WO2019189116A1 - Composite bearing - Google Patents

Composite bearing Download PDF

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Publication number
WO2019189116A1
WO2019189116A1 PCT/JP2019/012750 JP2019012750W WO2019189116A1 WO 2019189116 A1 WO2019189116 A1 WO 2019189116A1 JP 2019012750 W JP2019012750 W JP 2019012750W WO 2019189116 A1 WO2019189116 A1 WO 2019189116A1
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Prior art keywords
thrust
shaft
radial
outer ring
inner ring
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PCT/JP2019/012750
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French (fr)
Japanese (ja)
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圭吾 中山
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Ntn株式会社
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Publication of WO2019189116A1 publication Critical patent/WO2019189116A1/en

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • 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
    • F16C19/49—Bearings with both balls and rollers

Definitions

  • This invention relates to a composite bearing in which a thrust ball bearing and a radial roller bearing are integrated.
  • a bearing for a spindle support part of a machine tool or a transmission for example, a composite bearing in which a thrust ball bearing that receives an axial load and a radial needle roller bearing that receives a radial load shown in Patent Document 1 below is integrated is adopted.
  • a composite bearing in which a thrust ball bearing that receives an axial load and a radial needle roller bearing that receives a radial load shown in Patent Document 1 below is integrated is adopted.
  • the composite type bearing is space-saving compared to the case where the thrust ball bearing and the radial roller bearing are used separately, it can contribute to the compactness of the entire apparatus.
  • an appropriate amount of preload is usually applied in the axial direction in order to suppress slippage of the rolling elements, shaft runout, and vibration in the axial direction.
  • this preload By applying this preload, the center position of the ball groove formed in each of the inner ring of the thrust ball bearing and the outer ring of the thrust ball bearing integrated with the outer ring of the radial roller bearing is aligned when the shaft rotates. Further, the inner ring of the thrust ball bearing moves in the radial direction. By this alignment, a smooth rotation state of the thrust ball bearing can be ensured.
  • the inner ring inner diameter and outer ring outer diameter dimensional tolerances and shaft dimensional tolerances are set based on predetermined industrial standards (JIS). . Further, the dimensional tolerance of the housing is not specifically described, and an appropriate tolerance range class is selected so as to fit the outer ring outer diameter of the thrust ball bearing and provide a clearance.
  • the dimensional tolerance guideline for the thrust ball bearing cannot be used as it is.
  • various standards do not specify guidelines for dimensional tolerances of composite bearings.
  • an object of the present invention is to complete the alignment even after the preload is applied and to ensure a smooth rotation in the composite bearing.
  • the thrust fitting clearance between the shaft and the thrust inner ring is A
  • the radial internal clearance between the shaft and the roller is B
  • the minimum value in the tolerance range of the thrust fitting clearance A is Amin
  • the maximum value in the tolerance range of the radial inner clearance B is Bmax
  • the total coaxiality value is the sum of the inner diameter of the thrust inner ring and the coaxiality of the inner ring ball groove and the outer diameter of the radial outer ring and the coaxiality of the outer ring ball groove.
  • a composite bearing in which Amin> Bmax + C + ⁇ is formed when the sum of the numerical values of the basic
  • the basic tolerance of the shaft may be a tolerance class 6 defined by JISB0401-1
  • a basic tolerance of the housing may be a tolerance class 7 defined by JISB0401-1.
  • Sectional view showing a composite bearing according to the present invention Sectional view showing an assembly example of the composite bearing shown in FIG. Sectional drawing which shows the state which made the axial center of the compound-type bearing shown in FIG. Sectional view showing the state before alignment Sectional view showing the state after alignment Sectional view showing the state where alignment could not be completed
  • a composite bearing 10 according to the present invention will be described with reference to FIGS.
  • This composite bearing 10 is an integral part of a thrust ball bearing that receives an axial load and a radial needle roller bearing that receives a radial load, and is generally light in the axial direction and more than a normal load in the radial direction. It is applied when each load is applied.
  • the composite bearing 10 includes a thrust inner ring 11, a thrust outer ring 12, a plurality of balls 13, a thrust retainer 14, and a radial outer ring 15 constituting a radial needle roller bearing 10b.
  • a plurality of needle rollers 16 and a radial cage 17 are provided. Further, if necessary, a dustproof cover 18 that covers the thrust ball bearing portion may be provided.
  • the rollers 16 are not limited to needle rollers, but may be cylindrical rollers.
  • the inner ring ball groove 11 a is formed in the thrust inner ring 11.
  • the coaxiality of the inner diameter of the thrust inner ring 11 and the inner ring ball groove 11a is a1.
  • the thrust outer ring 12 is formed with an outer ring ball groove 12a facing the inner ring ball groove 11a.
  • the axial end surface (end surface on the radial needle roller bearing 10 b side) of the thrust outer ring 12 is in contact with the housing 2.
  • a plurality of balls 13 are interposed between the inner ring ball groove 11a and the outer ring ball groove 12a. These balls 13 are held at predetermined intervals by a thrust holder 14.
  • the radial outer ring 15 is formed integrally with the thrust outer ring 12, and is press-fitted into the housing 2 as shown in FIG.
  • the coaxiality of the outer diameter of the radial outer ring 15 and the outer ring ball groove 12a is a2.
  • a plurality of needle rollers 16 are provided between the radial outer ring 15 and the shaft 1 inserted through the composite bearing 10. These rollers 16 are held at a predetermined interval by a radial holder 17.
  • the shaft 1 is inserted through the inner periphery of the thrust inner ring 11 and the needle rollers 16.
  • the shaft 1 is a worm shaft of a rotary table that fixes a workpiece in a machine tool such as a machining center.
  • a worm reducer may be incorporated in the rotary table for the purpose of securing rotational torque.
  • the worm shaft 1 extends horizontally in the longitudinal direction of the needle rollers 16.
  • One end of the worm shaft 1 is supported by the housing 2 via a composite bearing 10.
  • One end of the worm shaft 1 is provided with a preload mechanism 3 for applying a preload to the thrust ball bearing 10 a portion of the composite bearing 10.
  • the preload mechanism 3 is constituted by a lock nut, and a preload in the axial direction is applied to the composite bearing 10 by tightening the lock nut.
  • the thrust fitting clearance between the shaft 1 and the thrust inner ring 11 is A
  • the radial internal clearance between the shaft 1 and the needle roller 16 is B
  • the minimum value in the tolerance range of the thrust fitting gap A is Amin
  • the maximum value is Amax
  • the minimum value in the tolerance range of the radial internal gap B is Bmin
  • the maximum value is Bmax.
  • the sum of the inner diameter of the thrust inner ring 11 and the coaxiality a1 of the inner ring ball groove 11a, and the outer diameter of the radial outer ring 15 and the coaxiality a2 of the outer ring ball groove 12a is defined as a coaxiality total value C.
  • the basic tolerance of shaft 1 is the tolerance class 6 specified by the industry standard (JISB0401-1: 2016)
  • the basic tolerance of the housing 2 is the tolerance class 7 specified by the industry standard (JISB0401-1: 2016).
  • the sum of the numerical values of the basic tolerances defined by the respective tolerance classes of the shaft 1 and the housing 2 is ⁇ .
  • the basic tolerance value of the tolerance class 6 is 13 ⁇ m
  • the basic tolerance value of the tolerance class 7 is 25 ⁇ m.
  • the sum ⁇ of the basic tolerance values is 38 ⁇ m.
  • FIG. 3 shows a state where the axis of the composite bearing 10 and the axis of the shaft 1 are coaxial.
  • a uniform thrust fitting gap (A / 2) is formed between the thrust inner ring 11 and the shaft 1 in the circumferential direction, and an equal size is provided between the plurality of needle rollers 16 and the shaft 1.
  • the radial internal gap (B / 2) is formed.
  • each component is designed so as to satisfy the relational expression Amin> Bmax + C + ⁇ .
  • the processing accuracy (eccentricity) of the inner ring ball groove 11a and the outer ring ball groove 12a formed in the radial inner ring 11 and the radial outer ring 12 and the variation in the processing accuracy of the shaft 1 and the housing 2 are not affected.
  • the alignment can be completed as shown in FIG.
  • the relational expression Amax Amin + shaft basic tolerance (tolerance class 6 defined in JISB0401-1) is also defined.
  • the composite bearing 10 according to each of the above embodiments is merely an example, and in the composite bearing 10, as long as the problem of the present invention that enables alignment by a preload load can be solved, It is allowed to change the arrangement and the like as appropriate.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

This composite bearing is configured such that when A is the thrust fitting gap between a shaft (1) and a thrust inner ring (11), B is the radial inner gap between the shaft (1) and a roller (16), Amin is the minimum value within an error range of the thrust fitting gap (A), Bmax is the maximum value within an error range of the radial inner gap (B), C is the sum of the coaxiality of the inner diameter of the thrust inner ring (11) and an inner ring ball groove (11a) and the coaxiality of a radial outer ring (15) and an outer ring ball groove (12a), and α is the sum of the numerical values of basic errors of the shaft (1) and a housing (2), the relationship Amin>Bmax +C+α is satisfied.

Description

複合形軸受Compound bearing
　この発明は、スラスト玉軸受とラジアルころ軸受を一体化した複合形軸受に関する。 This invention relates to a composite bearing in which a thrust ball bearing and a radial roller bearing are integrated.
　工作機や変速機の主軸支持部の軸受として、例えば、下記特許文献１に示す、アキシアル荷重を受けるスラスト玉軸受とラジアル荷重を受けるラジアル針状ころ軸受を一体化した複合形軸受が採用されることがある。複合形軸受は、スラスト玉軸受とラジアルころ軸受とを別々に用いる場合と比べて省スペースであるため、装置全体のコンパクト化に貢献することができる。 As a bearing for a spindle support part of a machine tool or a transmission, for example, a composite bearing in which a thrust ball bearing that receives an axial load and a radial needle roller bearing that receives a radial load shown in Patent Document 1 below is integrated is adopted. Sometimes. Since the composite type bearing is space-saving compared to the case where the thrust ball bearing and the radial roller bearing are used separately, it can contribute to the compactness of the entire apparatus.
　複合形軸受の使用に際しては、転動体の滑りや軸振れ、アキシアル方向の振動を抑制するために、通常は、アキシアル方向に適切な大きさの予圧が負荷される。この予圧を負荷することによって、軸の回転時において、スラスト玉軸受の内輪とラジアルころ軸受の外輪と一体化したスラスト玉軸受の外輪のそれぞれに形成されたボール溝の中心位置が調心するように、スラスト玉軸受の内輪が径方向に移動する。この調心によって、スラスト玉軸受のスムーズな回転状態を確保することができる。 When using a composite bearing, an appropriate amount of preload is usually applied in the axial direction in order to suppress slippage of the rolling elements, shaft runout, and vibration in the axial direction. By applying this preload, the center position of the ball groove formed in each of the inner ring of the thrust ball bearing and the outer ring of the thrust ball bearing integrated with the outer ring of the radial roller bearing is aligned when the shaft rotates. Further, the inner ring of the thrust ball bearing moves in the radial direction. By this alignment, a smooth rotation state of the thrust ball bearing can be ensured.
特開２００２－３１７８１７号公報JP 2002-317817 A
　一般的なスラスト玉軸受（ラジアルころ軸受と一体化されていないもの）の内輪内径及び外輪外径の寸法公差、軸の寸法公差は予め定められた工業規格（ＪＩＳ）に基づいて設定されている。また、ハウジングの寸法公差は、具体的には明記されておらず、スラスト玉軸受の外輪外径に嵌め合い隙間を与えるように、適切な公差域クラスが選定されている。 In general thrust ball bearings (not integrated with radial roller bearings), the inner ring inner diameter and outer ring outer diameter dimensional tolerances and shaft dimensional tolerances are set based on predetermined industrial standards (JIS). . Further, the dimensional tolerance of the housing is not specifically described, and an appropriate tolerance range class is selected so as to fit the outer ring outer diameter of the thrust ball bearing and provide a clearance.
　これに対し、複合形軸受においては、スラスト玉軸受と構成が異なるため、スラスト玉軸受に係る寸法公差の指針はそのまま転用することができない。また、各種の規格においても、複合形軸受の寸法公差の指針について明記されていない。この寸法公差に対する考慮が不十分である場合、図６に示す複合形軸受２０で見られるように、調心前の状態から、アキシアル方向に予圧を負荷したときに、スラスト内輪１１の内周面と軸１が接触して（図６中のＡ部参照）、調心を完了することができない場合がある。 On the other hand, since the configuration of the compound type bearing is different from that of the thrust ball bearing, the dimensional tolerance guideline for the thrust ball bearing cannot be used as it is. Also, various standards do not specify guidelines for dimensional tolerances of composite bearings. When the consideration on the dimensional tolerance is insufficient, as seen in the composite bearing 20 shown in FIG. 6, the inner peripheral surface of the thrust inner ring 11 when preload is applied in the axial direction from the state before alignment. May contact the shaft 1 (see section A in FIG. 6), and alignment may not be completed.
　このように、調心が完了しない状態のまま複合形軸受２０を作動させると、回転不良、トルクや振動の増大等の問題が生じる虞がある。 Thus, if the composite bearing 20 is operated in a state where alignment is not completed, problems such as poor rotation, increased torque and vibration may occur.
　そこで、この発明は、複合形軸受において、予圧負荷後でも調心を完了させて滑らかな回転を確保することを課題とする。 Therefore, an object of the present invention is to complete the alignment even after the preload is applied and to ensure a smooth rotation in the composite bearing.
　上記の課題を解決するために、この発明においては、スラスト内輪と、スラスト外輪と、前記スラスト内輪と前記スラスト外輪との間に介在する複数の玉とを有するスラスト玉軸受と、前記スラスト外輪と一体に形成されたラジアル外輪と、前記ラジアル外輪と軸との間に介在する複数のころとを有するラジアルころ軸受と、
を備え、前記軸と前記スラスト内輪とのスラスト嵌め合い隙間をＡ、及び、前記軸と前記ころとのラジアル内部隙間をＢとし、前記スラスト嵌め合い隙間Ａの公差レンジにおける最小値がＡｍｉｎ、前記ラジアル内部隙間Ｂの公差レンジにおける最大値がＢｍａｘ、前記スラスト内輪の内径と内輪ボール溝の同軸度と前記ラジアル外輪の外径と外輪ボール溝の同軸度との合計である同軸度合計値がＣであり、前記軸及びハウジングの前記各公差等級で規定される基本公差の数値の和がαであるときに、Ａｍｉｎ＞Ｂｍａｘ＋Ｃ＋αである複合形軸受を構成した。 In order to solve the above problem, in the present invention, a thrust inner ring, a thrust outer ring, a thrust ball bearing having a plurality of balls interposed between the thrust inner ring and the thrust outer ring, and the thrust outer ring, A radial roller bearing having a radially outer ring formed integrally, and a plurality of rollers interposed between the radial outer ring and the shaft;
The thrust fitting clearance between the shaft and the thrust inner ring is A, and the radial internal clearance between the shaft and the roller is B, and the minimum value in the tolerance range of the thrust fitting clearance A is Amin, The maximum value in the tolerance range of the radial inner clearance B is Bmax, and the total coaxiality value is the sum of the inner diameter of the thrust inner ring and the coaxiality of the inner ring ball groove and the outer diameter of the radial outer ring and the coaxiality of the outer ring ball groove. A composite bearing in which Amin> Bmax + C + α is formed when the sum of the numerical values of the basic tolerances defined by the respective tolerance grades of the shaft and the housing is α.
　このようにすると、ラジアル内部隙間の最大値Ｂｍａｘの範囲内で軸がその径方向に移動しても、スラスト内輪の内径面と軸との間に隙間を確保することができる。しかも、スラスト内輪及びスラスト外輪に形成された各ボール溝の加工精度に起因して同軸度が高い（スラスト内外輪に対する各ボール溝のずれが大きい）場合や、軸及びハウジングの加工精度が不十分である場合においても、それらを考慮してスラスト内輪の内径面と軸との間の隙間に余裕が生じるため、軸とスラスト内輪の内径面が干渉するのを防止して、調心を完了させることができる。 In this way, even if the shaft moves in the radial direction within the range of the maximum value Bmax of the radial internal gap, a gap can be secured between the inner diameter surface of the thrust inner ring and the shaft. Moreover, due to the processing accuracy of each ball groove formed in the thrust inner ring and the thrust outer ring, when the coaxiality is high (the displacement of each ball groove with respect to the thrust inner and outer rings is large), or the shaft and housing processing accuracy is insufficient. Even in this case, there is a margin in the gap between the inner diameter surface of the thrust inner ring and the shaft in consideration of them, so that the shaft and the inner diameter surface of the thrust inner ring are prevented from interfering to complete alignment. be able to.
　上記構成においては、前記軸の基本公差がＪＩＳＢ０４０１－１で規定される公差等級６、及び、前記ハウジングの基本公差がＪＩＳＢ０４０１－１で規定される公差等級７とすることができる。 In the above configuration, the basic tolerance of the shaft may be a tolerance class 6 defined by JISB0401-1, and a basic tolerance of the housing may be a tolerance class 7 defined by JISB0401-1.
　これにより、複合形軸受において、予圧負荷後でも調心を完了させて滑らかな回転を確保することができる。 This makes it possible to complete alignment and ensure smooth rotation even after preloading in a composite bearing.
この発明に係る複合形軸受を示す断面図Sectional view showing a composite bearing according to the present invention 図１に示す複合形軸受の組み付け例を示す断面図Sectional view showing an assembly example of the composite bearing shown in FIG. 図１に示す複合形軸受の軸心と軸の軸心を同軸とした状態を示す断面図Sectional drawing which shows the state which made the axial center of the compound-type bearing shown in FIG. 調心前の状態を示す断面図Sectional view showing the state before alignment 調心後の状態を示す断面図Sectional view showing the state after alignment 調心を完了できなかった状態を示す断面図Sectional view showing the state where alignment could not be completed
　この発明に係る複合形軸受１０を図１から図５を用いて説明する。この複合形軸受１０は、アキシアル荷重を受けるスラスト玉軸受とラジアル荷重を受けるラジアル針状ころ軸受を一体としたものであって、一般的にアキシアル方向に軽荷重、及び、ラジアル方向に普通荷重以上の荷重がそれぞれ負荷される場合に適用される。この複合形軸受１０は、スラスト玉軸受１０ａ部分を構成するスラスト内輪１１、スラスト外輪１２、複数の玉１３、及び、スラスト保持器１４、並びに、ラジアル針状ころ軸受１０ｂ部分を構成するラジアル外輪１５、複数の針状ころ１６、及び、ラジアル保持器１７を備えている。また、必要に応じて、スラスト玉軸受部分を覆う防塵カバー１８を設けることもできる。なお、ころ１６は、針状ころに限らず、円筒ころであってもよい。 A composite bearing 10 according to the present invention will be described with reference to FIGS. This composite bearing 10 is an integral part of a thrust ball bearing that receives an axial load and a radial needle roller bearing that receives a radial load, and is generally light in the axial direction and more than a normal load in the radial direction. It is applied when each load is applied. The composite bearing 10 includes a thrust inner ring 11, a thrust outer ring 12, a plurality of balls 13, a thrust retainer 14, and a radial outer ring 15 constituting a radial needle roller bearing 10b. A plurality of needle rollers 16 and a radial cage 17 are provided. Further, if necessary, a dustproof cover 18 that covers the thrust ball bearing portion may be provided. The rollers 16 are not limited to needle rollers, but may be cylindrical rollers.
　スラスト内輪１１には、内輪ボール溝１１ａが形成されている。スラスト内輪１１の内径と内輪ボール溝１１ａの同軸度は、ａ１である。スラスト外輪１２には、内輪ボール溝１１ａに対向する外輪ボール溝１２ａが形成されている。スラスト外輪１２の軸方向端面（ラジアル針状ころ軸受１０ｂ側の端面）は、ハウジング２に当接している。内輪ボール溝１１ａと外輪ボール溝１２ａの間には、複数の玉１３が介在して設けられている。これらの玉１３は、スラスト保持器１４によって、所定間隔で保持されている。 The inner ring ball groove 11 a is formed in the thrust inner ring 11. The coaxiality of the inner diameter of the thrust inner ring 11 and the inner ring ball groove 11a is a1. The thrust outer ring 12 is formed with an outer ring ball groove 12a facing the inner ring ball groove 11a. The axial end surface (end surface on the radial needle roller bearing 10 b side) of the thrust outer ring 12 is in contact with the housing 2. A plurality of balls 13 are interposed between the inner ring ball groove 11a and the outer ring ball groove 12a. These balls 13 are held at predetermined intervals by a thrust holder 14.
　ラジアル外輪１５は、スラスト外輪１２と一体に形成され、図２に示すように、ハウジング２に圧入されている。ラジアル外輪１５の外径と外輪ボール溝１２ａの同軸度は、ａ２である。ラジアル外輪１５と複合形軸受１０に挿通された軸１との間に、複数の針状ころ１６が介在して設けられている。これらのころ１６は、ラジアル保持器１７によって、所定間隔で保持されている。 The radial outer ring 15 is formed integrally with the thrust outer ring 12, and is press-fitted into the housing 2 as shown in FIG. The coaxiality of the outer diameter of the radial outer ring 15 and the outer ring ball groove 12a is a2. A plurality of needle rollers 16 are provided between the radial outer ring 15 and the shaft 1 inserted through the composite bearing 10. These rollers 16 are held at a predetermined interval by a radial holder 17.
　スラスト内輪１１及び針状ころ１６の内周には、軸１が挿通されている。本実施形態において、軸１は、マシニングセンタ等の工作機械において、ワークを固定する回転テーブルのウォーム軸である。回転テーブルには、回転トルクを確保する等を目的として、ウォーム減速機が組み込まれていることがある。ウォーム軸１は、針状ころ１６の長手方向に水平に延びている。ウォーム軸１の一端は、複合形軸受１０を介してハウジング２に支持されている。ウォーム軸１の一端には、複合形軸受１０のうちスラスト玉軸受１０ａ部分に予圧を与える予圧機構３が設けられている。本実施形態では、予圧機構３はロックナットで構成されており、当該ロックナットの締付により複合形軸受１０に対してアキシアル方向の予圧が負荷される。 The shaft 1 is inserted through the inner periphery of the thrust inner ring 11 and the needle rollers 16. In the present embodiment, the shaft 1 is a worm shaft of a rotary table that fixes a workpiece in a machine tool such as a machining center. A worm reducer may be incorporated in the rotary table for the purpose of securing rotational torque. The worm shaft 1 extends horizontally in the longitudinal direction of the needle rollers 16. One end of the worm shaft 1 is supported by the housing 2 via a composite bearing 10. One end of the worm shaft 1 is provided with a preload mechanism 3 for applying a preload to the thrust ball bearing 10 a portion of the composite bearing 10. In the present embodiment, the preload mechanism 3 is constituted by a lock nut, and a preload in the axial direction is applied to the composite bearing 10 by tightening the lock nut.
　ここで、軸１とスラスト内輪１１とのスラスト嵌め合い隙間をＡとし、軸１と針状ころ１６とのラジアル内部隙間をＢとする。また、スラスト嵌め合い隙間Ａの公差レンジにおける最小値をＡｍｉｎ、最大値をＡｍａｘ、ラジアル内部隙間Ｂの公差レンジにおける最小値をＢｍｉｎ、最大値をＢｍａｘとする。さらに、スラスト内輪１１の内径と内輪ボール溝１１ａの同軸度ａ１と、ラジアル外輪１５の外径と外輪ボール溝１２ａの同軸度ａ２との合計を同軸度合計値Ｃとする。 Here, the thrust fitting clearance between the shaft 1 and the thrust inner ring 11 is A, and the radial internal clearance between the shaft 1 and the needle roller 16 is B. Further, the minimum value in the tolerance range of the thrust fitting gap A is Amin, the maximum value is Amax, the minimum value in the tolerance range of the radial internal gap B is Bmin, and the maximum value is Bmax. Further, the sum of the inner diameter of the thrust inner ring 11 and the coaxiality a1 of the inner ring ball groove 11a, and the outer diameter of the radial outer ring 15 and the coaxiality a2 of the outer ring ball groove 12a is defined as a coaxiality total value C.
　さらに、軸１の基本公差を工業規格（ＪＩＳＢ０４０１－１：２０１６）で規定される公差等級６、及び、ハウジング２の基本公差を工業規格（ＪＩＳＢ０４０１－１：２０１６）で規定される公差等級７とし、軸１及びハウジング２の前記各公差等級で規定される基本公差の数値の和をαとする。例えば、ＪＩＳＢ０４０１－１の表１から、軸１の直径が３０ｍｍのとき公差等級６の基本公差の数値は１３μｍ、ハウジング２の内径が５０ｍｍのとき公差等級７の基本公差の数値は２５μｍとなるため、基本公差の数値の和αは３８μｍとなる。 Furthermore, the basic tolerance of shaft 1 is the tolerance class 6 specified by the industry standard (JISB0401-1: 2016), and the basic tolerance of the housing 2 is the tolerance class 7 specified by the industry standard (JISB0401-1: 2016). The sum of the numerical values of the basic tolerances defined by the respective tolerance classes of the shaft 1 and the housing 2 is α. For example, from Table 1 of JISB0401-1, when the diameter of the shaft 1 is 30 mm, the basic tolerance value of the tolerance class 6 is 13 μm, and when the inner diameter of the housing 2 is 50 mm, the basic tolerance value of the tolerance class 7 is 25 μm. The sum α of the basic tolerance values is 38 μm.
　複合形軸受１０の軸心と軸１の軸心を同軸とした状態を図３に示す。このとき、スラスト内輪１１と軸１の間には周方向に均等なスラスト嵌め合い隙間（Ａ／２）が形成されるとともに、複数の針状ころ１６と軸１の間には均等な大きさのラジアル内部隙間（Ｂ／２）が形成されている。この複合形軸受１０を軸１に組み込んだ際に、スラスト内輪１１の自重によって、このスラスト内輪１１は軸１に接触している。 FIG. 3 shows a state where the axis of the composite bearing 10 and the axis of the shaft 1 are coaxial. At this time, a uniform thrust fitting gap (A / 2) is formed between the thrust inner ring 11 and the shaft 1 in the circumferential direction, and an equal size is provided between the plurality of needle rollers 16 and the shaft 1. The radial internal gap (B / 2) is formed. When the composite bearing 10 is incorporated in the shaft 1, the thrust inner ring 11 is in contact with the shaft 1 due to the weight of the thrust inner ring 11.
　この実施例に係る複合形軸受１０においては、関係式Ａｍｉｎ＞Ｂｍａｘ＋Ｃ＋αを満たすように各構成部材の寸法設計がなされている。この関係式を満たすことによって、ラジアル内輪１１及びラジアル外輪１２に形成された内輪ボール溝１１ａ及び外輪ボール溝１２ａの加工精度（偏心度）や、軸１及びハウジング２の加工精度のばらつきに関係なく、この複合形軸受１０にアキシアル方向の予圧を負荷することによって、図５に示すように、調心を完了することができる。 In the composite bearing 10 according to this embodiment, the dimensions of each component are designed so as to satisfy the relational expression Amin> Bmax + C + α. By satisfying this relational expression, the processing accuracy (eccentricity) of the inner ring ball groove 11a and the outer ring ball groove 12a formed in the radial inner ring 11 and the radial outer ring 12 and the variation in the processing accuracy of the shaft 1 and the housing 2 are not affected. By applying a preload in the axial direction to the composite bearing 10, the alignment can be completed as shown in FIG.
　また、この複合形軸受１０においては、関係式Ａｍａｘ＝Ａｍｉｎ＋軸の基本公差（ＪＩＳＢ０４０１－１で規定される公差等級６）も規定する。このように規定することによって、アキシアル方向への予圧負荷時のスラスト内輪１１の調心をスムーズに行うことができるとともに、複合形軸受１０への軸１の組み立て性を向上することができる。 In the composite bearing 10, the relational expression Amax = Amin + shaft basic tolerance (tolerance class 6 defined in JISB0401-1) is also defined. By defining in this way, it is possible to smoothly align the thrust inner ring 11 at the time of preloading in the axial direction, and it is possible to improve the assemblability of the shaft 1 to the composite bearing 10.
　上記各実施例に係る複合形軸受１０はあくまでも例示に過ぎず、複合形軸受１０において、予圧の負荷によって調心可能とする、というこの発明の課題を解決し得る限りにおいて、各部材の形状や配置等を適宜変更することが許容される。 The composite bearing 10 according to each of the above embodiments is merely an example, and in the composite bearing 10, as long as the problem of the present invention that enables alignment by a preload load can be solved, It is allowed to change the arrangement and the like as appropriate.
１０　複合形軸受
１１　スラスト内輪
１１ａ　内輪ボール溝
１２　スラスト外輪
１２ａ　外輪ボール溝
１３　玉
１４　スラスト保持器
１５　ラジアル外輪
１６　ころ
１７　ラジアル保持器 DESCRIPTION OF SYMBOLS 10 Compound type bearing 11 Thrust inner ring 11a Inner ring ball groove 12 Thrust outer ring 12a Outer ring ball groove 13 Ball 14 Thrust retainer 15 Radial outer ring 16 Roller 17 Radial retainer

Claims (2)

  1. 　スラスト内輪と、スラスト外輪と、前記スラスト内輪と前記スラスト外輪との間に介在する複数の玉とを有するスラスト玉軸受と、
    　前記スラスト外輪と一体に形成されたラジアル外輪と、前記ラジアル外輪と軸との間に介在する複数のころとを有するラジアルころ軸受と、
    を備え、
    　前記軸と前記スラスト内輪とのスラスト嵌め合い隙間をＡ、及び、前記軸と前記ころとのラジアル内部隙間をＢとし、前記スラスト嵌め合い隙間Ａの公差レンジにおける最小値がＡｍｉｎ、前記ラジアル内部隙間Ｂの公差レンジにおける最大値がＢｍａｘ、前記スラスト内輪の内径と内輪ボール溝の同軸度と前記ラジアル外輪の外径と外輪ボール溝の同軸度との合計である同軸度合計値がＣであり、前記軸及びハウジングの基本公差の数値の和がαであるときに、Ａｍｉｎ＞Ｂｍａｘ＋Ｃ＋αである複合形軸受。     A thrust ball bearing having a thrust inner ring, a thrust outer ring, and a plurality of balls interposed between the thrust inner ring and the thrust outer ring;
    A radial roller bearing having a radial outer ring formed integrally with the thrust outer ring, and a plurality of rollers interposed between the radial outer ring and a shaft;
    With
    The thrust fitting clearance between the shaft and the thrust inner ring is A, and the radial internal clearance between the shaft and the roller is B. The minimum value in the tolerance range of the thrust fitting clearance A is Amin, and the radial internal clearance The maximum value in the tolerance range of B is Bmax, the coaxiality total value that is the sum of the inner diameter of the thrust inner ring and the coaxiality of the inner ring ball groove and the outer diameter of the radial outer ring and the coaxiality of the outer ring ball groove is C, A compound bearing in which Amin> Bmax + C + α when the sum of the numerical values of the basic tolerances of the shaft and the housing is α.
  2. 　前記軸の基本公差がＪＩＳＢ０４０１－１で規定される公差等級６、及び、前記ハウジングの基本公差がＪＩＳＢ０４０１－１で規定される公差等級７である、請求項１に記載の複合形軸受。 The composite bearing according to claim 1, wherein the basic tolerance of the shaft is a tolerance class 6 defined by JISB0401-1 and a basic tolerance of the housing is a tolerance class 7 defined by JISB0401-1.
PCT/JP2019/012750 2018-03-29 2019-03-26 Composite bearing WO2019189116A1 (en)

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CN113669367A (en) * 2021-08-20 2021-11-19 重庆美沣秦安汽车驱动***有限公司 Bearing structure for coaxial arrangement of input shaft and output shaft

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Publication number Priority date Publication date Assignee Title
GB864465A (en) * 1957-08-16 1961-04-06 Schaeffler Wilhelm Improvements in or relating to adjustable-clearance antifriction bearings
JP2002317817A (en) * 2001-04-19 2002-10-31 Nsk Ltd Radial roller bearing
JP2006070909A (en) * 2004-08-31 2006-03-16 Jtekt Corp Ball bearing
US20120199777A1 (en) * 2011-02-04 2012-08-09 Honeywell International Inc. Combination bearings having improved load capacities and lifespan and valve assemblies including the same

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB864465A (en) * 1957-08-16 1961-04-06 Schaeffler Wilhelm Improvements in or relating to adjustable-clearance antifriction bearings
JP2002317817A (en) * 2001-04-19 2002-10-31 Nsk Ltd Radial roller bearing
JP2006070909A (en) * 2004-08-31 2006-03-16 Jtekt Corp Ball bearing
US20120199777A1 (en) * 2011-02-04 2012-08-09 Honeywell International Inc. Combination bearings having improved load capacities and lifespan and valve assemblies including the same

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113669367A (en) * 2021-08-20 2021-11-19 重庆美沣秦安汽车驱动***有限公司 Bearing structure for coaxial arrangement of input shaft and output shaft

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