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WO2010022708A1 - Profilage de surfaces de guidage sur des paliers à roulement comprenant une cage guidée sur un bord - Google Patents

Profilage de surfaces de guidage sur des paliers à roulement comprenant une cage guidée sur un bord Download PDF

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Publication number
WO2010022708A1
WO2010022708A1 PCT/DE2009/001188 DE2009001188W WO2010022708A1 WO 2010022708 A1 WO2010022708 A1 WO 2010022708A1 DE 2009001188 W DE2009001188 W DE 2009001188W WO 2010022708 A1 WO2010022708 A1 WO 2010022708A1
Authority
WO
WIPO (PCT)
Prior art keywords
guide surface
rolling bearing
cage
profiling
groove
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.)
Ceased
Application number
PCT/DE2009/001188
Other languages
German (de)
English (en)
Inventor
Khosrow Sultani
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.)
IHO Holding GmbH and Co KG
Original Assignee
Schaeffler KG
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 Schaeffler KG filed Critical Schaeffler KG
Publication of WO2010022708A1 publication Critical patent/WO2010022708A1/fr
Anticipated expiration legal-status Critical
Ceased 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
    • F16C33/38—Ball cages
    • F16C33/3806—Details of interaction of cage and race, e.g. retention, centring
    • 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
    • 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
    • F16C33/66—Special parts or details in view of lubrication
    • F16C33/6603—Special parts or details in view of lubrication with grease as lubricant
    • F16C33/6629—Details of distribution or circulation inside the bearing, e.g. grooves on the cage or passages in the rolling elements
    • 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
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
    • F16C2240/42—Groove sizes
    • 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
    • F16C2300/10—Application independent of particular apparatuses related to size
    • F16C2300/14—Large applications, e.g. bearings having an inner diameter exceeding 500 mm
    • 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
    • F16C2360/00—Engines or pumps
    • F16C2360/31—Wind motors

Definitions

  • the present invention relates to a roller bearing, comprising an outer ring, an inner ring and an on-board cage, wherein the cage has a first cylindrical and concentric to a bearing axis guide surface over which the cage by a second cylindrical and concentric with the bearing axis guide surface, which is formed on a board of one of the two rings is guided radially on this ring.
  • on-board cages are guided radially on a bearing ring of the rolling bearing.
  • both the cage and the corresponding bearing ring each have at least one guide on.
  • a corresponding guide surface is located on at least one aboard the outer ring for this purpose.
  • a corresponding guide surface is provided for this purpose at least on one side of the inner ring.
  • the guide surfaces on the cage and on the corresponding bearing ring are arranged concentrically with respect to the bearing axis. Between the guide surfaces of the cage and bearing ring, an annular gap is formed. This gap must be dimensioned in its radial extent such that at each operating time sufficient radial guidance of the cage is made possible, in particular, this gap may not be too large.
  • the present invention is based on the object to provide a roller bearing of the type mentioned that allows over the prior art improved lubrication and at the same time has a simple and inexpensive construction.
  • the object is achieved in that the guide surface of the first and the second guide surface, which lies radially outward, has a profiling.
  • the profiling invention forms on the one hand an additional lubricant depot. Since this additional Liehe lubricant reservoir is formed axially in the region of the two concentrically arranged guide surfaces on the cage and on the bearing ring, thereby already a significant improvement in the lubrication of the Rolling received. Thus, the additional lubricant reservoir is located exactly at the point that represented a weak point in the prior art due to the lack of lubrication.
  • the profiling according to the invention also makes it possible to improve the lubricant transport between the lubricant depot and the raceway.
  • the lubricant located in the profiling will improve the replacement of the lubricant between the lubricant depot and the raceway.
  • this aspect of the invention can still be significantly improved.
  • the profiling should be formed in each case on the radially outer guide surface. Due to the centrifugal force generated by the relative rotation of the inner ring, outer ring and cage on the lubricant, the lubricant is conveyed radially outward. By now the profiling is formed in the respective radially outer guide surface, the lubricant is pressed into this profiling.
  • the advantages achieved by the profiling thus show a higher effect than if the profiling were formed in the radially inner guide surface. Even if, according to the invention, no profiling of the radially inner guide surface is provided, it is, however, in principle conceivable nevertheless to provide profiling on this guide surface.
  • the cage has a third cylindrical guide surface arranged concentrically with respect to the bearing axis, over which the cage is connected by a fourth cylindrical guide surface which is concentrically arranged to the bearing axis and which is formed on a rim of one of the two rings Ring is guided radially, wherein that guide surface of the third and the fourth guide surface, which lies radially outward, has a profiling.
  • the second and the fourth guide surface are arranged on different shelves of the same bearing ring, that is, the second guide surface is disposed on a first board and the fourth guide surface on a second board of a common bearing ring.
  • the cage is outboard-guided and the guide surface, which lies in each case radially outward, is formed on at least one board of the outer ring.
  • the guide surface which lies in each case radially outward, is formed on at least one board of the outer ring.
  • the cage it is also conceivable to design the cage on the inboard, in which case the radial outer guide surface is part of the cage and thus the cage must be profiled accordingly.
  • the profiling comprises at least one groove. If this groove is now arranged at an angle other than 90 degrees to the bearing axis, during operation of the rolling bearing a force component along the extent of the groove acts on the lubricant in the groove, due to the contact of the lubricant with the radially inner guide surface and the Relative movement between the radially outer and radially inner guide surface. This force component creates a lubricant delivery effect along the extension of the groove.
  • this groove extends axially over the entire extent of the first and / or second or third and / or fourth guide surface, whereby an optimal wetting of this guide surface is made possible with lubricant.
  • a groove is already sufficient, in the context of the invention, however, a plurality of parallel or angled grooves with the same or different cross-sectional profile are also conceivable. Possible are also combinations of the at least one groove with other profiling types, eg circular depressions, which can serve as a lubricant reservoir.
  • the groove extends helically over the cylindrical guide surface.
  • the pitch angle of the spiral groove extending over its entire length may be constant or vary. It is conceivable that the pitch angle of the at least one groove relative to the axial extent of the guide surface is selected such that the at least one groove has substantially a single turn.
  • the at least one groove runs in the axial direction completely over the guide surface and encloses an angle of 360 degrees.
  • a plurality of grooves offset from each other with the same or different pitch angle can be arranged.
  • the pitch angle of the at least one groove is in a range of 0 degrees to 5 degrees, in particular in a range of 0 angular minutes to 5 minutes, more particularly in a range of 0 angle seconds to 5 angle seconds. If the at least one groove is to be formed on two guide surfaces of the cage or of a bearing ring, slope angles of the same sign on both guide surfaces are preferably selected. This results in a lubricant delivery effect, which promotes the lubricant axially through the rolling bearing.
  • the ratio of groove depth to radial distance between the first and second guide surface and groove depth to radial distance between the third and fourth guide surface is in the range of 1 to 2 to 1 to 1, in particular at a value of 1 to 1.
  • the latter means that the groove depth and the radial distance between the first and second guide surface and the groove depth and the radial distance between the third and fourth guide surface at room temperature is the same.
  • a diameter of the first and second or of the third and fourth guide surface of approximately 800 mm in each case, 0.5 mm can be selected as the groove depth, for example, this value applies to the rolling bearing at room temperature.
  • the groove has a niksegmentför- miges, a rectangular, a u-shaped or a v-shaped cross-sectional profile.
  • the cross-sectional profile results essentially from the tools used for introducing the groove.
  • the groove When screwed into the outer ring, in the case of an outboard-guided cage, the groove therefore has, for example, a circular segment-shaped cross-sectional profile.
  • the rolling bearing is lubricated with grease. It was found that, especially with highly viscous lubricant, the initially described lack of lubrication occurs in the contact area of cage and bearing ring. Finally, the lubricant transport is low compared to low viscosity lubricant, e.g. Lubricating oil, more affected by the narrow gap between the guide surfaces.
  • the advantages of the roller bearing according to the invention therefore come into play particularly in grease-lubricated bearings. This can be a lifetime lubrication. In this case, the rolling bearing can be sealed so that no lubricant exchange takes place to the outside.
  • the invention can be applied to different rolling bearing types, e.g. can be used with ball bearings or with cylindrical roller bearings.
  • the rolling bearing is used in a wind turbine.
  • the rolling bearing can be used as a main bearing, gearbox bearings or generator bearings. Also conceivable are applications in electric motor bearings or generally in sealed slewing bearings.
  • Fig. 3 is a sectional view of a rolling bearing according to the embodiment of FIG. 2, and
  • FIG. 4 is a detail view of an outer ring of the embodiment of FIG .. 2
  • Fig. 2 shows an axial view of an embodiment of a rolling bearing 1 according to the invention, comprising outer ring 5a, inner ring 5b, on-board cage 6 and rolling elements 7.
  • the rolling elements 7 are circumferentially guided by the cage 6, so kept at a distance.
  • the cage 6 is guided radially through the outer ring 5a, as the cage starts on both edges of the outer ring.
  • corresponding guide surfaces are formed on the cage 6 and on the outer ring 5a.
  • a gap is formed, the radial extent in Fig. 2 is marked with 'a'.
  • the dimension 'a' is selected to be correspondingly small in order to guide the cage radially, ie to ensure that it remains arranged substantially concentric with the bearing axis 1 x 1 protruding vertically from the plane of the drawing. Too large a measure of 'a' would allow a radial migration of the cage, whereby the circumferential guidance of the rolling elements would be impaired.
  • a first, radially outwardly facing guide surface 8a is formed on the one-piece cage 6.
  • the first guide surface 8a is arranged circumferentially on the rotationally symmetrical cage 6 and consists of a cylindrical surface.
  • a second, radially inwardly facing guide surface 8b is arranged on the one-piece outer ring 5a.
  • the second guide surface 8b is arranged circumferentially and consists of a cylindrical surface.
  • the first guide surface 8a and the second guide surface 8b are arranged concentrically with each other and have an approximately equal axial extent along the bearing axis X.
  • a third guide surface on the cage and a fourth guide surface on the outer ring are not shown. Both guide surfaces on the outer ring 5a are located on the two, the raceway enclosing shelves.
  • the rolling bearing 1 according to this embodiment is a ball bearing.
  • Fig. 3 shows a sectional view of a roller bearing according to the embodiment of FIG. 2 can be seen, the grooves 10 with a circular segment-shaped cross-sectional profile.
  • the grooves 10 are formed on the first board 9a and the second board 9b of the outer ring 5a, namely, on the guide surfaces thereof for the cage, that is, the second guide surface 8b and the fourth guide surface 8d.
  • the value of the distance 'a' is substantially as large as the depth of the grooves 10 at room temperature.
  • Fig. 4 shows a detailed view of an outer ring of the embodiment of FIG. 2.
  • the raceway 4a of the outer ring 5a for receiving the balls is bordered by the two rims 9a, 9b.
  • the second guide surface 8b is arranged and on the second board 9b, the fourth guide surface 8d is arranged.
  • Profiles in the form of grooves 10 are located on both guide surfaces 8b, 8d of the outer ring 5a. These have a cross-sectional profile in the form of a circular segment and are arranged at an angle 'alpha 1 perpendicular to the bearing axis X.
  • the angle 'alpha' corresponds to the pitch angle of a groove and is approximately 6 degrees in this embodiment.
  • the grooves 10 Due to the relatively small axial extent of the ribs 9a, 9b or the relatively large angle 'alpha', the grooves 10 thus do not completely run over the guide surfaces 8b, 8d.
  • the pitch angle is constant for all grooves 10 of both guide surfaces 8b, 8d, in particular, this always has the same sign.
  • a reversal of the direction of rotation causes a reversal of this conveying direction.
  • the cage 6 on its guide surfaces no profiling.

Landscapes

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

Abstract

L'invention concerne un palier à roulement comprenant une bague extérieure (5a), une bague intérieure (5b) et une cage (6) guidée sur un bord, cette cage (6) présentant une première surface de guidage (8a) cylindrique qui est disposée concentriquement à un axe (X) du palier et par l'intermédiaire de laquelle la cage (6) est guidée radialement sur l'une des deux bagues (5a, 5b) par une deuxième surface de guidage (8b) cylindrique qui est disposée concentriquement à l'axe (X) du palier et est formée sur un bord (9a, 9b) de ladite bague (5a, 5b). L'objectif de l'invention est de fournir un palier à roulement de ce type qui permette d'obtenir un graissage amélioré par rapport à l'état de la technique et qui soit de conception simple et économique. À cet effet, la surface de guidage (8a, 8b) disposée à l'extérieur radialement, parmi la première et la deuxième surface de guidage (8a, 8b), présente un profilage.
PCT/DE2009/001188 2008-08-29 2009-08-21 Profilage de surfaces de guidage sur des paliers à roulement comprenant une cage guidée sur un bord Ceased WO2010022708A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008044907A DE102008044907A1 (de) 2008-08-29 2008-08-29 Profilierung von Führungsflächen bei Wälzlagern mit bordgeführtem Käfig
DE102008044907.5 2008-08-29

Publications (1)

Publication Number Publication Date
WO2010022708A1 true WO2010022708A1 (fr) 2010-03-04

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ID=41537526

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2009/001188 Ceased WO2010022708A1 (fr) 2008-08-29 2009-08-21 Profilage de surfaces de guidage sur des paliers à roulement comprenant une cage guidée sur un bord

Country Status (2)

Country Link
DE (1) DE102008044907A1 (fr)
WO (1) WO2010022708A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009048952A1 (de) 2009-10-10 2011-04-14 Schaeffler Technologies Gmbh & Co. Kg Lager mit einem bordgeführten Käfig
DE102010034216A1 (de) * 2010-08-07 2012-02-09 Minebea Co., Ltd. Wälzlager
DE102014224209A1 (de) 2014-11-27 2016-06-02 Schaeffler Technologies AG & Co. KG Wälzlagerkäfig und Wälzlager
DE102015202686A1 (de) * 2015-02-13 2016-08-18 Zf Friedrichshafen Ag Lager, Getriebe sowie Kraftfahrzeug

Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH122137A (de) * 1926-06-18 1927-09-01 Niederhauser Jakob Einrichtung zur Schmierung von Wälzlagern.
US3350147A (en) * 1966-02-01 1967-10-31 Skf Ind Inc Rolling bearing assembly
DE1425941A1 (de) * 1963-07-05 1969-03-20 Fafnir Bearing Company Waelzlager
JPS5072044A (fr) * 1973-10-29 1975-06-14
JPS63167125A (ja) * 1986-12-27 1988-07-11 Koyo Seiko Co Ltd ころがり軸受
JPH074429A (ja) * 1993-06-18 1995-01-10 Nippon Seiko Kk 転がり軸受
JPH0842578A (ja) * 1994-07-27 1996-02-13 Ntn Corp グリース潤滑玉軸受
WO2005026566A1 (fr) * 2003-09-18 2005-03-24 Ab Skf Roulement a reflux reduit
JP2006316846A (ja) * 2005-05-11 2006-11-24 Ntn Corp 転がり軸受
JP2007177837A (ja) * 2005-12-27 2007-07-12 Nsk Ltd ころ軸受用保持器及びころ軸受
DE102006052835A1 (de) * 2006-11-09 2008-05-15 Schaeffler Kg Radiallager

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005008668B4 (de) 2005-02-25 2010-04-22 Audi Ag Wälzlagerkäfig

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH122137A (de) * 1926-06-18 1927-09-01 Niederhauser Jakob Einrichtung zur Schmierung von Wälzlagern.
DE1425941A1 (de) * 1963-07-05 1969-03-20 Fafnir Bearing Company Waelzlager
US3350147A (en) * 1966-02-01 1967-10-31 Skf Ind Inc Rolling bearing assembly
JPS5072044A (fr) * 1973-10-29 1975-06-14
JPS63167125A (ja) * 1986-12-27 1988-07-11 Koyo Seiko Co Ltd ころがり軸受
JPH074429A (ja) * 1993-06-18 1995-01-10 Nippon Seiko Kk 転がり軸受
JPH0842578A (ja) * 1994-07-27 1996-02-13 Ntn Corp グリース潤滑玉軸受
WO2005026566A1 (fr) * 2003-09-18 2005-03-24 Ab Skf Roulement a reflux reduit
JP2006316846A (ja) * 2005-05-11 2006-11-24 Ntn Corp 転がり軸受
JP2007177837A (ja) * 2005-12-27 2007-07-12 Nsk Ltd ころ軸受用保持器及びころ軸受
DE102006052835A1 (de) * 2006-11-09 2008-05-15 Schaeffler Kg Radiallager

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