JP4244173B2 - Vibration control structure of rolling bearing - Google Patents

Vibration control structure of rolling bearing Download PDF

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JP4244173B2
JP4244173B2 JP2003298419A JP2003298419A JP4244173B2 JP 4244173 B2 JP4244173 B2 JP 4244173B2 JP 2003298419 A JP2003298419 A JP 2003298419A JP 2003298419 A JP2003298419 A JP 2003298419A JP 4244173 B2 JP4244173 B2 JP 4244173B2
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housing
outer ring
rolling bearing
bearing
damper
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JP2005069317A (en
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利彦 白木
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JTEKT Corp
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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16CSHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C27/00Elastic or yielding bearings or bearing supports, for exclusively rotary movement
    • F16C27/04Ball or roller bearings, e.g. with resilient rolling bodies
    • F16C27/045Ball or roller bearings, e.g. with resilient rolling bodies with a fluid film, e.g. squeeze film damping
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16CSHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/04Bearings 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
    • F16C19/06Bearings 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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16CSHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C35/00Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/04Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
    • F16C35/042Housings for rolling element bearings for rotary movement

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Support Of The Bearing (AREA)
  • Vibration Prevention Devices (AREA)

Description

本発明は、転がり軸受の制振構造に関する。   The present invention relates to a vibration damping structure for a rolling bearing.

従来、回転軸を支持する転がり軸受の制振構造として、回転軸の回転等に伴ない発生する振動が、ハウジングに伝達されないように、制振効果のあるオイルフィルムダンパーが設けられたものが周知である。かかる転がり軸受の制振構造は、軸受の外輪全周に環状のダンパー内輪が装着され、ダンパー内輪は、ハウジングに環状のダンパー空間を形成するように内嵌されている。   Conventionally, as a vibration damping structure for a rolling bearing that supports a rotating shaft, an oil film damper having a damping effect is provided so that vibrations generated by rotation of the rotating shaft and the like are not transmitted to the housing. It is. In the vibration damping structure of the rolling bearing, an annular damper inner ring is attached to the entire outer ring of the bearing, and the damper inner ring is internally fitted so as to form an annular damper space in the housing.

前記ダンパー空間には粘性流体が充填されており、この粘性流体圧力により、軸受をダンパー内輪と共に浮かせ、回転軸側の振動を吸収して振動がハウジングに伝達されるのを防止することができる(例えば、特許文献1参照)。
特開平11−193816号公報
The damper space is filled with a viscous fluid, and this viscous fluid pressure allows the bearing to float with the damper inner ring, absorbs vibration on the rotating shaft side, and prevents vibration from being transmitted to the housing ( For example, see Patent Document 1).
JP 11-193816 A

上記従来の転がり軸受の制振構造は、軸受と共にダンパー内輪がハウジングに対して浮いた状態であるため、軸受けの位置決めが困難になる問題があり、また、外輪が連れ回りを規制するための回り止めピンが必要となり、複雑な構造となっていた。   The conventional damping structure for a rolling bearing has a problem that positioning of the bearing is difficult because the inner ring of the damper together with the bearing floats with respect to the housing, and the rotation for the outer ring to restrict the rotation of the bearing. A stop pin was required and the structure was complicated.

[課題を解決するための手段]
本発明は、軸受と、前記軸受の外輪に装着される第1ハウジングと、前記第1ハウジングとの間にダンパー空間を形成する第2ハウジングと、を具備し、前記ダンパー空間に充填されている粘性流体からの流体圧力により、両ハウジング間に制振ダンパーが構成される転がり軸受の制振構造において、第1ハウジングは、外輪の外周面の負荷圏側に配置されて、外輪の外周面の円周方向の一部に第1ハウジングを未装着とされる未装着部分が構成されており、かつ、その未装着部分は、粘性流体からの流体圧力により、第2ハウジングの非負荷圏に形成された嵌合面に押圧されることにより、前記外輪は前記第1ハウジングと前記第2ハウジングとで挟持されて軸受の直径方向の位置決めがされる、ことにある。
[Means for solving problems]
The present invention includes a bearing, a first housing mounted on an outer ring of the bearing, and a second housing that forms a damper space between the first housing, and the damper space is filled. In a vibration damping structure of a rolling bearing in which a vibration damper is formed between both housings by fluid pressure from a viscous fluid, the first housing is disposed on the load zone side of the outer circumferential surface of the outer ring, An unmounted portion where the first housing is not mounted is configured in a part of the circumferential direction, and the unmounted portion is formed in the non-load zone of the second housing by the fluid pressure from the viscous fluid The outer ring is sandwiched between the first housing and the second housing and is positioned in the diametrical direction of the bearing by being pressed against the fitted surface.

そして、ダンパー空間に充填された粘性流体が、第1ハウジングを非負荷圏側に押圧すると、軸受の外輪の未装着部分は、第2ハウジングの嵌合面に押圧され、外輪は第1ハウジングと第2ハウジングとで挟持された状態となる。この結果、内輪に挿通された回転軸が回転しても、外輪が連れ回ることはなく、しかも、外輪の未装着部分が、第2ハウジングの嵌合面に当接することにより、軸受の直径方向の位置決めを確実に行える。 When the viscous fluid filled in the damper space presses the first housing toward the non-load zone, the unmounted portion of the outer ring of the bearing is pressed against the fitting surface of the second housing, and the outer ring is connected to the first housing. It will be in the state clamped with the 2nd housing. As a result, even if the rotation shaft inserted into the inner ring rotates, the outer ring does not rotate, and the non-mounted portion of the outer ring comes into contact with the fitting surface of the second housing, so that the diameter direction of the bearing Can be reliably positioned.

本発明の転がり軸受の制振構造によれば、簡単な構造により外輪の連れ回り防止と、軸受の直径方向の位置決めが可能となる。   According to the vibration damping structure of the rolling bearing of the present invention, it is possible to prevent the outer ring from rotating and to position the bearing in the diametrical direction with a simple structure.

図1ないし図4は、本発明の一実施形態を示している。図1は、転がり軸受装置を示す正面断面図、図2は、図1の転がり軸受装置の側面断面図、図3は、図1の転がり軸受装置の分解斜視図、図4は、軸受および第1ハウジングの斜視図である。   1 to 4 show an embodiment of the present invention. 1 is a front sectional view showing a rolling bearing device, FIG. 2 is a side sectional view of the rolling bearing device of FIG. 1, FIG. 3 is an exploded perspective view of the rolling bearing device of FIG. 1, and FIG. It is a perspective view of 1 housing.

図1および図2において、1は転がり軸受装置を示している。この転がり軸受装置1は、外輪2、内輪3、複数の例えば玉からなる転動体4及び保持器(図示省略)からなる軸受6と、第1ハウジング7と、第2ハウジング8とを備えるものである。   1 and 2, reference numeral 1 denotes a rolling bearing device. The rolling bearing device 1 includes an outer ring 2, an inner ring 3, a plurality of rolling elements 4 made of balls, for example, and a bearing 6 made of a cage (not shown), a first housing 7, and a second housing 8. is there.

第1ハウジング7は、ラジアル荷重を受ける外輪2の負荷圏側に装着されている。具体的には、第1ハウジング7は、略半環状に形成され、図1で示す如く外輪2の下方側に配置されている。従って、外輪2の非負荷圏側(負荷圏と軸受の直径方向反対側)の円周方向の略半分は、第1ハウジング7が未装着な(第1ハウジング7から露出し且つ突出する)未装着部分2aが構成されている。第1ハウジング7の内周面7aは、外輪2の外周面2bが直接当接して嵌合されるように、外輪2の外周面2bに沿う嵌合凹面となっている。第1ハウジング7の外周面7bは、内輪3に挿通された回転軸9の回転中心Oを中心とする円弧状の凸面を有している。第1ハウジング7の軸方向一端側の内周縁には、外輪2を軸方向に位置決めする凸状7cが形成されている。   The first housing 7 is mounted on the load zone side of the outer ring 2 that receives a radial load. Specifically, the first housing 7 is formed in a substantially semi-annular shape, and is disposed on the lower side of the outer ring 2 as shown in FIG. Accordingly, substantially half of the outer ring 2 in the circumferential direction on the non-load zone side (the opposite side of the load zone and the bearing in the diameter direction) is not attached to the first housing 7 (exposed and protrudes from the first housing 7). A mounting portion 2a is configured. The inner peripheral surface 7a of the first housing 7 is a fitting concave surface along the outer peripheral surface 2b of the outer ring 2 so that the outer peripheral surface 2b of the outer ring 2 is directly contacted and fitted. The outer peripheral surface 7 b of the first housing 7 has an arcuate convex surface centering on the rotation center O of the rotation shaft 9 inserted through the inner ring 3. A convex shape 7c for positioning the outer ring 2 in the axial direction is formed on the inner peripheral edge of the first housing 7 on one end side in the axial direction.

第1ハウジング7の両側面7d、7eおよび外周面7bの両先端面7fには、環状のリング溝7gが形成され、このリング溝7gにOリング12が変形した状態で嵌め込まれている。   An annular ring groove 7g is formed in both end faces 7d and 7e of the first housing 7 and both end faces 7f of the outer peripheral surface 7b, and the O-ring 12 is fitted into the ring groove 7g in a deformed state.

第1ハウジング7および軸受6は、第2ハウジング8に嵌入されている。この第2ハウジング8は、ハウジング本体部10と、このハウジング本体部10の他側に形成された段差面に、図示省略のボルト等の締結具で固定される補助体11とからなる。   The first housing 7 and the bearing 6 are fitted in the second housing 8. The second housing 8 includes a housing body 10 and an auxiliary body 11 fixed to a stepped surface formed on the other side of the housing body 10 with a fastener such as a bolt (not shown).

ハウジング本体部10には、回転軸9が貫通される開口15が形成され、このハウジング本体部10の内径面の非負荷圏側には、外輪2の未装着部分2aの外周面が当接して嵌合される嵌合面13が形成されている。また、ハウジング本体部10の内径面の負荷圏側には、段差面14が形成されている。   The housing body 10 is formed with an opening 15 through which the rotary shaft 9 passes, and the outer peripheral surface of the unmounted portion 2 a of the outer ring 2 is in contact with the non-load zone side of the inner diameter surface of the housing body 10. A fitting surface 13 to be fitted is formed. Further, a step surface 14 is formed on the load zone side of the inner diameter surface of the housing body 10.

段差面14は、第1ハウジング7の外周面7bとの間で所定の間隙を形成するように、第1ハウジング7の外周面7bに沿う形状の周面14aと、第1ハウジング7の一側面7dとの間で所定の間隙を形成する直径方向の壁面14bとからなる。従って、第1ハウジング7の外周面7bとハウジング本体部10の周面14aとの径方向の間には、間隔が数十μm〜数百μmであるラジアル空間19が形成されている。また、第1ハウジング7の一側面7dとハウジング本体部10の壁面14bとの軸方向の間には、間隔が数十μm〜数百μmであるアキシアル空間20が形成されている。   The step surface 14 has a circumferential surface 14 a shaped along the outer circumferential surface 7 b of the first housing 7 and one side surface of the first housing 7 so as to form a predetermined gap with the outer circumferential surface 7 b of the first housing 7. It consists of a diametric wall surface 14b that forms a predetermined gap with 7d. Therefore, a radial space 19 having a distance of several tens to several hundreds of μm is formed between the outer peripheral surface 7b of the first housing 7 and the peripheral surface 14a of the housing body 10. In addition, an axial space 20 having an interval of several tens of μm to several hundreds of μm is formed between the one side surface 7 d of the first housing 7 and the wall surface 14 b of the housing main body 10.

補助体11は、外輪2の外径と略同等の直径を有する切欠開口17が形成された半環状を呈している。また、補助体11の内面は、第1ハウジング7の他側面7eとの間で所定の間隙を形成し、両者間には、間隔が数十μm〜数百μmであるアキシアル空間21が形成されている。なお、ラジアル空間19および両方のアキシアル空間20、21により、ダンパー空間が構成され、第1ハウジング7に装着されたOリング12は、ハウジング本体部10の壁面14b、周面14aおよび補助体11の内面に密着してダンパー空間を密封している。   The auxiliary body 11 has a semi-annular shape in which a notch opening 17 having a diameter substantially equal to the outer diameter of the outer ring 2 is formed. In addition, a predetermined gap is formed between the inner surface of the auxiliary body 11 and the other side surface 7e of the first housing 7, and an axial space 21 having an interval of several tens to several hundreds of μm is formed therebetween. ing. The radial space 19 and the two axial spaces 20 and 21 constitute a damper space, and the O-ring 12 mounted on the first housing 7 includes the wall surface 14b, the peripheral surface 14a, and the auxiliary body 11 of the housing body 10. The damper space is sealed in close contact with the inner surface.

ハウジング本体部10には、粘性流体としての油をラジアル空間19および両方のアキシアル空間20、21に供給し充填するための油路23が形成されている。この油路23は、ラジアル空間19およびアキシアル空間20、21に油を均等に供給できるように、複数の分岐路23aを設けるのが好ましい。   The housing main body 10 is formed with an oil passage 23 for supplying and filling oil as a viscous fluid to the radial space 19 and both the axial spaces 20 and 21. The oil passage 23 is preferably provided with a plurality of branch passages 23a so that oil can be evenly supplied to the radial space 19 and the axial spaces 20, 21.

次に、上記転がり軸受装置1の動作を説明する。   Next, the operation of the rolling bearing device 1 will be described.

先ず、第2ハウジング8のハウジング本体部10に設けた油路23を介して、油を図示省略の粘性流体供給装置により第1ハウジング7と第2ハウジング8との間のラジアル空間19およびアキシアル空間20、21に供給する。この油がラジアル空間19およびアキシアル空間20、21に充填されると、第1ハウジング7は第2ハウジング8に対して浮いた状態となると共に、第1ハウジング7は負荷圏側で安定し回転することはない。このときの油圧力により、外輪2の未装着部分2aは、第2ハウジング8のハウジング本体部10の嵌合面13に押圧される。   First, the radial space 19 and the axial space between the first housing 7 and the second housing 8 are supplied by the viscous fluid supply device (not shown) through the oil passage 23 provided in the housing body 10 of the second housing 8. 20 and 21 are supplied. When this oil is filled in the radial space 19 and the axial spaces 20 and 21, the first housing 7 is in a floating state with respect to the second housing 8, and the first housing 7 rotates stably on the load zone side. There is nothing. Due to the oil pressure at this time, the unmounted portion 2 a of the outer ring 2 is pressed against the fitting surface 13 of the housing body 10 of the second housing 8.

さらに、回転軸8およびそれと一体の内輪3を回転させると、ラジアル荷重は、図1に矢印で示すように下方に作用する。ダンパー空間に充填されている油の圧力により、第1ハウジング7と第2ハウジング8との間で且つ負荷圏側に、制振ダンパーが構成される。このため、回転軸9の回転による荷重方向に発生する振動の吸収を効果的に行え、ハウジング7への振動伝達を抑制ないしは防止できるのである。   Further, when the rotating shaft 8 and the inner ring 3 integrated therewith are rotated, the radial load acts downward as indicated by an arrow in FIG. A damping damper is configured between the first housing 7 and the second housing 8 and on the load zone side by the pressure of the oil filled in the damper space. For this reason, the vibration generated in the load direction due to the rotation of the rotary shaft 9 can be effectively absorbed, and the vibration transmission to the housing 7 can be suppressed or prevented.

また、外輪2の未装着部分2aは、第2ハウジング8の嵌合面13に押圧されるため、外輪2は第1ハウジング7と第2ハウジング8とで挟持された状態となり、このときの摩擦力により、外輪2の連れ回りが防止できる共に、外輪2の未装着部分2aを、第2ハウジング8の嵌合面13に当接させて、軸受6の直径方向の位置決めを簡単な構造により行うことができる。   In addition, since the unmounted portion 2a of the outer ring 2 is pressed against the fitting surface 13 of the second housing 8, the outer ring 2 is sandwiched between the first housing 7 and the second housing 8, and the friction at this time The outer ring 2 can be prevented from being rotated by force, and the non-mounted portion 2a of the outer ring 2 is brought into contact with the fitting surface 13 of the second housing 8 so that the bearing 6 is positioned in the diametrical direction with a simple structure. be able to.

次に、本発明の他の実施形態を説明する。   Next, another embodiment of the present invention will be described.

図5に示す他の実施の形態は、第1ハウジング7は、外輪2の周方向の半周よりも大きく設けられ、しかも、外輪2は第1ハウジング7の内周面に非回転に嵌入(圧入)されたものである。なお、図1および図2で示した実施の形態と同一部材は、同一符号を付してそれぞれの説明は省略ないしは簡略にする。本実施の形態は、第1ハウジング7においても、外輪2の連れ回りが確実に防止できると共に、外輪2の未装着部分2aを、第2ハウジング8の嵌合面13に押圧して軸受6の位置決めを行うことができる。外輪2と第1ハウジング7の嵌合状態は、遊嵌状態であっても良い。   In the other embodiment shown in FIG. 5, the first housing 7 is provided larger than a half circumference in the circumferential direction of the outer ring 2, and the outer ring 2 is non-rotatably fitted (press-fit) on the inner circumferential surface of the first housing 7. ). The same members as those in the embodiment shown in FIGS. 1 and 2 are denoted by the same reference numerals, and the description thereof will be omitted or simplified. In the present embodiment, the rotation of the outer ring 2 can be reliably prevented even in the first housing 7, and the non-mounted portion 2 a of the outer ring 2 is pressed against the fitting surface 13 of the second housing 8. Positioning can be performed. The fitting state between the outer ring 2 and the first housing 7 may be a loose fitting state.

図6に示す他の実施の形態は、第1ハウジング7が矩形状に形成され、この第1ハウジング7に軸受6の負荷圏側が嵌合され、第1ハウジング7から突出する外輪2の未装着部分2aが、第2ハウジング8のハウジング本体部10の嵌合面13に嵌合するようになっている。なお、図1および図2で示した実施の形態と同一部材は、同一符号を付してそれぞれの説明は省略ないしは簡略する。   In another embodiment shown in FIG. 6, the first housing 7 is formed in a rectangular shape, the load zone side of the bearing 6 is fitted into the first housing 7, and the outer ring 2 protruding from the first housing 7 is not attached. The portion 2 a is adapted to be fitted to the fitting surface 13 of the housing body 10 of the second housing 8. The same members as those in the embodiment shown in FIGS. 1 and 2 are denoted by the same reference numerals, and the description thereof will be omitted or simplified.

図7および図8に示す他の実施の形態は、第1ハウジング7が矩形状に形成され、この第1ハウジング7に軸受6の外輪2の負荷圏側が嵌合され、突出する未装着部分2aが第2ハウジング8の嵌合面13に嵌合するようになっている。第1ハウジング7は、外輪2の周方向を半周よりも大きくなるように嵌合されている。第1ハウジング7と外輪2の嵌合状態は、圧入であっても遊嵌状態であっても良い。第1ハウジング7と外輪2の嵌合を圧入による場合には、第1ハウジング7においても、外輪2の連れ回りが防止できる。   In the other embodiment shown in FIGS. 7 and 8, the first housing 7 is formed in a rectangular shape, and the load housing side of the outer ring 2 of the bearing 6 is fitted into the first housing 7 so as to protrude and the unmounted portion 2a protruding. Is fitted to the fitting surface 13 of the second housing 8. The first housing 7 is fitted so that the circumferential direction of the outer ring 2 is larger than a half circumference. The fitting state between the first housing 7 and the outer ring 2 may be press-fit or loose fitting. When the fitting between the first housing 7 and the outer ring 2 is performed by press-fitting, the rotation of the outer ring 2 can be prevented also in the first housing 7.

また、第1ハウジング7と第2ハウジング8との間に形成されるラジアル空間19およびアキシアル空間20、21には、粘性流体としてグリースが充填されている。グリースは第1ハウジング7に嵌め込まれたOリングにより、封入されている。なお、図1および図2で示した実施の形態と同一部材は、同一符号を付してそれぞれの説明は省略ないしは簡略する。   Further, the radial space 19 and the axial spaces 20 and 21 formed between the first housing 7 and the second housing 8 are filled with grease as a viscous fluid. The grease is enclosed by an O-ring fitted in the first housing 7. The same members as those in the embodiment shown in FIGS. 1 and 2 are denoted by the same reference numerals, and the description thereof will be omitted or simplified.

上述したような各実施形態の転がり軸受装置1は、例えば自動車などの車両用のトランスミッションや、デファレンシャル等の内部に好適に用いることができる。特に、本発明は、マニュアルトランスミッション(MT)や連続可変変速機(CVT)用の軸受に対しては、その荷重負荷方向が略一定であり、外輪の負荷圏も略一方向となることから、特に有用である。   The rolling bearing device 1 of each embodiment as described above can be suitably used in a transmission for a vehicle such as an automobile, a differential, or the like. In particular, according to the present invention, for a bearing for a manual transmission (MT) or a continuously variable transmission (CVT), the load direction of the load is substantially constant, and the load zone of the outer ring is also approximately one direction. It is particularly useful.

本発明は、例えばマニュアルトランスミッションや連続可変変速機用の軸受の制振構造に利用可能である。   The present invention can be used for a vibration damping structure of a bearing for a manual transmission or a continuously variable transmission, for example.

転がり軸受装置を示す正面断面図Front sectional view showing a rolling bearing device 図1の転がり軸受装置の側面断面図Side sectional view of the rolling bearing device of FIG. 図1の転がり軸受装置の分解斜視図1 is an exploded perspective view of the rolling bearing device of FIG. 軸受および第1ハウジングの斜視図Perspective view of bearing and first housing 本発明の他の実施形態に係る転がり軸受装置を示す正面断面図Front sectional drawing which shows the rolling bearing apparatus which concerns on other embodiment of this invention. 本発明のさらに他の実施形態に係る転がり軸受装置を示す正面断面図Front sectional drawing which shows the rolling bearing apparatus which concerns on other embodiment of this invention. 本発明のさらに他の実施形態に係る転がり軸受装置を示す正面断面図Front sectional drawing which shows the rolling bearing apparatus which concerns on other embodiment of this invention. 図7の転がり軸受装置の側面断面図Side sectional view of the rolling bearing device of FIG.

符号の説明Explanation of symbols

1 転がり軸受装置 2 外輪
2a 未装着部分 2b 外周面
3 内輪 6 軸受
7 第1ハウジング 8 第2ハウジング
13 嵌合面
DESCRIPTION OF SYMBOLS 1 Rolling bearing apparatus 2 Outer ring 2a Unmounted part 2b Outer peripheral surface 3 Inner ring 6 Bearing 7 First housing 8 Second housing 13 Fitting surface

Claims (1)

軸受と、前記軸受の外輪に装着される第1ハウジングと、前記第1ハウジングとの間にダンパー空間を形成する第2ハウジングと、を具備し、
前記ダンパー空間に充填されている粘性流体からの流体圧力により、両ハウジング間に制振ダンパーが構成される転がり軸受の制振構造において、
第1ハウジングは、外輪の外周面の負荷圏側に配置されて、外輪の外周面の円周方向の一部に第1ハウジングを未装着とされる未装着部分が構成されており、かつ、その未装着部分は、粘性流体からの流体圧力により、第2ハウジングの非負荷圏に形成された嵌合面に押圧されることにより、前記外輪は前記第1ハウジングと前記第2ハウジングとで挟持されて軸受の直径方向の位置決めがされる、ことを特徴とする転がり軸受の制振構造。
A bearing, a first housing mounted on an outer ring of the bearing, and a second housing forming a damper space between the first housing,
In the damping structure of a rolling bearing in which a damping damper is configured between both housings by fluid pressure from the viscous fluid filled in the damper space,
The first housing is disposed on the load zone side of the outer peripheral surface of the outer ring, and a non-mounted portion in which the first housing is not mounted is configured in a part of the outer peripheral surface of the outer ring in the circumferential direction, and The unmounted portion is pressed against the fitting surface formed in the non-load zone of the second housing by the fluid pressure from the viscous fluid, so that the outer ring is sandwiched between the first housing and the second housing. A rolling bearing damping structure characterized in that the bearing is positioned in the diametrical direction .
JP2003298419A 2003-08-22 2003-08-22 Vibration control structure of rolling bearing Expired - Fee Related JP4244173B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2003298419A JP4244173B2 (en) 2003-08-22 2003-08-22 Vibration control structure of rolling bearing

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Application Number Priority Date Filing Date Title
JP2003298419A JP4244173B2 (en) 2003-08-22 2003-08-22 Vibration control structure of rolling bearing

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JP2005069317A JP2005069317A (en) 2005-03-17
JP4244173B2 true JP4244173B2 (en) 2009-03-25

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