bearing housing 6 (the right end in FIGS. 3 to 4), and the inner ring 12 is externally fitted to the other end of the rotary shaft 2. By fixing, the other end of the rotating shaft 2 is rotatably supported on the bearing housing 6. Further, a pair of outer races 10, 10 constituting the first and second ball bearings 7, 8 are provided with elasticity in a direction away from each other by a compression spring 16. That is, the pressing rings 17, 17 abut against the end faces of the outer rings 10, 10 facing each other, respectively.
The compression spring 16 is sandwiched between the members 7. Therefore, the first and second ball bearings 7 and 8 are assembled in a state where the directions of the contact angles are reversed with each other (back-side combination (DB) type).

【０００７】更に、上記軸受ハウジング６を納めたケー
シング１８内に給油通路１９を設け、この軸受ハウジン
グ６並びに上記第一、第二の玉軸受７、８を、冷却及び
潤滑自在としている。即ち、ターボチャージャを装着し
たエンジンの運転時に潤滑油は、上記給油通路１９の上
流端に設けたフィルタ２０により異物を除去されて、上
記ケーシング１８の内周面と上記軸受ハウジング６の外
周面との間に設けた、円環状の隙間空間２１に送り込ま
れる。尚、この隙間空間２１は、上記軸受ハウジング６
とケーシング１８との嵌合を隙間嵌にする事により設け
ている。そして、この隙間空間２１を上記潤滑油で満た
す事により、上記軸受ハウジング６の外周面と上記ケー
シング１８の内周面との間に全周に亙って油膜（オイル
フィルム）を形成し、これらケーシング１８及び軸受ハ
ウジング６を冷却すると共に、上記回転軸２の回転に基
づく振動を減衰する、オイルフィルムダンパを構成して
いる。更に、上記隙間空間２１に送り込まれた潤滑油の
一部は、上記外輪１０に隣接する押圧環１７に設けたノ
ズル孔２２から、上記第一の玉軸受７を構成する内輪１
２の外周面に向け、径方向外方から斜めに噴出し、この
第一の玉軸受７を冷却及び潤滑（オイルジェット潤滑）
する。この様にして第一の玉軸受７に送り込まれた潤滑
油は、この第一の玉軸受７の他、上記第二の玉軸受８も
冷却及び潤滑してから、排油口２３より排出される。Further, an oil supply passage 19 is provided in a casing 18 accommodating the bearing housing 6, so that the bearing housing 6 and the first and second ball bearings 7, 8 can be cooled and lubricated freely. That is, during operation of the engine equipped with the turbocharger, the lubricating oil is freed of foreign matter by the filter 20 provided at the upstream end of the oil supply passage 19, and the lubricating oil contacts the inner peripheral surface of the casing 18 and the outer peripheral surface of the bearing housing 6. And is fed into an annular gap space 21 provided between them. In addition, this clearance space 21 is provided in the bearing housing 6.
It is provided by fitting a gap between the casing and the casing 18. By filling the gap space 21 with the lubricating oil, an oil film (oil film) is formed over the entire circumference between the outer peripheral surface of the bearing housing 6 and the inner peripheral surface of the casing 18. An oil film damper is configured to cool the casing 18 and the bearing housing 6 and attenuate vibrations caused by the rotation of the rotary shaft 2. Further, a part of the lubricating oil sent into the gap space 21 is supplied from the nozzle hole 22 provided in the pressing ring 17 adjacent to the outer ring 10 to the inner ring 1 forming the first ball bearing 7.
2 to the outer peripheral surface of the first ball bearing 7 obliquely jetted from outside in the radial direction to cool and lubricate the first ball bearing 7 (oil jet lubrication).
I do. The lubricating oil sent to the first ball bearing 7 in this way cools and lubricates the second ball bearing 8 in addition to the first ball bearing 7, and then is discharged from the oil discharge port 23. You.

【０００８】尚、図示の例の場合、軸受ハウジング６の
内周面と第一、第二の玉軸受７、８の外周面との間に
も、それぞれ隙間空間２４、２４が存在している。そし
て、これら各隙間空間２４、２４にも上記潤滑油が満た
されており、上記回転軸２の回転に基づく振動の減衰を
図っている。又、図示は省略するが、軸受ハウジングと
ケーシングとを一体に形成する場合もある。この様な場
合は、少なくとも何れかの玉軸受の外周面と軸受ハウジ
ング（ケーシング）の内周面との間に隙間空間を設け、
この隙間空間を上述の様に潤滑油で満たす事により、回
転軸の回転に基づく振動の減衰を図る。又、この隙間空
間に送り込まれた潤滑油の一部を上記玉軸受に向けて送
り込む事により、この玉軸受の冷却及び潤滑を行なう。In the case of the illustrated example, gap spaces 24 are also provided between the inner peripheral surface of the bearing housing 6 and the outer peripheral surfaces of the first and second ball bearings 7 and 8, respectively. . Each of the clearance spaces 24 is also filled with the lubricating oil, thereby attenuating vibration caused by rotation of the rotating shaft 2. Although not shown, the bearing housing and the casing may be integrally formed. In such a case, a clearance space is provided between at least one of the outer peripheral surface of the ball bearing and the inner peripheral surface of the bearing housing (casing).
By filling the gap with the lubricating oil as described above, the vibration due to the rotation of the rotating shaft is attenuated. Further, by cooling a part of the lubricating oil fed into the gap space toward the ball bearing, the ball bearing is cooled and lubricated.

【０００９】ところで、上述の様なターボチャージャ用
回転支持装置の運転時に前記タービン３は、最高で１０
００℃近くの排気ガスに曝される。この為、前記回転軸
２を支持する第一、第二の玉軸受７、８、特にタービン
３側の第一の玉軸受７は、潤滑油による冷却が行なわれ
ていても、１５０℃以上（最高で３００℃程度）の高温
となる場合がある。そして、この様な高温環境で使用す
る第一、第二の玉軸受７、８を構成する保持器１４とし
て近年、耐熱性を有する合成樹脂製のものが一般に使用
されている。During operation of the above-described turbocharger rotation support device, the turbine 3 is operated at a maximum of 10
It is exposed to exhaust gas near 00 ° C. For this reason, the first and second ball bearings 7 and 8 that support the rotary shaft 2, particularly the first ball bearing 7 on the turbine 3 side, are at least 150 ° C. even when cooled by lubricating oil. (Up to about 300 ° C.). In recent years, a cage made of heat-resistant synthetic resin has been generally used as the cage 14 constituting the first and second ball bearings 7 and 8 used in such a high-temperature environment.

【００１０】この様な合成樹脂としては、耐熱性の確保
の面から熱硬化性樹脂、例えば熱硬化性のポリイミド系
樹脂を使用する事が考えられる。ところが、この様な熱
硬化性樹脂の場合、切削加工により上記保持器を造る必
要があり、製造コストが嵩む事が避けられない。これに
対して、合成樹脂として熱可塑性樹脂、例えば熱可塑性
のポリイミド系樹脂を使用すれば、金型を使用する射出
成形によって大量生産が容易となり、製造コストの大幅
な低減を図れる。又、上記熱硬化性樹脂に比べて耐熱性
の面で劣る上記熱可塑性樹脂に就いても、近年の技術進
歩により、耐熱性を確保できる様になってきた。As such a synthetic resin, it is conceivable to use a thermosetting resin, for example, a thermosetting polyimide resin from the viewpoint of securing heat resistance. However, in the case of such a thermosetting resin, it is necessary to manufacture the retainer by a cutting process, which inevitably increases the manufacturing cost. On the other hand, if a thermoplastic resin, for example, a thermoplastic polyimide resin is used as the synthetic resin, mass production is facilitated by injection molding using a mold, and the production cost can be significantly reduced. Further, even with respect to the thermoplastic resin, which is inferior in heat resistance as compared with the thermosetting resin, heat resistance can be ensured due to recent technological advances.

【００１１】ところが、この様な熱可塑性樹脂の場合、
耐熱性を確保できても、射出成形に伴って生じるばり
が、上記保持器の周面に形成される事が避けられない。
即ち、射出成形の際に、上記保持器を成形するキャビテ
ィを構成する為の金型同士の合わせ面部分に生じる不可
避的な微小隙間に合成樹脂が侵入し、この保持器の周面
にこの周面から突出した状態で上記ばりが形成される。
この様な保持器の周面、特に保持器案内面となるこの保
持器の外周面に形成された上記ばりは、ターボチャージ
ャの運転中に、外輪１０の内周面でこの保持器の外周面
と対向する部分に付着した潤滑油を掻き取って、これら
外輪１０の内周面と保持器１４の外周面との摺動部の摩
擦抵抗を大きくする可能性がある。この様な不都合を防
止する為には、上記保持器の周面に形成されたばりを取
り除く事が考えられるが、この様なばり取り作業は面倒
で加工コストが嵩む為、好ましくない。However, in the case of such a thermoplastic resin,
Even if the heat resistance can be ensured, it is inevitable that burrs generated by injection molding are formed on the peripheral surface of the cage.
That is, at the time of injection molding, synthetic resin penetrates into an unavoidable minute gap generated in a mating surface portion of the dies for forming the cavity for molding the retainer, and the peripheral surface of the retainer has this peripheral portion. The burrs are formed so as to protrude from the surface.
During the operation of the turbocharger, the above-mentioned burrs formed on the outer peripheral surface of the outer ring 10 during operation of the turbocharger are formed on the outer peripheral surface of the outer peripheral surface of the retainer. There is a possibility that the frictional resistance of the sliding portion between the inner peripheral surface of the outer ring 10 and the outer peripheral surface of the retainer 14 may be increased by scraping off the lubricating oil adhering to the portion opposed to the outer ring 10. In order to prevent such inconvenience, it is conceivable to remove burrs formed on the peripheral surface of the retainer. However, such a deburring operation is not preferable because it is troublesome and the processing cost increases.

【００１２】一方、国際公開ＷＯ９９／０１６７６号公
報には、図６に示す様な、熱可塑性樹脂により造られた
保持器１４ａの発明が記載されている。この保持器１４
ａは、全体が円環状で、それぞれが円筒状の複数のポケ
ット１５、１５を円周方向に亙り間欠的に設けたもみ抜
き型の保持器であり、この保持器１４ａの軸方向中間部
外周面に、径方向内方に凹入した凹溝２５を全周に亙っ
て設けている。そして、この凹溝２５の底面で上記各ポ
ケット１５、１５同士の間部分に、射出成形の際に金型
同士の合わせ面の端縁によって形成される筋状のばり
（パーティングライン）２６、２６を位置させている。
即ち、この保持器１４ａは、図７〜８に示す様に、円柱
状の内側金型２７の外周面に円周方向に亙り複数個（図
示の例は７個）の外側金型２８、２８を配置すると共
に、これら各外側金型２８、２８の軸方向両側に円輪状
の側面側金型２９、２９を配置し、これら各金型２７、
２８、２９によって形成されるキャビティ３０内に合成
樹脂を送り込み、上記保持器１４ａを形成している。上
記各外側金型２８、２８同士の合わせ面を、上記キャビ
ティ３０内で上記凹溝２５の底面を形成する部分に位置
させる事により、これら各外側金型２８、２８同士の合
わせ面の端縁によって生じる上記ばり２６、２６を、上
記凹溝２５の底面に形成している。この様にばり２６、
２６を上記凹溝２５の底面に存在させた分、これら各ば
り２６、２６による上述の様な潤滑油の掻き取りを防止
できる。On the other hand, International Publication WO99 / 01676 discloses an invention of a retainer 14a made of a thermoplastic resin as shown in FIG. This cage 14
Reference numeral a denotes a machined-type retainer in which a plurality of pockets 15, 15 each having an annular shape and each having a cylindrical shape are provided intermittently in the circumferential direction, and an outer periphery of an intermediate portion in the axial direction of the retainer 14a. On the surface, a concave groove 25 recessed inward in the radial direction is provided over the entire circumference. A streak-like flash (parting line) 26 formed by the edges of the mating surfaces of the dies at the time of injection molding is formed in the portion between the pockets 15 on the bottom surface of the concave groove 25. 26 is located.
That is, as shown in FIGS. 7 and 8, a plurality of (seven in the illustrated example) outer molds 28 are provided on the outer peripheral surface of the cylindrical inner mold 27 in the circumferential direction. Are arranged, and annular side molds 29, 29 are arranged on both axial sides of the outer molds 28, 28, respectively.
Synthetic resin is fed into a cavity 30 formed by 28 and 29 to form the retainer 14a. By positioning the mating surface between the outer molds 28, 28 at the portion forming the bottom surface of the groove 25 in the cavity 30, the edge of the mating surface between the outer molds 28, 28 is formed. The burrs 26, 26 generated by the above are formed on the bottom surface of the concave groove 25. Like this, 26
The lubrication oil can be prevented from being scraped off by the burrs 26, 26 by the presence of the 26 on the bottom surface of the concave groove 25.

【００１３】[0013]

【発明が解決しようとする課題】上述の様な国際公開Ｗ
Ｏ９９／０１６７６号公報に記載された構造の様に、保
持器１４ａの外周面に全周に亙って凹溝２５を設けると
共に、この凹溝２５の底面で各ポケット１５、１５同士
の間部にばり２６、２６を存在させた場合には、この様
なばり２６、２６の存在に拘わらず、潤滑油を掻き揚げ
にくくする事ができる可能性がある。但し、各部の諸元
を十分に検討していない為、必ずしも十分な効果を得ら
れない。SUMMARY OF THE INVENTION As described above, the international publication W
As in the structure described in Japanese Patent Application Publication No. O99 / 01676, a concave groove 25 is provided on the outer peripheral surface of the retainer 14a over the entire circumference, and the bottom surface of the concave groove 25 is provided between the pockets 15 and 15. When the burrs 26, 26 are present, there is a possibility that lubricating oil can be hardly scooped irrespective of the presence of such burrs 26, 26. However, since the specifications of each part are not sufficiently considered, a sufficient effect cannot always be obtained.

【００１４】即ち、上記凹溝２５の深さｈ｛保持器１４
ａの両端部で凹溝２５から外れた部分の外周面と凹溝２
５の底面との段差｝が小さく（浅く）なり過ぎると、こ
の凹溝２５の底面に形成された上記ばり２６、２６が上
記保持器１４ａの外周面よりも径方向外方に突出してし
まう。この結果、この様な保持器１４ａの外周面よりも
突出したばり２６、２６の先端縁が、外輪１０（図５）
の内周面でこれら各ばり２６、２６の先端縁が対向する
部分に付着した潤滑油を掻き取り、上記保持器１４ａの
外周面と外輪１０の内周面との摺動部の摩擦抵抗を大き
くする。そして、この摺動部での摩擦に基づく発熱が著
しくなり、焼き付き等の損傷が生じる可能性が大きくな
る。特に、上記保持器１４ａが軸方向に変位し、上記各
ばり２６、２６が、上記外輪１０の内周面のうちで上記
保持器１４ａの外周面との摺接面の一部に付着した潤滑
油を掻き取ると、潤滑不良の程度が著しくなる。これに
対して、上記凹溝２５の深さｈが大きく（深く）なり過
ぎると、上記保持器１４ａの内周面と上記凹溝２５の底
面との厚さ（保持器１４ａの厚さＨ−凹溝２５の深さ
ｈ）が小さく（薄く）なり過ぎて、この保持器１４ａの
強度を確保しにくくなる。この結果、この保持器１４ａ
が破損し易くなり、ターボチャージャの耐久性を低下さ
せる可能性がある。特に、ターボチャージャ用回転支持
装置を構成する、内輪１２の内径が１０mm程度である第
一、第二の玉軸受７、８に組み込む保持器１４ａの場
合、上記厚さＨが１〜２mm程度しかない為、上記深さｈ
を大きくし過ぎる事に伴う強度低下には十分に考慮しな
ければならない。本発明は、この様な事情に鑑みて、タ
ーボチャージャ用回転支持装置を構成する玉軸受の保持
器の寸法の適正化を図り、この玉軸受延てはターボチャ
ージャの耐久性を確保すべく発明したものである。That is, the depth h of the groove 25 and the cage 14
a of the outer peripheral surface of the portion deviated from the groove 25 at both ends and the groove 2
5 becomes too small (shallow), the burrs 26 formed on the bottom surface of the concave groove 25 project radially outward from the outer peripheral surface of the retainer 14a. As a result, the leading edges of the burrs 26 projecting beyond the outer peripheral surface of the retainer 14a are connected to the outer race 10 (FIG. 5).
The lubricating oil adhering to the portions of the inner peripheral surfaces of the burrs 26, 26 where the leading edges of the burrs oppose is scraped off, and the frictional resistance of the sliding portion between the outer peripheral surface of the retainer 14a and the inner peripheral surface of the outer ring 10 is reduced. Enlarge. Then, the heat generated by the friction in the sliding portion becomes remarkable, and the possibility of damage such as image sticking increases. In particular, the retainer 14a is displaced in the axial direction, and the burrs 26, 26 are attached to a part of the inner peripheral surface of the outer ring 10 which is in sliding contact with the outer peripheral surface of the retainer 14a. When the oil is scraped, the degree of poor lubrication becomes significant. On the other hand, when the depth h of the concave groove 25 becomes too large (deep), the thickness between the inner peripheral surface of the retainer 14a and the bottom surface of the concave groove 25 (the thickness H− The depth h) of the concave groove 25 becomes too small (thin), and it becomes difficult to secure the strength of the retainer 14a. As a result, this cage 14a
May be easily damaged, and the durability of the turbocharger may be reduced. Particularly, in the case of the cage 14a incorporated in the first and second ball bearings 7 and 8 in which the inner diameter of the inner ring 12 is about 10 mm, which constitutes the turbocharger rotation support device, the thickness H is only about 1 to 2 mm. No depth h
It is necessary to give due consideration to the decrease in strength caused by making the value too large. In view of such circumstances, the present invention aims at optimizing the dimensions of a ball bearing retainer constituting a rotary support device for a turbocharger, and in order to ensure the durability of the turbocharger, It was done.

【００１５】[0015]

【課題を解決するための手段】本発明のターボチャージ
ャ用転がり軸受の保持器とターボチャージャ用回転支持
装置のうち、請求項１に記載したターボチャージャ用転
がり軸受の保持器は、ターボチャージャの回転軸を軸受
ハウジングの内側に回転自在に支持する為の転がり軸受
に組み込んで、この転がり軸受を構成する複数個の転動
体を転動自在に保持する為、全体が円環状で、これら各
転動体を保持する為の複数のポケットを円周方向に亙り
間欠的に設けている。この様な本発明のターボチャージ
ャ用転がり軸受の保持器は、合成樹脂の射出成形により
造られており、軸方向中間部外周面に径方向内方に凹入
した凹溝を全周に亙って設けると共に、射出成形の際に
キャビティ内の金型同士の合わせ面の端縁によって形成
されるばりを、上記凹溝の底面で上記ポケット同士の間
部に存在させている。更に、上記保持器の径方向の厚さ
Ｈが１〜２mmであり、上記凹溝の深さをｈとした場合
に、ｈ／Ｈが０．０１〜０．４（更に好ましくは０．０
５〜０．２５）である。According to a first aspect of the present invention, there is provided a turbocharger rolling bearing retainer and a turbocharger rotation support device, wherein the turbocharger rolling bearing retainer according to the first aspect of the present invention is a turbocharger rotating bearing. The shaft is incorporated into a rolling bearing for rotatably supporting the shaft inside the bearing housing, and a plurality of rolling elements constituting the rolling bearing are rotatably held. Are provided intermittently in the circumferential direction. Such a cage of the rolling bearing for a turbocharger of the present invention is made by injection molding of a synthetic resin, and has a concave groove which is recessed inward in the radial direction on the outer peripheral surface of the axially intermediate portion over the entire circumference. In addition, the burrs formed by the edges of the mating surfaces of the dies in the cavity during the injection molding are present between the pockets on the bottom surface of the concave groove. Further, when the radial thickness H of the cage is 1 to 2 mm and the depth of the concave groove is h, h / H is 0.01 to 0.4 (more preferably 0.0 to 0.4).
5 to 0.25).

【００１６】更に、請求項２に記載したターボチャージ
ャ用回転支持装置は、前述した従来から知られているタ
ーボチャージャ用回転支持装置と同様に、一端部にター
ビンを、他端部にインペラを、それぞれ固定した回転軸
を、軸受ハウジングの内側に回転自在に支持するもので
ある。そして、この為に、この軸受ハウジングの内周面
と上記回転軸の外周面との間に、外輪の内周面に形成し
た外輪軌道と内輪の外周面に形成した内輪軌道との間に
保持器により保持された複数個の転動体を転動自在に配
置して成る転がり軸受を設けている。そして、この転が
り軸受に向けて潤滑油を送り込む事により、この転がり
軸受の潤滑を行なう様に構成している。特に、本発明の
ターボチャージャ用回転支持装置に於いては、上記保持
器を請求項１に記載したターボチャージャ用転がり軸受
の保持器としている。Further, the turbocharger rotary support device according to the second aspect of the present invention has a turbine at one end and an impeller at the other end, similarly to the above-described conventional rotary support device for a turbocharger. The fixed rotating shafts are rotatably supported inside the bearing housing. And, for this purpose, it is held between the inner peripheral surface of the bearing housing and the outer peripheral surface of the rotating shaft, between the outer raceway formed on the inner peripheral surface of the outer race and the inner raceway formed on the outer peripheral surface of the inner race. A rolling bearing is provided in which a plurality of rolling elements held by a container are arranged so as to freely roll. Then, lubrication of the rolling bearing is performed by feeding lubricating oil toward the rolling bearing. In particular, in the rotation supporting device for a turbocharger according to the present invention, the retainer is a retainer for a rolling bearing for a turbocharger according to the first aspect.

【００１７】[0017]

【作用】上述の様に構成する本発明のターボチャージャ
用転がり軸受の保持器とターボチャージャ用回転支持装
置の場合には、保持器の強度を確保し、しかも、射出成
形の際に金型同士の合わせ面の端縁によって凹溝に形成
された筋状のばりが、上記転がり軸受の潤滑すべき部分
に潤滑油を行き渡りにくくする事を有効に防止できる。
この為、射出成形により低コストで造れる保持器に拘わ
らず、上記転がり軸受延てはターボチャージャの耐久性
を、高次元で確保できる。In the case of the turbocharger rolling bearing retainer and the turbocharger rotary support device of the present invention configured as described above, the strength of the retainer is ensured, and the dies are joined together during injection molding. It is possible to effectively prevent the streaky burrs formed in the concave grooves by the edges of the mating surfaces from making it difficult for the lubricating oil to spread to the lubricating portions of the rolling bearing.
For this reason, the durability of the above-mentioned rolling bearings and the turbocharger can be ensured at a high level, irrespective of the cage formed at low cost by injection molding.

【００１８】尚、上記保持器の厚さＨと上記凹溝の深さ
ｈとの比ｈ／Ｈが０．０１未満の場合には、この凹溝の
深さｈが小さく（浅く）なり過ぎて、上記ばりが上記保
持器の両端部外周面よりも径方向外方に突出する可能性
が大きくなる。そして、突出した場合には、上記転がり
軸受に送り込まれて外輪の内周面に付着した潤滑油がこ
のばりにより掻き取られて、保持器の外周面と外輪の内
周面との摺動部に存在する潤滑油が不足する可能性が生
じる。そして、不足した場合には、上記両周面同士の摺
動部の摩擦抵抗が大きくなる結果、上記転がり軸受が高
温化し易くなると共に、上記保持器と上記外輪との摺動
部に異常摩耗や焼き付き等の損傷が生じる可能性が大き
くなる。一方、上記比ｈ／Ｈが０．４を越えた場合に
は、円周方向に隣り合うポケット同士の間に存在する柱
部の肉厚、即ち、上記保持器の内周面と上記凹溝の底面
との間の肉厚ｔ（＝Ｈ−ｈ）が小さく（薄く）なり過ぎ
て、上記柱部の強度が不十分になる。この為、この柱部
が、上記各ポケット内に保持された転動体から受ける力
により破損し易くなる。尚、製造誤差等を考慮して、上
記比ｈ／Ｈを０．０５〜０．２５の範囲に規制すれば、
上記摺動部及び保持器の耐久性確保を、より確実に図れ
る。If the ratio h / H of the thickness H of the cage to the depth h of the groove is less than 0.01, the depth h of the groove becomes too small (shallow). Therefore, the possibility that the burrs protrude radially outward from the outer peripheral surfaces of both ends of the cage is increased. If it protrudes, the lubricating oil fed into the rolling bearing and adhered to the inner peripheral surface of the outer ring is scraped off by the burrs, and the sliding portion between the outer peripheral surface of the cage and the inner peripheral surface of the outer ring is removed. There is a possibility that the lubricating oil present in the oil will run short. If it is insufficient, the frictional resistance of the sliding portion between the two peripheral surfaces becomes large, so that the rolling bearing tends to be heated to a high temperature, and the sliding portion between the retainer and the outer ring has abnormal wear and The possibility of damage such as burn-in increases. On the other hand, when the ratio h / H exceeds 0.4, the thickness of the column existing between the pockets adjacent in the circumferential direction, that is, the inner peripheral surface of the retainer and the concave groove The thickness t (= H−h) between the bottom and the bottom becomes too small (thin), and the strength of the column becomes insufficient. For this reason, this pillar portion is easily damaged by the force received from the rolling element held in each pocket. If the ratio h / H is restricted to a range of 0.05 to 0.25 in consideration of a manufacturing error and the like,
The durability of the sliding portion and the retainer can be more reliably ensured.

【００１９】[0019]

【発明の実施の形態】図１〜２は、本発明の実施の形態
の１例を示している。尚、本発明の特徴は、ターボチャ
ージャ用回転支持装置に組み込む玉軸受３１（請求項に
記載した転がり軸受に相当する）を構成する保持器１４
ｂの構造の改良に関し、この保持器１４ｂの諸元を適正
に規制し、この保持器１４ｂの強度を確保しつつ、この
保持器１４ｂの外周面と外輪１０の内周面との摺動部の
潤滑性を確保する点にある。上記ターボチャージャ用回
転支持装置の全体構成に就いては、前述の図３〜４に示
した構造を含み、従来から知られている回転支持装置と
同様であるから、同等部分に関する図示並びに説明は、
省略若しくは簡略にし、以下、本発明の特徴部分を中心
に説明する。1 and 2 show an embodiment of the present invention. A feature of the present invention is that the cage 14 that constitutes the ball bearing 31 (corresponding to the rolling bearing described in the claims) to be incorporated in the rotation support device for a turbocharger.
In connection with the improvement of the structure of the retainer 14b, the specifications of the retainer 14b are appropriately regulated, and the sliding portion between the outer peripheral surface of the retainer 14b and the inner peripheral surface of the outer ring 10 is secured while securing the strength of the retainer 14b. The point is to ensure lubricity. The entire structure of the turbocharger rotation support device includes the structure shown in FIGS. 3 and 4 and is the same as a conventionally known rotation support device. ,
The description will be omitted or simplified, and the following description will focus on features of the present invention.

【００２０】本例のターボチャージャ用回転支持装置を
構成する上記玉軸受３１（図３〜４に示す、第一、第二
の玉軸受７、８に相当する）は、内周面にアンギュラ型
の外輪軌道９を有する外輪１０と、外周面にアンギュラ
型の内輪軌道１１を有する内輪１２と、これら外輪軌道
９と内輪軌道１１との間に転動自在に設けられた、それ
ぞれが請求項に記載した転動体に相当する、複数個の玉
１３とを備える。又、これら各玉１３は、次述する保持
器１４ｂに設けた複数のポケット１５内に、それぞれ１
個ずつ転動自在に保持している。The above-described ball bearings 31 (corresponding to the first and second ball bearings 7 and 8 shown in FIGS. 3 and 4) which constitute the rotary support device for a turbocharger of the present embodiment have angular-type inner peripheral surfaces. An outer ring 10 having an outer ring raceway 9, an inner ring 12 having an angular inner raceway 11 on the outer peripheral surface, and a roller provided between the outer raceway 9 and the inner raceway 11 so as to freely roll. A plurality of balls 13 corresponding to the described rolling elements are provided. Each of these balls 13 is placed in a plurality of pockets 15 provided in a retainer 14b described below.
It is held so that it can roll freely one by one.

【００２１】又、上記保持器１４ｂは、もみ抜き型保持
器と呼ばれ、全体が円環状（円筒状）で、それぞれが円
筒形である複数のポケット１５を、円周方向に亙って等
間隔に形成している。そして耐熱性を有する熱可塑性樹
脂、例えばポリイミド樹脂の射出成形により造られてい
る。即ち、前述の図７〜８に示す様な、円筒状の内側金
型２７の周囲に複数個（図示の例は７個）の外側金型２
８、２８を、放射方向に配置すると共に、これら各外側
金型２８、２８の軸方向両側面に円環状の側面側金型２
９、２９を配置し、これら各金型２７、２８、２９によ
って形成されるキャビティ３０内に上記熱可塑性樹脂を
送り込み、上記保持器１４ｂを形成している。The retainer 14b is called an extruded retainer. The retainer 14b has a plurality of pockets 15, each of which has an annular shape (cylindrical shape) and is cylindrical in shape. It is formed at intervals. And it is made by injection molding of a thermoplastic resin having heat resistance, for example, a polyimide resin. That is, as shown in FIGS. 7 and 8 described above, a plurality of (seven in the illustrated example) outer molds 2 are provided around the cylindrical inner mold 27.
8 and 28 are arranged in the radial direction, and annular side molds 2 are formed on both axial sides of the outer molds 28 and 28.
9 and 29 are arranged, and the thermoplastic resin is fed into a cavity 30 formed by each of the molds 27, 28 and 29 to form the retainer 14b.

【００２２】又、上記保持器１４ｂの軸方向中間部外周
面に、径方向内方に凹入した凹溝２５を全周に亙って設
けると共に、上述の様な射出成形の際に、上記キャビテ
ィ３０内の外側金型２８、２８同士の合わせ面の端縁に
よって形成される筋状のばり２６、２６（図６参照）
を、上記凹溝２５の底面で上記ポケット１５同士の間部
分に存在する柱部３２の外周面に存在させている。更
に、上記保持器１４ｂの径方向の厚さをＨとし、上記凹
溝２５の深さをｈとした場合に、ｈ／Ｈを０．０１〜
０．４、更に好ましくは０．０５〜０．２５としてい
る。尚、上記厚さＨは１〜２mmとしている。又、上記保
持器１４ｂの外周面を、上記外輪１０の内周面に近接対
向させる事により、この保持器１４ｂの直径方向位置を
この外輪１０により規制する、外輪案内としている。Further, a concave groove 25 which is recessed inward in the radial direction is provided on the outer peripheral surface of the intermediate portion in the axial direction of the retainer 14b over the entire circumference. Streaked burrs 26, 26 formed by the edges of the mating surfaces of the outer molds 28, 28 in the cavity 30 (see FIG. 6).
Are present on the outer peripheral surface of the pillar portion 32 existing between the pockets 15 on the bottom surface of the concave groove 25. Further, when the radial thickness of the cage 14b is H and the depth of the concave groove 25 is h, h / H is 0.01 to
0.4, more preferably 0.05 to 0.25. The thickness H is set to 1 to 2 mm. By making the outer peripheral surface of the retainer 14b close to the inner peripheral surface of the outer ring 10, the outer ring guide restricts the diametric position of the retainer 14b by the outer ring 10.

【００２３】上述の様に構成する玉軸受３１に組み込ん
だ保持器１４ｂの場合には、この保持器１４ｂの強度を
確保し、しかも、射出成形の際に金型同士の合わせ面の
端縁によって上記凹溝２５に形成された筋状のばり２
６、２６が、上記玉軸受３１の潤滑すべき部分に潤滑油
を行き渡りにくくする事を確実に防止できる。この為、
射出成形により低コストで造れる保持器１４ｂに拘わら
ず、上記玉軸受３１延てはターボチャージャの耐久性
を、高次元で確保できる。In the case of the retainer 14b incorporated in the ball bearing 31 constructed as described above, the strength of the retainer 14b is ensured, and at the time of injection molding, the edge of the mating surface between the dies is used. Streaky burrs 2 formed in the concave grooves 25
6, 26 can reliably prevent the lubricating oil from hardly reaching the lubricating portion of the ball bearing 31. Because of this,
Regardless of the cage 14b that can be manufactured at low cost by injection molding, the durability of the above-described ball bearing 31 and the turbocharger can be ensured at a high level.

【００２４】尚、上記保持器１４ｂの厚さＨと上記凹溝
２５の深さｈとの比ｈ／Ｈが０．０１未満の場合には、
この凹溝２５の深さｈが小さく（浅く）なり過ぎて、上
記ばり２６、２６が上記保持器１４ｂの両端部外周面よ
りも径方向外方に突出する可能性が大きくなる。そし
て、突出した場合には、上記玉軸受３１に送り込まれて
上記外輪１０の内周面に付着した潤滑油が、上述の様な
ばり２６、２６に掻き取られ、上記保持器１４ｂの外周
面と上記外輪１０の内周面との摺動部に存在する潤滑油
が不足する可能性が生じる。そして、不足した場合に
は、上記保持器１４ｂの外周面と上記外輪１０の内周面
との摺動部の摩擦抵抗が大きくなる結果、上記玉軸受３
１の温度上昇が著しくなり易くなると共に、上記保持器
１４ｂの外周面と上記外輪１０の内周面との摺動部に異
常摩耗や焼き付き等の損傷が生じる可能性が大きくな
る。一方、上記比ｈ／Ｈが０．４を越えた場合には、前
記各柱部３２の肉厚である、上記保持器１４ｂの内周面
と上記凹溝２５の底面との間の肉厚ｔ（＝Ｈ−ｈ）が小
さく（薄く）なり過ぎて、上記各柱部３２の強度が不十
分になる。この為、これら各柱部３２が、上記各ポケッ
ト１５内に保持された玉１３から受ける力により破損し
易くなる。When the ratio h / H of the thickness H of the retainer 14b to the depth h of the concave groove 25 is less than 0.01,
Since the depth h of the concave groove 25 becomes too small (shallow), the possibility that the burrs 26 project radially outward from the outer peripheral surfaces of both ends of the retainer 14b increases. Then, when it protrudes, the lubricating oil fed into the ball bearing 31 and adhered to the inner peripheral surface of the outer race 10 is scraped off by the burrs 26, 26 as described above, and the outer peripheral surface of the retainer 14b is There is a possibility that the lubricating oil present in the sliding portion between the outer ring 10 and the inner peripheral surface of the outer ring 10 runs short. If the ball bearing 3 is insufficient, the frictional resistance of the sliding portion between the outer peripheral surface of the retainer 14b and the inner peripheral surface of the outer ring 10 increases.
The temperature rise of 1 becomes remarkable, and the possibility of occurrence of damage such as abnormal wear or seizure increases in the sliding portion between the outer peripheral surface of the cage 14b and the inner peripheral surface of the outer ring 10. On the other hand, when the ratio h / H exceeds 0.4, the thickness between the inner peripheral surface of the retainer 14 b and the bottom surface of the concave groove 25, which is the thickness of each of the column portions 32. t (= H-h) becomes too small (thin), and the strength of each column 32 becomes insufficient. Therefore, each of the pillars 32 is easily damaged by the force received from the ball 13 held in each of the pockets 15.

【００２５】[0025]

【実施例】次に、本発明の効果を確認する為に行なった
実験に就いて説明する。実験は、上述した比ｈ／Ｈ
（Ｈ：保持器の厚さ、ｈ：凹溝の深さ）がそれぞれ異な
る保持器を、前述の図１に示した様な構造を有する玉軸
受に組み込み、これら各玉軸受の耐久試験を行なった。
即ち、これら各玉軸受を、前述の図３〜４に示す様なタ
ーボチャージャ用回転支持装置と同様の構造を有する試
験装置に組み付け、以下の条件で運転した。 回転速度 ： ０〜１５万min-1 （停止状態からから加
速して、１５万min-1で５分間維持、その後減速して８
分間停止、これを繰り返す。） 回転支持装置の雰囲気温度 ： １５０℃ 第一、第二の玉軸受７、８の軸方向予圧 ： ２０ＮNext, an experiment conducted to confirm the effect of the present invention will be described. The experiment was performed using the ratio h / H described above.
Cages (H: thickness of cage, h: depth of groove), which are different from each other, are incorporated into ball bearings having the structure shown in FIG. 1 described above, and durability tests of these ball bearings are performed. Was.
That is, each of these ball bearings was assembled into a test device having the same structure as the turbocharger rotation support device as shown in FIGS. 3 and 4 and operated under the following conditions. Rotational speed: 0 to 150,000 min -1 (Accelerate from the stopped state, maintain at 150,000 min -1 for 5 minutes, and then decelerate to 8
Stop for a minute and repeat this. Ambient temperature of the rotary support device: 150 ° C. Axial preload of the first and second ball bearings 7, 8: 20 N

【００２６】そして、この様な条件で上記試験装置を運
転し、異常な振動や温度上昇が生じるまでの時間を測定
した。この結果を、下記の表１に示す。尚、本実験は、
玉の外径ｄ（図１参照）が２．７７８mm、２．８mm、
４．０mm、４．８mmの４つの異なるサイズの玉軸受に就
いて行ない、それぞれの玉の外径ｄに対応して上記保持
器の厚さＨを、１．０mm、１．３mm、１．６mm、２．０
mmとした。又、この保持器は、熱可塑性ポリイミド樹脂
（三井化学工業株式会社製の、商品名「オーラム」）製
で、前述の図７〜８に示す様な射出成形により製造した
ものである。又、運転時間が２００時間経過しても、異
常な振動や温度上昇が生じないものは、好ましい耐久性
を得られるものとし、下記の表１中○印で示した。The test apparatus was operated under these conditions, and the time until abnormal vibration or temperature rise occurred was measured. The results are shown in Table 1 below. In this experiment,
The outer diameter d of the ball (see FIG. 1) is 2.778 mm, 2.8 mm,
The operation is performed on ball bearings of four different sizes of 4.0 mm and 4.8 mm, and the thickness H of the retainer is set to 1.0 mm, 1.3 mm, and 1. mm corresponding to the outer diameter d of each ball. 6mm, 2.0
mm. The cage is made of a thermoplastic polyimide resin (trade name "Auram" manufactured by Mitsui Chemicals, Inc.) and is manufactured by injection molding as shown in FIGS. In addition, those having no abnormal vibration or temperature rise even after the operation time of 200 hours are assumed to have preferable durability, and are indicated by a circle in Table 1 below.

【００２７】[0027]

【表１】 [Table 1]

【００２８】この表１から明らかな通り、保持器の径方
向の厚さＨが１．０〜２．０mmの保持器で、上記比ｈ／
Ｈが０．０１〜０．４である場合には、２００時間を経
過しても異常な振動や温度上昇が生じず、十分な耐久性
を得られる。これに対して、上記比ｈ／Ｈが０．０１未
満の場合には、凹溝に存在するばりが保持器の外周面か
ら突出し易くなり、玉軸受に送り込まれた潤滑油が、潤
滑すべき部分に行き渡りにくくなる。又、上記比ｈ／Ｈ
が０．４を越えた場合には、ばりに基づく潤滑及び冷却
不良は生じないが、保持器の強度を確保できなくなり、
短時間でこの保持器が破損する。As is apparent from Table 1, the cage having a radial thickness H of 1.0 to 2.0 mm has a ratio h / h.
When H is 0.01 to 0.4, abnormal vibration and temperature rise do not occur even after 200 hours, and sufficient durability can be obtained. On the other hand, when the ratio h / H is less than 0.01, the burrs existing in the concave grooves are likely to protrude from the outer peripheral surface of the cage, and the lubricating oil fed into the ball bearings should be lubricated. It becomes difficult to reach the part. In addition, the above ratio h / H
When exceeds 0.4, lubrication and cooling failure based on burrs do not occur, but the strength of the cage cannot be secured.
This cage is broken in a short time.

【００２９】[0029]

【発明の効果】本発明のターボチャージャ用転がり軸受
の保持器は、以上に述べた通り構成し作用する為、射出
成形により低コストで造れるにも拘わらず、転がり軸受
の潤滑性能を十分に確保できる。この結果、低振動で優
れた応答特性を有するなターボチャージャ用回転支持装
置を実現できる。As described above, the cage of the rolling bearing for a turbocharger of the present invention is constructed and operates as described above, so that the lubricating performance of the rolling bearing is sufficiently ensured despite being manufactured at low cost by injection molding. it can. As a result, it is possible to realize a rotation supporting device for a turbocharger having low vibration and excellent response characteristics.

【図面の簡単な説明】[Brief description of the drawings]

【図１】本発明の実施の形態の１例を示す、玉軸受の部
分断面図。FIG. 1 is a partial sectional view of a ball bearing showing an example of an embodiment of the present invention.

【図２】保持器の部分拡大断面図。FIG. 2 is a partially enlarged cross-sectional view of the retainer.

【図３】ターボチャージャの全体構成を示す断面図。FIG. 3 is a cross-sectional view showing the overall configuration of the turbocharger.

【図４】図３のＡ部拡大図。FIG. 4 is an enlarged view of a portion A in FIG. 3;

【図５】従来のターボチャージャ用回転支持装置に組み
込んでいた玉軸受の断面図。FIG. 5 is a cross-sectional view of a ball bearing incorporated in a conventional turbocharger rotation support device.

【図６】従来の保持器の１例を示す斜視図。FIG. 6 is a perspective view showing an example of a conventional cage.

【図７】射出成形により保持器を成形する状態を示す、
図８のＢ−Ｂ断面図。FIG. 7 shows a state in which the cage is molded by injection molding.
FIG. 9 is a sectional view taken along line BB of FIG. 8.

【図８】同じく図７のＣ−Ｃ断面図。8 is a sectional view taken along the line CC in FIG. 7;

【符号の説明】[Explanation of symbols]

１ 排気流路 ２ 回転軸 ３ タービン ４ インペラ ５ 給気流路 ６ 軸受ハウジング ７ 第一の玉軸受 ８ 第二の玉軸受 ９ 外輪軌道 １０ 外輪 １１ 内輪軌道 １２ 内輪 １３ 玉 １４、１４ａ、１４ｂ 保持器 １５ ポケット １６ 圧縮ばね １７ 押圧環 １８ ケーシング １９ 給油通路 ２０ フィルタ ２１ 隙間空間 ２２ ノズル孔 ２３ 排油口 ２４ 隙間空間 ２５ 凹溝 ２６ ばり ２７ 内側金型 ２８ 外側金型 ２９ 側面側金型 ３０ キャビティ ３１ 玉軸受 ３２ 柱部 DESCRIPTION OF SYMBOLS 1 Exhaust flow path 2 Rotary shaft 3 Turbine 4 Impeller 5 Air supply flow path 6 Bearing housing 7 First ball bearing 8 Second ball bearing 9 Outer ring raceway 10 Outer ring 11 Inner ring raceway 12 Inner ring 13 Balls 14, 14a, 14b Cage 15 Pocket 16 Compression spring 17 Pressing ring 18 Casing 19 Oil supply passage 20 Filter 21 Crevice space 22 Nozzle hole 23 Oil discharge port 24 Gap space 25 Concave groove 26 Burr 27 Inner die 28 Outer die 29 Side die 30 Cavity 31 Ball bearing 32 pillar

Claims (2)

【特許請求の範囲】[Claims] 【請求項１】 ターボチャージャの回転軸を軸受ハウジ
ングの内側に回転自在に支持する為の転がり軸受に組み
込んで、この転がり軸受を構成する複数個の転動体を転
動自在に保持する為、全体が円環状で、これら各転動体
を保持する為の複数のポケットを円周方向に亙り間欠的
に設けた保持器であって、合成樹脂の射出成形により造
られており、軸方向中間部外周面に径方向内方に凹入し
た凹溝を全周に亙って設けると共に、射出成形の際にキ
ャビティ内の金型同士の合わせ面の端縁によって形成さ
れるばりを、上記凹溝の底面で上記ポケット同士の間部
分に存在させており、上記保持器の径方向の厚さＨが
１．０〜２．０mmであり、上記凹溝の深さをｈとした場
合に、ｈ／Ｈが０．０１〜０．４であるターボチャージ
ャ用転がり軸受の保持器。The present invention relates to a rolling bearing for rotatably supporting a rotary shaft of a turbocharger inside a bearing housing, and a plurality of rolling elements constituting the rolling bearing to be rollably held. Is a cage having a plurality of pockets for holding these rolling elements intermittently in the circumferential direction, which is made by injection molding of a synthetic resin, A groove is formed on the entire surface of the groove. The groove is formed on the entire surface of the groove. When the thickness H in the radial direction of the retainer is 1.0 to 2.0 mm and the depth of the concave groove is h, h / Holding of a rolling bearing for a turbocharger in which H is 0.01 to 0.4 . 【請求項２】 一端部にタービンを、他端部にインペラ
を、それぞれ固定した回転軸を、ハウジングの内側に回
転自在に支持する為、この軸受ハウジングの内周面と上
記回転軸の外周面との間に、外輪の内周面に形成した外
輪軌道と内輪の外周面に形成した内輪軌道との間に保持
器により保持された複数個の転動体を転動自在に配置し
て成る転がり軸受を設け、この転がり軸受に向けて潤滑
油を送り込む事により、この転がり軸受の潤滑を行なう
様に構成したターボチャージャ用回転支持装置に於い
て、上記保持器を請求項１に記載したターボチャージャ
用転がり軸受の保持器とした事を特徴とするターボチャ
ージャ用回転支持装置。2. An inner peripheral surface of the bearing housing and an outer peripheral surface of the rotating shaft for rotatably supporting a rotating shaft having a turbine fixed to one end and an impeller fixed to the other end, respectively, inside the housing. Between the outer raceway formed on the inner peripheral surface of the outer race and the inner raceway formed on the outer peripheral surface of the inner race, a plurality of rolling elements held by a retainer are rollably arranged. A turbocharger according to claim 1, wherein a bearing is provided and lubricating oil is fed toward the rolling bearing to lubricate the rolling bearing. Rotary support device for a turbocharger, characterized in that it is used as a cage for rolling bearings.
JP2001046610A 2001-02-22 2001-02-22 Cage for rolling bearing for turbocharger and rotary support device for turbocharger Pending JP2002250345A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2001046610A JP2002250345A (en) 2001-02-22 2001-02-22 Cage for rolling bearing for turbocharger and rotary support device for turbocharger

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2001046610A JP2002250345A (en) 2001-02-22 2001-02-22 Cage for rolling bearing for turbocharger and rotary support device for turbocharger

Publications (1)

Publication Number Publication Date
JP2002250345A true JP2002250345A (en) 2002-09-06

Family

ID=18908202

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2001046610A Pending JP2002250345A (en) 2001-02-22 2001-02-22 Cage for rolling bearing for turbocharger and rotary support device for turbocharger

Country Status (1)

Country Link
JP (1) JP2002250345A (en)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2012036855A (en) * 2010-08-09 2012-02-23 Ihi Corp Turbocharger using rolling bearing
JP2013160333A (en) * 2012-02-07 2013-08-19 Jtekt Corp Bearing resin retainer, method for manufacturing the same, and rolling bearing
JP2018189167A (en) * 2017-05-08 2018-11-29 日本精工株式会社 Angular contact ball bearing
JPWO2018199285A1 (en) * 2017-04-28 2020-06-11 Ntn株式会社 Angular ball bearing cage and angular ball bearing

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2012036855A (en) * 2010-08-09 2012-02-23 Ihi Corp Turbocharger using rolling bearing
JP2013160333A (en) * 2012-02-07 2013-08-19 Jtekt Corp Bearing resin retainer, method for manufacturing the same, and rolling bearing
JPWO2018199285A1 (en) * 2017-04-28 2020-06-11 Ntn株式会社 Angular ball bearing cage and angular ball bearing
JP7142629B2 (en) 2017-04-28 2022-09-27 Ntn株式会社 Angular contact ball bearing cage and angular contact ball bearing
JP2018189167A (en) * 2017-05-08 2018-11-29 日本精工株式会社 Angular contact ball bearing

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