EP0943058A1 - Systeme de palier a element roulant, dote d'un amortissement ameliore - Google Patents

Systeme de palier a element roulant, dote d'un amortissement ameliore

Info

Publication number
EP0943058A1
EP0943058A1 EP97950485A EP97950485A EP0943058A1 EP 0943058 A1 EP0943058 A1 EP 0943058A1 EP 97950485 A EP97950485 A EP 97950485A EP 97950485 A EP97950485 A EP 97950485A EP 0943058 A1 EP0943058 A1 EP 0943058A1
Authority
EP
European Patent Office
Prior art keywords
bearing
damping layer
ring
bearing system
damping
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.)
Withdrawn
Application number
EP97950485A
Other languages
German (de)
English (en)
Inventor
Gerrit Cornelis Van Nijen
Alexander Jan Carel De Vries
Eustathios Ioannides
Jeroen Anton Wensing
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
SKF Engineering and Research Centre BV
Original Assignee
SKF Engineering and Research Centre BV
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
Priority claimed from NL1004760A external-priority patent/NL1004760C2/nl
Priority claimed from NL1004763A external-priority patent/NL1004763C2/nl
Application filed by SKF Engineering and Research Centre BV filed Critical SKF Engineering and Research Centre BV
Publication of EP0943058A1 publication Critical patent/EP0943058A1/fr
Withdrawn legal-status Critical Current

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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • 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
    • F16C27/00—Elastic or yielding bearings or bearing supports, for exclusively rotary movement
    • F16C27/04—Ball or roller bearings, e.g. with resilient rolling bodies
    • F16C27/045—Ball or roller bearings, e.g. with resilient rolling bodies with a fluid film, e.g. squeeze film damping
    • 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
    • F16C27/00—Elastic or yielding bearings or bearing supports, for exclusively rotary movement
    • F16C27/06—Elastic or yielding bearings or bearing supports, for exclusively rotary movement by means of parts of rubber or like materials
    • F16C27/066—Ball or roller bearings
    • 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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/60—Raceways; Race rings divided or split, e.g. comprising two juxtaposed rings
    • 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
    • F16C19/04—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly
    • F16C19/06—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly with a single row or 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
    • F16C2300/00—Application independent of particular apparatuses
    • F16C2300/02—General use or purpose, i.e. no use, purpose, special adaptation or modification indicated or a wide variety of uses mentioned
    • 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
    • F16C35/042—Housings for rolling element bearings for rotary movement
    • F16C35/047—Housings for rolling element bearings for rotary movement with a base plate substantially parallel to the axis of rotation, e.g. horizontally mounted pillow blocks

Definitions

  • the invention is related to a bearing system, comprising a rolling element bearing having an inner ring and an outer ring which enclose a bearing space containing at least one series of rolling elements, a shaft connected to the inner ring, and a bearing support connected to the outer ring.
  • Rolling element bearing systems are applied in rotating machinery, such as motors, vehicles, domestic appliances etc.
  • the bearings should have a low noise level, such as for applications in electric motors which are used for driving domestic appliances.
  • the object of the invention is therefore to provide a bearing which has the required stiffness characteristics, but which also offers improved damping characteristics.
  • This object is achieved in that at least one of the rings of the bearing engages a damping layer which at least partly consists of a visco-elastic material or a damping fluid, which damping layer is at a distance from the raceway of said ring.
  • the damping layer provides an increased damping due to its visco- elastic properties. Moreover, said layer can be rather thin, whereby virtually no displacements in radial direction are possible and thus the radial stiffness of the bearing is not, or only in a limited way influenced by the visco-elastic material. Despite the small deformation of the visco-elastic layer, a sufficient damping is obtained due to the shear stresses which are generated in said layer as a result of the relatively high pressures in the contact between the rolling element set and the ring.
  • the radial deformation of the damping layer is preferably of the same order of magnitude as the indentation or contact deformation of the raceway which occurs between rolling elements and said ring under nominal load without the presence of such layer Under these conditions, the radial stiffness of the bearing is about of the same order of magnitude to the radial stiffness of a standard bearing
  • the layer of visco-elastic material may be applied in a number of positions According to a first possibility, at least one of the rings comprises two concentric ring parts which are mutually connected by the damping layer The visco-elastic layer thus may form an integral part of one of the bearing rings
  • damping layer is situated near the region of maximum shear stress which occurs in said ring as a result of the contact of the rolling elements over the raceway
  • the layer can be at sufficient distance from the outer surface of the outer ring or the bore of the inner ring, where reduced shear stresses are encountered so that the bearing and in particular the layer have sufficient fatigue life
  • the damping layer may be situated on the outer circumference of the outer ring, and/or on the inner circumference of the inner ring
  • the damping obtained can also be influenced by selecting a proper material or layout
  • the damping layer may be composed of at least two layers with different material characteristics and/or thickness
  • the annular damping layer need not be of a continuous character in axial direction
  • the damping layer may comprise segments of visco-elastic material separated by axial air gaps
  • the bearing may comprise at least two concentric damping layers
  • bearing systems which for instance may comprise a deep groove ball bearing
  • the rolling elements such as balls exert a force on the raceways of the rings
  • these rings are locally deformed as a result of the contact forces
  • the deformation is maximal in the middle region close to the contact area, and thus in the middle region of the rings
  • the adjacent edge regions of the rings are deformed in a far less degree
  • the rings and thereby the raceways may have form deviations such as out-of-roundness or waviness in circumferential direction
  • Such waviness induces vibrations in the bearing system, which give rise to noise.
  • these phenomena are aggravated.
  • a bearing system can be obtained which performs better with respect to such vibrations. This is achieved in that at least one of the cooperating surfaces of the outer ring and the bearing support, and/or at least one of the cooperating surfaces of the inner ring and the shaft have a circumferential groove directly opposite the raceway of said ring.
  • the ring in question of the bearing system according to the invention is able to locally deform in the contact area between raceway and rolling element, due to the fact that the ring is exposed to supporting forces only in the adjacent edge areas thereof.
  • the damping effect can be obtained by filling at least one groove with a damping fluid or a solid visco-elastic material.
  • the outer ring may have a groove in its outer circumference; in the alternative, the bearing support may have a groove in its contact surface.
  • the inner ring may have a groove in its outer circumference, or the shaft may have a groove in its contact surface.
  • the groove according to US-A-5310268 plays a role in fixing the outer ring of the bearing in a housing.
  • the groove has protruding, sharp edges which cut into the housing wall.
  • Such layout is not suitable for attenuating vibrations, but would rather lead to fretting when subjected to vibrations.
  • the edges between the groove and the surface in which the groove opens out are rounded off in a cross-section through the axis of the bearing.
  • the smooth transition between groove and opposite wall of e.g. a housing provides a reduction of vibrations, without causing damage to the adjoining components in question.
  • the ratio of the minimum distance between the raceway of a bearing ring, and the damping layer, to the thickness of the damping layer is between 5-15.
  • the mimimum distance between the raceway of a bearing ring, and the damping layer, to the thickness of the damping layer may be between 7-10.
  • the ratio of the minimum distance between the raceway of a bearing ring, and the damping layer, to the thickness of the damping layer is 8.
  • the invention is also related to a rolling element bearing having an inner ring and an outer ring which enclose a bearing space containing at least one series of rolling elements; according to the invention, at least one of the rings comprises a damping layer which at least partly consists of a visco-elastic material, which damping layer is at a distance from the raceway of said ring.
  • the outer ring and/or the inner ring may have a circumferential groove directly opposite the raceway of said ring, which ring is at least partly filled with a visco-elastic material.
  • Figure 1 shows a first embodiment of a bearing system according to the invention.
  • Figure 2 shows a second embodiment
  • Figure 3 shows a cross-section through a third embodiment.
  • Figure 4 shows a cross-section through a fourth embodiment.
  • Figure 5 shows a fifth embodiment of the bearing system according to the invention.
  • Figure 6 shows a sixth embodiment.
  • Figure 7 shows a detail of figure 5.
  • a bearing 1 is shown which is supported in a support 2.
  • the bearing 1 comprises an outer ring 3 and an inner ring 4, which is connected to a shaft 5.
  • the outer ring 3 and the inner ring 4 are rotatable with respect to each other by means of balls 6.
  • a thin visco-elastic layer 7 is present around the outside of the outer ring 3, which visco-elastic layer 7 itself is supported in a correspondingly shaped hole in bearing support 2.
  • the deformation of the visco-elastic layer 7 is about the same order of magnitude as the contact deformation of the raceways of outer ring 3 and inner ring 4, as generated at the contact spots between rolling elements 6 and outer ring 3 or inner ring 4. Thanks to the small thickness of the visco-elastic layer 7, the shaft 5 is supported in a relatively stiff way in the radial direction, as is the case with normal bearings. On the other hand, despite the small deformation of the visco-elastic layer 7, it is able to dampen out vibrations in the shaft 5.
  • a ball bearing comprising an outer ring 8, an inner ring 9 connected to a shaft 10, and balls 11.
  • the outer ring is split into two concentric outer rings halves 12, 13, which are interconnected by a thin visco-elastic layer 14.
  • the deformation of this intermediate visco-elastic layer 14 is of the same order of magnitude as the contact deformation.
  • the distance of the visco-elastic layer 14 with respect to the raceway of the outer ring is selected such that the visco-elastic layer 14 finds itself where the shear stresses in the outer ring 8 are at a maximum. Some distance to the area of maximum shear stress is however required, such that the fatigue life of said layer is not reduced.
  • the embodiment of figure 3 shows a cross-section through the axis of a bearing.
  • the bearing comprises an outer ring 15, and an inner ring 16 as well as balls 17.
  • Outer ring 15 comprises two outer ring halves 18, 19, enclosing a thin visco-elastic layer 20.
  • the thin visco-elastic layer 20 is chevron-shaped, such that in the legs 21 of each chevron additional shear forces are generated under load.
  • FIG 4 shows a bearing having an intermediate visco-elastic layer 24 which is sandwiched between metal foil layers 23.
  • the sandwich of these layers 23, 24 forms a unity, and has been applied in the inner ring of a bearing.
  • the outer ring of this bearing has been indicated by 26; the balls are indicated by 25.
  • Figure 5 shows a bearing system comprising a deep groove ball bearing 31, the outer ring 32 two of which is supported in a housing 33.
  • the inner ring 34 in turn rotatably supports a shaft 35. Between the rings 32, 34, balls 36 have been accommodated.
  • the outer ring 32 has a circumferential groove 37, which at that area does not contact the housing 33, and which is filled with a visco-elastic material 45.
  • the outer ring 32 is able to flex a little bit under the forces exerted thereon by the balls 36, in such a way that vibrations, such as caused by the waviness of the outer and inner ring, are reduced by the visco-elastic material 45.
  • the deep groove ball bearing 38 is of standard design, and has rings 39, 40 between which balls 41 are accommodated.
  • the housing 42 has a groove 43, at the spot directly opposite the raceway 44 of inner ring 50, which groove 43 is filled with a visco-elastic material 46.
  • the shaft 35 may have a circumferential groove, directly opposite the corresponding raceway of the inner ring 39.
  • figure 7 shows the edge area 44 of the groove 37.
  • This edge area 44 is rounded off somewhat, so as to provide a smooth transition zone. Such smooth transition is favourable with respect to vibration reduction, and prevents fretting under dynamic loads.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Support Of The Bearing (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

Ce système de palier comprend un palier à roulement à billes, lequel présente un anneau intérieur et un anneau extérieur entourant un espace de palier contenant au moins une série de roulements à billes, ainsi qu'un axe, relié à l'anneau intérieur, un support de palier étant relié à l'anneau extérieur. L'un au moins des anneaux est en contact avec une couche d'amortissement, laquelle se compose au moins partiellement d'une matière viscoélastique ou d'un fluide d'amortissement, cette couche étant située à une certaine distance du chemin de roulement dudit anneau.
EP97950485A 1996-12-12 1997-12-12 Systeme de palier a element roulant, dote d'un amortissement ameliore Withdrawn EP0943058A1 (fr)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
NL1004760A NL1004760C2 (nl) 1996-12-12 1996-12-12 Lagersysteem met verlaagde trillingsopwekking.
NL1004763A NL1004763C2 (nl) 1996-12-12 1996-12-12 Wentellager met verbeterde demping.
NL1004763 1996-12-12
NL1004760 1996-12-12
PCT/NL1997/000690 WO1998026190A1 (fr) 1996-12-12 1997-12-12 Systeme de palier a element roulant, dote d'un amortissement ameliore

Publications (1)

Publication Number Publication Date
EP0943058A1 true EP0943058A1 (fr) 1999-09-22

Family

ID=26642494

Family Applications (1)

Application Number Title Priority Date Filing Date
EP97950485A Withdrawn EP0943058A1 (fr) 1996-12-12 1997-12-12 Systeme de palier a element roulant, dote d'un amortissement ameliore

Country Status (4)

Country Link
EP (1) EP0943058A1 (fr)
JP (1) JP2001507107A (fr)
AU (1) AU5346998A (fr)
WO (1) WO1998026190A1 (fr)

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DE19854094C2 (de) * 1998-11-24 2002-11-07 Audi Ag Lagerung für einen Fahrzeugsitz und Rolle hierfür
CN100478147C (zh) 2004-06-21 2009-04-15 皇家飞利浦电子股份有限公司 剃须设备
DE102005003986A1 (de) * 2005-01-28 2006-08-03 Schaeffler Kg Lager
DE102005007986A1 (de) * 2005-02-22 2006-08-31 Schaeffler Kg Gewindering zur Schallisolierung von Lagerstellen
WO2007002903A1 (fr) * 2005-06-29 2007-01-04 The Timken Company Dispositif d'amortissement des vibrations pour paliers, et procede d'amortissement des vibrations
JP2011515639A (ja) * 2008-10-27 2011-05-19 コーヨー ベアリングス ユーエスエイ、エルエルシー クランクシャフト用騒音遮断転動体軸受
CN101922503A (zh) * 2010-08-11 2010-12-22 洛阳轴研科技股份有限公司 一种夹心式整体阻尼外圈构成的高速球轴承设计方法
JP2014513783A (ja) * 2011-05-16 2014-06-05 アクティエボラゲット・エスコーエッフ 絶縁材料を有する回転ベアリング
WO2014000798A1 (fr) * 2012-06-28 2014-01-03 Aktiebolaget Skf Agencement de machine
KR101697769B1 (ko) * 2012-12-28 2017-01-19 주식회사 에스앤씨 직각좌표 로봇
DE102014118553A1 (de) * 2014-12-12 2016-06-16 Universität Stuttgart Wälzlager
US9470263B2 (en) 2015-02-19 2016-10-18 United Technologies Corporation Squeeze film damper
JP6599947B2 (ja) 2017-09-14 2019-10-30 ファナック株式会社 軸受および偏心補正方法
DE102018206242A1 (de) * 2018-04-24 2019-10-24 Aktiebolaget Skf Wälzlager, das elektrisches Isolierungsmaterial hat, und Herstellungsverfahren eines solchen Wälzlagers
CN111637157B (zh) * 2020-05-15 2021-11-05 大连理工大学 一种基于粘弹性阻尼元件的复合结构抗振轴承

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CH244128A (fr) * 1944-11-15 1946-08-31 Sa Benjamin Pellaton Roulement à billes.
US2674505A (en) * 1951-07-07 1954-04-06 Connecticut Hard Rubber Co Rubber mounted bearing
BE522004A (fr) * 1952-09-11
DE1037211B (de) * 1957-01-26 1958-08-21 Duerkoppwerke Ag Kegelrollenlager
GB860973A (en) * 1959-05-14 1961-02-15 Francesco Vasta Di Pietro E Di Improvements in ball or roller bearings
US3513480A (en) * 1967-04-26 1970-05-19 North American Rockwell Low stress bearing
CS177052B2 (fr) * 1969-10-10 1977-07-29
NL7114660A (fr) * 1971-10-25 1973-04-27
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JPH0198712A (ja) * 1987-10-07 1989-04-17 Koyo Seiko Co Ltd 円筒ころ軸受
JPH0450529A (ja) * 1990-06-18 1992-02-19 Mitsubishi Heavy Ind Ltd オーバーハングロータの制振装置
US5071262A (en) * 1990-11-05 1991-12-10 General Electric Company Squeeze film damper fluid control
DE4134604C2 (de) * 1991-10-19 2000-01-13 Schaeffler Waelzlager Ohg Wälzlager mit Geräuschdämpfung
US5247855A (en) * 1992-03-10 1993-09-28 Allied Signal Inc. Roller bearing assembly with compliant anti-rotation ring

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Also Published As

Publication number Publication date
JP2001507107A (ja) 2001-05-29
WO1998026190A1 (fr) 1998-06-18
AU5346998A (en) 1998-07-03

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