JP4622250B2 - Bearing device - Google Patents

Bearing device Download PDF

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JP4622250B2
JP4622250B2 JP2004011528A JP2004011528A JP4622250B2 JP 4622250 B2 JP4622250 B2 JP 4622250B2 JP 2004011528 A JP2004011528 A JP 2004011528A JP 2004011528 A JP2004011528 A JP 2004011528A JP 4622250 B2 JP4622250 B2 JP 4622250B2
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ring
damping member
damping
end side
peripheral surface
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JP2005207438A (en
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誠二 多田
正 深尾
良 大西
清 谷本
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JTEKT Corp
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JTEKT Corp
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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
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
    • F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
    • F16C35/07—Fixing them on the shaft or housing with interposition of an element
    • F16C35/077—Fixing them on the shaft or housing with interposition of an element between housing and outer race ring
    • 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
    • F16C27/00—Elastic or yielding bearings or bearing supports, for exclusively rotary movement
    • F16C27/04—Ball or roller bearings, e.g. with resilient rolling bodies
    • 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
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/24—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for radial load mainly
    • F16C19/26—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for radial load mainly with a single row of rollers

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Vibration Prevention Devices (AREA)
  • Mounting Of Bearings Or Others (AREA)
  • Rolling Contact Bearings (AREA)

Description

本発明は、周面に制振部材を備えた軸受装置に関する。   The present invention relates to a bearing device having a damping member on a peripheral surface.

軸受装置の近傍で発生する種々の有害な振動を吸収するため、軸受装置と外部部材（ハウジング等）との間に制振材料を介在させることがある。
たとえば、内外輪及び転動体を備えた管楽器用の玉軸受において、外輪の外周面や内輪の内周面などの軌道輪周面に、比較的低い弾性係数を有する樹脂等よりなる制振部材を設ける技術が知られている（特許文献１参照。）。
特開２０００−１１０８４４号公報（図２、図３、第３頁） In order to absorb various harmful vibrations generated in the vicinity of the bearing device, a vibration damping material may be interposed between the bearing device and an external member (housing or the like).
For example, in a ball bearing for wind instruments provided with inner and outer rings and rolling elements, a damping member made of resin or the like having a relatively low elastic coefficient is provided on the outer peripheral surface of the outer ring or the inner peripheral surface of the inner ring. The technique to provide is known (refer patent document 1).
JP 2000-110844 A (FIG. 2, FIG. 3, page 3)

しかし、制振部材が樹脂等の耐熱性や剛性に乏しい部材よりなる場合には、高温となる部位や高剛性を要する部位に設置することができないという問題がある。
また、従来技術においては、制振部材を軌道輪周面上に固定する手法は、単に外部部材と軸受の軌道輪周面との間に制振部材を挟み込んでいるだけである。よって、軸受を外部部材に対して強固に固定しようとすると、軸受−外部部材間のしめしろを比較的大きくして圧入する必要があるが、この場合制振部材の残留圧縮応力が大きくなり制振効果が低下することとなる。逆に、制振効果の低下を避けるべく制振部材の残留圧縮応力を少なくしようとすると、振動等の影響もあり軸受が外部部材から脱落しやすくなる。 However, when the damping member is made of a member having poor heat resistance and rigidity, such as a resin, there is a problem that it cannot be installed at a part that becomes high temperature or a part that requires high rigidity.
Further, in the prior art, the method of fixing the vibration damping member on the raceway ring circumferential surface simply sandwiches the vibration damping member between the external member and the raceway ring circumferential surface of the bearing. Therefore, in order to firmly fix the bearing to the external member, it is necessary to press-fit with a relatively large interference between the bearing and the external member. The vibration effect will be reduced. On the other hand, if the residual compressive stress of the damping member is reduced to avoid a decrease in the damping effect, the bearing is likely to drop off from the external member due to the influence of vibration and the like.

本発明は、かかる状況に鑑みなされたものであり、制振部材を備えた軸受装置において、耐熱性と剛性が比較的高く、且つ、制振部材の残留圧縮応力を最小限としつつ脱落を防止できる軸受装置を提供することを目的としている。   The present invention has been made in view of such a situation, and in a bearing device provided with a vibration damping member, heat resistance and rigidity are relatively high, and dropout is prevented while minimizing residual compressive stress of the vibration damping member. It aims at providing the bearing device which can be performed.

本発明の軸受装置は、外輪と、残留圧縮応力の増加によって制振効果が低下する制振合金よりなり前記外輪の外周面に設けられる円環状の制振部材と、を備え、リング用溝を有する外部ケースに装着される軸受装置であって、前記外輪は、前記外周面の軸方向一端側において径方向に突出し前記制振部材の軸方向一端側への移動を防止する固定部と、前記外周面の軸方向他端側に設けられた周溝と、を備えており、更に、前記周溝に嵌合して固定され、前記制振部材の軸方向他端側への移動を防止するとともに、前記制振部材よりも径方向外方に突出し、この突出した部分が前記リング用溝に装着されるリング状部材と、を備え、前記制振部材は、軸方向一端側に形成された薄肉部と、軸方向他端側に形成された前記薄肉部以外の残余の部分と、を有するとともに、前記外部ケースから脱落しうるしめしろ又はすきまで当該外部ケースに嵌合され、前記薄肉部は、前記制振部材の軸方向一端側及び軸方向他端側への移動を阻止すべく、前記固定部の一部を収容することにより又は前記固定部に圧入されることにより前記固定部と係合され、前記残余の部分は、残留圧縮応力が作用していない状態又は残留圧縮応力が極めて弱い状態で外輪の外周面に固定されていることを特徴とする。 A bearing device of the present invention includes an outer ring and an annular damping member made of a damping alloy whose damping effect is reduced due to an increase in residual compressive stress, and is provided on the outer peripheral surface of the outer ring. The outer ring has a fixing portion that protrudes in a radial direction on one end side in the axial direction of the outer peripheral surface and prevents movement of the damping member toward one end side in the axial direction. a circumferential groove provided on the other axial end side of the outer peripheral surface provided with a further, fixed fitted in the circumferential groove to prevent axial movement of the other end of the damping member together, projecting radially outward from the damping member, and a ring-shaped member which is the protruded portion is attached to the ring groove, wherein the damping member is formed in one axial end Thin portion and the remaining portion other than the thin portion formed on the other axial end side , Which has a said that in tanning filtration or gap Shi may fall off the outer case fitted to the outer case, the thin portion is prevented from moving in the axial direction one end side and the other axial end of said vibration member Therefore, the remaining portion is engaged with the fixing portion by accommodating a part of the fixing portion or by being press-fitted into the fixing portion, and the remaining portion is in a state where residual compressive stress is not applied or residual compression. stress is characterized that you have been fixed to the outer peripheral surface of the outer ring in a very weak state.

このようにすると、制振部材が制振合金からなるので、一般的な樹脂等からなる場合と比較して耐熱性と剛性とが向上する。そして、外輪の外周面に設けられた制振部材は固定部とリング状部材とにより挟まれているから、制振部材を強く圧入しなくても外輪の外周面から脱落しない。且つリング状部材は制振部材よりも径方向に突出しているから、リング状部材の当該突出部分を外部ケース等に係合させることにより、強く圧入しなくても軸受装置が外部ケース等から脱落することがない。よって、制振部材の残留圧縮応力を最小限としつつ、制振部材や軸受装置自体の脱落を確実に防止することができる。 If it does in this way, since a damping member consists of damping alloy, heat resistance and rigidity will improve compared with the case where it consists of general resin etc. Then, since the damping member provided on the outer peripheral surface of the outer ring is sandwiched by the fixed portion and the ring-shaped member, not fall off from the outer peripheral surface of the outer ring without pressed strongly damping member. Also, since the ring-shaped member protrudes in the radial direction from the damping member, the bearing device can be removed from the outer case even if it is not strongly pressed by engaging the protruding portion of the ring-shaped member with the outer case. There is nothing to do. Therefore, it is possible to reliably prevent the vibration damping member and the bearing device itself from falling off while minimizing the residual compressive stress of the vibration damping member.

本発明の軸受装置は、その軸受部分が円筒ころ軸受又は針状ころ軸受であるのが好ましい。円筒ころ軸受や針状ころ軸受は、通常、アキシャル荷重がほとんど作用しない部位で用いられ、外部部材に対して強く圧入しない状態で使用されるため、同じく強い圧入を要しない構成とされた本発明において好適に用いられる。   In the bearing device of the present invention, the bearing portion is preferably a cylindrical roller bearing or a needle roller bearing. Cylindrical roller bearings and needle roller bearings are usually used in areas where little axial load is applied, and are used in a state where they are not strongly pressed into external members. Is preferably used.

制振部材として制振合金を用い、また、固定部及び各リング状部材を固定手段として用いたので、耐熱性や剛性が比較的高く、且つ、制振部材の残留圧縮応力を最小限としつつ脱落を防止できる軸受装置とすることができる。   Since the damping alloy is used as the damping member, and the fixing portion and each ring-like member are used as the fixing means, the heat resistance and rigidity are relatively high, and the residual compressive stress of the damping member is minimized. It can be set as the bearing apparatus which can prevent drop-off.

本発明の実施形態について、以下に図面を参照しつつ説明する。
図１（ａ）は、本発明の第一実施形態である自動車のトランスミッション用の軸受装置１の断面図である。なお、図１（ａ）及び後述の図２〜図６では、断面図は中心軸から半分のみ図示し、残りの部分は図示を省略している。
この軸受装置１は、その軸受部分が円筒ころ軸受１１とされている。この円筒ころ軸受１１は、周方向略等間隔おきに配置された転動体としての複数の円筒ころ２と、この円筒ころ２が転動する軌道面３ａを備えた軌道輪としての外輪３と、円筒ころ２の配置を周方向略等間隔おきに保持する保持器４と、を有している。そしてこの軸受装置１は、外輪３の外周面３ｂに設けられた円環状の制振部材５を備えている。制振部材５は、例えばＦｅ−Ａｌ系合金、Ｆｅ−Ｃｒ系合金、Ｍｎ−Ｃｕ系合金、Ｆｅ−Ｃｒ−Ａｌ系合金、Ｎｉ−Ｔｉ系合金、Ｍｇ系合金等の制振合金よりなる。
軸受装置１はトランスミッションのアルミ製のミッションケース１２に装着され且つトランスミッション内の駆動軸１０に外嵌しており、ミッションケース１２に対して駆動軸１０を回動自在に支持している。従って、軸受装置１の円筒ころ軸受１１とミッションケース１２との間に制振部材５が介在する状態となっている。 Embodiments of the present invention will be described below with reference to the drawings.
Fig.1 (a) is sectional drawing of the bearing apparatus 1 for motor vehicle transmissions which is 1st embodiment of this invention. In FIG. 1A and FIGS. 2 to 6 to be described later, the cross-sectional view shows only half from the central axis, and the remaining portions are not shown.
The bearing device 1 has a cylindrical roller bearing 11 at the bearing portion. The cylindrical roller bearing 11 includes a plurality of cylindrical rollers 2 as rolling elements arranged at substantially equal intervals in the circumferential direction, an outer ring 3 as a bearing ring having a raceway surface 3a on which the cylindrical rollers 2 roll, And a cage 4 that holds the arrangement of the cylindrical rollers 2 at substantially equal intervals in the circumferential direction. The bearing device 1 includes an annular damping member 5 provided on the outer peripheral surface 3 b of the outer ring 3. The damping member 5 is made of a damping alloy such as an Fe—Al alloy, an Fe—Cr alloy, an Mn—Cu alloy, an Fe—Cr—Al alloy, a Ni—Ti alloy, and an Mg alloy.
The bearing device 1 is mounted on a transmission case 12 made of aluminum of the transmission and is externally fitted to a drive shaft 10 in the transmission, and the drive shaft 10 is rotatably supported with respect to the transmission case 12. Therefore, the damping member 5 is interposed between the cylindrical roller bearing 11 of the bearing device 1 and the transmission case 12.

外輪３は、その外周面３ｂの軸方向一端側において径方向外側に突出するフランジ状の固定部６を有している。円環状の制振部材５の軸方向一端側端面５ａはこの固定部６に当接しており、この固定部６により制振部材５の軸方向一端側への移動が防止されている。   The outer ring 3 has a flange-shaped fixing portion 6 that protrudes radially outward at one axial end side of the outer peripheral surface 3b. An end surface 5a in the axial direction of the annular damping member 5 is in contact with the fixed portion 6, and the fixed portion 6 prevents the vibration controlling member 5 from moving toward the one end side in the axial direction.

一方、外輪３の外周面３ｂの軸方向他端側には、当該外周面３ｂの全周に亘って周溝９が設けられている。そして、この周溝９には、第一リング状部材７が嵌合しており、第一リング状部材７はかかる周溝９への嵌合により外輪３の外周面３ｂ側に固定されている。なお第一リング状部材７は、Ｃリングであり、一旦拡径するように弾性変形させた後に周溝９内に嵌め込んで設置され、その弾性力により周溝９内に固定されている。
第一リング状部材７の厚み（軸方向厚み）は周溝９の溝幅（軸方向幅）と略同一とされているため、第一リング状部材７は周溝９に嵌合しつつ着実に固定されている。また、第一リング状部材７の径方向幅は周溝９の径方向深さよりも大きくされているので、第一リング状部材７は外周面３ｂよりも径方向外側に突出している。 On the other hand, on the other end side in the axial direction of the outer circumferential surface 3b of the outer ring 3, a circumferential groove 9 is provided over the entire circumference of the outer circumferential surface 3b. The first ring-shaped member 7 is fitted into the circumferential groove 9, and the first ring-shaped member 7 is fixed to the outer circumferential surface 3 b side of the outer ring 3 by fitting into the circumferential groove 9. . The first ring-shaped member 7 is a C-ring, which is elastically deformed so as to expand once and then fitted into the circumferential groove 9 and is fixed in the circumferential groove 9 by its elastic force.
Since the thickness (axial thickness) of the first ring-shaped member 7 is substantially the same as the groove width (axial width) of the circumferential groove 9, the first ring-shaped member 7 is steadily fitted into the circumferential groove 9. It is fixed to. Further, since the radial width of the first ring-shaped member 7 is larger than the radial depth of the circumferential groove 9, the first ring-shaped member 7 protrudes radially outward from the outer peripheral surface 3b.

さらに、この第一リング状部材７と制振部材５との間には、スナップリングである第二リング状部材８が設けられている。第二リング状部材８は、第一リング状部材７と制振部材５の軸方向他端側端面５ｂとの間の隙間に挿入もしくは挟まれることにより、外輪３の外周面３ｂ上に固定されている。換言すれば、制振部材５は、その軸方向他端側に設けられ第一リング状部材７により軸方向他端側から支持された第二リング状部材８と、その軸方向一端側に設けられた固定部６と、により支持されている。かかる構成により、制振部材５は外輪３の外周面３ｂ上に固定され、当該外周面３ｂから脱落しないようにされている。
なお、このように制振部材５が固定部６と第二リング状部材８（及び第一リング状部材７）とに挟まれつつ固定された構成となるように周溝９の軸方向位置が決定される。即ち、周溝９の軸方向位置は、第二リング状部材８の厚み（軸方向厚み）や制振部材５の軸方向幅等を勘案して決定される。 Further, a second ring-shaped member 8 that is a snap ring is provided between the first ring-shaped member 7 and the damping member 5. The second ring-shaped member 8 is fixed on the outer peripheral surface 3 b of the outer ring 3 by being inserted or sandwiched in a gap between the first ring-shaped member 7 and the end surface 5 b on the other end side in the axial direction of the damping member 5. ing. In other words, the damping member 5 is provided on the other end side in the axial direction and is provided on the other end side in the axial direction by the first ring-like member 7 and on the one end side in the axial direction. The fixed portion 6 is supported. With this configuration, the vibration damping member 5 is fixed on the outer peripheral surface 3b of the outer ring 3 so as not to drop off from the outer peripheral surface 3b.
It should be noted that the axial position of the circumferential groove 9 is such that the damping member 5 is fixed while being sandwiched between the fixed portion 6 and the second ring-shaped member 8 (and the first ring-shaped member 7). It is determined. That is, the axial position of the circumferential groove 9 is determined in consideration of the thickness (axial thickness) of the second ring-shaped member 8, the axial width of the vibration damping member 5, and the like.

第二リング状部材８の径方向幅は、制振部材５の厚み（径方向厚み）よりも大とされているため、第二リング状部材８は制振部材５よりも径方向外側に突出する突出部８ａを有している。そして、この突出部８ａをミッションケース１２内に嵌合させることにより、軸受装置１がミッションケース１２に対して軸方向に移動しないようになっている。即ちこの突出部８ａがミッションケース１２と係合することにより、軸受装置１はミッションケース１２から脱落しないようにされている。   Since the radial width of the second ring-shaped member 8 is larger than the thickness (diametrical thickness) of the damping member 5, the second ring-shaped member 8 protrudes radially outward from the damping member 5. It has a protruding portion 8a. Then, by fitting the projecting portion 8 a into the mission case 12, the bearing device 1 is prevented from moving in the axial direction with respect to the mission case 12. That is, the protrusion 8 a is engaged with the transmission case 12, so that the bearing device 1 is not dropped from the transmission case 12.

軸受装置１の組立は次の手順により行う。先ず、円筒ころ軸受１１の外輪３の軸方向他端側（図１（ａ）における右側）から制振部材５を外嵌する。外輪３の外周面３ｂの外径は、固定部６（及び周溝９）の各部を除いて制振部材５の内径と略同一とされており、且つ、外周面３ｂの軸方向他端側には固定部６のような突出部（径方向外側に突出する部分）は無いので、外輪３の軸方向他端側から制振部材５を外輪３の外周面３ｂに外嵌することができる。次に、第一リング状部材７及び第二リング状部材８を設置する。これらリング状部材７，８は、Ｃリング又はスナップリングであるから、一旦拡径するように弾性変形させたのち外輪３の外周面３ｂ上に外嵌させて設置する。この際、第一リング状部材７は外周面３ｂの周溝９に嵌め込んで設置する。   The assembly of the bearing device 1 is performed according to the following procedure. First, the damping member 5 is externally fitted from the other axial end side (the right side in FIG. 1A) of the outer ring 3 of the cylindrical roller bearing 11. The outer diameter of the outer peripheral surface 3b of the outer ring 3 is substantially the same as the inner diameter of the damping member 5 except for each part of the fixed portion 6 (and the peripheral groove 9), and the other end side in the axial direction of the outer peripheral surface 3b. Since there is no protruding portion (portion protruding radially outward) like the fixed portion 6, the damping member 5 can be fitted on the outer peripheral surface 3 b of the outer ring 3 from the other axial end side of the outer ring 3. . Next, the first ring member 7 and the second ring member 8 are installed. Since these ring-shaped members 7 and 8 are C-rings or snap rings, they are elastically deformed so as to be once expanded in diameter, and are then fitted on the outer peripheral surface 3b of the outer ring 3. At this time, the first ring-shaped member 7 is installed by being fitted into the circumferential groove 9 of the outer peripheral surface 3b.

第二リング状部材８の突出部８ａとミッションケース１２とを係合させる方法は次の通りである。軸受装置１が装着されるミッションケース１２の内周面には、軸受装置１における第二リング状部材８の突出部８ａが挿入されるリング用溝１２ａが略全周に亘って設けられている。そして、軸受装置１をミッションケース１２に取り付ける際には、第二リング状部材８を縮径するように弾性変形させた状態でミッションケース１２に嵌め込む。（図１の断面図にあるように、かかる縮径を許容する隙間ｋが存在している。）そして、第二リング状部材８がリング用溝１２ａの位置に達すると第二リング状部材８が拡径して、第二リング状部材８の突出部８ａがリング用溝１２ａ内に挿入される。
なお、例えば第二リング状部材８をスナップリングとする場合、図１（ｂ）に示すように、ミッションケース１２には、スナップリングの端部ｔをミッションケース１２の他端側から挿入でき且つ軸受装置１をミッションケース１２に装着した状態において前記端点ｔを収容可能な切欠き部１２ｂを設ける。そして、スナップリングを縮径させた状態で切欠き部１２ｂに端点ｔを挿入し、前記リング用溝１２ａ位置でスナップリングを解放拡径する。なお、図１（ｂ）は、ミッションケース１２の切欠き部１２ｂ付近をミッションケース１２の他端側（図１（ａ）の右側）から見た図であり、軸受装置１の記載は省略している。 A method of engaging the protruding portion 8a of the second ring-shaped member 8 with the mission case 12 is as follows. On the inner peripheral surface of the transmission case 12 to which the bearing device 1 is mounted, a ring groove 12a into which the protruding portion 8a of the second ring-shaped member 8 in the bearing device 1 is inserted is provided over substantially the entire circumference. . And when attaching the bearing apparatus 1 to the mission case 12, it fits into the mission case 12 in the state elastically deformed so that the diameter of the 2nd ring-shaped member 8 might be reduced. (As shown in the cross-sectional view of FIG. 1, there is a gap k that allows such a diameter reduction.) When the second ring-shaped member 8 reaches the position of the ring groove 12a, the second ring-shaped member 8 Is expanded, and the protruding portion 8a of the second ring-shaped member 8 is inserted into the ring groove 12a.
For example, when the second ring-shaped member 8 is a snap ring, the end t of the snap ring can be inserted into the mission case 12 from the other end side of the mission case 12 as shown in FIG. In a state where the bearing device 1 is mounted on the transmission case 12, a notch 12b that can accommodate the end point t is provided. Then, the end point t is inserted into the notch 12b with the snap ring having a reduced diameter, and the snap ring is released and enlarged at the position of the ring groove 12a. 1B is a view of the vicinity of the notch 12b of the mission case 12 as viewed from the other end side of the mission case 12 (the right side of FIG. 1A), and the description of the bearing device 1 is omitted. ing.

軸受装置１のミッションケース１２への固定は、強力に圧入されたものではなく、そのしめしろは最小限とされるか、又はすきまばめとされている。上述のように第二リング状部材８の突出部８ａがミッションケース１２内に嵌合しているから、すきまばめ又はしめしろが最小限であったとしても軸受装置１はミッションケース１２から脱落しない。   The fixing of the bearing device 1 to the transmission case 12 is not strongly press-fitted, and the interference is minimized or a clearance fit. Since the protruding portion 8a of the second ring-shaped member 8 is fitted in the mission case 12 as described above, the bearing device 1 is removed from the mission case 12 even if the clearance fit or interference is minimal. do not do.

以上のように構成された第一実施形態の軸受装置１は、以下の作用効果を奏する。
制振部材が制振合金からなるので、一般的な樹脂等からなる場合と比較して耐熱性と剛性とが向上する。よって、最高で１５０℃程度の高温となるトランスミッション内温度に耐えうる軸受装置とすることができる。そして、制振部材５により、駆動軸１０とミッションケース１２との間の振動伝達を効果的に抑制することができる。 The bearing device 1 of the first embodiment configured as described above has the following effects.
Since the vibration damping member is made of a vibration damping alloy, heat resistance and rigidity are improved as compared with a case of being made of a general resin or the like. Therefore, it is possible to provide a bearing device that can withstand the internal temperature of the transmission that is as high as about 150 ° C. The vibration control member 5 can effectively suppress vibration transmission between the drive shaft 10 and the transmission case 12.

また、軌道輪たる外輪３の外周面３ｂに設けられた制振部材５は固定部６とリング状部材７，８とにより挟まれているから、制振部材５を外輪３の外周面３ｂに強く圧入しなくても制振部材５は当該外周面３ｂ上に確実に固定され、脱落することがない。即ち、制振部材５は外輪３に対してすきまばめとすることができ、又は最小限のしめしろで圧入することができる。これに加えて、第二リング状部材８は制振部材よりも径方向に突出しているから、第二リング状部材８の突出部８ａをミッションケース１２に係合させることにより、強く圧入しなくても軸受装置１がミッションケース１２等から脱落することがない。即ち、軸受装置１はミッションケース１２に対してすきまばめとすることができ、又は最小限のしめしろで圧入することができる。よって、制振部材５の残留圧縮応力を最小限又はゼロとしつつ、制振部材５の外輪３からの脱落や、軸受装置１のミッションケース１２からの脱落を確実に防止することができる。制振合金よりなる制振部材５は、残留圧縮応力が高いほどその制振効果が少なくなる傾向があるが、この残留圧縮応力を最小限又はゼロとすることにより、制振部材５の制振効果を最大限に引き出すことができる。   In addition, since the damping member 5 provided on the outer circumferential surface 3b of the outer ring 3 serving as the raceway ring is sandwiched between the fixed portion 6 and the ring-shaped members 7 and 8, the damping member 5 is placed on the outer circumferential surface 3b of the outer ring 3. Even if it is not strongly press-fitted, the damping member 5 is securely fixed on the outer peripheral surface 3b and does not fall off. That is, the damping member 5 can be a clearance fit with respect to the outer ring 3, or can be press-fitted with a minimum interference. In addition, since the second ring-shaped member 8 protrudes in the radial direction from the vibration damping member, the projecting portion 8a of the second ring-shaped member 8 is engaged with the transmission case 12 so that it does not press fit strongly. However, the bearing device 1 does not fall off the mission case 12 or the like. That is, the bearing device 1 can be a clearance fit with respect to the mission case 12, or can be press-fitted with a minimum interference. Therefore, it is possible to reliably prevent the damping member 5 from dropping from the outer ring 3 and the bearing device 1 from dropping from the transmission case 12 while minimizing or eliminating the residual compressive stress of the damping member 5. The damping member 5 made of a damping alloy tends to reduce the damping effect as the residual compressive stress increases. By reducing the residual compressive stress to a minimum or zero, the damping member 5 The effect can be maximized.

図２は、本発明に第二実施形態の軸受装置１である。なお、以下の図２〜図６においては、ミッションケース１２や駆動軸１０の記載を適宜省略する。この第二実施形態と第一実施形態との主たる相違点は、リング状部材の構成である。即ち、第一実施形態では、周溝９に嵌合して固定されるとともに制振部材５の軸方向他端側への移動を防止する第一リング状部材７と、外輪３の外周面３ｂに固定されつつ制振部材５よりも径方向外側に突出する第二リング状部材８とが別体であったが、本第二実施形態では、第一実施形態における第一リング状部材７と第二リング状部材８とが一体となった単一のリング状部材１３を用いている。このように、周溝９に嵌合して固定されるとともに制振部材５の軸方向他端側への移動を防止するリング状部材と、外輪３の外周面３ｂに固定されつつ制振部材５よりも径方向外側に突出するリング状部材とは別体でもよく、また両者を共通化した単一のリング状部材であってもよい。また、リング状部材１３（第一リング状部材７及び第二リング状部材８）としては、拡径するように弾性変形しうるリング状部材、即ち、スナップリングやＣリング等を用いることができる。   FIG. 2 shows a bearing device 1 according to a second embodiment of the present invention. In addition, in the following FIGS. 2-6, description of the mission case 12 and the drive shaft 10 is abbreviate | omitted suitably. The main difference between the second embodiment and the first embodiment is the configuration of the ring-shaped member. That is, in the first embodiment, the first ring-shaped member 7 that is fitted and fixed to the circumferential groove 9 and prevents the vibration damping member 5 from moving to the other axial end side, and the outer peripheral surface 3 b of the outer ring 3. The second ring-shaped member 8 that protrudes radially outward from the damping member 5 while being fixed to the vibration-damping member 5 is a separate body, but in the second embodiment, the first ring-shaped member 7 in the first embodiment and A single ring-shaped member 13 in which the second ring-shaped member 8 is integrated is used. As described above, the ring-shaped member that is fitted and fixed to the circumferential groove 9 and prevents the vibration-damping member 5 from moving toward the other end in the axial direction, and the vibration-damping member that is fixed to the outer peripheral surface 3 b of the outer ring 3. It may be a separate member from the ring-shaped member protruding outward in the radial direction from 5, or a single ring-shaped member in which both are made common. Moreover, as the ring-shaped member 13 (the first ring-shaped member 7 and the second ring-shaped member 8), a ring-shaped member that can be elastically deformed so as to expand its diameter, that is, a snap ring, a C ring, or the like can be used. .

また、この第二実施形態では、制振部材５の内周面の軸方向一端側に、径方向外側に向かって凹む凹部５ｃを備えており、この凹部５ｃが外輪３における固定部６の一部を収容することにより当該固定部６と係合している。かかる係合状態は、外輪３に対して制振部材５を軸方向他端側（図２の右側）から圧入することにより作製した。よって、制振部材５は、固定部６により軸方向一端側（図２の左側）に移動することが防止されているのみならず、軸方向他端側への移動もある程度阻止されている。したがって、リング状部材１３を取り付けていない状態でも、円筒ころ軸受１１と制振部材５とが分離しないように組み合わされた軸受部材として取り扱うことが可能である。そして更にリング状部材１３を設置することにより、制振部材５が外輪３の軸方向他端側から脱落することが確実に防止されている。   Further, in the second embodiment, a concave portion 5 c that is recessed toward the radially outer side is provided on one axial end side of the inner peripheral surface of the vibration damping member 5, and the concave portion 5 c is a part of the fixing portion 6 in the outer ring 3. The fixing portion 6 is engaged by accommodating the portion. Such an engaged state was produced by press-fitting the damping member 5 into the outer ring 3 from the other axial end side (the right side in FIG. 2). Therefore, the damping member 5 is not only prevented from moving to one end side in the axial direction (left side in FIG. 2) by the fixing portion 6, but also to some extent from moving to the other end side in the axial direction. Therefore, even when the ring-shaped member 13 is not attached, the cylindrical roller bearing 11 and the damping member 5 can be handled as a combined bearing member so as not to be separated. Further, by installing the ring-shaped member 13, the damping member 5 is reliably prevented from falling off from the other axial end side of the outer ring 3.

図３は、本発明の第三実施形態の軸受装置１の断面図である。この第三実施形態では、制振部材５の軸方向一端側縁部の内周面に段差があり、この段差により、制振部材５の軸方向一端側縁部において他の部分よりも内径が大きい薄肉部５ｄが形成されている。そして、制振部材５と外輪３とは、薄肉部５ｄの内周面と固定部６の外周面との間においてのみ比較的強く圧入されている。換言すれば、制振部材５が外輪３の外周面３ｂに装着された状態において、制振部材５のうち薄肉部５ｄの部分のみに比較的強い残留圧縮応力が作用しているが、制振部材５の薄肉部５ｄ以外の部分には残留圧縮応力が作用していない（あるいは残留圧縮応力が極めて弱い）状態である。この場合、薄肉部５ｄが外輪３に圧入されているから、リング状部材１３を取り付けていない状態でも、円筒ころ軸受１１と制振部材５とが分離しないように組み合わされた軸受部材として取り扱うことが可能である。そして更にリング状部材１３を設置することにより、外輪３の軸方向他端側からの制振部材５の脱落が確実に防止されている。この第三実施形態でも、制振部材５の薄肉部５ｄを除く大部分には残留圧縮応力が無いか又は極めて少ないため、制振部材５の制振効果が最大限に発揮される。   FIG. 3 is a cross-sectional view of the bearing device 1 according to the third embodiment of the present invention. In this third embodiment, there is a step on the inner peripheral surface of the edge on the one end side in the axial direction of the damping member 5, and this step makes the inner diameter of the edge on the one end side in the axial direction of the damping member 5 larger than the other portions. A large thin portion 5d is formed. And the damping member 5 and the outer ring | wheel 3 are press-fitted comparatively strongly only between the internal peripheral surface of the thin part 5d, and the outer peripheral surface of the fixing | fixed part 6. FIG. In other words, in the state where the damping member 5 is mounted on the outer peripheral surface 3b of the outer ring 3, a relatively strong residual compressive stress acts only on the thin portion 5d of the damping member 5. Residual compressive stress is not acting on the portions other than the thin portion 5d of the member 5 (or the residual compressive stress is extremely weak). In this case, since the thin wall portion 5d is press-fitted into the outer ring 3, the cylindrical roller bearing 11 and the vibration damping member 5 are handled as a combined bearing member so as not to be separated even when the ring-shaped member 13 is not attached. Is possible. Further, by installing the ring-shaped member 13, the vibration damping member 5 is reliably prevented from falling off from the other axial end side of the outer ring 3. Even in the third embodiment, since most of the damping member 5 except the thin portion 5d has no or very little residual compressive stress, the damping effect of the damping member 5 is maximized.

図４は、本発明の第四実施形態の軸受装置１の断面図である。この第四実施形態は、制振部材５が３つの部材に分割されている点以外は図１（ａ）に示す第一実施形態と同様の構成である。第四実施形態では、制振部材５は、軸方向に隣接配置された３つの円環状部材である第一制振部材５１、第二制振部材５２、第三制振部材５３からなる。３つの制振部材５１，５２，５３は全て同一の矩形断面を有する同一形状の部材である。そして、隣り合う第一制振部材５１と第二制振部材５２との間、及び、同じく隣り合う第二制振部材５２と第三制振部材５３との間には、制振部材同士が摺動しうる接触面ｓが存在する。この２つの接触面ｓは、いずれも径方向に対して平行な面である。この接触面ｓにおいて制振部材同士が摺動するため、制振部材５による制振効果がより一層高くなる。   FIG. 4 is a cross-sectional view of the bearing device 1 according to the fourth embodiment of the present invention. The fourth embodiment has the same configuration as that of the first embodiment shown in FIG. 1A except that the damping member 5 is divided into three members. In the fourth embodiment, the vibration damping member 5 includes a first vibration damping member 51, a second vibration damping member 52, and a third vibration damping member 53 that are three annular members arranged adjacent to each other in the axial direction. The three damping members 51, 52, 53 are all members having the same rectangular cross section. And between the adjacent 1st damping member 51 and the 2nd damping member 52, and between the adjacent 2nd damping member 52 and the 3rd damping member 53, vibration damping members are mutually. There is a slidable contact surface s. The two contact surfaces s are both parallel to the radial direction. Since the damping members slide on the contact surface s, the damping effect of the damping member 5 is further enhanced.

この第四実施形態では、第一制振部材５１と第三制振部材５３とが同一の制振合金からなり、第二制振部材５２、制振部材５１，５３とは別種類の制振合金からなる。このように制振部材を複数種類の制振合金よりなる構成とすることにより、各合金材料の特性をそれぞれ生かした制振部材とすることができ、制振部材の設計自由度を高めることができる。本実施形態では、第一制振部材５１及び第三制振部材５３は比較的耐油性に優れた材料であり、第二制振部材５２は比較的耐油性に乏しい材料としている。耐油性の比較的乏しい第二制振部材５２を、耐油性に比較的優れた第一制振部材５１，第三制振部材５３で挟み込むことにより、潤滑オイルが多く存在するトランスミッション内の軸受において耐油性に比較的乏しい第二制振部材５２を使用することが可能となる。一方、制振部材５１，５３の材料と、制振部材５２の材料とは、それぞれトランスミッション内における複数の振動周波数領域（ピーク）のそれぞれを吸収するのに適した材料とされている。よって、制振性能が更に高くされている。   In the fourth embodiment, the first damping member 51 and the third damping member 53 are made of the same damping alloy, and the second damping member 52 and the damping members 51 and 53 are different types of damping. Made of alloy. In this way, by configuring the vibration damping member to be made of a plurality of types of vibration damping alloys, it is possible to obtain a vibration damping member that takes advantage of the characteristics of each alloy material, thereby increasing the degree of freedom in designing the vibration damping member. it can. In the present embodiment, the first damping member 51 and the third damping member 53 are materials that are relatively excellent in oil resistance, and the second damping member 52 is a material that is relatively poor in oil resistance. In a bearing in a transmission in which a large amount of lubricating oil exists, the second damping member 52 having relatively low oil resistance is sandwiched between the first damping member 51 and the third damping member 53 having relatively high oil resistance. It becomes possible to use the second vibration damping member 52 that is relatively poor in oil resistance. On the other hand, the material of the damping members 51 and 53 and the material of the damping member 52 are materials suitable for absorbing each of a plurality of vibration frequency regions (peaks) in the transmission. Therefore, the damping performance is further enhanced.

図５は、第五実施形態の軸受装置１の断面図である。図４の第四実施形態では制振部材５を３つに分割したが、この第五実施形態では更に分割数を増やしており、制振部材５は軸方向に分割された８つの制振部材５１〜５８よりなる。制振部材５１〜５８は全て同一形状の部材であり、それぞれの断面形状も同一の矩形である。そして、制振部材同士が摺動しうる接触面ｓは径方向に平行とされている。
このように制振部材を８つとしたことにより、接触面ｓがさらに増加して制振効果が高くなる。また、分割数を増やすほど制振部材の軸方向厚みが薄くなるため、制振合金の加工性が高くなり、制振部材の作製が容易となる。また、制振部材の分割数を増やすことにより、異種合金材料を組み合わせて使用する際における組合せ自由度も更に高まる。 FIG. 5 is a cross-sectional view of the bearing device 1 of the fifth embodiment. In the fourth embodiment of FIG. 4, the vibration damping member 5 is divided into three, but in the fifth embodiment, the number of divisions is further increased, and the vibration damping member 5 is divided into eight vibration damping members divided in the axial direction. 51-58. The damping members 51 to 58 are all members having the same shape, and their cross-sectional shapes are also the same rectangle. The contact surface s on which the damping members can slide is parallel to the radial direction.
Thus, by using eight damping members, the contact surface s further increases and the damping effect is enhanced. Further, since the axial thickness of the damping member is reduced as the number of divisions is increased, the workability of the damping alloy is increased and the production of the damping member is facilitated. Further, by increasing the number of divisions of the damping member, the degree of freedom of combination when different alloy materials are used in combination is further increased.

図４や図５の実施形態のように、制振部材５を複数の円環状部材が軸方向に隣接配置された構成とすることにより、更に別の効果もある。即ちこの場合、軸受装置１がミッションケース１２に対して傾いた場合に当該傾きに対する許容度が大きくなる。つまり、軸方向に隣接配置された複数の制振部材５のそれぞれが姿勢を変化させることにより、制振部材５全体として変形しやすくなる。つまり、制振部材５全体として軸受装置１の前記傾きに追従して変形しやすくなる。   As in the embodiment of FIGS. 4 and 5, the vibration damping member 5 has a configuration in which a plurality of annular members are arranged adjacent to each other in the axial direction. That is, in this case, when the bearing device 1 is tilted with respect to the mission case 12, the tolerance for the tilt increases. That is, the vibration damping member 5 as a whole is easily deformed by changing the posture of each of the plurality of vibration damping members 5 arranged adjacent to each other in the axial direction. That is, the vibration damping member 5 as a whole is easily deformed following the inclination of the bearing device 1.

図６は、本発明の第六実施形態である軸受装置１の断面図である。ここでは、制振部材５は軸方向に６分割されている。即ち制振部材５は、軸方向に隣接配置された複数の円環状部材である制振部材５１〜制振部材５６の合計６つの制振部材よりなる。そして、これら６つの制振部材５１〜５６が接触面ｓを介して軸方向に隙間なく隣接配置されている点は図４及び図５の実施形態と同様である。ただし、この第六実施形態では、接触面ｓが径方向に対して平行な面のみから構成されているのではなく、接触面ｓが径方向に対して傾斜した面をも含んでいる。この場合、当該傾斜面により隣接する制振部材同士の摺動面が広くなり、制振効果を更に高めることができる。また、特にラジアル荷重が作用した場合に制振部材の当該傾斜面同士で摺動が起こり制振部材を変形させることになるため、制振効果をさらに高めることができる。
なお、本実施形態形態では、接触面ｓのうち径方向に傾斜した部分は平面としているが、これが曲面であってもよい。 FIG. 6 is a sectional view of the bearing device 1 according to the sixth embodiment of the present invention. Here, the damping member 5 is divided into six in the axial direction. That is, the damping member 5 includes a total of six damping members including a damping member 51 to a damping member 56 that are a plurality of annular members arranged adjacent to each other in the axial direction. And the point which these six damping members 51-56 are adjacently arrange | positioned through the contact surface s without a gap in the axial direction is the same as that of embodiment of FIG.4 and FIG.5. However, in the sixth embodiment, the contact surface s is not composed only of a surface parallel to the radial direction, but includes a surface in which the contact surface s is inclined with respect to the radial direction. In this case, the sliding surface between the adjacent damping members is widened by the inclined surface, and the damping effect can be further enhanced. In addition, particularly when a radial load is applied, sliding occurs between the inclined surfaces of the vibration damping member, and the vibration damping member is deformed. Therefore, the vibration damping effect can be further enhanced.
In the present embodiment, the radially inclined portion of the contact surface s is a flat surface, but it may be a curved surface.

上述の第一乃至第六実施形態では、軸受装置における軸受部分が円筒ころ軸受であったが、本発明は円筒ころ又は針状ころ軸受であるのが好ましい。円筒ころ軸受や針状ころ軸受は、通常、アキシャル荷重がほとんど作用しない部位で用いられる。したがって、これら円筒ころ軸受や針状ころ軸受は、外部ケース等の外部部材に対して強く圧入しない状態又はすきまばめの状態とされ、例えばスナップリング等を用いて外部ケース等に取り付けられている。一方、本発明では、軸受装置１を外部ケース等に圧入しなくても軸受装置１や制振部材５が脱落しない構造とされており、これにより制振部材５の残留圧縮応力をゼロ又は最小限として制振性能を最大限に引き出している。したがって、強い圧入をしなくてもよい構成とされた本発明は、同様に強く圧入しない状態で用いられる円筒ころ軸受や針状ころ軸受において好適に用いられる。   In the first to sixth embodiments described above, the bearing portion in the bearing device is a cylindrical roller bearing, but the present invention is preferably a cylindrical roller or a needle roller bearing. Cylindrical roller bearings and needle roller bearings are usually used at sites where little axial load is applied. Therefore, these cylindrical roller bearings and needle roller bearings are in a state where they are not strongly pressed into an external member such as an external case or in a state of clearance fit, and are attached to the external case using a snap ring or the like, for example. . On the other hand, in the present invention, the bearing device 1 and the damping member 5 do not fall off even if the bearing device 1 is not press-fitted into the outer case or the like, so that the residual compressive stress of the damping member 5 is zero or minimized. As a limit, the damping performance is maximized. Therefore, the present invention which does not require strong press-fitting is suitably used in a cylindrical roller bearing and a needle roller bearing which are similarly used without being strongly press-fitted.

上記の各実施形態では、制振部材５は外輪３の外周面に設けられているが、軸受が内輪を備える場合には当該内輪の内周面に制振部材５を設けても良いことはいうまでもない。また、軌道輪の固定部６と制振部材５の軸方向一端側の端面５ａ（図１（ａ）参照）との間に他部材が介在していてもよいことも当然である。   In each of the above embodiments, the damping member 5 is provided on the outer circumferential surface of the outer ring 3, but when the bearing includes an inner ring, the damping member 5 may be provided on the inner circumferential surface of the inner ring. Needless to say. Of course, another member may be interposed between the fixed portion 6 of the bearing ring and the end face 5a on one end side in the axial direction of the damping member 5 (see FIG. 1A).

本発明では、図３に示す如く、軌道輪の軌道面３ａと転動体（円筒ころ２）との接触部分の軸方向長さである有効接触幅Ｌ１は、制振部材５の軸方向長さ（制振部材５と軌道輪とが接触している部分の軸方向長さ）Ｌ２以下の長さとするのが好ましい。さらに、制振部材５と軌道輪（外輪３）とが接触している部分の軸方向存在範囲Ｈ２は、軌道面３ａと転動体（円筒ころ２）との接触部分の軸方向存在範囲Ｈ１の全てを含んでいるのが好ましい。軸受装置１を介して伝達される振動（駆動軸１０とミッションケース１２との間の振動）は、転動体（円筒ころ２）と軌道面３ａとの接触部分を通じて伝達されるが、かかる接触部分の軸方向存在範囲Ｈ１をカバーする範囲に制振部材５が設けられているため、軸受装置１としての制振性能がより一層高まるからである。   In the present invention, as shown in FIG. 3, the effective contact width L1, which is the axial length of the contact portion between the raceway surface 3a of the raceway and the rolling element (cylindrical roller 2), is the axial length of the damping member 5. (Axial length of a portion where the vibration damping member 5 and the raceway are in contact with each other) The length is preferably equal to or less than L2. Furthermore, the axial direction existence range H2 of the part where the damping member 5 and the raceway ring (outer ring 3) are in contact is the axial direction existence range H1 of the contact part between the raceway surface 3a and the rolling element (cylindrical roller 2). Preferably all are included. The vibration transmitted through the bearing device 1 (vibration between the drive shaft 10 and the transmission case 12) is transmitted through the contact portion between the rolling element (cylindrical roller 2) and the raceway surface 3a. This is because the vibration damping member 5 is provided in a range that covers the axial direction existence range H1, and hence the vibration damping performance as the bearing device 1 is further enhanced.

（ａ）は、本発明の第一実施形態である軸受装置の断面図であり、（ｂ）は、ミッションケース（アルミ外ケース）に設けられたスナップリング挿入用切欠きを示す図である。(A) is sectional drawing of the bearing apparatus which is 1st embodiment of this invention, (b) is a figure which shows the notch for snap ring insertion provided in the mission case (aluminum outer case). 本発明の第二実施形態である軸受装置の断面図である。It is sectional drawing of the bearing apparatus which is 2nd embodiment of this invention. 本発明の第三実施形態である軸受装置の断面図である。It is sectional drawing of the bearing apparatus which is 3rd embodiment of this invention. 本発明の第四実施形態である軸受装置の断面図である。It is sectional drawing of the bearing apparatus which is 4th embodiment of this invention. 本発明の第五実施形態である軸受装置の断面図である。It is sectional drawing of the bearing apparatus which is 5th embodiment of this invention. 本発明の第六実施形態である軸受装置の断面図である。It is sectional drawing of the bearing apparatus which is 6th embodiment of this invention.

符号の説明Explanation of symbols

１ 軸受装置
２ 円筒ころ
３ 外輪（軌道輪）
３ｂ 外輪の外周面（周面）
５ 制振部材
６ 固定部
７ 第一リング状部材（リング状部材）
８ 第二リング状部材（リング状部材）
９ 周溝
１１ 円筒ころ軸受
１３ リング状部材
５１〜５８ 複数の制振部材（円環状部材）
ｓ 接触面（隣接配置された制振部材相互間の接触面） 1 Bearing device 2 Cylindrical roller 3 Outer ring (Raceway ring)
3b Outer ring outer peripheral surface (peripheral surface)
5 Damping member 6 Fixed part 7 First ring-shaped member (ring-shaped member)
8 Second ring-shaped member (ring-shaped member)
9 Circumferential groove 11 Cylindrical roller bearing 13 Ring-shaped member 51-58 A plurality of damping members (annular members)
s Contact surface (contact surface between adjacent damping members)

Claims (2)

外輪と、残留圧縮応力の増加によって制振効果が低下する制振合金よりなり前記外輪の外周面に設けられる円環状の制振部材と、を備え、リング用溝を有する外部ケースに装着される軸受装置であって、
前記外輪は、前記外周面の軸方向一端側において径方向に突出し前記制振部材の軸方向一端側への移動を防止する固定部と、前記外周面の軸方向他端側に設けられた周溝と、を備えており、
更に、前記周溝に嵌合して固定され、前記制振部材の軸方向他端側への移動を防止するとともに、前記制振部材よりも径方向外方に突出し、この突出した部分が前記リング用溝に装着されるリング状部材と、を備え、
前記制振部材は、軸方向一端側に形成された薄肉部と、軸方向他端側に形成された前記薄肉部以外の残余の部分と、を有するとともに、前記外部ケースから脱落しうるしめしろ又はすきまで当該外部ケースに嵌合され、
前記薄肉部は、前記制振部材の軸方向一端側及び軸方向他端側への移動を阻止すべく、前記固定部の一部を収容することにより又は前記固定部に圧入されることにより前記固定部と係合され、
前記残余の部分は、残留圧縮応力が作用していない状態又は残留圧縮応力が極めて弱い状態で外輪の外周面に固定されていることを特徴とする軸受装置。 An outer ring and an annular damping member made of a damping alloy whose damping effect is reduced by an increase in residual compressive stress and provided on the outer peripheral surface of the outer ring, and is attached to an outer case having a ring groove A bearing device,
The outer ring includes a fixed portion that protrudes in a radial direction on one axial end side of the outer peripheral surface and prevents the vibration damping member from moving toward one axial end side, and a circumferential portion provided on the other axial end side of the outer peripheral surface. And a groove,
Furthermore, fixed fitted to the circumferential groove, thereby preventing axial movement of the other end of the damping member, projects radially outward from the damping member and the projecting portion A ring-shaped member mounted in the ring groove ,
The vibration damping member has a thin portion formed on one end side in the axial direction, and a remaining portion other than the thin portion formed on the other end side in the axial direction, and can be removed from the outer case. Or it fits into the outer case until it is opened,
The thin-walled portion is accommodated by accommodating a part of the fixed portion or by being press-fitted into the fixed portion so as to prevent the vibration damping member from moving toward one axial end and the other axial end. Engaged with the fixed part,
The remainder of the bearing device according to claim Rukoto state or residual compressive stress residual compressive stress is not applied is in a very weak state is fixed to the outer peripheral surface of the outer ring. 軸受部分が円筒ころ軸受又は針状ころ軸受であることを特徴とする請求項１に記載の軸受装置。 The bearing device according to claim 1, wherein the bearing portion is a cylindrical roller bearing or a needle roller bearing .
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