WO2007087776A1 - Mehrreihiges symmetrisches wälzlager - Google Patents
Mehrreihiges symmetrisches wälzlager Download PDFInfo
- Publication number
- WO2007087776A1 WO2007087776A1 PCT/DE2007/000070 DE2007000070W WO2007087776A1 WO 2007087776 A1 WO2007087776 A1 WO 2007087776A1 DE 2007000070 W DE2007000070 W DE 2007000070W WO 2007087776 A1 WO2007087776 A1 WO 2007087776A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- rolling
- rows
- diameter
- rolling bearing
- bearing
- Prior art date
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
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/50—Other types of ball or roller bearings
- F16C19/505—Other types of ball or roller bearings with the diameter of the rolling elements of one row differing from the diameter of those of another row
-
- 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
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
- B60B27/00—Hubs
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
- B60B27/00—Hubs
- B60B27/0005—Hubs with ball bearings
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
- B60B27/00—Hubs
- B60B27/0015—Hubs for driven wheels
- B60B27/0021—Hubs for driven wheels characterised by torque transmission means from drive axle
- B60B27/0026—Hubs for driven wheels characterised by torque transmission means from drive axle of the radial type, e.g. splined key
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
- B60B27/00—Hubs
- B60B27/0078—Hubs characterised by the fixation of bearings
- B60B27/0084—Hubs characterised by the fixation of bearings caulking to fix inner race
-
- 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
- F16C19/181—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 with angular contact
- F16C19/182—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 with angular contact in tandem arrangement
-
- 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
- F16C19/181—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 with angular contact
- F16C19/183—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 with angular contact with two rows at opposite angles
- F16C19/184—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 with angular contact with two rows at opposite angles in O-arrangement
-
- 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
- F16C19/50—Other types of 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
-
- 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
- F16C2240/70—Diameters; Radii
- F16C2240/80—Pitch circle diameters [PCD]
-
- 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
- F16C2326/00—Articles relating to transporting
- F16C2326/01—Parts of vehicles in general
- F16C2326/02—Wheel hubs or castors
Definitions
- the present invention is directed to a symmetrical rolling bearing and more particularly to a multi-row symmetric rolling bearing.
- the invention will be described with reference to a wheel bearing unit for driven or non-driven wheels of motor vehicles such as pickup trucks, light trucks or SUVs (Sports Utility Vehicles). It should be noted, however, that the present invention can also be applied to other rolling bearings.
- Rolling bearings are known from the prior art, which have an outer ring, an inner ring and disposed between these rings rolling elements. It is also known from the prior art to arrange these rolling elements in several rows. From DE 100 60 638 A1, for example, a double-row roller bearing is known. In this way it is possible to distribute the loads acting on the bearing on several rows of rolling elements and thus on several rolling elements.
- the use of balls in such double-row roller bearings is disadvantageous in that it is unsuitable for high axle loads.
- the use of tapered rollers in double row wheel bearings has the disadvantage that in this way a high friction torque is generated.
- Rolling bearings with more than two rows are relatively expensive to manufacture and besides suitable geometric dimensions are to be determined during manufacture.
- the present invention is therefore based on the object to provide a roller bearing available, which is suitable on the one hand for high axle load and on the other hand to produce and assemble with reasonable effort.
- a rolling bearing is to be provided, which can be exchanged for a conventional rolling bearing with tapered rollers.
- the rolling bearing according to the invention has a first bearing ring and a second bearing ring. Between these bearing rings a plurality of rolling elements is arranged.
- the rolling bodies are arranged in at least four rows, wherein at least two rows have a first pitch circle diameter and two further rows have a second pitch circle diameter different from the first pitch circle diameter.
- those rows which have the same pitch circle diameter, respectively are arranged symmetrically with respect to a plane that is perpendicular to a longitudinal direction of the bearing.
- the pitch circle diameter is understood to be the distance from an axis of symmetry of a rolling body to an axis of symmetry of a rolling body which is exactly opposite this rolling body in the same row.
- the load acting on the bearing can be distributed over a plurality of rows and therefore several rolling elements.
- the camp is generally suitable for receiving higher loads.
- the bearing By providing different pitch circle diameter, the bearing can be adjusted in a particularly suitable manner for receiving forces acting in different directions. Those rows with the larger pitch circle diameter are suitable for receiving larger forces.
- the advantage of conical rolling elements namely a higher load capacity, can be achieved without the disadvantages of conical rolling bodies, namely a higher friction, a higher weight and a displacement of the bearing rings relative to one another, having to be accepted ,
- the rows are arranged symmetrically with respect to a plane that is perpendicular to the longitudinal direction of the bearing, which is preferably a central plane.
- the rolling bearing according to the invention is a symmetrical roller bearing.
- the rolling bearing has a total width of more than 35mm. Extensive research has shown that rolling bearings with a total width of more than 35mm are particularly suitable for absorbing the forces acting on the bearing.
- the pitch circle diameter of the outer rows are greater than the pitch circle diameter of the inner rows.
- the rolling element diameter of the rolling elements differ at least two rows, and particularly preferably the rolling element diameter of the rolling elements of the outer rows are greater than the rolling element diameter of the rolling elements of the inner lying rows. Due to the decreasing from outside to inside rolling element diameter, the advantages of conical rolling elements can also be achieved without the above-mentioned disadvantages must be taken into account.
- a carrier-side outer diameter of the bearing is larger by more than 6 mm than the sum of the carrier-side pitch circle diameter and the rolling body diameter of the carrier-side rolling elements.
- the carrier-side row is also referred to below as the row arranged inside the vehicle.
- a flange-side outer diameter of the bearing is larger by more than 6 mm than the sum of the flange-side pitch circle diameter and the rolling element diameter of the flange-side rolling elements.
- the flange-side row is also referred to below as the vehicle outside arranged row.
- the geometries mentioned apply to both the carrier-side and the flange-side outer diameter of the bearing.
- the pitch circle diameter of an inner row is greater than 3.5 mm greater than the bore diameter of the rolling bearing.
- the bore diameter preferably corresponds to the inner diameter of the bearing ring.
- the axial distance between the first row and the second row spaced from that first row is less than the axial distance between the second row and the third row spaced from that second row.
- the first and the second row and the third and the fourth row are arranged in tandem and between the second row and the third row is a center of the outer and / or the inner ring.
- At least one bearing ring and particularly preferably the inner ring is constructed from two inner ring halves.
- the mounting of the bearing is simplified.
- the two inner ring halves are clamped together in the axial direction of the rolling bearing by a flared collar.
- each of the inner ring halves has two raceways for the rolling elements.
- the outer ring is preferably formed in one piece.
- At least one and particularly preferably a radially inner raceway for the rolling elements is provided on a flange body.
- This flange is preferably braced with the inner ring or an inner ring half, so rotationally fixed with respect to this.
- the tracks of two rows so for example, the raceways of the carrier-side rows in an inner ring half.
- a second inner ring half is not provided in this embodiment, and instead the raceways for the flange-side rows are provided directly on or in the flange body on which the wheel flange is also arranged. In this way, the installation costs for the invention The proper storage be reduced.
- the rolling elements are selected from a group of rolling elements, which contains balls, cylindrical rollers, cones and the like.
- rolling bodies of the same type are located in all rows, but it is also possible to provide rolling bodies of different types in different rows.
- the pressure angles of at least two rows are different from each other. Under the pressure angle those angles are understood, under which compressive forces are transmitted from the outer ring on the rolling elements on the inner ring or the inner ring halves. More specifically, the rolling elements are braced along obliquely extending to the longitudinal direction of the bearing contact lines. The contact angles are defined between these contact lines and the midplane. Preferably, the pressure angles of the outer rows are greater than the pressure angles of the inner rows. In each case, the pressure angles of the inner rows on the one hand and the pressure angles of the outer rows on the other hand are particularly preferably equal in magnitude. Due to the different pressure angles, it is possible to optimally adjust the load absorption of the bearing.
- the rolling bearing has a device for detecting the wheel speed.
- This may be, for example, a magnetic disk which, as a result of rotation, outputs a changing signal to a sensor.
- the present invention is further directed to a wheel bearing with a rolling bearing of the type described above.
- Fig. 1 is a schematic representation of a rolling bearing according to the invention.
- Fig. 2 shows the representation of Fig. 1 with marked geometries.
- the rolling bearing shown in Fig. 1 has four rows 11, 12, 13 and 14, in each of which rolling elements 5 are arranged.
- the rolling elements 5 are each arranged in rings and extend in a plane perpendicular to the plane of the figure.
- the individual rolling elements 5 can run in (not shown in detail) bearing cages. For simplicity, only one half of the bearing is shown in FIGS. 1 and 2.
- the individual rows 11, 12, 13 and 14 different pitch circle diameter Tk1, Tk2, Tk3, Tk4, which, as mentioned above, from the distance of a rolling element center of a rolling element to an opposite rolling element and there again give the Wälzkör- permitte.
- the two rows 11 and 14 have larger pitch circle diameter Tk1, Tk4 than the rows 12 and 13.
- the pitch circle diameters of the rows 11 and 14 are the same and also the pitch circle diameters Tk2 and Tk3 of the rows 12 and 13 equal.
- the rolling bearing shown in Fig. 1 is symmetrical with respect to a center plane ME both in terms of the number of rows and with respect to the respective pitch circle diameter.
- the rolling elements of the rows 11 and 14 continue to have a larger rolling element diameter than the rows 12 and 13. In this way, by the tandem arrangement of the rows 11 and 12 on the one hand and the Tandem arrangement of the rows 13, 14 on the other hand can be achieved that can be dispensed in the bearing on the known from the prior art tapered rollers and on the other hand, the benefits of tapered rollers can be used.
- a flange 24 is provided, which in turn serves for connection to a (not shown) carrier. Between the two rows 12 and 13, the outer ring 2 has a substantially radially inwardly facing center board 23. In the embodiment shown in FIG. 1, the flange 24 is not arranged in the longitudinal direction exactly in the middle of the roller bearing but offset in the direction of a flange 17.
- the flange 17 is formed in one piece with a flange body 18, on which inner ring halves 3 a and 3 b of a bearing inner ring 3 are arranged. More specifically, the inner ring halves 3a, 3b are braced in the axial direction of the rolling bearing by means of a flange collar 21 and a shoulder 22 which is arranged in the flange body 18.
- two raceways 9 for the rolling elements are respectively arranged on the two inner ring halves 3 a and 3 b.
- the inner ring half 3b could be dispensed with.
- the reference numeral 19 refers to a radially outwardly facing outboard of the inner ring 3 and the inner ring half 3b. This outboard joins the runway 9 of the row 14.
- the reference numeral 15 refers to a seal for the rolling bearing.
- This seal is designed here as a cassette seal and has on a arranged on the outer ring 2 reinforcement 20 three sealing lips 15a, 15b and 15c on.
- One of the sealing lips 15a is circumferentially radially biased against the inner ring 3 and its inner ring half 3b.
- Another sealing lip 15b bears axially against a centrifugal plate.
- the third sealing lip bears radially against the centrifugal plate.
- only one flange 17 is provided, which can be connected to a (not shown) wheel and is integrally formed with the flange 18.
- Fig. 2 shows the representation of Fig. 1 for illustrating the geometries.
- reference character B denotes the total bearing width
- reference character D denotes the bearing height, d. H. the distance between a radially inwardly facing surface of the bearing inner ring 3 and a radially outer surface of the bearing outer ring 2 under consideration of the flange 24.
- the reference numeral F denotes the flange outer diameter of the outer ring and the reference numeral E the ginneninnen- or carrier-side outer diameter of the bearing.
- the reference symbol A denotes the bore diameter of the roller bearing.
- the reference symbols Dw denote the individual diameters of the respective rolling bodies, for example the reference symbol Dw1 den
- the reference symbols Db1-Db4 designate the respective on-board diameter of the individual rows. For the sake of clarity, however, only the
- Reference signs Tk1 and Db4 are drawn.
- the reference numeral n denotes the width of the middle board between the rows 12 and 13.
- the reference numeral m denotes the width of the flange of the inner ring or the inner ring half 3b on the vehicle inner side facing side.
- the reference numerals ⁇ 1- ⁇ 4 denote the pressure angles, respectively.
- the total bearing width B is greater than the sum of all rolling element diameter added with the widths m of the inner ring and the mid-board width n. In addition, the total bearing width is greater than 35 mm.
- the respective outer rows have larger pitch circle diameter. That is, the pitch circle diameter Tk1 of the row 11 is larger than the pitch circle diameter Tk2 of the row 12 and the pitch circle diameter Tk4 of the row 14 is larger than the pitch circle diameter Tk3 of the row 13.
- the carrier-side outer diameter E of the outer ring in the embodiment shown in FIG. 2 is greater than the sum of the pitch circle diameter Tk4 and the diameter Dw4 of the rolling elements in the row 14.
- the carrier-side outer diameter E is at least 6 mm greater than said sum.
- the pitch circle diameter Tk3 is larger by at least 3.5 mm than the hole diameter A.
- the flange-side outer diameter F is preferably more than 6 mm larger than the pitch circle diameter Tk1 of the row 11 plus the rolling element diameter Dw1.
- the respective contact angles ⁇ 1 and ⁇ 4 of the rows 11 and 14 are greater than the contact angles ⁇ 2, ⁇ 3 of the rows 12 and 13.
- the angles with respect to the median plane ME are considered. This means that the pressure angles of the outer rows, ie the angles at which the forces are transmitted from the outer ring to the inner ring, in the outer rows are greater than the pressure angle of the inner rows.
- Tk1 - Tk4 pitch circle diameter ⁇ 1, ⁇ 2, ⁇ 3, contact angle ⁇ 4
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Rolling Contact Bearings (AREA)
Abstract
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP07702351A EP1979637A1 (de) | 2006-01-31 | 2007-01-17 | Mehrreihiges symmetrisches wälzlager |
US12/162,664 US8075195B2 (en) | 2006-01-31 | 2007-01-17 | Multi-row symmetrical rolling bearing |
JP2008555605A JP2009525447A (ja) | 2006-01-31 | 2007-01-17 | 複列対称転がり軸受 |
CA2641534A CA2641534C (en) | 2006-01-31 | 2007-01-17 | Multi-row symmetrical rolling bearing |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102006004273.5 | 2006-01-31 | ||
DE102006004273A DE102006004273A1 (de) | 2006-01-31 | 2006-01-31 | Mehrreihiges symmetrisches Wälzlager |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2007087776A1 true WO2007087776A1 (de) | 2007-08-09 |
Family
ID=37891977
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/DE2007/000070 WO2007087776A1 (de) | 2006-01-31 | 2007-01-17 | Mehrreihiges symmetrisches wälzlager |
Country Status (9)
Country | Link |
---|---|
US (1) | US8075195B2 (de) |
EP (1) | EP1979637A1 (de) |
JP (1) | JP2009525447A (de) |
KR (1) | KR20080091227A (de) |
CN (1) | CN101379311A (de) |
CA (1) | CA2641534C (de) |
DE (1) | DE102006004273A1 (de) |
RU (1) | RU2428596C2 (de) |
WO (1) | WO2007087776A1 (de) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2011501058A (ja) * | 2007-10-18 | 2011-01-06 | クノール−ブレミゼ ジュステーメ フューア ヌッツファーツォィゲ ゲーエムベーハー | 特に輸送用車両の車輪を軸承するためのころがり軸受 |
Families Citing this family (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102007045248B4 (de) * | 2007-09-21 | 2010-09-09 | Ab Skf | Radlagerung für ein Kraftfahrzeug |
DE102007060565A1 (de) * | 2007-12-15 | 2009-06-18 | Schaeffler Kg | Radmodul, insbesondere für die angetriebenen Räder von Personenkraftfahrzeugen |
DE102008053444A1 (de) * | 2008-10-28 | 2010-04-29 | Schaeffler Kg | Wälzlager, insbesondere Radlager |
JP2011106600A (ja) * | 2009-11-19 | 2011-06-02 | Ntn Corp | 車輪用軸受装置 |
JP5927773B2 (ja) * | 2010-04-19 | 2016-06-01 | 日本精工株式会社 | タンデムアンギュラ型玉軸受 |
DE102012204039A1 (de) * | 2012-03-15 | 2013-09-19 | Schaeffler Technologies AG & Co. KG | Radlager mit einer Sensoraufnahme |
DE102012215280A1 (de) * | 2012-08-29 | 2014-03-06 | Schaeffler Technologies AG & Co. KG | Ritzelwellenlagerung |
DE102013203005A1 (de) * | 2013-02-25 | 2014-08-28 | Schaeffler Technologies Gmbh & Co. Kg | Radlagereinheit mit einem spannungsoptimierten Aufbau |
DE102013224545B4 (de) * | 2013-11-29 | 2021-06-24 | Bayerische Motoren Werke Aktiengesellschaft | Radlager eines Fahrzeugs mit vier Schrägkugellager-Einheiten |
DE102017112338A1 (de) * | 2017-06-06 | 2018-12-06 | Schaeffler Technologies AG & Co. KG | Zweireihiges Schrägkugellager |
Citations (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US983792A (en) * | 1910-06-23 | 1911-02-07 | Frank Whitney | Roller-bearing. |
US990946A (en) * | 1909-11-23 | 1911-05-02 | Luther Badger | Roller-bearing. |
DE9202230U1 (de) * | 1992-02-21 | 1992-04-23 | INA Wälzlager Schaeffler KG, 8522 Herzogenaurach | Schrägkugellager |
DE10060638A1 (de) * | 2000-01-11 | 2001-08-16 | Ntn Toyo Bearing Co Ltd | Radlagereinheit |
GB2371603A (en) * | 2000-12-18 | 2002-07-31 | Nsk Rhp Europe Technology Co Ltd | Shaft Bearing Arrangements |
DE10331936A1 (de) * | 2003-07-15 | 2005-02-10 | Fag Kugelfischer Ag & Co. Ohg | Radlagereinheit in Schrägkugellagerausführung |
DE202004020400U1 (de) * | 2004-11-18 | 2005-06-02 | Fag Kugelfischer Ag | Radlagereinheit |
WO2006119738A1 (de) * | 2005-05-13 | 2006-11-16 | Schaeffler Kg | Vierreihiges kegelrollenlager |
Family Cites Families (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US466446A (en) * | 1892-01-05 | Ball-bearing | ||
US1325113A (en) * | 1919-12-16 | Ball-bearing | ||
US804954A (en) * | 1904-07-02 | 1905-11-21 | Eric Johanson | Bearing for vehicles. |
US845778A (en) * | 1904-08-29 | 1907-03-05 | August C Hachfield | Ball-bearing |
US918422A (en) * | 1906-11-24 | 1909-04-13 | Evans Coppins & Starks Company | Ball-bearing. |
US1392912A (en) * | 1921-04-29 | 1921-10-11 | Chesnutt John Loucien | Ball-bearing string-proof wheel |
US2130258A (en) * | 1936-05-25 | 1938-09-13 | Timken Roller Bearing Co | Multiple-row taper roller bearing |
IT1227656B (it) * | 1988-12-01 | 1991-04-23 | Omet S R L L | Cuscinetto volvente |
DE3940274A1 (de) * | 1989-12-06 | 1991-06-13 | Esjot Antriebstech Gmbh & Co | Tretlagereinheit zum einbau in tretlagergehaeuse von fahrraedern o. dgl. und verfahren zum zusammenbau der tretlagereinheit |
DE4339847C2 (de) * | 1993-11-23 | 2000-09-14 | Kugelfischer G Schaefer & Co | Lagereinheit |
US6824489B2 (en) * | 1998-08-29 | 2004-11-30 | Ina-Schaeffler Kg | Differential for a motor vehicle |
DE10218937B4 (de) * | 2002-04-27 | 2013-04-25 | Schaeffler Technologies AG & Co. KG | Schutzeinrichtung für ein Wälzlager mit Drehzahlmessung |
-
2006
- 2006-01-31 DE DE102006004273A patent/DE102006004273A1/de not_active Ceased
-
2007
- 2007-01-17 US US12/162,664 patent/US8075195B2/en not_active Expired - Fee Related
- 2007-01-17 WO PCT/DE2007/000070 patent/WO2007087776A1/de active Application Filing
- 2007-01-17 EP EP07702351A patent/EP1979637A1/de not_active Withdrawn
- 2007-01-17 CA CA2641534A patent/CA2641534C/en not_active Expired - Fee Related
- 2007-01-17 RU RU2008135349/11A patent/RU2428596C2/ru active
- 2007-01-17 KR KR1020087019955A patent/KR20080091227A/ko not_active Application Discontinuation
- 2007-01-17 JP JP2008555605A patent/JP2009525447A/ja active Pending
- 2007-01-17 CN CNA2007800041813A patent/CN101379311A/zh active Pending
Patent Citations (8)
Publication number | Priority date | Publication date | Assignee | Title |
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US990946A (en) * | 1909-11-23 | 1911-05-02 | Luther Badger | Roller-bearing. |
US983792A (en) * | 1910-06-23 | 1911-02-07 | Frank Whitney | Roller-bearing. |
DE9202230U1 (de) * | 1992-02-21 | 1992-04-23 | INA Wälzlager Schaeffler KG, 8522 Herzogenaurach | Schrägkugellager |
DE10060638A1 (de) * | 2000-01-11 | 2001-08-16 | Ntn Toyo Bearing Co Ltd | Radlagereinheit |
GB2371603A (en) * | 2000-12-18 | 2002-07-31 | Nsk Rhp Europe Technology Co Ltd | Shaft Bearing Arrangements |
DE10331936A1 (de) * | 2003-07-15 | 2005-02-10 | Fag Kugelfischer Ag & Co. Ohg | Radlagereinheit in Schrägkugellagerausführung |
DE202004020400U1 (de) * | 2004-11-18 | 2005-06-02 | Fag Kugelfischer Ag | Radlagereinheit |
WO2006119738A1 (de) * | 2005-05-13 | 2006-11-16 | Schaeffler Kg | Vierreihiges kegelrollenlager |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2011501058A (ja) * | 2007-10-18 | 2011-01-06 | クノール−ブレミゼ ジュステーメ フューア ヌッツファーツォィゲ ゲーエムベーハー | 特に輸送用車両の車輪を軸承するためのころがり軸受 |
Also Published As
Publication number | Publication date |
---|---|
CA2641534A1 (en) | 2007-08-09 |
RU2008135349A (ru) | 2010-03-10 |
CA2641534C (en) | 2013-03-26 |
DE102006004273A1 (de) | 2007-08-02 |
RU2428596C2 (ru) | 2011-09-10 |
KR20080091227A (ko) | 2008-10-09 |
EP1979637A1 (de) | 2008-10-15 |
JP2009525447A (ja) | 2009-07-09 |
CN101379311A (zh) | 2009-03-04 |
US20090116778A1 (en) | 2009-05-07 |
US8075195B2 (en) | 2011-12-13 |
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