JPH0529368Y2 - - Google Patents

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Publication number
JPH0529368Y2
JPH0529368Y2 JP1987003464U JP346487U JPH0529368Y2 JP H0529368 Y2 JPH0529368 Y2 JP H0529368Y2 JP 1987003464 U JP1987003464 U JP 1987003464U JP 346487 U JP346487 U JP 346487U JP H0529368 Y2 JPH0529368 Y2 JP H0529368Y2
Authority
JP
Japan
Prior art keywords
inner ring
outer ring
bearing
fixed part
rotating part
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.)
Expired - Lifetime
Application number
JP1987003464U
Other languages
Japanese (ja)
Other versions
JPS63112621U (en
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed filed Critical
Priority to JP1987003464U priority Critical patent/JPH0529368Y2/ja
Publication of JPS63112621U publication Critical patent/JPS63112621U/ja
Application granted granted Critical
Publication of JPH0529368Y2 publication Critical patent/JPH0529368Y2/ja
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F16C19/22—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
    • F16C19/34—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 both radial and axial load
    • F16C19/36—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 both radial and axial load with a single row of rollers
    • F16C19/361—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 both radial and axial load with a single row of rollers with cylindrical rollers
    • F16C19/362—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 both radial and axial load with a single row of rollers with cylindrical rollers the rollers being crossed within the single row
    • 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
    • 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
    • F16C19/525—Bearings with rolling contact, for exclusively rotary movement with devices affected by abnormal or undesired conditions related to temperature and heat, e.g. insulation
    • 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
    • F16C2226/00—Joining parts; Fastening; Assembling or mounting parts
    • F16C2226/50—Positive connections
    • F16C2226/60—Positive connections with threaded parts, e.g. bolt and nut connections
    • 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
    • F16C2380/00—Electrical apparatus
    • F16C2380/26—Dynamo-electric machines or combinations therewith, e.g. electro-motors and generators

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)

Description

【考案の詳細な説明】 ［産業上の利用分野］ 本考案はころがり軸受の温度特性の改良に関す
るものである。[Detailed Description of the Invention] [Industrial Application Field] The present invention relates to improving the temperature characteristics of a rolling bearing.

［従来の技術］ 第４図に従来におけるころがり軸受の構成例を
示す。図で、１は外輪、２は内輪、３は外輪１と
内輪２の間に挟まれた円柱形状の転動体である。
転動体３は、ａとｂが交互に回転軸になるように
外輪１と内輪２の円周方向に配列されていて、こ
れによつてラジアル方向とスラスト方向の荷重を
分けている。以下、このような構成の軸受をクロ
スローラ軸受とする。[Prior Art] FIG. 4 shows an example of the configuration of a conventional rolling bearing. In the figure, 1 is an outer ring, 2 is an inner ring, and 3 is a cylindrical rolling element sandwiched between the outer ring 1 and the inner ring 2.
The rolling elements 3 are arranged in the circumferential direction of the outer ring 1 and the inner ring 2 so that a and b alternately serve as rotating axes, thereby dividing the load in the radial direction and the thrust direction. Hereinafter, a bearing having such a configuration will be referred to as a cross roller bearing.

ころがり軸受の外輪１は回転部４に篏合され、
内輪２は固定部５に篏合されている。これによつ
てクロスローラ軸受により回転部４が固定部５に
回転可能に支持されている。回転部４と固定部５
は例えばモータのロータとステータのハウジング
である。クロスローラ軸受は耐摩耗性が必要なこ
とから鉄で構成され、ハウジング４と５は軽量化
が必要なことからアルミニウムで構成されてい
る。 The outer ring 1 of the rolling bearing is fitted into the rotating part 4,
The inner ring 2 is fitted into the fixed part 5. As a result, the rotating part 4 is rotatably supported by the fixed part 5 by the cross roller bearing. Rotating part 4 and fixed part 5
are, for example, the housings of the motor rotor and stator. The cross roller bearing is made of iron because it requires wear resistance, and the housings 4 and 5 are made of aluminum because it needs to be lightweight.

［考案が解決しようとする問題点］ 鉄とアルミニウムの熱膨脹係数は約12×10-6
［１／℃］と22×10-6［１／℃］である。このた
め、温度が上昇すると、内輪２とハウジング５の
篏合部では内輪２に力ｆが加わる。[Problem that the invention aims to solve] The coefficient of thermal expansion of iron and aluminum is approximately 12×10 -6
[1/℃] and 22×10 -6 [1/℃]. Therefore, when the temperature rises, a force f is applied to the inner ring 2 at the engagement portion between the inner ring 2 and the housing 5.

また、軸受軌道面６，７の半径r1，r2も半径の
大きさに比例して膨脹する。このため、軸受軌道
面間隔δは大きくなる。 Furthermore, the radii r 1 and r 2 of the bearing raceway surfaces 6 and 7 also expand in proportion to the size of the radius. Therefore, the bearing raceway surface spacing δ increases.

しかし、熱応力ｆによる内輪２のふくらみが熱
膨脹量よりも大きいと、逆に軌道面間隔δは小さ
くなる。 However, if the bulge of the inner ring 2 due to the thermal stress f is larger than the amount of thermal expansion, the raceway spacing δ becomes smaller.

軌道面間隔δの変化分Δδに比例して転動体３
に加わる押し付け力が変わり、転動体３のころが
り摩擦力が変化する。このため、熱応力により軌
道面間隔δが小さくなると、静止状態からハウジ
ング４を回転するのに要するトルク（以下、軸受
起動トルクとする）が大きくなる。このように第
４図のころがり軸受では温度の上昇により軸受起
動トルクが大きくなるという問題点があつた。 The rolling elements 3
The pressing force applied to the rolling element 3 changes, and the rolling friction force of the rolling element 3 changes. Therefore, when the raceway spacing δ decreases due to thermal stress, the torque required to rotate the housing 4 from a stationary state (hereinafter referred to as bearing starting torque) increases. As described above, the rolling bearing shown in FIG. 4 has a problem in that the bearing starting torque increases as the temperature rises.

本考案は上述した問題点を解決するためになさ
れたものであり、軸受軌道トルクが温度上昇の影
響を受けにくいころがり軸受を実現することを目
的とする。 The present invention was made to solve the above-mentioned problems, and aims to realize a rolling bearing in which the bearing orbital torque is less susceptible to temperature rise.

［問題点を解決するための手段］ 本考案は、 外輪と内輪で転動体を挟んだ構成になつてい
て、この転動体のころがりで回転部を固定部に回
転可能に支持するとともに、前記外輪と内輪は前
記回転部と固定部よりも熱膨脹係数が小さい材料
で構成されたころがり軸受において、 前記外輪と内輪には径方向につばが形成され、
前記回転部と固定部にはこのつばを受け得る形状
の溝が形成されていて、温度が変化したときに回
転部または固定部からつばに熱応力を加え、外輪
と内輪の径の変化量を回転部と固定部の径の変化
量に追従させるようにしたことを特徴とするころ
がり軸受である。[Means for Solving the Problems] The present invention has a structure in which a rolling element is sandwiched between an outer ring and an inner ring, and the rolling element rotatably supports a rotating part on a fixed part, and the outer ring In a rolling bearing, the inner ring is made of a material having a coefficient of thermal expansion smaller than that of the rotating part and the fixed part, and the outer ring and the inner ring are formed with a radial collar,
A groove shaped to receive the collar is formed in the rotating part and the fixed part, and when the temperature changes, thermal stress is applied to the collar from the rotating part or the fixed part, and the amount of change in the diameter of the outer ring and the inner ring is controlled. This rolling bearing is characterized in that it follows the amount of change in diameter of the rotating part and the fixed part.

［実施例］ 以下、図面を用いて本考案を説明する。[Example] The present invention will be explained below with reference to the drawings.

第１図は本考案にかかるころがり軸受の一実施
例の構成図である。図で、第４図と同一のものは
同一符号を付ける。 FIG. 1 is a configuration diagram of an embodiment of a rolling bearing according to the present invention. In the figure, the same parts as in FIG. 4 are given the same reference numerals.

外輪１と内輪２には円周方向に沿つたつば８と
９がそれぞれ形成されている。ハウジング４と５
にはつば８と９を受け得る形状の溝１０と１１が
それぞれ形成されている。また、ハウジング５に
固定されたクランプ１２もつば９を受け得る形状
になつている。外輪１と内輪２は、ハウジング４
と５に対して焼きばめ、冷しばめ等により篏合さ
れている。 Flanges 8 and 9 are formed along the circumferential direction on the outer ring 1 and the inner ring 2, respectively. housing 4 and 5
Grooves 10 and 11 each having a shape capable of receiving the flanges 8 and 9 are formed therein. Further, the clamp 12 fixed to the housing 5 is also shaped to be able to receive the collar 9. The outer ring 1 and the inner ring 2 are connected to the housing 4
and 5 are fitted together by shrink fitting, cold fitting, etc.

このような構成のころがり軸受で、温度が変化
した場合の各部の寸法変化について説明する。 In a rolling bearing having such a configuration, dimensional changes in each part when the temperature changes will be explained.

温度が上昇した場合について考える。 Consider the case where the temperature rises.

第２図は温度が上昇したときの軸受各部の寸法
変化を示した概念的構成図である。 FIG. 2 is a conceptual diagram showing dimensional changes in each part of the bearing when the temperature rises.

温度が上昇すると、内輪２もハウジング５も膨
脹する。ハウジング５は内輪２よりも熱膨脹係数
が大きいため、ハウジング５と内輪２の篏合部で
は、ハウジング５は内輪２に外側へ押し拡げる応
力ｆを加える。これによつて内輪２はｃだけ外側
に変形する。また、内輪２自体もｄだけ外側に熱
膨脹する。これによつて内輪２の外側面１３はｃ
＋ｄだけ外側に変形する。このとき、つば９は変
形に関与しない。 When the temperature rises, both the inner ring 2 and the housing 5 expand. Since the housing 5 has a larger coefficient of thermal expansion than the inner ring 2, at the engagement portion between the housing 5 and the inner ring 2, the housing 5 applies stress f to the inner ring 2 to push it outward. As a result, the inner ring 2 is deformed outward by c. Further, the inner ring 2 itself thermally expands outward by d. As a result, the outer surface 13 of the inner ring 2 is c
Deforms outward by +d. At this time, the collar 9 does not participate in the deformation.

一方、外輪１とハウジング４の篏合部分では、
ハウジング４が外輪１よりも熱膨脹係数が大きい
ため、ハウジング４はつば８に熱応力f1を加えて
外輪１を外側に押し拡げる。これによつて外輪１
はｅだけ外側に変形する。また、外輪１自体もｇ
だけ外側に熱膨脹する。これによつて、外輪１の
内側面１４はｅ＋ｇだけ外側に変形する。 On the other hand, at the part where the outer ring 1 and the housing 4 fit together,
Since the housing 4 has a larger coefficient of thermal expansion than the outer ring 1, the housing 4 applies a thermal stress f 1 to the collar 8 and pushes the outer ring 1 outward. With this, outer ring 1
is deformed outward by e. In addition, the outer ring 1 itself also has a g
Thermal expansion only occurs outwards. As a result, the inner surface 14 of the outer ring 1 is deformed outward by e+g.

熱膨脹による長さの変化量はr0・α・Δt（r0：
変化前の長さ、α：熱膨脹係数、Δt：温度の変
化量）である。また、篏合部の熱応力は次のよう
になる。 The amount of change in length due to thermal expansion is r 0・α・Δt (r 0 :
(length before change, α: coefficient of thermal expansion, Δt: amount of change in temperature). Further, the thermal stress at the mating portion is as follows.

σ＝（LB−LH）・Δt・EB／１＋hB／hH EB／EH αH：ハウジング４または５の熱膨脹係数 αB：外輪１または内輪２の熱膨脹係数 EH：ハウジング４または５の縦弾性係数 EB：外輪１または内輪２の縦弾性係数 hH：ハウジング４または５の肉厚 hB：外輪１または内輪２の肉厚 このように内輪２がそれ自体の熱膨脹に加えて
熱応力により外側に変形したときは、外輪１もそ
れ自体の熱膨脹に加えて、つば８にかかる熱応力
により外側に変形させられる。これによつて、温
度上昇が上昇しても内輪の外側面１３と外輪の内
側面１４の間隔がほぼ一定に保たれる。変化の前
後の間隔はそれぞれΔδとΔδ′になる。 σ=(L B −L H )・Δt・E B /1+h B /h H E B /E H α H : Coefficient of thermal expansion of housing 4 or 5 α B : Coefficient of thermal expansion of outer ring 1 or inner ring 2 E H : Housing 4 or 5 longitudinal elastic modulus E B : Longitudinal elastic modulus of outer ring 1 or inner ring 2 h H : Wall thickness of housing 4 or 5 h B : Wall thickness of outer ring 1 or inner ring 2 In this way, inner ring 2 undergoes its own thermal expansion. When the outer ring 1 is deformed outwardly due to thermal stress in addition to this, the outer ring 1 is also deformed outwardly due to the thermal stress applied to the collar 8 in addition to its own thermal expansion. Thereby, even if the temperature rises, the distance between the outer surface 13 of the inner ring and the inner surface 14 of the outer ring is maintained substantially constant. The intervals before and after the change are Δδ and Δδ′, respectively.

第４図の軸受では、温度が上昇したときに外輪
１の変形はそれ自体の熱膨脹によるものだけであ
るため、内輪の外側面１３と外輪の内側面１４の
間隔は第１図の軸受よりも小さくなる。 In the bearing shown in FIG. 4, when the temperature rises, the deformation of the outer ring 1 is only due to its own thermal expansion, so the distance between the outer surface 13 of the inner ring and the inner surface 14 of the outer ring is smaller than in the bearing shown in FIG. becomes smaller.

温度が下がつたときは外輪と内輪の関係が逆に
なり、内輪２のつば９にかかる熱応力f2により内
輪２が強制的に変形させられることになる。 When the temperature drops, the relationship between the outer ring and the inner ring is reversed, and the inner ring 2 is forcibly deformed by the thermal stress f2 applied to the collar 9 of the inner ring 2.

なお、ハウジング４と５は軸受よりも熱膨脹係
数が大きい材料で構成されていればよく、ハウジ
ング４と５および軸受はそれぞれ鉄およびアルミ
ニウム以外の材料で構成されていてもよい。 Note that the housings 4 and 5 may be made of a material having a larger coefficient of thermal expansion than the bearing, and the housings 4 and 5 and the bearing may be made of materials other than iron and aluminum, respectively.

また、ハウジング４と５はモータのハウジング
以外のものであつてもよい。 Furthermore, the housings 4 and 5 may be other than motor housings.

また、軸受はクロスローラ軸受以外の軸受例え
ばラジアル玉軸受、スラスト玉軸受等であつても
よい。 Further, the bearing may be a bearing other than a cross roller bearing, such as a radial ball bearing, a thrust ball bearing, or the like.

［効果］ 本考案によれば、外輪と内輪につばが設けられ
ているため、温度が変化すると、つばにかかる熱
応力による外輪と内輪は回転部と固定部の変形に
追従するよう変形させられる。これによつて、温
度による外輪と内輪の間隔の変化が小さくなり、
温度変化による軸受起動トルクの変化を低減でき
る。軸受起動トルクＴと温度変化Δtの関係を示
すと第３図のようになり、直線l1で表わされる本
考案にかかる軸受は直線l2で表わされる第４図の
軸受に比べてトルクＴの変化率が小さくなる。[Effect] According to the present invention, since the outer ring and the inner ring are provided with ribs, when the temperature changes, the outer ring and the inner ring are deformed to follow the deformation of the rotating part and the fixed part due to thermal stress applied to the ribs. . This reduces the change in the distance between the outer ring and inner ring due to temperature,
Changes in bearing starting torque due to temperature changes can be reduced. The relationship between bearing starting torque T and temperature change Δt is shown in Figure 3, and the bearing according to the present invention represented by straight line l1 has a lower torque T than the bearing shown in Figure 4 represented by straight line l2 . The rate of change becomes smaller.

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

第１図は本考案にかかるころがり軸受の一実施
例の構成図、第２図は第１図の軸受の動作説明
図、第３図は本考案にかかる軸受の効果の説明
図、第４図はころがり軸受の従来における構成例
を示した図である。 １……外輪、２……内輪、３……転動体、４…
…回転部、５……固定部、８，９……つば、１
０，１１……溝。 Fig. 1 is a configuration diagram of an embodiment of the rolling bearing according to the present invention, Fig. 2 is an explanatory diagram of the operation of the bearing in Fig. 1, Fig. 3 is an explanatory diagram of the effect of the bearing according to the present invention, and Fig. 4 1 is a diagram showing an example of a conventional configuration of a rolling bearing. 1...Outer ring, 2...Inner ring, 3...Rolling element, 4...
...Rotating part, 5...Fixed part, 8, 9...Brim, 1
0,11...groove.

Claims (1)

【実用新案登録請求の範囲】 外輪と内輪で転動体を挟んだ構成になつてい
て、この転動体のころがりで回転部を固定部に回
転可能に支持するとともに、前記外輪と内輪は前
記回転部と固定部よりも熱膨脹係数が小さい材料
で構成されたころがり軸受において、 前記外輪と内輪には径方向につばが形成され、
前記回転部と固定部にはこのつばを受け得る形状
の溝が形成されていて、温度が変化したときに回
転部または固定部からつばに熱応力を加え、外輪
と内輪の径の変化量を回転部と固定部の径の変化
量に追従させるようにしたことを特徴とするころ
がり軸受。[Claims for Utility Model Registration] A rolling element is sandwiched between an outer ring and an inner ring, and the rolling of the rolling element rotatably supports a rotating part on a fixed part, and the outer ring and inner ring support the rotating part. and a rolling bearing made of a material with a coefficient of thermal expansion smaller than that of the fixed part, wherein the outer ring and the inner ring are formed with a radial collar,
A groove shaped to receive the collar is formed in the rotating part and the fixed part, and when the temperature changes, thermal stress is applied to the collar from the rotating part or the fixed part, and the amount of change in the diameter of the outer ring and the inner ring is controlled. A rolling bearing characterized in that it follows the amount of change in diameter of a rotating part and a fixed part.
JP1987003464U 1987-01-13 1987-01-13 Expired - Lifetime JPH0529368Y2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP1987003464U JPH0529368Y2 (en) 1987-01-13 1987-01-13

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP1987003464U JPH0529368Y2 (en) 1987-01-13 1987-01-13

Publications (2)

Publication Number Publication Date
JPS63112621U JPS63112621U (en) 1988-07-20
JPH0529368Y2 true JPH0529368Y2 (en) 1993-07-28

Family

ID=30783245

Family Applications (1)

Application Number Title Priority Date Filing Date
JP1987003464U Expired - Lifetime JPH0529368Y2 (en) 1987-01-13 1987-01-13

Country Status (1)

Country Link
JP (1) JPH0529368Y2 (en)

Also Published As

Publication number Publication date
JPS63112621U (en) 1988-07-20

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