JPS60172720A - Pressurized bearing device - Google Patents
Pressurized bearing deviceInfo
- Publication number
- JPS60172720A JPS60172720A JP2519784A JP2519784A JPS60172720A JP S60172720 A JPS60172720 A JP S60172720A JP 2519784 A JP2519784 A JP 2519784A JP 2519784 A JP2519784 A JP 2519784A JP S60172720 A JPS60172720 A JP S60172720A
- Authority
- JP
- Japan
- Prior art keywords
- inner ring
- hollow shaft
- expansion
- preload
- housing
- 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.)
- Granted
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
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/52—Bearings with rolling contact, for exclusively rotary movement with devices affected by abnormal or undesired conditions
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Support Of The Bearing (AREA)
Abstract
Description
【発明の詳細な説明】
本発明は中空軸に軸受を増付け、該軸受を定位置予圧す
る予圧軸受装置の改良に係わるものである。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an improvement in a preload bearing device that adds a bearing to a hollow shaft and preloads the bearing in a fixed position.
従来より例えば工作機械の主軸用軸受装置に、軸のラジ
アル方向度びアキシアル方向の位置決めを正確にすると
共に軸の振れを抑えるため更に、軸受の剛性を高めるた
め等の目的で軸受を予圧して用いる予圧軸受装置が知ら
れている。この定位 。Conventionally, for example, bearing devices for the main shaft of machine tools have been preloaded to ensure accurate radial and axial positioning of the shaft, to suppress shaft runout, and to increase the rigidity of the bearing. Preload bearing devices for use are known. This localization.
置予圧を得る方法として、
（１） あらかじめ内輪及び外輪の端面の軸方向の差す
なわち差幅寸法または軸方向すきまを調整した組合わせ
軸受を、締付けて使用する方法、（２）予圧を与えるよ
うに寸法調整した間座やシムを２個の軸受間に使用する
方法、
（３）軸方向すきまが調整できるボルト、ナツトなどを
締付けて使用する方法、
が知られ、実施されている。There are two ways to obtain preload: (1) use a combination bearing in which the axial difference between the end faces of the inner ring and outer ring, that is, the differential width dimension or axial clearance, is adjusted in advance; The following methods are known and practiced: (3) using a spacer or shim with adjusted dimensions between two bearings; and (3) tightening bolts, nuts, etc. whose axial clearance can be adjusted.
一カ、回転軸についても、例えば切削機械は主軸の内部
にチャックや工具等の操作機構を備えるために、中空軸
を使用したものは多数ある。Regarding the rotary shaft, for example, many cutting machines use a hollow shaft because they have operating mechanisms such as chucks and tools inside the main shaft.
従来の上記予圧軸受装置にあっては次の欠点を有してい
る。すなわち、上記軸受装置が高速回転すると、内輪や
中空軸が遠心力によって膨張し、軸受の予圧すきまが増
大する。その結果、軸受装置の予圧量が過大となり、発
熱や摩擦モーメントの増大あるいは疲れ寿命の低下を招
くのである。The conventional preload bearing device described above has the following drawbacks. That is, when the bearing device rotates at high speed, the inner ring and the hollow shaft expand due to centrifugal force, increasing the preload clearance of the bearing. As a result, the amount of preload on the bearing device becomes excessive, leading to an increase in heat generation and frictional moment, or a reduction in fatigue life.
本発明の目的は、従来の予圧軸受装置の欠点である高速
回転すると予圧量が増大する点を解決した予圧軸受装置
を提供することにある。SUMMARY OF THE INVENTION An object of the present invention is to provide a preload bearing device that solves the drawback of conventional preload bearing devices in that the amount of preload increases when rotating at high speed.
本発明は上記目的達成する手段として、中空軸の線膨張
係数を軸受の内輪、外輪やハウジングのそり、よりも小
さくし、高速回転時に発生する熱によって中空軸と軸受
及びハウジングとの膨張の差を利用し、中空軸と内輪と
のはめあいしめじろを減小させることに着目して、なさ
れたものである本発明は、中空軸及びハウジング及び軸
受かもなる軸受装置であって、前記軸受が高速回転時に
も必要なしめしろで前記中空軸に嵌合し、かつハウジン
グに嵌合し、さらに定位置予圧になるように組込まれる
予圧軸受装置において、前記中空軸の線膨張係数が前記
内輪、前記外輪及び前記ハウジングの線膨張係数よりも
小さく、その結果、高速回転時に生ずる発熱による前記
内輪と前記中空れぞれの′線膨張係数の差は前記内輪が
回転遠心力で膨張することによって増大する予圧量な相
殺する分であることを特徴とする予圧軸受装置である次
に図を用いて本発明の詳細な説明する。As a means to achieve the above object, the present invention makes the linear expansion coefficient of the hollow shaft smaller than that of the inner ring, outer ring, and housing of the bearing, and the difference in expansion between the hollow shaft, the bearing, and the housing due to the heat generated during high-speed rotation. The present invention was made by focusing on reducing the fit between a hollow shaft and an inner ring by utilizing In a preload bearing device that is fitted to the hollow shaft with a necessary interference even during rotation, is fitted into a housing, and is incorporated so as to be preloaded in a fixed position, the coefficient of linear expansion of the hollow shaft is equal to that of the inner ring, the The coefficient of linear expansion is smaller than that of the outer ring and the housing, and as a result, the difference in the coefficient of linear expansion between the inner ring and the hollow space due to heat generated during high-speed rotation increases as the inner ring expands due to rotational centrifugal force. DESCRIPTION OF THE PREFERRED EMBODIMENTS Next, the present invention will be described in detail with reference to the drawings.
第１図は本発明の予圧軸受装置で、中空軸１ｏ及びハウ
ジング加及び２個のアンギュラ玉軸受（資）からなる。FIG. 1 shows a preload bearing device of the present invention, which consists of a hollow shaft 1o, a housing member, and two angular contact ball bearings.
アンギュラ玉軸受間の内輪３１は高速回転時にも必要な
しめしるで中空軸ＩＯに嵌合している。−カアンギュラ
玉軸受Ｉの外輪３２はハウジング加に嵌合している。内
輪３１と外輪３２との間には複輪間座力とが介装されて
いる。内輪間座４０と外輪間座間のそれぞれの軸方向長
さは両軸受間に予圧を与えるように寸法調整されている
。内輪３１，３１と内輪間座４０は中空軸１０の屑１１
と中空軸に遊嵌するスリーブ６００間にスリーブ６０の
外側に配置する軸受ナツト７０を締めつけることによっ
て軸方向に固定されている、外輪３２．３２と外輪間座
犯はハウジング加の屑２１と屑２１と反対側に配設する
前蓋８０との間に前蓋８０をボルト９０によってハウジ
ング加に螺着することによって固定されている。以上、
軸方向に各部品（内輪３１．３１と内輪間座４０、外輪
３２．３２と外輪間座５０）間にすきまのない状態で固
定し、軸受間が定位置予圧される。The inner ring 31 between the angular contact ball bearings is fitted onto the hollow shaft IO with the necessary fit even during high speed rotation. - The outer ring 32 of the angular contact ball bearing I is fitted into the housing. A double wheel spacer is interposed between the inner ring 31 and the outer ring 32. The respective axial lengths between the inner ring spacer 40 and the outer ring spacer are adjusted to provide preload between both bearings. The inner rings 31, 31 and the inner ring spacer 40 are the scraps 11 of the hollow shaft 10.
The outer ring 32, 32 and the outer ring are fixed in the axial direction by tightening the bearing nut 70 disposed on the outside of the sleeve 60 between the sleeve 600 which loosely fits on the hollow shaft. The front cover 80 is fixed between the housing 21 and a front cover 80 disposed on the opposite side by screwing the front cover 80 onto the housing with bolts 90. that's all,
Each component (inner ring 31.31 and inner ring spacer 40, outer ring 32.32 and outer ring spacer 50) is fixed in the axial direction with no gaps between them, and the bearings are preloaded in a fixed position.
そして、中空軸１００線膨張係数が内輪３１、外輪３２
及びハウジング加の線膨張係数よりも高速回転時に内輪
３１及び中空軸１０が回転遠心力で膨張することによる
予圧量の増大を内輪３Ｉと中空軸１０の膨張量の差から
はめあいしめじろの減少で相殺する分だけ小さくなって
いる。中空軸１０の外径１００ｍｍ、内径５０ ｍｍ
、内輪３１の内径１００＋ｎｍ、軌道径１１４ｍＩｎ書
の、予圧軸受装置の場合、線膨張係数をほぼ６刈０″に
し、内輪、外輪及びハウジングの線膨張係数をほぼ１２
，５Ｘｌ（ｒ’とすることが好適な実施例であある。The linear expansion coefficient of the hollow shaft 100 is 31 for the inner ring and 32 for the outer ring.
The increase in the amount of preload due to the expansion of the inner ring 31 and the hollow shaft 10 due to rotational centrifugal force during high-speed rotation than the coefficient of linear expansion of the housing can be achieved by reducing the amount of interference caused by the fit due to the difference in the amount of expansion between the inner ring 3I and the hollow shaft 10. It is smaller by the amount that cancels it out. Hollow shaft 10 has an outer diameter of 100 mm and an inner diameter of 50 mm.
In the case of a preload bearing device in which the inner ring 31 has an inner diameter of 100+nm and a raceway diameter of 114 mIn, the coefficient of linear expansion is approximately 60'', and the coefficient of linear expansion of the inner ring, outer ring, and housing is approximately 12.
, 5Xl(r') is a preferred embodiment.
（１）線図ａ：内輪と中空軸とがはめあいしめしろを持
たないときの回転数に応じ
た内輪軌道径の膨張量の変化。(1) Diagram a: Change in the amount of expansion of the inner ring raceway diameter according to the rotational speed when the inner ring and the hollow shaft fit and have no interference.
（２）線図ｂ：内輪と中空軸とがはめあいしめしろを持
たないときの回転数に応じ
た内輪内径の膨張量の変化。(2) Diagram b: Change in the amount of expansion of the inner diameter of the inner ring depending on the rotational speed when the inner ring and the hollow shaft fit together and have no interference.
（３）線図Ｃ：内輪と中空軸とがはめあいしめじろを持
たないときの回転数に応じ
た中空軸の外径の膨張量の変化。(3) Diagram C: Change in the amount of expansion of the outer diameter of the hollow shaft according to the rotational speed when the inner ring and the hollow shaft fit together without any interference.
（４）線図ｄ：上記の内輪内径の膨張量（ｂ）から中空
軸の外径の膨張：ｌ （Ｃ）を引いた量に肉厚係数（約
０．８５）を乗じたも
のの変化（はめあいしめじろの減
少に伴う内輪軌道径の収縮量の変
化）。(4) Diagram d: Change in the amount obtained by subtracting the expansion amount of the outer diameter of the hollow shaft (C) from the expansion amount of the inner diameter of the inner ring (b) multiplied by the wall thickness coefficient (approximately 0.85) ( (Change in the amount of contraction of the inner ring raceway diameter due to a decrease in fit).
（５）線図ｅ：上記の内輪軌道径の膨張量（ａｌかも、
上記の線図ｄの量を１Ｊ１１．・たものの変化（各部品
の線膨張係数が同
じと仮定し、高速回転時に内輪が
膨張しても中空軸にはめあいしめ
じろを有して嵌合している場合に
実質的に内輪軌道径が回転の上昇
に伴って増大する弾の変化）。(5) Diagram e: The amount of expansion of the inner ring raceway diameter (Al may be
The quantity in the above diagram d is 1J11.・Changes in the inner ring raceway diameter (assuming that the coefficient of linear expansion of each part is the same, and even if the inner ring expands during high-speed rotation, the inner ring raceway diameter will actually change if it is fitted onto the hollow shaft with an interlocking margin) bullet change that increases with increasing rotation).
上記各線図の説明からも理解できるように、内輪軌道径
は軸の回転が上昇するにつれて線図ａの量だけ膨張する
。しかし、内輪内径の膨張（線図ｂ）よりも中空軸の外
径の膨張（線図Ｃ）が少ないので、内輪と中空軸のはめ
あいしめじろは回転の上昇に伴って減少する。従って、
内輪軌道径は線図ｄ分だけの量が膨張しない。すなわち
、内輪軌道径は線図ａより線図ｄを差し引いた分だけ回
転に伴って膨張°する。よって、この膨張ｉＫ見合った
予圧が増大する。例えば、回転数２００００では０．０
２０ｍｍのラジアル方向のマイナスすきま（アキシアル
方向では接触角１５″ で０．０７４ｍｍ）が増大し輪
及びハウジングの線膨張係数がほぼ１２．５刈Ｑ−６で
あるので、通常２００００回転程度回転速時には周囲温
度よりも軸受装置は３０’Ｃ，程度の温度上昇があり、
中空軸の膨張量が約０．０１８ｍｍ、内輪内径の膨張量
が約０．０３８ｍｍあり、その差０．０２０＋ｎｍのは
めあいしめじろの減少がある。すなわち温度膨張による
はめあいしめしろの減少分が丁度、回転に伴う内輪軌道
径の膨張０．０２０ｍｍを相殺するように作用し、軸受
の予圧すきま（マイナスすきま）は増大せず、従って予
圧過大となることが防止される。As can be understood from the explanation of each of the diagrams above, the inner ring raceway diameter expands by the amount shown in diagram a as the rotation of the shaft increases. However, since the expansion of the outer diameter of the hollow shaft (line C) is smaller than the expansion of the inner diameter of the inner ring (line B), the fit between the inner ring and the hollow shaft decreases as the rotation increases. Therefore,
The inner ring raceway diameter does not expand by the amount d in the diagram. That is, the inner ring raceway diameter expands with rotation by an amount obtained by subtracting line d from line a. Therefore, the preload increases commensurate with this expansion iK. For example, at rotation speed 20,000, 0.0
The negative clearance in the radial direction of 20 mm (0.074 mm in the axial direction at a contact angle of 15") has increased, and the coefficient of linear expansion of the ring and housing is approximately 12.5 Q-6, so at a rotation speed of about 20,000 rpm, There is a temperature rise of about 30'C in the bearing device compared to the ambient temperature.
The amount of expansion of the hollow shaft is about 0.018 mm, and the amount of expansion of the inner diameter of the inner ring is about 0.038 mm, and the difference between them is 0.020+nm, which reduces the fit. In other words, the reduction in fitting interference due to temperature expansion acts to exactly offset the 0.020 mm expansion of the inner ring raceway diameter due to rotation, and the preload clearance (minus clearance) of the bearing does not increase, resulting in excessive preload. This will be prevented.
上記の説明の通り、本発明は中空軸の線膨張係数を軸受
の内輪、外輪及びノーウジングのそれよりも小さくして
あり、高速回転時に温度上昇に伴うはめあいしめしろの
減少を利用し、回転に伴って増大する内輪の膨張による
予圧の増大を防止することができる予圧軸受装置である
。なお、この発明思想を中空軸についても適用できるが
その効果は中空軸の場合がより太きい。As explained above, in the present invention, the coefficient of linear expansion of the hollow shaft is made smaller than that of the inner ring, outer ring, and nousing of the bearing. This is a preload bearing device that can prevent an increase in preload due to the accompanying expansion of the inner ring. Note that this inventive idea can also be applied to a hollow shaft, but the effect is greater in the case of a hollow shaft.
第１図は本発明の実施例の縦断面図、第２図に回転の上
昇に伴う各部品の膨張量及びはめあ（・しめじろの減少
量の関係を示す線図で、符号ｌＯは中空軸、３１は内輪
である。
特許出願人 日本精工株式会社
第１図
αＰ、／Ｉ’Ｌ）Fig. 1 is a longitudinal cross-sectional view of an embodiment of the present invention, and Fig. 2 is a diagram showing the relationship between the expansion amount of each part and the reduction amount of fit (tightness) as the rotation increases. 31 is the inner ring of the shaft. Patent applicant NSK Ltd. (Figure 1 αP, /I'L)
Claims (4)
転時においても必要なしめしろで嵌合する内輪と、前記
ハウジングに嵌合する外輪と、前記内輪と前記外輪との
間に多数配設される転動体とからなる軸受で槽成し、前
記軸受が定位置予圧で前記中空軸及び前記ハウジングに
組み込まれる予圧軸受装置Ｎにおいて、前記中空軸の線
膨張係数が前記内輪、前記外輪及び前記ハウジングの線
膨張係数よりも高速回転時に前記内輪が回転遠心力で膨
張することによる予圧量の増大を相殺する亦だけ小さい
ことを特徴とする予圧軸受装置。(1) A hollow shaft and a housing, an inner ring that fits into the hollow shaft with necessary interference even during high speed rotation, an outer ring that fits into the housing, and a large number of rings arranged between the inner ring and the outer ring. In a preload bearing device N, the linear expansion coefficient of the hollow shaft is equal to that of the inner ring, the outer ring, and the housing. A preload bearing device characterized in that the coefficient of linear expansion is smaller than the coefficient of linear expansion by enough to offset an increase in the amount of preload due to expansion of the inner ring due to rotational centrifugal force during high-speed rotation.
’で、前記内輪、前記外輪及びハウジングの線膨張係数
がほぼ１２．５ＸｌＯ−６である特許請求の範囲第１項
記載の予圧軸受装置。(2) The coefficient of linear expansion of the hollow shaft is approximately 6 x 1ff-
The preload bearing device according to claim 1, wherein the inner ring, the outer ring, and the housing have linear expansion coefficients of approximately 12.5XlO-6.
囲第１項記載の予圧軸受装置。(3) The preload bearing device according to claim 1, wherein the bearing is an angular contact ball bearing.
アンギュラ玉軸受間に予圧を与えるように寸法調整した
間座を配設して得られる特許請求の範囲第３項記載の予
圧軸受装置。(4) The fixed position preload is obtained by arranging a spacer whose dimensions are adjusted so as to apply a preload between two angular ball bearings fitted on the hollow shaft. Preload bearing device.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2519784A JPS60172720A (en) | 1984-02-15 | 1984-02-15 | Pressurized bearing device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2519784A JPS60172720A (en) | 1984-02-15 | 1984-02-15 | Pressurized bearing device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS60172720A true JPS60172720A (en) | 1985-09-06 |
| JPH0457891B2 JPH0457891B2 (en) | 1992-09-16 |
Family
ID=12159226
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2519784A Granted JPS60172720A (en) | 1984-02-15 | 1984-02-15 | Pressurized bearing device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS60172720A (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH04249616A (en) * | 1990-12-29 | 1992-09-04 | Nagano Nippon Densan Kk | Bearing structure body and spindle motor using the same |
| JP2002019935A (en) * | 2000-07-07 | 2002-01-23 | Sanyo Mach Works Ltd | Roller conveyor |
| JP4484397B2 (en) * | 2001-05-18 | 2010-06-16 | 本田技研工業株式会社 | Bearing assembly method |
| JP2022510825A (en) * | 2018-12-18 | 2022-01-28 | ワルター マシーネンバオ ゲーエムベーハー | Machine tool shaft arrangement |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5088987U (en) * | 1973-12-17 | 1975-07-28 | ||
| JPS52142143A (en) * | 1976-05-20 | 1977-11-26 | Matsushita Electric Ind Co Ltd | Bearing system |
-
1984
- 1984-02-15 JP JP2519784A patent/JPS60172720A/en active Granted
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5088987U (en) * | 1973-12-17 | 1975-07-28 | ||
| JPS52142143A (en) * | 1976-05-20 | 1977-11-26 | Matsushita Electric Ind Co Ltd | Bearing system |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH04249616A (en) * | 1990-12-29 | 1992-09-04 | Nagano Nippon Densan Kk | Bearing structure body and spindle motor using the same |
| JP2002019935A (en) * | 2000-07-07 | 2002-01-23 | Sanyo Mach Works Ltd | Roller conveyor |
| JP4597324B2 (en) * | 2000-07-07 | 2010-12-15 | 三洋機工株式会社 | Roller conveyor |
| JP4484397B2 (en) * | 2001-05-18 | 2010-06-16 | 本田技研工業株式会社 | Bearing assembly method |
| JP2022510825A (en) * | 2018-12-18 | 2022-01-28 | ワルター マシーネンバオ ゲーエムベーハー | Machine tool shaft arrangement |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0457891B2 (en) | 1992-09-16 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US4884903A (en) | Inter-shaft bearing for multiple body turbo-engines | |
| US4792244A (en) | Ceramic bearing construction | |
| US4729252A (en) | Bearing for the shaft of a machine element | |
| KR20080021736A (en) | A constant-velocity joint for a driven wheel | |
| JPS59101548A (en) | Inter-shaft bearing apparatus of multiple barrel type turbine engine | |
| US5820272A (en) | Bearing structure for a rotating shaft | |
| JP5638331B2 (en) | Preload adjustment structure for rolling bearings | |
| JP5704213B2 (en) | Bearing device | |
| JPS60172720A (en) | Pressurized bearing device | |
| JP2012026496A (en) | Angular ball bearing, and bearing installation structure | |
| JP3855304B2 (en) | Cross roller bearing preload adjustment structure | |
| JPH0730788B2 (en) | Rolling bearing | |
| JP5453764B2 (en) | Bearing device and assembly method thereof | |
| JP2005069252A (en) | Rolling bearing unit | |
| JPH11239902A (en) | Spindle supporting device for machine tool | |
| JPH11108055A (en) | Rolling bearing device | |
| JPH0378488B2 (en) | ||
| US3441325A (en) | Detachable stop ring for a shaft | |
| JP3572710B2 (en) | Radial ball bearing preloading method and radial ball bearing device with preload | |
| JPH0192005A (en) | Preload regulation spindle unit | |
| JPH01135916A (en) | Preload adjustable type spindle unit | |
| JPH0345258B2 (en) | ||
| JPS6230609Y2 (en) | ||
| JPS5931934Y2 (en) | Spacer for combination bearing | |
| JP2535876Y2 (en) | Fixed structure of rolling bearing |