JPH034026A - Mounting structure for ceramic bearing - Google Patents
Mounting structure for ceramic bearingInfo
- Publication number
- JPH034026A JPH034026A JP13563789A JP13563789A JPH034026A JP H034026 A JPH034026 A JP H034026A JP 13563789 A JP13563789 A JP 13563789A JP 13563789 A JP13563789 A JP 13563789A JP H034026 A JPH034026 A JP H034026A
- Authority
- JP
- Japan
- Prior art keywords
- metal
- ceramic bearing
- thermal expansion
- coefficient
- rotating shaft
- 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
- 239000000919 ceramic Substances 0.000 title claims abstract description 47
- 229910052751 metal Inorganic materials 0.000 claims description 81
- 239000002184 metal Substances 0.000 claims description 81
- 239000000463 material Substances 0.000 description 7
- 230000000694 effects Effects 0.000 description 5
- PCHJSUWPFVWCPO-UHFFFAOYSA-N gold Chemical compound [Au] PCHJSUWPFVWCPO-UHFFFAOYSA-N 0.000 description 3
- 229910052737 gold Inorganic materials 0.000 description 3
- 239000010931 gold Substances 0.000 description 3
- KXGFMDJXCMQABM-UHFFFAOYSA-N 2-methoxy-6-methylphenol Chemical compound [CH]OC1=CC=CC([CH])=C1O KXGFMDJXCMQABM-UHFFFAOYSA-N 0.000 description 2
- 229910000831 Steel Inorganic materials 0.000 description 2
- VNTLIPZTSJSULJ-UHFFFAOYSA-N chromium molybdenum Chemical compound [Cr].[Mo] VNTLIPZTSJSULJ-UHFFFAOYSA-N 0.000 description 2
- 230000008878 coupling Effects 0.000 description 2
- 238000010168 coupling process Methods 0.000 description 2
- 238000005859 coupling reaction Methods 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 239000005011 phenolic resin Substances 0.000 description 2
- 229920001568 phenolic resin Polymers 0.000 description 2
- 239000010959 steel Substances 0.000 description 2
- 229910000838 Al alloy Inorganic materials 0.000 description 1
- 229910000975 Carbon steel Inorganic materials 0.000 description 1
- 229910000881 Cu alloy Inorganic materials 0.000 description 1
- 229910000861 Mg alloy Inorganic materials 0.000 description 1
- 238000005299 abrasion Methods 0.000 description 1
- 239000010962 carbon steel Substances 0.000 description 1
- ZGDWHDKHJKZZIQ-UHFFFAOYSA-N cobalt nickel Chemical compound [Co].[Ni].[Ni].[Ni] ZGDWHDKHJKZZIQ-UHFFFAOYSA-N 0.000 description 1
- 230000007613 environmental effect Effects 0.000 description 1
- 230000037431 insertion Effects 0.000 description 1
- 238000003780 insertion Methods 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- XNGIFLGASWRNHJ-UHFFFAOYSA-L phthalate(2-) Chemical compound [O-]C(=O)C1=CC=CC=C1C([O-])=O XNGIFLGASWRNHJ-UHFFFAOYSA-L 0.000 description 1
- 229920001296 polysiloxane Polymers 0.000 description 1
- 239000010935 stainless steel Substances 0.000 description 1
- 229910001220 stainless steel Inorganic materials 0.000 description 1
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
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Mounting Of Bearings Or Others (AREA)
- Rolling Contact Bearings (AREA)
Abstract
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。[Detailed description of the invention] [Industrial application field] The present invention relates to the structure of a bearing 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。[Conventional technology] Ceramics have excellent strength at high temperatures and abrasion resistance, so
Ceramic bearings are used for bearings used in high-temperature environments.
このセラミック軸受（熱膨張係数αａ）は、取付は段部
が形成された金属製回転軸（熱膨張係数αｂ）に直接液
め込まれる。This ceramic bearing (coefficient of thermal expansion αa) is mounted directly into a metal rotating shaft (coefficient of thermal expansion αb) having a stepped portion.
［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 conventional technology has the following drawbacks.
温度が上昇すると、金属製回転軸の径方向の熱膨張の影
ｇ（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 g of thermal expansion in the radial direction of the metal rotating shaft (usually αa<αb) is transmitted to the ceramic bearing, which may damage the ceramic bearing.
本発明の目的は、使用環境温度か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堤倶にある。An object of the present invention is to provide a mounting structure for a ceramic bearing that is less likely to cause problems even if the operating environment temperature rises.
し課題を解決するための手段１ 上記目的達成のため、本発明はつぎの構成を採用した。Means to solve the problem 1 In order to achieve the above object, the present invention employs the following configuration.
第１の発明として、径小部を備えた金トル製凹転軸、お
よび前記径小部に収イ１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」二である金属製套管を、萌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
のハｆｕｌｌ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°Ｃ２締結部材によ
り固着している。As a first invention, in a ceramic bearing mounting structure comprising a concave rotating shaft made of metal and a small diameter portion and a ceramic bearing accommodated in the small diameter portion, the coefficient of thermal expansion is
A metal sleeve, which is smaller than the metal rotating shaft and smaller than the inner ring of the ceramic bearing, is fitted into the small diameter portion with a clearance and arranged between the small diameter portion and the inner ring, and Fitting rings having a coefficient of thermal expansion larger than the rotating shaft are coaxially interposed on the full or both sides of the sleeve and are fixed by a °C2 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Ｂｆ４１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４
１向のうち、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, each end face of the fitting ring and the metal sleeve, the fitting ring and the fastening member, the gold Bf41 sleeve and the metal rotating shaft, and the fitting ring and the metal rotating shaft are in surface contact with each other, and 4
At least one set in one direction is formed into 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。[Action and effect of invention] The present invention has the following functions and effects.
（ＪＩｌ求項１について）
（１）金属ツ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−１−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 JIl Requirement 1) (1) The coefficient of thermal expansion of the metal sleeve is smaller than that of the metal rotating shaft, and is greater than the inner ring of the ceramic bearing.Furthermore, the metal sleeve and the metal rotating shaft are a loose fit. has been done. Therefore, even if the operating environment temperature rises by -1, the effect of thermal expansion (in the radial direction) of the metal rotating shaft is not easily transmitted to the inner ring of the ceramic bearing, and damage to the ceramic bearing can be prevented.
（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ｌｌｊ張差により、これら部材間に軸
〃向における隙間の発生が考えられる。しかし、嵌め輪
の熱Ｍ３張係数を金に４製回転軸より大きくして１ｂ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 coefficient of thermal expansion of the metal sleeve is smaller than that of the metal rotating shaft.Here, when the operating environment temperature rises, the thermal tension difference between the metal sleeve and the metal rotating shaft causes the shaft to expand between these parts. It is possible that a gap may occur in the direction. However, since the thermal M3 tensile coefficient of the fitting ring is 1b larger than that of the rotating shaft made of gold and 4, the metal sleeve is pressed by the fitting ring and acts to prevent the above-mentioned gap from occurring. Therefore, even if the operating environment temperature rises, loosening of the metal sleeve and the metal rotating shaft is extremely unlikely to occur.
（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え′Ｌ′Ｃいる。このため、調芯（
ｐ用が生じ金属製套管の軸ずれが防止できる。(Regarding Claim 2) The end surfaces 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 fitting ring and the metal rotating shaft are in surface contact, and Among them, at least one set is formed into a conical taper. For this reason, alignment (
This can prevent the metal sleeve from shifting its axis.
［実施例１
つぎに、本発明の第１実施例を第１図に基づき説明する
。[Embodiment 1] Next, a first embodiment of the present invention will be described based on FIG.
第１図に示すごとく、本実施例のセラミック軸受の取イ
・１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４と、ワッシ
ャ５１およびナツト５とを備える。As shown in FIG. 1, the structure A of the ceramic bearing of this embodiment has a metal rotating 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 onto the distal end side of the metal sleeve 2; and a ceramic bearing 4 fitted onto the metal sleeve 2. It includes a washer 51 and a nut 5.
金属製回転軸１は、熱膨張係数α１が１１，５Ｘ １０
−’／’Ｃ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Ｉ２が螺
刻されている。径小部１】の後端はテーパ而１３が形成
され、ｉｉ前記金属製ｇ管２の後端面２１に面接触して
いる。The metal rotating shaft 1 has a thermal expansion coefficient α1 of 11.5X 10
-'/'C chromium molybdenum steel. A screw I2 is threaded into the small diameter portion 11 (diameter 17 mm at room temperature). A tapered portion 13 is formed at the rear end of the small diameter portion 1 and is in surface contact with the rear end surface 21 of the metal g-tube 2.
金属製套管２は、熱＆ｌｊ？Ｊ、係数α２が６ＸｉＯ−
’／℃の超硬合金で形成されている。また、外周Ｖ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（θ１、θ２・二１５′″）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１７ ｔｒ目ＴＩ 、長さｌ−。The metal sleeve 2 is heat & lj? J, coefficient α2 is 6XiO−
'/℃ made of cemented carbide. Further, a locking step 22 is provided around the outer periphery V, and the rear end surface 21 and the front end surface 23 are formed into a conical taper (θ1, θ2・215′″). , the outer diameter is 30 mm at room temperature,
The inner diameter is approximately 17th tr, and the length is l-.
２４ｍｍ（金属製套管２の平均長さ）の円筒形状である
。なお５０ｑ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°Ｃ以」の使用温度下で嵌め合い
隙間がＯｍ ＋ｎ以］４（常温では隙ｊｊ）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１
１に挿入される。なお、Ｒ（嵌め輪３の位置３０におけ
る半径）は１１７５ ｎｉ ｍである。It has a cylindrical shape of 24 mm (average length of the metal sleeve 2). Note that the small-diameter portion 11 of the metal rotating shaft 1 and the inner diameter of the metal sleeve 2 described in 50q have a fitting clearance of Om + n or less at a working temperature of 100°C or less (gap jj at room temperature) 14. After the ceramic bearing 4 is attached to the metal sleeve 2, which is designed to have a small diameter portion 1 of the metal rotating shaft 1,
1 is inserted. Note that R (radius at position 30 of the fitting ring 3) is 1175 nim.
嵌め輪３は、熱膨張係数α３が２２．０Ｘｉ０６／℃、
長さ’Ｉ ＝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３
１がテーパに形成されている。The fitting ring 3 has a thermal expansion coefficient α3 of 22.0Xi06/℃,
It is made of aluminum alloy and has a length 'I = 6 mm (average distance of the fitting ring 3). This fitting ring 3 is the rear end surface 3
1 is formed into a tapered shape.
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．ｌＸｌ０”／℃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Ｏｍｍ
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。Ceramic bearing 4 (metal ball bearing number 6206
) consists of an inner ring 41, an outer ring 42, and a ball 43, and has a thermal expansion coefficient α4 of 3. The outer diameter of the metal sleeve 2 and the inner ring diameter of the ceramic bearing 4 fit together at room temperature with a gap of 0 mm.
It is designed to be. This ceramic bearing 4 is fixed to the metal sleeve 2 by press fitting.
ナツト５（金属製）は前記ワッシャ５１（金属製）を介
して前記底め輪３を締め付けている。The nut 5 (made of metal) tightens the bottom ring 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 optimal range of each numerical value in this example is as follows.
（１）セラミック軸受４の熱ｍｇｉ係数α４と金属製套
管２の熱ｍ張係数α２との関係は、
０≦α２−α４≦６ Ｘ １０−’／”Ｃとされる。α
２くα４は通常者えられず、α２−α４＞６Ｘ１０−’
／”Ｃ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 thermal mgi coefficient α4 of the ceramic bearing 4 and the thermal mgi coefficient α2 of the metal sleeve 2 is 0≦α2−α4≦6×10−′/”C.α
2 × α4 cannot be obtained normally, α2−α4>6X10−'
/''C, the ceramic bearing is likely to be destroyed due to temperature rise.
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く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 coefficient of thermal expansion α2 of the metal sleeve 2 and the coefficient of thermal expansion α1 of the metal rotating shaft 1 is α2 × α1. If α2>α1, the diameter of the metal rotating shaft 1 increases as the temperature rises. Stress due to directional expansion is transmitted to the ceramic bearing 4 without being suppressed by the metal sleeve 2.
金ＩＸ！！！回転軸ｌの熱膨張係数α１と嵌め輪３の！
！！、１ｊ８Ｉ係数α３との関係は、α１く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ツト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。Gold IX! ! ! The thermal expansion coefficient α1 of the rotating shaft l and the fit ring 3!
! ! , 1j8I coefficient α3 is α1 × α3. If α1>α3, the loosening of the nut 5 due to the difference in thermal expansion in the axial direction between the metal rotating shaft 1 and the metal sleeve 2 can be absorbed by the fitting ring. 3 cannot be compensated for due to axial thermal expansion.
以上、纒めると、
α４≦α２〈α１くα３
（但しα２−α４≦６ ｘ １０−６／’Ｃ）（２）温
度上昇時の金属製回転軸１の軸方向のｌｌｊ張に関係す
る長さ（９＋Ｉ、）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（４１）により補償できれば
良いので以下の式が成り立つ。To summarize the above, α4≦α2〈α1×α3 (however, α2−α4≦6 x 10-6/'C) (2) Related to the axial tension of the metal rotating shaft 1 when the temperature rises The length (9+I,) is the corresponding length (L) of the metal sleeve 2
Since it is only necessary to compensate by the corresponding length (41) of the fitting ring 3, the following formula holds true.
α１ （Ｎ ＋Ｌ）≦
α２ ・Ｌ＋ａ３ （Ｊ ＋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」〕昇時の締め付は応力が軸方向とならず
径方向になる。α1 (N + L)≦ α2 ·L+a3 (J +NR-tan θ) (where N is the taper number) (3) θ1 and θ2 are less than 45°. If the temperature exceeds 45°, the stress will not be in the axial direction but in the radial direction when tightening as the temperature increases.
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、ナツトらの緩み
（金属製套管２と金属製回転１ＩＩＩｌとの緩み）は生
じなかった。In the ceramic bearing mounting structure A of this example, even when the operating temperature was raised from room temperature to 200° C., loosening of the nuts (loosening of the metal sleeve 2 and the metal rotating shaft 1III1) did not occur.
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。Moreover, no loosening occurred between the ceramic bearing 4 and the metal sleeve 2, and no significant compressive stress was generated in the ceramic bearing 4. Further, even when the metal rotating shaft 1 was rotated at 3000 revolutions per minute, no shaft runout 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 invention.
嵌め輪３は熱ＩＩｊ張係数１９ Ｘ １０−’／’Ｃ１
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（θ
３＝１５’）とされている。Fitting ring 3 has thermal IIj tensile coefficient 19 x 10-'/'C1
It is made of copper alloy with a length of 10 mm, the rear end surface 31 is perpendicular to the rotation axis, and the front end surface 32 has a conical taper (θ
3=15').
５２は座金（熱膨張係数が１１．．５Ｘ１０’−’／℃
のクロムモリブデンｗ４）であり、前記金属製回転軸１
と同材料で形成されている。52 is a washer (thermal expansion coefficient is 11.5X10'-'/℃
chromium molybdenum w4), and the metal rotating shaft 1
It is made of the same material.
座金５２の後端面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 surface 53 of the washer 52 and the distal end surface 32 of the fitting ring 3 are in surface contact with each other, and the rear end surface 31 of the fitting ring 3 and the distal end surface 23 of the metal sleeve 2 are in surface contact with each other.
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 ceramic bearing mounting structure B of this 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 does not have to 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。The metal rotating shaft 1 and the washer 52 made of the same material stabilize the tightness.
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よりは大きい）材料を使うことが
できる。By increasing the length of the fitting ring 3, a material with a small coefficient of thermal expansion (larger than that of the metal rotating shaft 1) can be used for the fitting ring 3.
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 rotating 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 invention.
嵌め輪３は熱膨張係数３ ｘ １０−”／”Ｃ１長さ６
ｍｍ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。Fitting ring 3 has thermal expansion coefficient 3 x 10-”/”C1 length 6
It is made of a phenolic resin having a heat resistance of mm, the rear end surface 31 is perpendicular to the rotation axis, and the rear end surface 31 and the front end surface 32 are tapered conically (θ5, θ6-10°).
座き５２は第２実施例と同じものである。The seat 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
やしたりずれば、θ４、θ５、θ６（径方向と端面との
成す角度）は小さくできる。In the ceramic bearing mounting structure C of this embodiment, the fitting ring 3
θ4, θ5, and θ6 (angles formed between the radial direction and the end face) can be made smaller by using a material with a large coefficient of thermal expansion or by increasing the number of tapers.
第４図は本発明の第４実施例を示す。FIG. 4 shows a fourth embodiment of the invention.
金属製套管２は、熱膨張係数が５ｘｉｏ−６，／”Ｃの
超硬合金であり、後端面２１、先端向２３は歯形状に形
成されている。The metal sleeve 2 is made of cemented carbide with a thermal expansion coefficient of 5xio-6,/''C, and the rear end surface 21 and the front end 23 are tooth-shaped.
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 arranged 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１７Ｘ１０−’
／’Ｃ１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は円鉾状のテーパ（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
４１而２１、先端向２３と歯合する歯形状に形成されζ
いる。The fitting ring 6 and the fitting ring 3 have a thermal expansion coefficient of 17X10-'
/'C1 It is made of stainless steel and has a length of 12 mm. Here, the rear end surface 61 of the fitting ring 6 and the tip surface 32 of the fitting ring 3 are tapered in the shape of a circular hoop (θ8, θ7=15°), and the tip surface 62 and the rear end surface 31 are respectively rearward. 41 and 21, formed into a tooth shape that meshes with the tip direction 23 ζ
There is.
本実施例のセラミック軸受の取付構造りでは、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の先端向２３、後端（ｍ２４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ｌＩｊ＋５Ｍをカーピ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を破壊に土らしぬる
ことはない。In the ceramic bearing mounting structure of this embodiment, the fitting rings 3.6 are arranged on both sides of the metal sleeve 2, so the taper in the forward direction 23 and rear end (m24) of the metal sleeve 2 is unnecessary. Furthermore, since a curvic coupling is used to connect the metal sleeve 2 and the fitting ring 3.6, even when the environmental temperature is around room temperature (when the gap 14 is wide), the metal sleeve 2 is held stably, and the ceramic bearing 4 does not become misaligned or wobble. Also, since the fitting ring 3.6 suppresses the heat lIj+5M of the metal sleeve 2 through the car pick coupling, the ceramic bearing 4 The bearing 4 will not be destroyed.
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Ｗ３張係数が１１．．０Ｘ１０−
’／’Ｃの炭素鋼で形成されている。The metal rotating shaft 1 has a thermal W3 tensile coefficient of 11. ．． 0X10-
It is made of '/'C carbon steel.
金ｍ製套管２は、熱膨張係数が８．０ＸｔＯ”６／℃の
コバルトニッケル鋼で形成されている。後端面２】、先
端面２３は回転軸に対して垂直である。The gold sleeve tube 2 is made of cobalt nickel steel with a thermal expansion coefficient of 8.0XtO''6/°C.The rear end surface 2 and the front end surface 23 are perpendicular to the axis of rotation.
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’Ｃ程度の使用温度下（８０℃）で前記隙間
１４がほぼＯｒｎｍとなるようにされている。The clearance fit between the metal sleeve 2 (inner diameter is approximately 17 mm at room temperature) and the metal rotating shaft 1 (diameter 17 mm at room temperature) is such that when the temperature is relatively low near room temperature, the gap 14 (the small diameter portion 11 and the metal With the cannula 2), there is no misalignment (axial runout),
Moreover, the gap 14 is designed to be approximately Ornm at an operating temperature of about 100'C (80°C).
嵌め輸３は、熱１ｌｊＩ３１係数が３．０Ｘ１０−’／
’Ｃ５長さ１０ｍｍのフェノール樹脂で形成されている
。Insertion 3 has a heat 1ljI31 coefficient of 3.0X10-'/
'C5 is made of phenolic resin with a length of 10 mm.
この嵌め輪３の後４１面３１は回転軸に対して垂直であ
る。The rear surface 31 of this fitting ring 3 is perpendicular to the axis of rotation.
本実施例のセラミック軸受の取付ＪＩＥは使用温度の一
ト、限値が池の実施例のものより低い、また、嵌め輪３
に熱ｌＩ５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ｌｊ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。The ceramic bearing installation JIE of this example has a working temperature of 1 and a lower limit value than that of the example of Ike, and the fitting ring 3
It is necessary to use a material with a large thermal lI5 tensile coefficient, and the metal rotating shaft 1 needs to have a thermal lj tensile coefficient as close to that of the ceramic bearing 4 as possible.
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、ｆｆ！華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 mentioned above, if the specifications between each material are satisfied and the operating temperature is relatively low, ff! It has an elegant structure and is effective as a low-cost mounting structure for ceramic bearings.
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７１２、球４３がセラミ
ックでなくても良い。a. In the ceramic bearing 4, the outer ring 712 and the balls 43 do not need to be made of 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、ボリテｌ〜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 metal such as magnesium alloy, silicone, polydiallyl phthalate, heat resistant plastic such as bolite-lafluoroethylene, etc.
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Ｗｉ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ｉ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。FIG. 1 is a sectional view of a ceramic bearing mounting structure 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 ceramic bearing mounting structure according to a third embodiment of the present invention. FIG. 4 is a sectional view of a ceramic bearing mounting structure according to a fourth embodiment of the present invention. FIG. 5 is a sectional view of a ceramic bearing mounting structure according to a fifth embodiment of the present invention.
Claims (1)
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。 ２）前記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。[Claims] 1) A ceramic bearing mounting structure comprising a metal rotating shaft having a small diameter portion and a ceramic bearing attached to the small diameter portion, the coefficient of thermal expansion being smaller than that of the metal rotating shaft. , and a metal sleeve whose diameter is larger than the inner ring of the ceramic bearing is loosely fitted into the small-diameter portion and arranged between the small-diameter portion and the inner ring; A mounting structure for a ceramic bearing characterized in that a fitting ring having a coefficient of thermal expansion larger than that of the shaft is interposed coaxially and fixed by a fastening member. 2) The respective end surfaces 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 fitting ring and the metal rotating shaft are brought into surface contact, and at least 2. The ceramic bearing mounting structure according to claim 1, wherein one set is formed into 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 true JPH034026A (en) | 1991-01-10 |
| JP2641762B2 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 (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH05321940A (en) * | 1992-05-21 | 1993-12-07 | Ngk Insulators Ltd | Bearing unit |
| EP0636804A1 (en) * | 1993-07-29 | 1995-02-01 | S.N.R. Roulements | Mounting of a bearing on a shaft |
| WO1996018047A1 (en) * | 1994-12-08 | 1996-06-13 | Sihi Gmbh & Co. Kg | Centring a bush made of a material sensitive to tensile stress on a shaft |
| JP2007192120A (en) * | 2006-01-19 | 2007-08-02 | Toyota Motor Corp | Turbocharger |
| DE102010025371B4 (en) | 2010-06-28 | 2018-10-11 | Schaeffler Technologies AG & Co. KG | bearing arrangement |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5045283B2 (en) | 2007-07-13 | 2012-10-10 | 株式会社ジェイテクト | Driving force transmission device |
-
1989
- 1989-05-29 JP JP13563789A patent/JP2641762B2/en not_active Expired - Fee Related
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH05321940A (en) * | 1992-05-21 | 1993-12-07 | Ngk Insulators Ltd | Bearing unit |
| EP0636804A1 (en) * | 1993-07-29 | 1995-02-01 | S.N.R. Roulements | Mounting of a bearing on a shaft |
| FR2708685A1 (en) * | 1993-07-29 | 1995-02-10 | Roulements Soc Nouvelle | Bearing mounting on a shaft. |
| WO1996018047A1 (en) * | 1994-12-08 | 1996-06-13 | Sihi Gmbh & Co. Kg | Centring a bush made of a material sensitive to tensile stress on a shaft |
| US5775816A (en) * | 1994-12-08 | 1998-07-07 | Sihi Gmbh & Co Kg | Bearing arrangement |
| JP2007192120A (en) * | 2006-01-19 | 2007-08-02 | Toyota Motor Corp | Turbocharger |
| DE102010025371B4 (en) | 2010-06-28 | 2018-10-11 | Schaeffler Technologies AG & Co. KG | bearing arrangement |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2641762B2 (en) | 1997-08-20 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| LAPS | Cancellation because of no payment of annual fees |