JP3783278B2 - Rolling bearing for fluid coupling - Google Patents

Rolling bearing for fluid coupling Download PDF

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Publication number
JP3783278B2
JP3783278B2 JP12873496A JP12873496A JP3783278B2 JP 3783278 B2 JP3783278 B2 JP 3783278B2 JP 12873496 A JP12873496 A JP 12873496A JP 12873496 A JP12873496 A JP 12873496A JP 3783278 B2 JP3783278 B2 JP 3783278B2
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Japan
Prior art keywords
ring
peripheral surface
fluid coupling
rolling bearing
seal ring
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Expired - Fee Related
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JP12873496A
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Japanese (ja)
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JPH09310720A (en
Inventor
康博 秋元
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NSK Ltd
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NSK Ltd
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    • 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
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F16C33/784—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race
    • F16C33/7843—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race with a single annular sealing disc
    • F16C33/7853—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race with a single annular sealing disc with one or more sealing lips to contact the inner race
    • 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
    • F16C19/04—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly
    • F16C19/06—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly with a single row or balls

Description

【０００１】
【産業上の利用分野】
この発明に係る流体継手用転がり軸受は、自動車用エンジンのラジエータに通風する為の冷却ファンに付属した流体継手と、この冷却ファンを駆動する為の駆動軸との間に設けた状態で使用する。
【０００２】
【従来の技術】
前置エンジン・後輪駆動車（ＦＲ車）用エンジンの冷却水放熱用のラジエータに送風する為の冷却ファンは、エンジンのクランクシャフトによりベルトを介して駆動する。即ち、上記クランクシャフトの端部に固定した駆動プーリと、冷却ファンを回転駆動する為の駆動軸に固定した従動プーリとの間にベルトを掛け渡し、上記クランクシャフトの回転に伴って上記駆動軸を回転駆動し、この駆動軸に支持した冷却ファンを回転駆動する。
【０００３】
上記駆動軸の回転速度はクランクシャフトの回転速度に比例して増大するのに対して、上記冷却ファンの回転速度は、必ずしもクランクシャフトの回転速度に伴って増大させる必要はない。一方、冷却ファンを回転させる為に要するトルクは、この冷却ファンの回転速度が増大するのに伴って増大する。従って、冷却ファンの回転速度を上記クランクシャフトの回転速度に応じて増大させると、エンジンの動力が無駄に消費される事になり、好ましくない。この為従来から、上記駆動軸と冷却ファンとの間に流体継手を設けて、この冷却ファンの回転速度が或る程度以上は上昇しない様にしている。
【０００４】
図１は、この様な理由で流体継手を組み込んだ、冷却ファンの駆動機構を示している。この図１に示した構造は、冷却水を循環させる為のウォータポンプ１と冷却ファン２とを、単一の駆動軸３により回転駆動させる構造を示している。この駆動軸３は、上記ウォータポンプ１のハウジング４に支持した軸受ユニット５により、その中間部を回転自在に支持している。そして、上記駆動軸３の内端部（図１の右端部）で上記ハウジング４内に位置する部分にはインペラ６を、同じく外端部（図１の左端部）で上記ハウジング４外に位置する部分には従動プーリ７を、それぞれ固定している。この従動プーリ７と、図示しないクランクシャフトの端部に固定した駆動プーリとの間にはベルト８を掛け渡して、エンジンの運転時に上記駆動軸３を回転駆動自在としている。尚、この駆動軸３の一部で、上記インペラ６と軸受ユニット５との間にはメカニカルシール９を設けて、上記ハウジング４内を流通する冷却水が軸受ユニット５側に入り込まない様にしている。
【０００５】
一方、上記従動プーリ７を上記駆動軸３の外端部に固定する為の内側ハブ１０の外半部（図１の左半部）には上記冷却ファン２を、転がり軸受１１及び流体継手１２を介して支持している。これら転がり軸受１１と流体継手１２とは、動力の伝達方向に対して互いに並列に配置している。即ち、上記冷却ファン２の中央部に設けた外側ハブ１３の一部を上記内側ハブ１０の中間部に、上記転がり軸受１１により回転自在に支持している。又、上記内側ハブ１０の外端部で上記転がり軸受１１よりも外方に突出した部分に、上記流体継手１２を構成するロータ１４を外嵌固定している。そして、このロータ１４と上記転がり軸受１１との間に、粘性流体である、シリコンオイル１５を充填している。
【０００６】
エンジンの運転に伴って上記駆動軸３及び内側ハブ１０が回転すると（この時エンジンルーム内の温度は低い）、この回転は軸受トルクと上記シリコンオイル１５の粘性に基づき、上記ロータ１４から外側ハブ１３に伝わり、上記冷却ファン２がゆっくりと回転する。エンジンルーム内の温度が上昇すると、バイメタル２６の作用により、ラビリンス部２７を上記シリコンオイル１５が通過する様になり、粘性抵抗がより大きくなり、上記冷却ファン２の回転速度が増す。この様にエンジンルーム内の温度に対応して適切に上記冷却ファン２を回転させると共に、シリコンオイル１５の粘性抵抗に基づき、上記冷却ファン２を回転させる事により、上記駆動軸３の回転上昇に拘らず、上記冷却ファン２の回転速度が過度に上昇する事を防止し、動力の消費を軽減する。
【０００７】
上述の様に構成され作用する冷却ファンの駆動機構に組み込む転がり軸受１１は、例えば図２〜３に示す様に構成されている。即ち、内周面に外輪軌道１６を有する外輪１７と、外周面に内輪軌道１８を有する内輪１９と、上記外輪軌道１６と内輪軌道１８との間に転動自在に設けられた複数の転動体２０、２０と、第一、第二のシールリング２１、２２とを備える。このうちの第一のシールリング２１は、上記外輪１７の軸方向一端部（図２〜３の左端部）内周面と上記内輪１９の軸方向一端部外周面との間に設けて、上記外輪１７の内周面と上記内輪１９の外周面との間の空間２３の軸方向一端開口を塞ぐ。又、上記第二のシールリング２２は、上記外輪１７の軸方向他端部（図２〜３の右端部）内周面と上記内輪１９の軸方向他端部外周面との間に設けて、上記空間２３の軸方向他端開口を塞ぐ。
【０００８】
この様な転がり軸受１１は、上記第一のシールリング２１を、上記流体継手１２を構成するシリコンオイル１５に対向させ、上記第二のシールリング２２をこの流体継手１２と反対側（図１の右側）に向けた状態で使用する。この状態で上記第一のシールリング２１は、上記シリコンオイル１５が上記空間２３内に入り込む事を防止すると共に、この空間２３内に封入したグリースが上記シリコンオイル１５を封入した空間側に漏れ出す事を防止する。又、上記第二のシールリング２２は、上記グリースが外部空間に漏洩する事を防止すると共に、外部空間に浮遊する異物が上記空間２３内に入り込む事を防止する。
【０００９】
ところで、エンジンの運転時に上記シリコンオイル１５の温度は、前記ロータ１４による攪拌抵抗に基づき上昇する。従って、このシリコンオイル１５と接触する第一のシールリング２１には、十分な耐熱性を持たせる必要がある。この為従来は、第一、第二の両シールリング２１、２２を、優れた耐熱性を有する弗素ゴムにより構成していた。即ち、第一、第二のシールリング２１、２２として、弗素ゴムであるシール材２４を金属製で円環状の芯金２５により補強したものを使用していた。
【００１０】
【発明が解決しようとする課題】
弗素ゴムは耐熱性が優れている反面、高価な為、第一、第二のシールリング２１、２２を構成するシール材２４、２４を何れをも弗素ゴムにより造った場合には、転がり軸受１１全体としてのコストが嵩んでしまう。一方、流体継手１２と反対側に配置される第二のシールリング２２は、冷却ファン２によって冷却された雰囲気中に曝らされる為、それ程温度上昇しない。従って、弗素ゴム程優れた耐熱性を有する材料を使用しなくても、十分な耐久性を確保できる。
本発明の流体継手用転がり軸受は、上述の様な事情に鑑みて発明したものである。
【００１１】
【課題を解決するための手段】
本発明の流体継手用転がり軸受は、前述した従来の流体継手用転がり軸受と同様、例えば図２〜３に示す様に、内周面に外輪軌道１６を有する外輪１７と、外周面に内輪軌道１８を有する内輪１９と、上記外輪軌道１６と内輪軌道１８との間に転動自在に設けられた複数の転動体２０、２０と、第一、第二のシールリング２１、２２とを備える。このうちの第一のシールリング２１は、上記外輪１７の軸方向一端部内周面と上記内輪１９の軸方向一端部外周面との間に設けて、上記外輪１７の内周面と上記内輪１９の外周面との間の空間２３の軸方向一端開口を塞ぐ。又、上記第二のシールリング２２は、上記外輪１７の軸方向他端部内周面と上記内輪１９の軸方向他端部外周面との間に設けて、上記空間２３の軸方向他端開口を塞ぐ。
【００１２】
この様な転がり軸受１１は、図１に示す様に、上記第一のシールリング２１を、上記流体継手１２を構成するシリコンオイル１５に対向させ、上記第二のシールリング２２をこの流体継手１２と反対側に向けた状態で使用する。この状態で上記第一のシールリング２１は、上記シリコンオイル１５が上記空間２３内に入り込む事を防止すると共に、この空間２３内に封入したグリースが上記シリコンオイル１５を封入した空間側に漏れ出す事を防止する。又、上記第二のシールリング２２は、上記グリースが外部空間に漏洩する事を防止すると共に、外部空間に浮遊する異物が上記空間２３内に入り込む事を防止する。
【００１３】
特に、本発明の流体継手用転がり軸受に於いては、上記第一のシールリング２１を構成するゴムとして、上記第二のシールリング２２を構成するゴムよりも耐熱温度の高いものを使用する。即ち、上記シリコンオイル１５に接触する為、十分な耐熱性を確保する必要がある第一のシールリング２１を構成するシール材２４は、弗素ゴム等の、優れた耐熱性を有するゴムにより造る。これに対して、余り耐熱性を要求されない、第二のシールリング２２を構成するシール材２４は、水添加ニトリルゴム、アクリルゴム、ニトリルゴム等、弗素ゴムに比較して安価なゴムにより造る。
【００１４】
【作用】
上述の様に構成される本発明の流体継手用転がり軸受が、流体継手１２との組み合わせにより、駆動軸３と冷却ファン２との間で、所望範囲の回転力伝達を行なう際の作用は、前述した従来構造の場合と同様である。
【００１５】
特に、本発明の流体継手用転がり軸受の場合には、あまり耐熱性を要求されない第二のシールリング２２を構成するシール材２４を、安価なゴムにより造っているので、流体継手用転がり軸受全体としてのコスト低減を図れる。
【００１６】
【発明の効果】
本発明は、以上に述べた通り構成され作用するので、十分な耐久性を確保しつつ、低廉な流体継手用転がり軸受を提供できる。
【図面の簡単な説明】
【図１】本発明の対象となる流体継手用転がり軸受を組み込んだ冷却ファンの駆動機構の断面図。
【図２】本発明の対象となる流体継手用転がり軸受の第１例を示す断面図。
【図３】同第２例を示す断面図。
【符号の説明】
１ ウォータポンプ
２ 冷却ファン
３ 駆動軸
４ ハウジング
５ 軸受ユニット
６ インペラ
７ 従動プーリ
８ ベルト
９ メカニカルシール
１０ 内側ハブ
１１ 転がり軸受
１２ 流体継手
１３ 外側ハブ
１４ ロータ
１５ シリコンオイル
１６ 外輪軌道
１７ 外輪
１８ 内輪軌道
１９ 内輪
２０ 転動体
２１ 第一のシールリング
２２ 第二のシールリング
２３ 空間
２４ シール材
２５ 芯金
２６ バイメタル
２７ ラビリンス部[0001]
[Industrial application fields]
The fluid coupling rolling bearing according to the present invention is used in a state of being provided between a fluid coupling attached to a cooling fan for ventilating a radiator of an automobile engine and a drive shaft for driving the cooling fan. .
[0002]
[Prior art]
A cooling fan for blowing air to a radiator for radiating cooling water of an engine for a front engine and a rear wheel drive vehicle (FR vehicle) is driven via a belt by a crankshaft of the engine. That is, a belt is stretched between a driving pulley fixed to the end of the crankshaft and a driven pulley fixed to a driving shaft for rotationally driving the cooling fan, and the driving shaft is rotated along with the rotation of the crankshaft. And the cooling fan supported on the drive shaft is driven to rotate.
[0003]
While the rotational speed of the drive shaft increases in proportion to the rotational speed of the crankshaft, the rotational speed of the cooling fan does not necessarily increase with the rotational speed of the crankshaft. On the other hand, the torque required to rotate the cooling fan increases as the rotation speed of the cooling fan increases. Therefore, if the rotation speed of the cooling fan is increased in accordance with the rotation speed of the crankshaft, the engine power is wasted, which is not preferable. For this reason, conventionally, a fluid coupling is provided between the drive shaft and the cooling fan so that the rotational speed of the cooling fan does not increase to a certain extent.
[0004]
FIG. 1 shows a cooling fan drive mechanism incorporating a fluid coupling for this reason. The structure shown in FIG. 1 shows a structure in which a water pump 1 and a cooling fan 2 for circulating cooling water are rotationally driven by a single drive shaft 3. The drive shaft 3 rotatably supports an intermediate portion thereof by a bearing unit 5 supported on the housing 4 of the water pump 1. An impeller 6 is located at the inner end portion (right end portion in FIG. 1) of the drive shaft 3 and located outside the housing 4 at the outer end portion (left end portion in FIG. 1). The driven pulleys 7 are fixed to the portions to be performed. A belt 8 is stretched between the driven pulley 7 and a driving pulley fixed to an end of a crankshaft (not shown) so that the driving shaft 3 can be driven to rotate during engine operation. In addition, a mechanical seal 9 is provided between the impeller 6 and the bearing unit 5 in a part of the drive shaft 3 so that the cooling water flowing through the housing 4 does not enter the bearing unit 5 side. Yes.
[0005]
On the other hand, the cooling fan 2 is connected to the outer half (the left half in FIG. 1) of the inner hub 10 for fixing the driven pulley 7 to the outer end of the drive shaft 3, and the rolling bearing 11 and the fluid coupling 12. Support through. The rolling bearing 11 and the fluid coupling 12 are arranged in parallel to each other in the power transmission direction. That is, a part of the outer hub 13 provided at the center of the cooling fan 2 is rotatably supported by the rolling bearing 11 at the intermediate portion of the inner hub 10. A rotor 14 constituting the fluid coupling 12 is externally fitted and fixed to a portion of the outer end portion of the inner hub 10 that protrudes outward from the rolling bearing 11. And between this rotor 14 and the said rolling bearing 11, the silicone oil 15 which is a viscous fluid is filled.
[0006]
When the drive shaft 3 and the inner hub 10 rotate with the operation of the engine (at this time, the temperature in the engine room is low), this rotation is based on the bearing torque and the viscosity of the silicon oil 15 and from the rotor 14 to the outer hub. 13, the cooling fan 2 rotates slowly. When the temperature in the engine room rises, the silicon oil 15 passes through the labyrinth portion 27 by the action of the bimetal 26, the viscosity resistance becomes larger, and the rotation speed of the cooling fan 2 increases. In this manner, the cooling fan 2 is appropriately rotated according to the temperature in the engine room, and the cooling fan 2 is rotated based on the viscous resistance of the silicone oil 15 to increase the rotation of the drive shaft 3. Regardless, the rotational speed of the cooling fan 2 is prevented from excessively increasing, and power consumption is reduced.
[0007]
The rolling bearing 11 incorporated in the driving mechanism of the cooling fan configured and acting as described above is configured as shown in FIGS. That is, an outer ring 17 having an outer ring raceway 16 on an inner peripheral surface, an inner ring 19 having an inner ring raceway 18 on an outer peripheral surface, and a plurality of rolling elements provided between the outer ring raceway 16 and the inner ring raceway 18 so as to be rollable. 20 and 20 and first and second seal rings 21 and 22. Of these, the first seal ring 21 is provided between the inner peripheral surface of the axial end of the outer ring 17 (the left end in FIGS. 2 to 3) and the outer peripheral surface of the axial end of the inner ring 19. One axial end opening of the space 23 between the inner peripheral surface of the outer ring 17 and the outer peripheral surface of the inner ring 19 is closed. The second seal ring 22 is provided between the inner peripheral surface of the outer ring 17 in the other axial end portion (the right end portion in FIGS. 2 to 3) and the outer peripheral surface of the inner ring 19 in the other axial end portion. The other end in the axial direction of the space 23 is closed.
[0008]
In such a rolling bearing 11, the first seal ring 21 is opposed to the silicone oil 15 constituting the fluid coupling 12, and the second seal ring 22 is opposed to the fluid coupling 12 (in FIG. 1). Use in the state of facing to the right. In this state, the first seal ring 21 prevents the silicon oil 15 from entering the space 23, and the grease sealed in the space 23 leaks out to the space side where the silicon oil 15 is sealed. Prevent things. The second seal ring 22 prevents the grease from leaking into the external space and prevents foreign matter floating in the external space from entering the space 23.
[0009]
By the way, the temperature of the silicon oil 15 rises based on the stirring resistance by the rotor 14 during operation of the engine. Therefore, the first seal ring 21 in contact with the silicon oil 15 needs to have sufficient heat resistance. For this reason, conventionally, both the first and second seal rings 21 and 22 are made of fluorine rubber having excellent heat resistance. That is, as the first and second seal rings 21 and 22, a seal material 24 made of fluorine rubber and made of metal and reinforced by an annular cored bar 25 is used.
[0010]
[Problems to be solved by the invention]
Although fluorine rubber is excellent in heat resistance, it is expensive. Therefore, when both the sealing materials 24 and 24 constituting the first and second seal rings 21 and 22 are made of fluorine rubber, the rolling bearing 11 is used. The cost as a whole increases. On the other hand, since the second seal ring 22 disposed on the side opposite to the fluid coupling 12 is exposed to the atmosphere cooled by the cooling fan 2, the temperature does not increase so much. Accordingly, sufficient durability can be secured without using a material having heat resistance as excellent as that of fluorine rubber.
The rolling bearing for a fluid coupling of the present invention has been invented in view of the above-described circumstances.
[0011]
[Means for Solving the Problems]
The fluid coupling rolling bearing of the present invention is similar to the above-described conventional fluid coupling rolling bearing, for example, as shown in FIGS. 2 and 3, an outer ring 17 having an outer ring raceway 16 on the inner peripheral surface and an inner ring raceway on the outer peripheral surface. 18, an inner ring 19 having a plurality of rolling elements 20 and 20 provided between the outer ring raceway 16 and the inner ring raceway 18, and first and second seal rings 21 and 22. Among these, the first seal ring 21 is provided between the inner peripheral surface of one end portion in the axial direction of the outer ring 17 and the outer peripheral surface of one end portion in the axial direction of the inner ring 19, and the inner peripheral surface of the outer ring 17 and the inner ring 19. The opening in the axial direction of the space 23 between the outer peripheral surfaces of the two is closed. The second seal ring 22 is provided between the inner peripheral surface of the other end portion in the axial direction of the outer ring 17 and the outer peripheral surface of the other end portion in the axial direction of the inner ring 19. Block.
[0012]
As shown in FIG. 1, such a rolling bearing 11 has the first seal ring 21 opposed to the silicone oil 15 constituting the fluid coupling 12, and the second seal ring 22 is configured to the fluid coupling 12. Use the product facing the opposite side. In this state, the first seal ring 21 prevents the silicon oil 15 from entering the space 23, and the grease sealed in the space 23 leaks out to the space side where the silicon oil 15 is sealed. Prevent things. The second seal ring 22 prevents the grease from leaking into the external space and prevents foreign matter floating in the external space from entering the space 23.
[0013]
In particular, in the rolling bearing for a fluid coupling according to the present invention, a rubber having a higher heat resistance temperature than that of the rubber constituting the second seal ring 22 is used as the rubber constituting the first seal ring 21. That is, the sealing material 24 constituting the first seal ring 21 that needs to ensure sufficient heat resistance in contact with the silicon oil 15 is made of rubber having excellent heat resistance, such as fluorine rubber. On the other hand, the sealing material 24 constituting the second seal ring 22 that does not require much heat resistance is made of rubber that is less expensive than fluorine rubber, such as water-added nitrile rubber, acrylic rubber, and nitrile rubber.
[0014]
[Action]
When the rolling bearing for a fluid coupling according to the present invention configured as described above is combined with the fluid coupling 12 to transmit a rotational force within a desired range between the drive shaft 3 and the cooling fan 2, This is the same as in the case of the conventional structure described above.
[0015]
In particular, in the case of the rolling joint for a fluid coupling according to the present invention, the sealing material 24 constituting the second seal ring 22 that does not require much heat resistance is made of an inexpensive rubber. As a result, the cost can be reduced.
[0016]
【The invention's effect】
Since the present invention is configured and operates as described above, it is possible to provide an inexpensive rolling bearing for a fluid coupling while ensuring sufficient durability.
[Brief description of the drawings]
FIG. 1 is a cross-sectional view of a driving mechanism of a cooling fan incorporating a fluid coupling rolling bearing which is an object of the present invention.
FIG. 2 is a cross-sectional view showing a first example of a fluid coupling rolling bearing which is an object of the present invention.
FIG. 3 is a sectional view showing the second example.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 Water pump 2 Cooling fan 3 Drive shaft 4 Housing 5 Bearing unit 6 Impeller 7 Driven pulley 8 Belt 9 Mechanical seal 10 Inner hub 11 Rolling bearing 12 Fluid coupling 13 Outer hub 14 Rotor 15 Silicon oil 16 Outer ring track 17 Outer ring 18 Inner ring track 19 Inner ring 20 Rolling element 21 First seal ring 22 Second seal ring 23 Space 24 Seal material 25 Core metal 26 Bimetal 27 Labyrinth part

Claims (1)

内周面に外輪軌道を有する外輪と、外周面に内輪軌道を有する内輪と、上記外輪軌道と内輪軌道との間に転動自在に設けられた複数の転動体と、上記外輪の軸方向一端部内周面と上記内輪の軸方向一端部外周面との間に設けて、上記外輪の内周面と上記内輪の外周面との間の空間の軸方向一端開口を塞いだ第一のシールリングと、上記外輪の軸方向他端部内周面と上記内輪の軸方向他端部外周面との間に設けて、上記空間の軸方向他端開口を塞いだ第二のシールリングとを備え、上記第一のシールリングを流体継手を構成する粘性流体に対向させ、上記第二のシールリングをこの流体継手と反対側に向けた状態で使用する流体継手用転がり軸受に於いて、上記第一のシールリングを構成するゴムとして、上記第二のシールリングを構成するゴムよりも耐熱温度の高いものを使用した事を特徴とする流体継手用転がり軸受。An outer ring having an outer ring raceway on an inner peripheral surface, an inner ring having an inner ring raceway on an outer peripheral surface, a plurality of rolling elements provided between the outer ring raceway and the inner ring raceway, and one axial end of the outer ring A first seal ring that is provided between the inner peripheral surface of the inner ring and the outer peripheral surface of one end in the axial direction of the inner ring, and closes one axial opening of the space between the inner peripheral surface of the outer ring and the outer peripheral surface of the inner ring And a second seal ring provided between the inner peripheral surface of the other end in the axial direction of the outer ring and the outer peripheral surface of the other end in the axial direction of the inner ring, and closing the other end opening in the axial direction of the space, In a rolling bearing for a fluid coupling that is used in a state where the first seal ring is opposed to the viscous fluid constituting the fluid coupling and the second seal ring is directed to the opposite side of the fluid coupling, As the rubber constituting the seal ring, the rubber constituting the second seal ring Rolling bearing fluid coupling, characterized in that using a high heat-resistant temperature than.
JP12873496A 1996-05-23 1996-05-23 Rolling bearing for fluid coupling Expired - Fee Related JP3783278B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP12873496A JP3783278B2 (en) 1996-05-23 1996-05-23 Rolling bearing for fluid coupling

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP12873496A JP3783278B2 (en) 1996-05-23 1996-05-23 Rolling bearing for fluid coupling

Publications (2)

Publication Number Publication Date
JPH09310720A JPH09310720A (en) 1997-12-02
JP3783278B2 true JP3783278B2 (en) 2006-06-07

Family

ID=14992139

Family Applications (1)

Application Number Title Priority Date Filing Date
JP12873496A Expired - Fee Related JP3783278B2 (en) 1996-05-23 1996-05-23 Rolling bearing for fluid coupling

Country Status (1)

Country Link
JP (1) JP3783278B2 (en)

Also Published As

Publication number Publication date
JPH09310720A (en) 1997-12-02

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