WO2018221080A1 - Palier de support d'arbre de pignon - Google Patents

Palier de support d'arbre de pignon Download PDF

Info

Publication number
WO2018221080A1
WO2018221080A1 PCT/JP2018/016577 JP2018016577W WO2018221080A1 WO 2018221080 A1 WO2018221080 A1 WO 2018221080A1 JP 2018016577 W JP2018016577 W JP 2018016577W WO 2018221080 A1 WO2018221080 A1 WO 2018221080A1
Authority
WO
WIPO (PCT)
Prior art keywords
pinion shaft
ball bearing
row angular
bearing
angular contact
Prior art date
Application number
PCT/JP2018/016577
Other languages
English (en)
Japanese (ja)
Inventor
康浩 江尻
敏宏 河合
Original Assignee
株式会社不二越
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 by 株式会社不二越 filed Critical 株式会社不二越
Publication of WO2018221080A1 publication Critical patent/WO2018221080A1/fr

Links

Images

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
    • F16C19/02—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
    • F16C19/16—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 with a single row of balls
    • 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
    • F16C19/18—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 with two or more rows of balls
    • 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
    • F16C19/54—Systems consisting of a plurality of bearings with rolling friction
    • 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
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/021—Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with bearings

Definitions

  • the present invention relates to a pinion shaft support bearing for supporting a pinion shaft of a pinion gear of a differential gear device for an automobile.
  • An automobile differential gear device is a device that makes a difference in rotational speed for each wheel when turning a curve, and is simply called a differential gear or a differential gear for short.
  • engine power is received by a pinion shaft extending in the vehicle longitudinal direction through a propeller shaft, and the pinion gear at the tip of the pinion shaft rotates from the pinion gear and various gears to the left and right wheels at different speeds. It conveys power.
  • the above pinion shaft is rotatably supported by a bearing with respect to the housing. Since the pinion shaft is a particularly heavy load component among the differential gear devices for automobiles, conventionally, the pinion shaft is often supported by using two tapered roller bearings having high rigidity. In recent years, tapered roller bearings have a large rotational torque, and it has been proposed to support a pinion shaft by combining a double-row angular ball bearing and a single-row angular ball bearing for the purpose of improving fuel efficiency (for example, Patent Document 1). ).
  • the contact angle ⁇ between the ball, the outer ring and the inner ring in the rolling bearing on the companion flange side is set to 30 ° ⁇ ⁇ ⁇ 45 ° in consideration of the load capacity (axial rigidity) with respect to the axial load. .
  • the load capacity axial rigidity
  • the companion flange of the pinion shaft is a connecting portion between the differential gear device and the propeller shaft, and the radial rigidity of the rolling bearing supporting the companion flange side greatly affects the displacement of the connecting portion. If the radial rigidity of the rolling bearing on the companion flange side is insufficient, the amount of displacement of the connecting portion between the differential gear device and the propeller shaft increases, which may cause vibration and noise when the vehicle travels.
  • the present invention has been made in view of such a problem, and an object of the present invention is to provide a pinion shaft support bearing capable of achieving both axial rigidity and radial rigidity and improving the life of the bearing and the fuel consumption of the vehicle.
  • a typical configuration of a pinion shaft support bearing according to the present invention is a pinion shaft support bearing for supporting a pinion shaft of a pinion gear of a differential gear device for an automobile.
  • the contact angle between the ball and the outer ring and the inner ring is 20 ° or more and 30 ° or less.
  • the radial rigidity of a single row angular contact ball bearing will be improved, and by combining this single row angular contact ball bearing and a double row angular contact ball bearing, the connection part of the said differential gear apparatus for motor vehicles and a propeller shaft ( The amount of displacement of the companion flange) can be reduced. Therefore, for example, it is possible to suppress vibration and noise when the vehicle travels, which may occur at the location. Moreover, the bearing life can be improved by making the axial rigidity and the radial rigidity of the single-row angular contact ball bearing compatible.
  • the groove R ratio (Ri / Bd) of the inner ring raceway groove is 0.5125 ⁇ Ri / Bd. It is good to satisfy. Contributing to the improvement of the fuel consumption of the vehicle by reducing the dynamic torque by reducing the contact area between the raceway groove and the ball by ensuring the groove R ratio to 0.5125 or more while ensuring the rigidity by the contact angle under the above-mentioned conditions. Is possible.
  • a pinion shaft support bearing capable of achieving both axial rigidity and radial rigidity and improving bearing life and fuel consumption of the vehicle.
  • DESCRIPTION OF SYMBOLS 100 Bearing for pinion shaft support, 102 ... Differential gear, 104 ... Housing, 106 ... Pinion gear, 108 ... Ring gear, 110 ... Pinion shaft, 112 ... Double row angular contact ball bearing, 113 ... Companion flange, 114 ... Single row angular contact Ball bearing, 116 ... outer ring, 118 ... inner ring, 120 ... ball, 122 ... raceway groove
  • FIG. 1 is a diagram of an automotive differential gear device (hereinafter, differential gear 102) using a pinion shaft support bearing 100 according to an embodiment of the present invention.
  • a differential gear 102 shown in FIG. 1 includes a pinion gear 106 and a ring gear 108 inside a housing 104, receives power from the engine by a pinion shaft 110 of the pinion gear 106 through a propeller shaft (not shown), and the ring gear. Rotational forces at different speeds are transmitted to the left and right wheels via 108 and various gears (not shown).
  • the pinion gear 106 is provided at one end of the pinion shaft 110 and meshes with the ring gear 108.
  • the other end of the pinion shaft 110 is provided with a companion flange 113 that is a part connected to a propeller shaft (not shown).
  • the pinion shaft 110 is supported by the pinion shaft support bearing 100 so as to be rotatable with respect to the housing 104.
  • the pinion shaft support bearing 100 includes a double-row angular ball bearing 112 and a single-row angular ball bearing 114.
  • the double row angular ball bearing 112 is disposed in the vicinity of the pinion gear 106 side of the pinion shaft 110.
  • the single row angular ball bearing 114 is disposed on the side opposite to the pinion gear 106 (on the companion flange 113 side) when viewed from the double row angular ball bearing 112 in the pinion shaft 110.
  • FIG. 2 is an enlarged view of the single-row angular contact ball bearing 114 of FIG.
  • the single-row angular contact ball bearing 114 includes an outer ring 116, an inner ring 118, and a row of balls 120 sandwiched between the outer ring 116 and the inner ring 118.
  • the contact angle ⁇ of the balls 120 of the single-row angular contact ball bearing 114 is set to an angle that can suitably exhibit rigidity not only in the axial direction but also in the radial direction.
  • a large load in the radial direction is applied to the pinion shaft 110 of FIG. 1 because the pinion gear 106 is engaged with the ring gear 108 and rotates. Therefore, the contact angle ⁇ is set slightly closer to the radial direction.
  • the contact angle ⁇ between the ball 120 of the single-row angular ball bearing 114 and the outer ring 116 and the inner ring 118 is set to 20 ° or more and 30 ° or less.
  • FIG. 3 is a diagram showing the results of a test relating to the contact angle ⁇ of the single row angular contact ball bearing 114.
  • 3 (a) to 3 (c) show the relationship between the contact angle ⁇ and each performance, where the horizontal axis is the contact angle ⁇ (deg) and the vertical axis is the other performance (displacement amount and bearing life).
  • Setting the contact angle ⁇ to 20 ° or more and 30 ° or less not only reduces the displacement of the connecting portion (companion flange 113) between the differential gear 102 and the propeller shaft but also improves the bearing life. Useful.
  • FIG. 3A is a line graph showing the relationship between the contact angle ⁇ in the single-row angular contact ball bearing 114 and the displacement ( ⁇ m) of the end face position of the companion flange 113.
  • the radial displacement increases as the contact angle ⁇ increases. This is because the radial rigidity of the single row angular contact ball bearing 114 decreases as the contact angle ⁇ increases.
  • the amount of displacement in the axial direction is not so dependent on the contact angle ⁇ . This is presumably because the contribution of the double-row angular contact ball bearing 112 is dominant in the axial displacement.
  • FIG. 3B is a line graph showing the relationship between the contact angle ⁇ and the bearing life (total number of rotations (M (mega) rev) that can be rotated without causing damage to the material due to rolling fatigue). From FIG. 3 (b), the bearing life becomes longer as the contact angle ⁇ increases. This is presumably because the radial load in the single-row angular contact ball bearing 114 decreases as the contact angle ⁇ increases.
  • the horizontal axis is the contact angle ⁇ (deg)
  • the left vertical axis is the bearing life (Mrev) of FIG. 3B
  • the right vertical axis is the radial direction of FIG. 3A. It is a graph made into the reciprocal number of displacement amount (micrometer). From FIG. 3C, it can be seen that the contact angle ⁇ in the single-row angular contact ball bearing 114 is preferably 20 ° or more and 30 ° or less from the relationship between the bearing life and the displacement.
  • the contact angle ⁇ between the ball 120 of the single row angular ball bearing 114 (see FIG. 2) and the outer ring 116 and the inner ring 118 is 20 It is set in the range of not less than 30 ° and not more than 30 °.
  • the radial rigidity of the single-row angular contact ball bearing 114 is improved, and the single-row angular contact ball bearing 114 and the double-row angular contact ball bearing 112 are combined to thereby connect the differential gear 102 and the propeller shaft (companion).
  • the amount of displacement of the flange 113) can be reduced, and vibration and noise during traveling of the vehicle that can occur at the relevant location can be suppressed.
  • the bearing life of the single row angular contact ball bearing 114 can be improved by making the axial stiffness and radial stiffness of the single row angular contact ball bearing 114 compatible.
  • the fuel efficiency of the vehicle is also improved.
  • the single-row angular contact ball bearing 114 of FIG. 2 has a groove R ratio (Ri / Bd) of the raceway groove 122 when the radius of curvature of the raceway groove 122 of the inner ring 118 is Ri and the diameter of the ball 120 is Bd. Is set to satisfy the condition of 0.5125 ⁇ Ri / Bd.
  • FIG. 4 is a diagram showing the results of a test regarding the groove R ratio and dynamic torque of the inner ring 118.
  • the horizontal axis is the groove R ratio (Ri / Bd) of the inner ring 118
  • the vertical axis is the dynamic torque (Nm).
  • the dynamic torque of the single-row angular contact ball bearing 114 decreases to near 0.200 when the groove R ratio is around 0.5125. This is because as the groove R ratio increases, that is, as the radius of curvature Ri of the track groove 122 increases, the contact area between the track groove 122 and the ball 120 also decreases.
  • the contact angle ⁇ is set to 20 ° or more and 30 ° or less to ensure rigidity
  • the groove R ratio of the inner ring 118 is set to 0.5125 or more.
  • the dynamic torque is lowered to improve vehicle fuel efficiency.
  • the amount of displacement of the connecting portion (companion flange 113) between the differential gear 102 and the propeller shaft is reduced by securing the radial rigidity of the single row angular ball bearing 114, and the single row angular ball bearing. The improvement in fuel efficiency of the vehicle due to a decrease in the dynamic torque 114 is achieved.
  • the present invention can be used for a pinion shaft support bearing that supports a pinion shaft of a pinion gear of a differential gear device for an automobile.

Landscapes

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

Abstract

L'invention concerne un palier de support d'arbre de pignon qui peut obtenir à la fois une rigidité axiale et une rigidité radiale et avec lequel la durée de vie du palier et l'économie de carburant d'un véhicule peuvent être améliorées. L'invention porte sur un palier de support d'arbre de pignon (100) destiné à supporter un arbre de pignon (110) d'un engrenage de pignon (106) d'un dispositif d'engrenage différentiel d'automobile, lequel palier comprend un roulement à billes à contact angulaire à rangées multiples (112) disposé sur le côté engrenage de pignon (106) de l'arbre de pignon (110), et un roulement à billes à contact angulaire à rangée unique (114) disposé sur l'arbre de pignon (110) sur le côté opposé à l'engrenage de pignon (106) lorsqu'il est vu depuis le roulement à billes à contact angulaire à rangées multiples (112). Le roulement à billes à contact angulaire à rangée unique (114) a un angle de contact entre une bille (120) et une bague externe (116) et une bague interne (118) de 20° à 30°.
PCT/JP2018/016577 2017-06-01 2018-04-24 Palier de support d'arbre de pignon WO2018221080A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2017-108963 2017-06-01
JP2017108963 2017-06-01

Publications (1)

Publication Number Publication Date
WO2018221080A1 true WO2018221080A1 (fr) 2018-12-06

Family

ID=64455978

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2018/016577 WO2018221080A1 (fr) 2017-06-01 2018-04-24 Palier de support d'arbre de pignon

Country Status (1)

Country Link
WO (1) WO2018221080A1 (fr)

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2004505219A (ja) * 2000-08-01 2004-02-19 ザ　ティムケン　カンパニー 高速アンギュラコンタクト玉軸受
JP2004169890A (ja) * 2002-11-22 2004-06-17 Koyo Seiko Co Ltd ピニオン軸支持用軸受装置
JP2007298184A (ja) * 2006-08-25 2007-11-15 Nsk Ltd アンギュラ玉軸受
JP2009036348A (ja) * 2007-08-03 2009-02-19 Ntn Corp タンデム型複列アンギュラ玉軸受及びピニオン軸用軸受装置
WO2011062269A1 (fr) * 2009-11-19 2011-05-26 日本精工株式会社 Dispositif de support de rotation pour arbre-pignon
JP2013508633A (ja) * 2009-10-21 2013-03-07 シェフラー テクノロジーズ アクチエンゲゼルシャフト ウント コンパニー コマンディートゲゼルシャフト 保持器ガイドが改善されたアンギュラ玉軸受け、特に主軸軸受け
US20150110434A1 (en) * 2012-03-15 2015-04-23 Aktiebolaget Skf Pinion Bearing Arrangement

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2004505219A (ja) * 2000-08-01 2004-02-19 ザ　ティムケン　カンパニー 高速アンギュラコンタクト玉軸受
JP2004169890A (ja) * 2002-11-22 2004-06-17 Koyo Seiko Co Ltd ピニオン軸支持用軸受装置
JP2007298184A (ja) * 2006-08-25 2007-11-15 Nsk Ltd アンギュラ玉軸受
JP2009036348A (ja) * 2007-08-03 2009-02-19 Ntn Corp タンデム型複列アンギュラ玉軸受及びピニオン軸用軸受装置
JP2013508633A (ja) * 2009-10-21 2013-03-07 シェフラー テクノロジーズ アクチエンゲゼルシャフト ウント コンパニー コマンディートゲゼルシャフト 保持器ガイドが改善されたアンギュラ玉軸受け、特に主軸軸受け
WO2011062269A1 (fr) * 2009-11-19 2011-05-26 日本精工株式会社 Dispositif de support de rotation pour arbre-pignon
US20150110434A1 (en) * 2012-03-15 2015-04-23 Aktiebolaget Skf Pinion Bearing Arrangement

Similar Documents

Publication Publication Date Title
US5711738A (en) Conical roller bearing for supporting a pinion shaft of differential gear
US7648283B2 (en) Bearing apparatus for a wheel of vehicle
CN101535665A (zh) 车轮用轴承装置
WO2011062269A1 (fr) Dispositif de support de rotation pour arbre-pignon
CN102939470B (zh) 车轮用轴承装置
JP3359501B2 (ja) デファレンシャルギヤのピニオン軸支持用円錐ころ軸受
US8678663B2 (en) Wheel hub assembly with two rows of rolling elements
US8714828B2 (en) Wheel hub assembly with dual rows of rolling elements
CN105378308A (zh) 用于将变速器轮支承在变速器轴上的不对称的锥形滚子轴承
US20080226213A1 (en) Wheel Bearing Unit
WO2018221080A1 (fr) Palier de support d'arbre de pignon
CN101031439A (zh) 滚动轴承装置
JP4823269B2 (ja) 車輪用軸受装置
US20200158166A1 (en) Automotive differential gear and automotive transmission
US9133876B2 (en) Wheel bearing device
JP6500356B2 (ja) 軸受機構
JP2006316904A (ja) 車輪用軸受装置
WO2018220899A1 (fr) Roulement à billes à double rangée et de contact sur quatre points
US20240191754A1 (en) Wheel hub bearing unit with optimized positioning of inboard rollers
JP3974156B2 (ja) 車輪用軸受装置
US11788578B2 (en) Wheel hub assembly with optimized raceways
KR20230055729A (ko) 드라이브 액슬 조립체
JP2006316905A (ja) 車輪用軸受装置
US20220290717A1 (en) Wheel hub assembly having low friction and high performance
JP2019019893A (ja) 後輪用ハブユニット軸受

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 18810381

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 18810381

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: JP