US2700581A - Precision fit for bearings and the like - Google Patents

Precision fit for bearings and the like Download PDF

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Publication number
US2700581A
US2700581A US413865A US41386554A US2700581A US 2700581 A US2700581 A US 2700581A US 413865 A US413865 A US 413865A US 41386554 A US41386554 A US 41386554A US 2700581 A US2700581 A US 2700581A
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US
United States
Prior art keywords
ring
housing
expansion
fit
steel
Prior art date
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Expired - Lifetime
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US413865A
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English (en)
Inventor
Louis P Migny
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.)
ALUMINIUM FRANCAIS I
I'ALUMINIUM FRANCAIS
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ALUMINIUM FRANCAIS I
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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
    • C—CHEMISTRY; METALLURGY
    • C25—ELECTROLYTIC OR ELECTROPHORETIC PROCESSES; APPARATUS THEREFOR
    • C25C—PROCESSES FOR THE ELECTROLYTIC PRODUCTION, RECOVERY OR REFINING OF METALS; APPARATUS THEREFOR
    • C25C3/00—Electrolytic production, recovery or refining of metals by electrolysis of melts
    • C25C3/06—Electrolytic production, recovery or refining of metals by electrolysis of melts of aluminium
    • C25C3/16—Electric current supply devices, e.g. bus bars
    • 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
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/12—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load
    • F16C17/22—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load with arrangements compensating for thermal expansion
    • 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
    • F16C33/583—Details of specific parts of races
    • F16C33/586—Details of specific parts of races outside the space between the races, e.g. end faces or bore of inner ring
    • 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
    • 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
    • F16C35/067—Fixing them in a housing
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
    • F16D1/06—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end
    • F16D1/08—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key
    • F16D1/0829—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key with radial loading of both hub and shaft by an intermediate ring or sleeve
    • F16D1/0835—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key with radial loading of both hub and shaft by an intermediate ring or sleeve due to the elasticity of the ring or sleeve
    • 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
    • F16C2202/00—Solid materials defined by their properties
    • F16C2202/20—Thermal properties
    • F16C2202/22—Coefficient of expansion
    • 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
    • F16C2208/00—Plastics; Synthetic resins, e.g. rubbers
    • F16C2208/20—Thermoplastic resins
    • F16C2208/60—Polyamides [PA]
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S384/00—Bearings
    • Y10S384/90—Cooling or heating
    • Y10S384/905—Temperature compensation

Definitions

  • the present invention relates to precision fits of parts formed of materials which do not have the same coetticient of expansion.
  • the present invention has for its object to overcome this drawback. Essentially, it consists in lining the bore of the part, or housing, in which the cylindrical steel part is mounted, with a solid material which simultaneously possesses, relatively to the material of the housing, a considerably larger coefiicient of expansion, and a considerably smaller modulus of elasticity; the applied solid material constitutes a cylindrical ring which is interposed between said bore and said steel part.
  • the interposed ring is connected to the housing either by cementing thereto or, simply, by its own elasticity. It is thereupon possible, if the ratio of the internal and external diameters of the ring possesses a well defined value relatively to the same ratio of the diameters of the part of the housing where the fitting takes place, to obtain the result that the apparent coetficient of expansion of the interior diameter of the ring be the same as that of the steel part, which eliminates all variation in the lit by reason of temperature (variations). If the fit be tight, then, the pressure exerted on the steel part remains substantially constant when the temperature varies; if the fit permits sliding, it remains a sliding fit at all temperatures, without appreciable variation in play.
  • the material of which the intermediate ring is constituted have a coeflicient of expansion ranging between SOXlO- and 10 a modulus of elasticity less than 700 kg./mm.'-, and an elastic limit on compression greater than 2 kg./mm.
  • the ratio between the external and internal diameters of the intermediate ring preferably varies between 1.02 and 1.30, according to circumstances.
  • the intermediate ring can be suitably formed of ebonite or hard rubber, and of a large number of plastics, polyarnides or nylons being specially adapted for this purpose.
  • the selection of a particular material is governed by the other conditions to be satisfied, for example, be havior in the presence of lubricating oils, hydrocarbons, or aqueous products, temperature ranges, etc.
  • a particularly interesting application of the present invention pertains to the mounting of ball bearings in housings of motors or of machines, and there will be given below an example of such an application.
  • the method can be used in every case where it is desired to compensate a harmful ex pansion in order to obtain a more accurate fit, as for example, in the case of plungers of hydraulic pumps or related apparatus, pistons of fuel injection pumps for heat engines, etc.
  • the apparent coefiicient of expansion of the internal bore of the ring can be reduced to zero or, at least, very close to zero, thereby enabling application of the present invention to metrology (precise measurements).
  • the intermediate ring can be cast or injected in place in the housing, or else produced separately with suitable (end) side dimensions. In the latter case, it can be provided with a side dimension slightly larger than the recess in which it is to fit and be press-fitted therein. It can also be cemented in place, or else forced in by hammering or by any other method resulting in auto-frettage (selfhooping).
  • nonbinding rings in either simple or composite form, the latter comprising a thin internal steel ring and, when required, a thin external ring formed of the same material as that of the housing in which the non-binding ring is to be mounted.
  • Figures 1 and 2 represent exploded views-in cross section-of two different embodiments of the invention as applied to the mounting of ball bearings in housings of light alloys.
  • FIG. 3 represents a still different embodiment
  • Figure 4 represents a section along a radial plane through the circumference of a special construction of an anti-binding (non-seizing) ring of the present invention
  • Figure represents a section, likewise along a radial plane, of the same ring fitted in a recess in a housing.
  • Figure 6 is a section along a radial plane of a ball bearing, whose outer ring is constructed as a non-seiz ing ring in accordance with the special form of the present invention illustrated in Figs. 4 and 5.
  • Figure 7 is a graph illustrative of the present inventron.
  • the ball-bearing assembly designated as a whole by numeral 1 is here provided with a ring' or lining 2 of plastic material which is positioned and retained in a circumferential recess on the exterior of the outer race 10.
  • the housing. 4 which has a; greater coefiicient of expansion than the material of the ball bearing; assembly, is positioned externally of the latter.
  • the plastic. liner or ring 2 is attached-in any suitable mannerto the internal surface of the bore 5 in the housing 4.
  • the steel shaft. 6. fits within a bore in the light alloy housing 4 through the intermediary of the plastic ring 2.
  • the metal of the housing has a greater coefiicient of, expansion than the steel shaft 6, and is external to the latter.
  • the plastic ring when suitably dimensioned, in accordance with applicants teachings herein, functions to maintain the desired fit between shaft and hous in'g despite wide temperature variations that may occur during operation of the assembly.
  • the anti-binding ring or lining in accordance with the present invention has a composite structure.
  • it consists of an inner ring of steel provided with lateral shoulders, between which is fitted another ring constituted of a plastic material having a polyamide base.
  • another ring constituted of a plastic material having a polyamide base.
  • Polyamide base plastics progressively lose their elastic resistance properties with rise in temperature and are subject to a solid flow phenomenon, with possible resultant variation of their (relative) thickness; such flow only becomes appreciable at temperatures above 100 C., a temperature which is generally not attained in normal operation in the case of the majority of mechanisms, but may be accidently exceeded in certain cases.
  • the total thickness of the composite ring must evidently be provided for in the housing, in addition to the radius of the part to be fitted, and this leads to an excessive bore size, which may be harmful.
  • This recess is bound at either side by shoulders 13, and its bottom is formed of' fine circumferential grooves 14' which, in the righthand portion" thereof (looking at Figure 4'), possess each on their left, a plane annular support surface 15; on the otherhand, the lefthand portion of the same recess 12 present on theirright analogous supporting surfaces 16.
  • the lining material'2 is defined at its exterior by In this connection, refa cylindrical surface of diameter D; slightly larger than the external diameter D2 of the lateral shoulder on the steel ring.
  • the total thickness 2 to be given to the said material is a function of the coefiicient of expansion a of the liner material, of an of the steel, and of d1 of the housing material.
  • the number and the dimensions of the grooves 14 are determined by the condition that, the total area of the supporting surfaces 15 (or of the supporting surfaces 16, which is equal thereto) be distinctly larger than the annular cross section of the liner material at its central portion, which is designated on Figure 4 by the thickness e1.
  • This double expansion which varies with the temperature, produces a proportional deformation in a radial direction which is added to the linear expansion of the material in this direction.
  • each of the bearings was 85 mm., and there were 7 circular grooves on each side on the bottom of the recess in the case of the construction according to the present invention, each groove being 0.2 mm. deep.
  • the Rilsan" liner material referred to above is formed of polyamide derivative of ricinoleic acid. Nylon may also be employed.
  • An assembly of machine parts comprising in combination: a cylindrical element; a housing constituted of a material having a higher thermal coefficient of expansion than the material of said element; a bore in said housing, said cylindrical element being disposed in said bore; a liner comprising a plastic material having a considerably higher thermal coefiicient of expansion and a much lower modulus of elasticity than the material of the housing, said liner being interposed between the housing and said element whereby, when the parts in assembled relationship form a precision-fit assembly, the initial precision fit will be maintained substantially between said parts over a wide range of operating temperatures.
  • the liner comprises a plastic material having a thermal coefiicient of expansion ranging between 5O l0 and 150 l0 a modulus of elasticity not in excess of 700 kgs./mm. and an elastic limit on compression greater than 2 kg./mm.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Electrochemistry (AREA)
  • Materials Engineering (AREA)
  • Metallurgy (AREA)
  • Organic Chemistry (AREA)
  • Rolling Contact Bearings (AREA)
  • Sliding-Contact Bearings (AREA)
  • Mounting Of Bearings Or Others (AREA)
  • Support Of The Bearing (AREA)
US413865A 1953-03-13 1954-03-03 Precision fit for bearings and the like Expired - Lifetime US2700581A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR2700581X 1953-03-13
FR318272X 1954-02-09

Publications (1)

Publication Number Publication Date
US2700581A true US2700581A (en) 1955-01-25

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US (1) US2700581A (fr)
CH (1) CH318272A (fr)
DE (1) DE1116481B (fr)

Cited By (29)

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US3322001A (en) * 1964-02-14 1967-05-30 Joseph J Mele Potted bushing
US3365256A (en) * 1964-07-02 1968-01-23 Mpb Interfrence connection
US3451736A (en) * 1967-03-24 1969-06-24 Gen Motors Corp Antirotation means
FR2065887A5 (fr) * 1969-10-10 1971-08-06 Bando Kiko Co
JPS5131960Y1 (fr) * 1970-03-18 1976-08-10
FR2417673A1 (fr) * 1978-02-15 1979-09-14 Toyota Motor Co Ltd Palier, notamment pour monter un roulement en metal dur dans un corps en metal mou
DE3216958A1 (de) * 1982-05-06 1983-11-17 FAG Kugelfischer Georg Schäfer KGaA, 8720 Schweinfurt Befestigung von waelzlagern
US4443044A (en) * 1980-04-11 1984-04-17 Tribotech Bearing mount and method of mounting a bearing therein
US4452654A (en) * 1982-05-28 1984-06-05 General Dynamics, Pomona Division Method of assembling a gyroscope gimbal fixture
US4460284A (en) * 1981-12-31 1984-07-17 Cummins Engine Company, Inc. Turbocharger assembly including a flexible anti-friction bearing support
US4473309A (en) * 1981-11-28 1984-09-25 Rolls-Royce Limited Bearing assembly with thermal compensation
FR2547879A1 (fr) * 1983-06-27 1984-12-28 Brissonneau & Lotz Dispositif de montage dans un carter d'un element anime d'un mouvement rectiligne alternatif ou de rotation autour d'un axe
US4772139A (en) * 1987-09-23 1988-09-20 Bretton Kenneth M Liner for bearing assemblies and the like
US5028152A (en) * 1990-03-21 1991-07-02 The Timken Company Machine with thermally compensated bearings
US5073039A (en) * 1988-11-15 1991-12-17 Sundstrand Corporation Bearing assembly with thermal compensation
US5501638A (en) * 1994-03-29 1996-03-26 Dana Corporation Bearing cup retainer strap for universal joint
US5598747A (en) * 1995-05-04 1997-02-04 Dana Corporation Thermal compensating bearing support structure for transmission case
US6467959B1 (en) * 2001-04-17 2002-10-22 Delphi Technologies, Inc. EGR valve with self-temperature compensated bearing
US6599022B2 (en) * 2000-06-19 2003-07-29 Minebea Kabushiki-Kaisha Bearing apparatus
FR2835580A1 (fr) * 2002-02-05 2003-08-08 Skf Ab Palier a roulement, notamment pour moteur electrique
US6939052B1 (en) 2003-01-27 2005-09-06 Precision Components, Inc. Bearing with integrated mounting features
US20060018582A1 (en) * 2004-07-26 2006-01-26 Mircea Gradu Bearing having thermal compensating capability
US20090080824A1 (en) * 2004-07-26 2009-03-26 The Timken Company Bearing having thermal compensating capability
US20120028773A1 (en) * 2010-07-28 2012-02-02 Felix Bottcher Gmbh & Co. Kg Method For Repairing A Roller, And Roller
EP1437518B1 (fr) * 2003-01-10 2014-07-02 Geräte- und Pumpenbau GmbH, Dr. Eugen Schmidt Arrangement de paliers
US20150252841A1 (en) * 2014-03-05 2015-09-10 Schaeffler Technologies AG & Co. KG Bearing assembly with integrated spring
US20150308504A1 (en) * 2014-04-28 2015-10-29 Aktiebolaget Skf Bearing ring including a temperature compensation ring, bearing including the bearing ring, and method for manufacturing a bearing ring
US9217473B2 (en) 2013-03-15 2015-12-22 King Cycle Group, Inc. Cylinder assembly using a shim
US10087986B2 (en) * 2016-10-18 2018-10-02 Aktiebolaget Skf Temperature compensation ring as well as bearing ring with the temperature compensation ring

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DE19801014B4 (de) * 1998-01-14 2008-09-18 Schaeffler Kg Anordnung zur Verbindung von zwei mit Präzisionspassung ineinandergesteckten Bauteilen
DE19811495B4 (de) * 1998-03-17 2010-04-01 Skf Linearsysteme Gmbh Lagerbefestigung
DE102005043945A1 (de) * 2005-09-15 2007-03-22 Schaeffler Kg Radialwälzlager, insbesondere einreihiges Schrägkugellager für das Festlager einer Werkzeugmaschinen-Hauptspindel
DE102005043954A1 (de) * 2005-09-15 2007-03-22 Schaeffler Kg Radialwälzlager, insbesondere einreihiges Zylinderrollenlager für das Loslager einer Werkzeugmaschinen-Hauptspindel
AT503000B1 (de) * 2005-12-21 2008-02-15 Austrian Aerospace Gmbh Wälzlager mit temperaturgesteuerter vorspannungsverstellung für raumfahrtanwendungen
DE102006053715A1 (de) * 2006-11-15 2008-05-21 Schaeffler Kg Wälzlager mit Zwischenschicht
DE102008044246A1 (de) * 2008-12-02 2010-06-10 Robert Bosch Gmbh Lageranordnung
DE102011006291A1 (de) * 2011-03-29 2012-10-04 Schaeffler Technologies Gmbh & Co. Kg Pressverband für eine Lageranordnung
DE102012202900A1 (de) * 2012-02-27 2013-08-29 Aktiebolaget Skf Lageranordnung
US20160053812A1 (en) * 2013-03-28 2016-02-25 Aktiebolaget Skf Bearing assembly and method for assembling and mounting said bearing assembly with a component supporting said bearing assembly
CN105074242A (zh) * 2013-03-28 2015-11-18 斯凯孚公司 轴承组件及组装和安装轴承组件与支撑轴承组件的部件的方法
DE102013215170A1 (de) * 2013-08-01 2015-02-05 Aktiebolaget Skf Röhrenförmiger Körper zur Montage auf einer Welle oder in einer Bohrung und Verfahren zur Montage
DE102016210276B4 (de) * 2016-06-10 2020-08-13 Schaeffler Technologies AG & Co. KG Lagerkonzept für ein Getriebe mit einem Dämpfungsring
DE102018219358A1 (de) * 2018-11-13 2020-05-14 Robert Bosch Gmbh Pressverband mit kraftschlüssiger Verbindung zwischen einer Welle und einer Nabe
DE102021101125A1 (de) 2021-01-20 2022-07-21 Koenig & Bauer Ag Verfahren zur Herstellung einer Lagereinrichtung für ein rotierendes Bauteil einer bahn- oder bogenver- oder bearbeitenden Maschine, Lagereinrichtung zur Lagerung eines rotierenden Bauteils sowie Aggregat mit einer Lagereinrichtung
DE102023134702A1 (de) * 2023-12-11 2025-06-12 Valeo Eautomotive Germany Gmbh Gehäuseteil für ein Getriebe mit verbesserter Lagerung von Getriebewellen

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Cited By (32)

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US3322001A (en) * 1964-02-14 1967-05-30 Joseph J Mele Potted bushing
US3365256A (en) * 1964-07-02 1968-01-23 Mpb Interfrence connection
US3451736A (en) * 1967-03-24 1969-06-24 Gen Motors Corp Antirotation means
FR2065887A5 (fr) * 1969-10-10 1971-08-06 Bando Kiko Co
JPS5131960Y1 (fr) * 1970-03-18 1976-08-10
FR2417673A1 (fr) * 1978-02-15 1979-09-14 Toyota Motor Co Ltd Palier, notamment pour monter un roulement en metal dur dans un corps en metal mou
US4443044A (en) * 1980-04-11 1984-04-17 Tribotech Bearing mount and method of mounting a bearing therein
US4473309A (en) * 1981-11-28 1984-09-25 Rolls-Royce Limited Bearing assembly with thermal compensation
US4460284A (en) * 1981-12-31 1984-07-17 Cummins Engine Company, Inc. Turbocharger assembly including a flexible anti-friction bearing support
DE3216958C2 (fr) * 1982-05-06 1991-06-06 Fag Kugelfischer Georg Schaefer Kgaa, 8720 Schweinfurt, De
DE3216958A1 (de) * 1982-05-06 1983-11-17 FAG Kugelfischer Georg Schäfer KGaA, 8720 Schweinfurt Befestigung von waelzlagern
DE3216958C3 (de) * 1982-05-06 1995-04-20 Kugelfischer G Schaefer & Co Befestigung einer Tretlagerwelle
US4452654A (en) * 1982-05-28 1984-06-05 General Dynamics, Pomona Division Method of assembling a gyroscope gimbal fixture
FR2547879A1 (fr) * 1983-06-27 1984-12-28 Brissonneau & Lotz Dispositif de montage dans un carter d'un element anime d'un mouvement rectiligne alternatif ou de rotation autour d'un axe
US4772139A (en) * 1987-09-23 1988-09-20 Bretton Kenneth M Liner for bearing assemblies and the like
US5073039A (en) * 1988-11-15 1991-12-17 Sundstrand Corporation Bearing assembly with thermal compensation
US5028152A (en) * 1990-03-21 1991-07-02 The Timken Company Machine with thermally compensated bearings
US5501638A (en) * 1994-03-29 1996-03-26 Dana Corporation Bearing cup retainer strap for universal joint
US5598747A (en) * 1995-05-04 1997-02-04 Dana Corporation Thermal compensating bearing support structure for transmission case
US6599022B2 (en) * 2000-06-19 2003-07-29 Minebea Kabushiki-Kaisha Bearing apparatus
US6467959B1 (en) * 2001-04-17 2002-10-22 Delphi Technologies, Inc. EGR valve with self-temperature compensated bearing
FR2835580A1 (fr) * 2002-02-05 2003-08-08 Skf Ab Palier a roulement, notamment pour moteur electrique
EP1437518B1 (fr) * 2003-01-10 2014-07-02 Geräte- und Pumpenbau GmbH, Dr. Eugen Schmidt Arrangement de paliers
US6939052B1 (en) 2003-01-27 2005-09-06 Precision Components, Inc. Bearing with integrated mounting features
US20060018582A1 (en) * 2004-07-26 2006-01-26 Mircea Gradu Bearing having thermal compensating capability
US20090080824A1 (en) * 2004-07-26 2009-03-26 The Timken Company Bearing having thermal compensating capability
US20120028773A1 (en) * 2010-07-28 2012-02-02 Felix Bottcher Gmbh & Co. Kg Method For Repairing A Roller, And Roller
US9217473B2 (en) 2013-03-15 2015-12-22 King Cycle Group, Inc. Cylinder assembly using a shim
US20150252841A1 (en) * 2014-03-05 2015-09-10 Schaeffler Technologies AG & Co. KG Bearing assembly with integrated spring
US20150308504A1 (en) * 2014-04-28 2015-10-29 Aktiebolaget Skf Bearing ring including a temperature compensation ring, bearing including the bearing ring, and method for manufacturing a bearing ring
US9689428B2 (en) * 2014-04-28 2017-06-27 Aktiebolaget Skf Bearing ring including a temperature compensation ring, bearing including the bearing ring, and method for manufacturing a bearing ring
US10087986B2 (en) * 2016-10-18 2018-10-02 Aktiebolaget Skf Temperature compensation ring as well as bearing ring with the temperature compensation ring

Also Published As

Publication number Publication date
CH318272A (fr) 1956-12-31
DE1116481B (de) 1961-11-02

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