JP2641762B2 - Mounting structure of ceramic bearing - Google Patents
Mounting structure of ceramic bearingInfo
- Publication number
- JP2641762B2 JP2641762B2 JP13563789A JP13563789A JP2641762B2 JP 2641762 B2 JP2641762 B2 JP 2641762B2 JP 13563789 A JP13563789 A JP 13563789A JP 13563789 A JP13563789 A JP 13563789A JP 2641762 B2 JP2641762 B2 JP 2641762B2
- Authority
- JP
- Japan
- Prior art keywords
- metal
- ceramic bearing
- metal sleeve
- fitting
- thermal expansion
- 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 - Fee Related
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
- 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
- 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
- F16C35/073—Fixing them on the shaft or housing with interposition of an element between shaft and inner race ring
Description
【発明の詳細な説明】 ［産業上の利用分野］ 本発明は高温環境下で使用する軸受の構造に関する。The present invention relates to a bearing structure used in a high-temperature environment.
［従来の技術］ セラミックは高温での強度や、耐磨耗性に優れるた
め、高温環境下で使用する軸受にはセラミック軸受が用
いられる。[Prior Art] Ceramics are used for bearings used in a high-temperature environment because ceramics have excellent strength and wear resistance at high temperatures.
このセラミック軸受（熱膨張係数αａ）は、取付け段
部が形成された金属製回転軸（熱膨張係数αｂ）に直接
嵌め込まれる。This ceramic bearing (coefficient of thermal expansion αa) is directly fitted to a metal rotary shaft (coefficient of thermal expansion αb) on which a mounting step is formed.
［発明が解決しようとする課題］ しかるに、上記従来の技術はつぎのような欠点があ
る。[Problem to be Solved by the Invention] However, the above-mentioned conventional technology has the following disadvantages.
温度が上昇すると、金属製回転軸の径方向の熱膨張の
影響（通常αａ＜αｂである為）がセラミック軸受に伝
わるのでセラミック軸受が破損する場合がある。When the temperature rises, the influence of the radial thermal expansion of the metal rotary shaft (usually because αa <αb) is transmitted to the ceramic bearing, so that the ceramic bearing may be damaged.
本発明の目的は、使用環境温度が上昇しても不具合が
生じ難いセラミック軸受の取付構造の提供にある。SUMMARY OF THE INVENTION An object of the present invention is to provide a ceramic bearing mounting structure that is unlikely to cause a problem even when a use environment temperature rises.
［課題を解決するための手段］ 上記目的達成のため、本発明はつぎの構成を採用し
た。[Means for Solving the Problems] To achieve the above object, the present invention employs the following constitution.
第１の発明として、径小部を備えた金属製回転軸、お
よび前記径小部に取付けられるセラミック軸受からなる
セラミック軸受の取付構造において、熱膨張係数が、前
記金属製回転軸より小さく、かつセラミック軸受けの内
輪以上である金属製套管を、前記径小部にすきま嵌めし
て前記径小部と内輪との間に配し、前記金属製套管の片
側または両側に、前記回転軸より熱膨張係数が大きい嵌
め輪を同軸的に介在させて、締結部材により固着してい
る。As a first invention, in a metal rotary shaft having a small diameter portion and a ceramic bearing mounting structure including a ceramic bearing mounted on the small diameter portion, a thermal expansion coefficient is smaller than that of the metal rotary shaft, and A metal sleeve, which is equal to or more than the inner race of the ceramic bearing, is disposed between the small diameter part and the inner race by loosely fitting the small diameter part, and one or both sides of the metal sleeve, from the rotation shaft. A fitting wheel having a large thermal expansion coefficient is coaxially interposed and fixed by a fastening member.
第２の発明として、さらに、嵌め輪と金属製套管、嵌
め輪と締結部材、金属製套管と金属製回転軸、および嵌
め輪と金属製回転軸の各端面は面当接され、これら端面
のうち、少なくとも１組は円錐状のテーパに形成されて
いる。As a second invention, further, each end surface of the fitting wheel and the metal sleeve, the fitting ring and the fastening member, the metal sleeve and the metal rotating shaft, and the end faces of the fitting wheel and the metal rotating shaft are brought into surface contact with each other. At least one set of the end faces is formed in a conical taper.
［作用および発明の効果］ 本発明はつぎの作用および効果を奏する。[Functions and Effects of the Invention] The present invention has the following functions and effects.
（請求項１について） （１）金属製套管は熱膨張係数が、金属製回転軸より小
さく、かつセラミック軸受の内輪以上であるさらに、金
属製套管と金属製回転軸とはすきま嵌めされている。こ
のため、使用環境温度が上昇しても、金属製回転軸の熱
膨張（径方向）の影響がセラミック軸受の内輪に伝わり
難く、セラミック軸受の破損が防止できる。(Regarding Claim 1) (1) The metal sleeve has a smaller thermal expansion coefficient than the metal rotary shaft and is equal to or larger than the inner ring of the ceramic bearing. Further, the metal sleeve and the metal rotary shaft are loosely fitted. ing. For this reason, even if the use environment temperature rises, the influence of the thermal expansion (radial direction) of the metal rotary shaft is not easily transmitted to the inner ring of the ceramic bearing, and the ceramic bearing can be prevented from being damaged.
（２）金属製套管は熱膨張係数が金属製回転軸より小さ
い。ここで、使用環境温度が上昇すると金属製套管と金
属製回転軸との熱膨張差により、これら部材間に軸方向
における隙間の発生が考えられる。しかし、嵌め輪の熱
膨張係数を金属製回転軸より大きくしてあるので、金属
製套管は嵌め輪により押され、上記隙間を生じさせない
ように作用する。よって、使用環境温度が上昇しても金
属製套管と金属製回転軸との緩みは極めて起こり難い。(2) The metal sleeve has a smaller thermal expansion coefficient than the metal rotating shaft. Here, when the use environment temperature rises, a gap in the axial direction may be generated between these members due to a difference in thermal expansion between the metal sleeve and the metal rotary shaft. However, since the thermal expansion coefficient of the fitting ring is set to be larger than that of the metal rotary shaft, the metal sleeve is pushed by the fitting ring and acts so as not to generate the above-mentioned gap. Therefore, even if the use environment temperature rises, loosening of the metal sleeve and the metal rotary shaft hardly occurs.
（請求項２について） 嵌め輪と金属製套管、嵌め輪と締結部材、金属製套管
と金属製回転軸、および嵌め輪と金属製回転軸の各端面
は面当接され、これら端面のうち、少なくとも１組は円
錐状のテーパに形成されている。このため、調芯作用が
生じ金属製套管の軸ずれが防止できる。(Regarding Claim 2) Each end face of the fitting ring and the metal sleeve, the fitting ring and the fastening member, the metal sleeve and the metal rotary shaft, and the end faces of the fitting wheel and the metal rotary shaft are in surface contact with each other. At least one set is formed in a conical taper. For this reason, a centering action occurs, and the axial displacement of the metal sleeve can be prevented.
［実施例］ つぎに、本発明の第１実施例を第１図に基づき説明す
る。Next, a first embodiment of the present invention will be described with reference to FIG.
第１図に示すごとく、本実施例のセラミック軸受の取
付構造Ａは、径小部11が形成される金属製回転軸１と、
前記径小部11に嵌め込まれる金属製套管２と、該金属製
套管２の先端側に嵌め込まれる嵌め輪３と、前記金属製
套管２に外嵌されるセラミック軸受と、ワッシャ51およ
びナット５とを備える。As shown in FIG. 1, the mounting structure A of the ceramic bearing of the present embodiment includes a metal rotary shaft 1 on which a small-diameter portion 11 is formed,
A metal sleeve 2 fitted into the small-diameter portion 11, a fitting ring 3 fitted to the distal end side of the metal sleeve 2, a ceramic bearing fitted externally to the metal sleeve 2, a washer 51, and A nut 5.
金属製回転軸１は、熱膨張係数α１が11.5×10-6/℃
のクロムモリブデン鋼で形成されている。前記径小部11
（常温で直径17mm）にはねじ12が螺刻されている。径小
部11の後端はテーパ面13が形成され、前記金属製套管２
の後端面21に面接触している。The metal rotary shaft 1 has a thermal expansion coefficient α1 of 11.5 × 10 -6 / ° C.
Chromium molybdenum steel. The small diameter part 11
A screw 12 is threaded at (17 mm in diameter at room temperature). The tapered surface 13 is formed at the rear end of the small-diameter portion 11, and the metal sleeve 2 is formed.
Is in surface contact with the rear end face 21.
金属製套管２は、熱膨張係数α２が６×10-6/℃の超
硬合金で形成されている。また、外周には係止段22が周
設され、前記後端面21、先端面23は円錐形のテーパ（θ
１、θ２＝15゜）に形成されている。この金属製套管２
は、常温で、外径が30mm、内径がほぼ17mm、長さＬ＝24
mm（金属製套管２の平均長さ）の円筒形状である。な
お、前記金属製回転軸１の径小部11と金属製套管２の内
径とは100℃以上の使用温度下で嵌め合い隙間が0mm以上
（常温では隙間14を有する）になるようにされている。
金属製套管２は前記セラミック軸受４を取付けた後、金
属製回転軸１の径小部11に挿入される。なお、Ｒ（嵌め
輪３の位置30における半径）は11.75mmである。The metal sleeve 2 is formed of a cemented carbide having a coefficient of thermal expansion α2 of 6 × 10 −6 / ° C. A locking step 22 is provided around the outer circumference, and the rear end face 21 and the front end face 23 have a conical taper (θ
1, θ2 = 15 °). This metal sleeve 2
Is at normal temperature, outer diameter is 30mm, inner diameter is almost 17mm, length L = 24
mm (average length of the metal sleeve 2). The small-diameter portion 11 of the metal rotary shaft 1 and the inner diameter of the metal sleeve 2 are fitted at an operating temperature of 100 ° C. or more so that the gap becomes 0 mm or more (has a gap 14 at room temperature). ing.
After attaching the ceramic bearing 4, the metal sleeve 2 is inserted into the small-diameter portion 11 of the metal rotary shaft 1. Note that R (the radius at the position 30 of the fitting ring 3) is 11.75 mm.
嵌め輪３は、熱膨張係数α３が22.0×10-6/℃、長さ
ｌ＝6mm（嵌め輪３の平均距離）のアルミニウム合金で
形成されている。この嵌め輪３は後端面31がテーパに形
成されている。The fitting ring 3 is formed of an aluminum alloy having a thermal expansion coefficient α3 of 22.0 × 10 −6 / ° C. and a length 1 = 6 mm (average distance of the fitting ring 3). The rear end face 31 of the fitting wheel 3 is tapered.
セラミック軸受４（金属製玉軸受けの呼び番号6206に
相当）は、内輪41、外輪42、球43からなり、熱膨張係数
α４が3.1×10-6/℃のサイアロンで全て形成されてい
る。なお、前記金属製套管２の外径とセラミック軸受４
の内輪径とは常温で嵌め合い隙間が0mmとなるようにさ
れている。このセラミック軸受４は、圧入により前記金
属製套管２に固定される。The ceramic bearing 4 (corresponding to the nominal number 6206 of a metal ball bearing) includes an inner ring 41, an outer ring 42, and a ball 43, and is entirely formed of a sialon having a thermal expansion coefficient α4 of 3.1 × 10 −6 / ° C. The outer diameter of the metal sleeve 2 and the ceramic bearing 4
The inner ring diameter is set at room temperature so that the clearance is 0 mm. The ceramic bearing 4 is fixed to the metal sleeve 2 by press fitting.
ナット５（金属製）は前記ワッシャ51（金属製）を介
して前記嵌め輪３を締め付けている。The nut 5 (made of metal) fastens the fitting wheel 3 via the washer 51 (made of metal).
本実施例における各数値の最適範囲は以下のごとくで
ある。The optimum range of each numerical value in the present embodiment is as follows.
（１）セラミック軸受４の熱膨張係数α４と金属製套管
２の熱膨張係数α２との関係は、 ０≦α２−α４≦６×10-6/℃ とされる。α２＜α４は通常考えられず、α２−α４＞
６×10-6/℃であると温度上昇によりセラミック軸受が
破壊され易い。(1) The relationship between the coefficient of thermal expansion α4 of the ceramic bearing 4 and the coefficient of thermal expansion α2 of the metal sleeve 2 is 0 ≦ α2−α4 ≦ 6 × 10 −6 / ° C. α2 <α4 is not usually considered, and α2−α4>
When the temperature is 6 × 10 −6 / ° C., the ceramic bearing is easily broken by a rise in temperature.
金属製套管２の熱膨張係数α２と金属製回転軸１の熱
膨張係数α１との関係は、 α２＜α１ とされる。α２＞α１であると金属製回転軸１の温度上
昇に伴う径方向の膨張による応力が金属製套管２により
抑制されることなくセラミック軸受４に伝わる。The relationship between the thermal expansion coefficient α2 of the metal sleeve 2 and the thermal expansion coefficient α1 of the metal rotary shaft 1 is expressed as α2 <α1. If α2> α1, the stress due to radial expansion caused by the temperature rise of the metal rotary shaft 1 is transmitted to the ceramic bearing 4 without being suppressed by the metal sleeve 2.
金属製回転軸１の熱膨張係数α１と嵌め輪３の熱膨張
係数α３との関係は、 α１＜α３ とされる。α１＞α３であると、金属製回転軸１と金属
製套管２との軸方向の熱膨張差によるナット５の緩みを
嵌め輪３の軸方向の熱膨張により補償することができな
い。The relationship between the thermal expansion coefficient α1 of the metal rotary shaft 1 and the thermal expansion coefficient α3 of the fitting wheel 3 is expressed as α1 <α3. If α1> α3, the looseness of the nut 5 due to the difference in axial thermal expansion between the metal rotary shaft 1 and the metal sleeve 2 cannot be compensated for by the axial thermal expansion of the fitting wheel 3.
以上、纏めると、 α４≦α２＜α１＜α３ （但しα２−α４≦６×10-6/℃） （２）温度上昇時の金属製回転軸１の軸方向の膨張に関
係する長さ（ｌ＋Ｌ）が、金属製套管２の該当長さ
（Ｌ）および嵌め輪３の該当長さ（ｌ）により補償でき
れば良いので以下の式が成り立つ。In summary, α4 ≦ α2 <α1 <α3 (where α2−α4 ≦ 6 × 10 −6 / ° C.) (2) Length (l + L) related to the axial expansion of the metal rotary shaft 1 when the temperature rises ) Can be compensated for by the corresponding length (L) of the metal sleeve 2 and the corresponding length (l) of the fitting ring 3, so that the following equation holds.
α１＋（ｌ＋Ｌ）≦α２・Ｌ ＋α３（ｌ＋Ｎ・Ｒ・tanθ） （但しＮはテーパ数） （３）θ１およびθ２は45゜未満とされる。45゜を越え
ると温度上昇時の締め付け応力が軸方向とならず径方向
になる。α1 + (l + L) ≦ α2 · L + α3 (l + N · R · tan θ) (where N is the number of taper) (3) θ1 and θ2 are set to be less than 45 °. If it exceeds 45 °, the tightening stress at the time of temperature rise is not axial but radial.
本実施例のセラミック軸受の取付構造Ａでは、使用温
度を常温から200℃まで上昇させても、ナット５の緩み
（金属製套管２と金属製回転軸１との緩み）は生じなか
った。In the mounting structure A of the ceramic bearing of this embodiment, even when the operating temperature was raised from room temperature to 200 ° C., the nut 5 did not loosen (the metal sleeve 2 and the metal rotary shaft 1 loosened).
また、セラミック軸受４と金属製套管２との緩みも生
じず、セラミック軸受４には著しい圧縮応力も生じなか
った。さらに、金属製回転軸１を毎分3000回転させても
軸振れは生じなかった。Also, the ceramic bearing 4 and the metal sleeve 2 did not loosen, and no significant compressive stress was generated in the ceramic bearing 4. Further, even when the metal rotary shaft 1 was rotated at 3000 revolutions per minute, no shaft run-out occurred.
第２図は本発明の第２実施例を示す。 FIG. 2 shows a second embodiment of the present invention.
嵌め輪３は熱膨張係数19×10-6/℃、長さ10mmの銅合
金で形成され、後端面31は回転軸に対して垂直とされ、
先端面32は円錐状のテーパ（θ３＝15゜）とされてい
る。The ferrule 3 is made of a copper alloy having a coefficient of thermal expansion of 19 × 10 −6 / ° C. and a length of 10 mm, and the rear end face 31 is perpendicular to the rotation axis.
The tip surface 32 is formed in a conical taper (θ3 = 15 °).
52は座金（熱膨張係数が11.5×10-6/℃のクロムモリ
ブデン鋼）であり、前記金属製回転軸１と同材料で形成
されている。Reference numeral 52 denotes a washer (chromium molybdenum steel having a thermal expansion coefficient of 11.5 × 10 −6 / ° C.), which is formed of the same material as the metal rotary shaft 1.
座金52の後端部53と嵌め輪３の先端面32および嵌め輪
３の後端面31と金属製套管２の先端面23とはそれぞれ面
接触されている。The rear end 53 of the washer 52, the front end face 32 of the fitting ring 3, and the rear end face 31 of the fitting ring 3 are in surface contact with the front end face 23 of the metal sleeve 2.
本実施例のセラミック軸受の取付構造Ｂはつぎの効果
を奏する。The mounting structure B of the ceramic bearing according to the present embodiment has the following effects.
金属製套管２の先端面23はテーパとしなくても良い。 The distal end surface 23 of the metal sleeve 2 need not be tapered.
金属製回転軸１と同材料の座金52により締まりが安定
する。Tightening is stabilized by the washer 52 of the same material as the metal rotary shaft 1.
嵌め輪３の長さを長くすれば嵌め輪３は熱膨張係数の
小さい（金属製回転軸１より大きい）材料を使うことが
できる。If the length of the fitting wheel 3 is increased, the fitting wheel 3 can use a material having a small thermal expansion coefficient (larger than the metal rotary shaft 1).
金属製回転軸１の径小部11が長くとれる場合に好適で
ある。This is suitable when the small diameter portion 11 of the metal rotary shaft 1 can be made long.
第３図は本発明の第３実施例を示す。 FIG. 3 shows a third embodiment of the present invention.
嵌め輪３は熱膨張係数３×10-5/℃、長さ6mmの耐熱性
を有するフェノール樹脂で形成され、後端面31は回転軸
に対して垂直とされ、後端面31および先端面32は円錐状
のテーパ（θ５、θ６＝10゜）とされている。The fitting wheel 3 is formed of a heat-resistant phenol resin having a coefficient of thermal expansion of 3 × 10 −5 / ° C. and a length of 6 mm, the rear end face 31 is perpendicular to the rotation axis, and the rear end face 31 and the front end face 32 It has a conical taper (θ5, θ6 = 10 °).
座金52は第２実施例と同じものである。 The washer 52 is the same as in the second embodiment.
本実施例のセラミック軸受の取付構造Ｃでは、嵌め輪
３に熱膨張係数の大きいものを使ったり、テーパの数を
増やしたりすれば、θ４、θ５、θ６（径方向と端面と
の成す角度）は小さくできる。In the mounting structure C of the ceramic bearing of the present embodiment, if the fitting ring 3 has a large coefficient of thermal expansion or the number of tapers is increased, θ4, θ5, θ6 (the angle formed between the radial direction and the end face). Can be small.
第４図は本発明の第４実施例を示す。 FIG. 4 shows a fourth embodiment of the present invention.
金属製套管２は、熱膨張係数が６×10-6/℃の超硬合
金であり、後端面21、先端面23は歯形状に形成されてい
る。The metal sleeve 2 is a cemented carbide having a coefficient of thermal expansion of 6 × 10 −6 / ° C., and the rear end face 21 and the front end face 23 are formed in a tooth shape.
本実施例では金属製套管２の後端側にも嵌め輪６が配
されている。In this embodiment, a fitting ring 6 is also provided on the rear end side of the metal sleeve 2.
嵌め輪６および嵌め輪３は、熱膨張係数17×10-6/
℃、長さ12mmのステンレス鋼で形成されている。ここ
で、嵌め輪６の後端面61および嵌め輪３の先端面32は円
錐状のテーパ（θ８、θ７＝15゜）とされている。ま
た、先端面62、後端面31は、それぞれ後端面21、先端面
23と歯合する歯形状に形成されている。The ferrule 6 and the ferrule 3 have a thermal expansion coefficient of 17 × 10 −6 /
It is made of stainless steel with a length of 12mm at ℃. Here, the rear end face 61 of the fitting ring 6 and the tip end face 32 of the fitting ring 3 are formed in a conical taper (θ8, θ7 = 15 °). The front end face 62 and the rear end face 31 are respectively the rear end face 21 and the front end face.
It is formed in a tooth shape that meshes with 23.
本実施例のセラミック軸受の取付構造Ｄでは、金属製
套管２の両側に嵌め輪３、６を配しているので、金属製
套管２の先端面23、後端面24のテーパは不要となる。さ
らに、金属製套管２と嵌め輪３、６との結合はカービッ
クカップリングを用いているので環境温度が常温程度の
とき（隙間14が広いとき）でも、金属製套管２は安定に
保持され、セラミック軸受４は芯ずれを起こしたり、が
たついたりしない。また、嵌め輪３、６が金属製套管２
の熱膨張をカービックカップリングを介して抑制するの
でセラミック軸受４を破壊に至らしめることはない。In the mounting structure D of the ceramic bearing of this embodiment, since the fitting rings 3 and 6 are arranged on both sides of the metal sleeve 2, the taper of the front end face 23 and the rear end face 24 of the metal sleeve 2 is unnecessary. Become. Further, since the metal sleeve 2 and the fitting rings 3 and 6 are connected using a Carbic coupling, the metal sleeve 2 can be stably maintained even when the ambient temperature is about room temperature (when the gap 14 is wide). The ceramic bearing 4 is held and does not cause misalignment or rattling. In addition, the fitting rings 3 and 6 are
The thermal expansion of the ceramic bearing is suppressed via the Carvic coupling, so that the ceramic bearing 4 is not broken.
第５図は本発明の第５実施例（請求項１に対応）を示
す。FIG. 5 shows a fifth embodiment (corresponding to claim 1) of the present invention.
金属製回転軸１は、熱膨張係数が11.0×10-6/℃の炭
素鋼で形成されている。The metal rotating shaft 1 is formed of carbon steel having a thermal expansion coefficient of 11.0 × 10 −6 / ° C.
金属製套管２は、熱膨張係数が8.0×10-6/℃のコバル
トニッケル鋼で形成されている。後端面21、先端面23は
回転軸に対して垂直である。The metal sleeve 2 is formed of cobalt nickel steel having a thermal expansion coefficient of 8.0 × 10 −6 / ° C. The rear end face 21 and the front end face 23 are perpendicular to the rotation axis.
金属製套管２（内径は常温でほぼ17mm）と金属製回転
軸１（常温で直径17mm）とのすきま嵌めは、常温に近い
比較的低い温度の時、隙間14（径小部11と金属製套管２
との）により芯ずれ（軸振れ）を起こさず、かつ100℃
程度の使用温度下（80℃）で前記隙間14がほぼ0mmとな
るようにされている。The clearance fit between the metal sleeve 2 (the inner diameter is approximately 17 mm at room temperature) and the metal rotary shaft 1 (diameter at room temperature 17 mm) is relatively small at room temperature. Mantle tube 2
And 100 ° C without misalignment (axis run-out)
At about a use temperature (80 ° C.), the gap 14 is set to be approximately 0 mm.
嵌め輪３は、熱膨張係数が3.0×10-5/℃、長さ10mmの
フェノール樹脂で形成されている。この嵌め輪３の後端
面31は回転軸に対して垂直である。The fitting ring 3 is formed of a phenol resin having a coefficient of thermal expansion of 3.0 × 10 −5 / ° C. and a length of 10 mm. The rear end face 31 of the fitting wheel 3 is perpendicular to the rotation axis.
本実施例のセラミック軸受の取付構造Ｅは使用温度の
上限値が他の実施例のものより低い。また、嵌め輪３に
熱膨張係数の大きい材料を使う必要があり、また、金属
製回転軸１は熱膨張係数をできるだけセラミック軸受４
に近付ける必要がある。In the mounting structure E of the ceramic bearing of this embodiment, the upper limit of the operating temperature is lower than those of the other embodiments. In addition, it is necessary to use a material having a large thermal expansion coefficient for the fitting wheel 3.
Need to be closer to.
本実施例の効果をつぎに述べる。 The effects of this embodiment will be described below.
上記の様に、各材料間の規定が満足でき、使用温度が
比較的低い場合には、簡単な構造および低コストのセラ
ミック軸受の取付構造として有効である。As described above, when the specifications among the materials can be satisfied and the operating temperature is relatively low, it is effective as a simple structure and a low-cost ceramic bearing mounting structure.
本発明は上記実施例以外につぎの実施態様を含む。 The present invention includes the following embodiments in addition to the above embodiments.
a.セラミック軸受４は、外輪42、球43がセラミックでな
くても良い。a. In the ceramic bearing 4, the outer ring 42 and the ball 43 need not be ceramic.
b.嵌め輪の材料は、マグネシウム合金等の金属、シリコ
ーン、ポリジアリルフタレート、ポリテトラフルオロエ
チレン等の耐熱性プラスチックでも良い。b. The material of the fitting ring may be a metal such as a magnesium alloy or a heat-resistant plastic such as silicone, polydiallyl phthalate, or polytetrafluoroethylene.
第１図は本発明の第１実施例であるセラミック軸受の取
付構造の断面図である。 第２図は本発明の第２実施例であるセラミック軸受の取
付構造の断面図である。 第３図は本発明の第３実施例であるセラミック軸受の取
付構造の断面図である。 第４図は本発明の第４実施例であるセラミック軸受の取
付構造の断面図である。 第５図は本発明の第５実施例であるセラミック軸受の取
付構造の断面図である。 図中 １……金属製回転軸、２……金属製套管、３……
嵌め輪、４……セラミック軸受、５……ナット（締結部
材）、11……径小部、12……ねじ、13……テーパ面（端
面）、21……後端面（端面）、23……先端面（端面）、
31……後端面（端面）、32……先端面（端面）、41……
内輪、θ１、θ２、θ３、θ４、θ５、θ６……径方向
と端面との成す角、Ａ、Ｂ、Ｃ、Ｄ……セラミック軸受
の取付構造FIG. 1 is a sectional view of a mounting structure of a ceramic bearing according to a first embodiment of the present invention. FIG. 2 is a sectional view of a ceramic bearing mounting structure according to a second embodiment of the present invention. FIG. 3 is a sectional view of a mounting structure for a ceramic bearing according to a third embodiment of the present invention. FIG. 4 is a sectional view of a mounting structure of a ceramic bearing according to a fourth embodiment of the present invention. FIG. 5 is a sectional view of a mounting structure of a ceramic bearing according to a fifth embodiment of the present invention. In the figure, 1 ... Metal rotating shaft, 2 ... Metal sleeve, 3 ...
Fitting ring, 4 ... Ceramic bearing, 5 ... Nut (fastening member), 11 ... Small diameter part, 12 ... Screw, 13 ... Tapered surface (end surface), 21 ... Rear end surface (end surface), 23 ... … Tip surface (end surface),
31… rear end face (end face), 32… tip end face (end face), 41…
Inner ring, θ1, θ2, θ3, θ4, θ5, θ6 ... angle between radial direction and end face, A, B, C, D ... mounting structure of ceramic bearing
Claims (2)
径小部に取付けられるセラミック軸受からなるセラミッ
ク軸受の取付構造において、 熱膨張係数が、前記金属製回転軸より小さく、かつセラ
ミック軸受けの内輪以上である金属製套管を、前記径小
部にすきま嵌めして前記径小部と内輪との間に配し、 前記金属製套管の片側または両側に、前記回転軸より熱
膨張係数が大きい嵌め輪を同軸的に介在させて、締結部
材により固着したことを特徴とするセラミック軸受の取
付構造。1. A ceramic bearing mounting structure comprising a metal rotary shaft having a small diameter portion and a ceramic bearing mounted on the small diameter portion, wherein a coefficient of thermal expansion is smaller than that of the metal rotary shaft, and A metal sleeve, which is equal to or larger than the inner ring of the bearing, is disposed between the small diameter portion and the inner ring by loosely fitting the small diameter portion, and heat is applied to the one or both sides of the metal sleeve by the rotating shaft. A mounting structure for a ceramic bearing, wherein a fitting ring having a large expansion coefficient is coaxially interposed and fixed by a fastening member.
材、金属製套管と金属製回転軸、および嵌め輪と金属製
回転軸の各端面は面当接され、 これら端面のうち、少なくとも１組は円錐状のテーパに
形成されていることを特徴とする請求項１記載のセラミ
ック軸受の取付構造。2. The end faces of the fitting ring and the metal sleeve, the fitting ring and the fastening member, the metal sleeve and the metal rotating shaft, and the end faces of the fitting wheel and the metal rotating shaft are in surface contact with each other. 2. The ceramic bearing mounting structure according to claim 1, wherein at least one set is formed in a conical taper.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP13563789A JP2641762B2 (en) | 1989-05-29 | 1989-05-29 | Mounting structure of ceramic bearing |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP13563789A JP2641762B2 (en) | 1989-05-29 | 1989-05-29 | Mounting structure of ceramic bearing |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH034026A JPH034026A (en) | 1991-01-10 |
| JP2641762B2 true JP2641762B2 (en) | 1997-08-20 |
Family
ID=15156467
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP13563789A Expired - Fee Related JP2641762B2 (en) | 1989-05-29 | 1989-05-29 | Mounting structure of ceramic bearing |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2641762B2 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2009019744A (en) * | 2007-07-13 | 2009-01-29 | Jtekt Corp | Drive power transmitting device |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2503157B2 (en) * | 1992-05-21 | 1996-06-05 | 日本碍子株式会社 | Bearing unit |
| FR2708685B1 (en) * | 1993-07-29 | 1995-09-08 | Roulements Soc Nouvelle | Bearing mounting on a shaft. |
| DE9419709U1 (en) * | 1994-12-08 | 1996-04-04 | Sihi Gmbh & Co Kg | Arrangement for centering a bushing made of tension-sensitive material on a shaft |
| JP4736817B2 (en) * | 2006-01-19 | 2011-07-27 | トヨタ自動車株式会社 | Turbocharger |
| DE102010025371B4 (en) | 2010-06-28 | 2018-10-11 | Schaeffler Technologies AG & Co. KG | bearing arrangement |
-
1989
- 1989-05-29 JP JP13563789A patent/JP2641762B2/en not_active Expired - Fee Related
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2009019744A (en) * | 2007-07-13 | 2009-01-29 | Jtekt Corp | Drive power transmitting device |
| US8123018B2 (en) | 2007-07-13 | 2012-02-28 | Jtekt Corporation | Power transmitting device |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH034026A (en) | 1991-01-10 |
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| LAPS | Cancellation because of no payment of annual fees |