WO2005054697A1 - 円すいころ軸受 - Google Patents
円すいころ軸受 Download PDFInfo
- Publication number
- WO2005054697A1 WO2005054697A1 PCT/JP2004/018113 JP2004018113W WO2005054697A1 WO 2005054697 A1 WO2005054697 A1 WO 2005054697A1 JP 2004018113 W JP2004018113 W JP 2004018113W WO 2005054697 A1 WO2005054697 A1 WO 2005054697A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- roller bearing
- tapered roller
- cage
- tapered
- rollers
- 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
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/46—Cages for rollers or needles
- F16C33/467—Details of individual pockets, e.g. shape or roller retaining means
-
- 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
- F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
- F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
- F16C19/36—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers
- F16C19/364—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
-
- 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
- F16C33/46—Cages for rollers or needles
- F16C33/4617—Massive or moulded cages having cage pockets surrounding the rollers, e.g. machined window cages
- F16C33/4623—Massive or moulded cages having cage pockets surrounding the rollers, e.g. machined window cages formed as one-piece cages, i.e. monoblock cages
- F16C33/4635—Massive or moulded cages having cage pockets surrounding the rollers, e.g. machined window cages formed as one-piece cages, i.e. monoblock cages made from plastic, e.g. injection moulded window cages
-
- 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
- F16C2240/30—Angles, e.g. inclinations
-
- 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
-
- 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]
- F16C2240/82—Degree of filling, i.e. sum of diameters of rolling elements in relation to PCD
- F16C2240/84—Degree of filling, i.e. sum of diameters of rolling elements in relation to PCD with full complement of balls or rollers, i.e. sum of clearances less than diameter of one rolling element
-
- 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
- F16C2361/00—Apparatus or articles in engineering in general
- F16C2361/61—Toothed gear systems, e.g. support of pinion shafts
Definitions
- the present invention relates to a tapered roller bearing, and more particularly to a tapered roller bearing suitably incorporated in a gear device of an automobile transmission.
- Automobile transmissions can be broadly classified into manual types and automatic types.
- a front axle (FWD) transaxle a rear wheel drive (RWD) transmission, and a four-wheel drive
- FWD front axle
- RWD rear wheel drive
- 4 WD transfer
- 4 WD transfer
- FIG. 7 shows an example of the configuration of a vehicle transmission.
- This transmission is of the synchronous type, in which the left side is the engine side and the right side is the driving wheel side.
- a tapered roller bearing 43 is interposed between the main shaft 41 and the main drive gear 42.
- the outer raceway surface of the tapered roller bearing 43 is formed directly on the inner periphery of the main drive gear 42.
- the main drive gear 42 is rotatably supported by the tapered roller bearings 44 with respect to the casing 45.
- a clutch gear 46 is engaged and connected to the main drive gear 42, and a synchronizing mechanism 47 is disposed near the clutch gear 46.
- the synchronizing mechanism 47 includes a sleeve 48 that moves in the axial direction (left and right directions in the figure) by actuation of a selector (not shown), and a synchronizer key movably mounted in the inner circumference of the sleeve 48 so as to be axially movable. 49, a hub 50 engaged with and connected to the outer periphery of the main shaft 41, a synchronizer ring 51 slidably mounted on the outer periphery (cone portion) of the clutch gear 46, and a synchronizer key A pressing pin 52 and a spring 53 for elastically pressing the sleeve 49 against the inner periphery of the sleeve 48 are provided.
- the sleeve 48 and the synchronizer key 49 are held at the neutral position by the holding pin 52. At this time, the main drive gear 42 rotates idly with respect to the main shaft 41.
- the synchronizer key 49 moves to the left side in the axial direction following the sleeve 48, and the sink opening One ring 51 is pressed against the inclined surface of the cone of the clutch gear 46. As a result, the rotation speed of the clutch gear 46 decreases, and conversely, the rotation speed of the synchronization mechanism 47 increases.
- the sleeve 48 moves further to the left in the axial direction, meshes with the clutch gear 46, and a synchronization mechanism is provided between the main shaft 41 and the main drive gear 42. Connected via 4 7. Thereby, the main shaft 41 and the main drive gear 42 rotate synchronously.
- low-viscosity oil has been used in automobile transmissions in order to achieve AT, CVT and low fuel consumption of transmissions.
- poor conditions such as (1) high oil temperature, (2) low oil level, and (3) preload loss may result from poor lubrication.
- Very short-lived surface-originated delamination may occur on the inner raceway surface with high surface pressure.
- reducing the maximum surface pressure is a direct and effective solution.
- change the bearing dimensions or, if the bearing dimensions are not changed increase the number of bearing rollers.
- the pocket interval of the cage In order to increase the number of rollers without reducing the roller diameter, the pocket interval of the cage must be narrowed, but for that purpose, the pitch circle of the cage must be increased and the cage must be as close as possible to the outer ring side.
- FIG. 8 shows a tapered roller bearing as an example in which the cage is brought close to contact with the inner surface of the outer ring (see Patent Document 1).
- the tapered roller bearing 6 1 is configured such that the outer peripheral surface of the small-diameter annular portion 62 a and the outer peripheral surface of the large-diameter annular portion 62 b of the cage 62 are brought into sliding contact with the outer ring 63 and the inner diameter surface of the retainer 62.
- the surface 63a is kept in a non-contact state.
- the retainer 62 includes a small-diameter annular portion 62 a, a large-diameter annular portion 62b, a small-diameter annular portion 62a, and a large-diameter annular portion 6. 2b in the axial direction and a plurality of column portions 62c having recesses 64 formed on the outer diameter surface. A plurality of pockets are provided between the column portions 62c so as to freely accommodate the tapered rollers 65.
- the small-diameter annular portion 62a is provided with a flange 62d extending integrally on the inner diameter side.
- the cage 62 is intended to improve the strength of the cage 62.
- the cage 62 is connected to the inner surface of the outer ring 63. This is an example that is brought up to contact.
- Patent Document 1 Japanese Unexamined Patent Publication No. 2003-281665 Disclosure of the Invention
- the cage 62 is moved to the outer diameter until it comes into contact with the inner diameter surface of the outer ring 63 to increase the circumferential width of the column portion 62 c of the cage 62. .
- the plate thickness is inevitably reduced, and the rigidity of the cage 62 is reduced.
- the cage 62 is deformed or the cage 62 is deformed while the bearing 61 is rotating.
- roller coefficient r roller filling rate
- roller coefficient r (Z ⁇ D A) / ( ⁇ ⁇ P C D)
- Z Number of rollers
- DA Roller average diameter
- PCD Roller pitch circle diameter
- An object of the present invention is to prevent an early breakage due to an increase in load capacity and an excessive surface pressure on a raceway surface.
- the tapered roller bearing according to the present invention includes: an inner ring; an outer ring; and a rolling element between the inner ring and the outer ring.
- a tapered roller bearing comprising: a plurality of freely arranged tapered rollers; and a retainer for holding the tapered rollers at a predetermined circumferential interval, wherein a roller coefficient r exceeds 0.94.
- the window angle of the pocket is set to 55 ° or more and 80 ° or less.
- the window angle is the angle formed by the guide surface of the pillar that contacts the peripheral surface of one roller.
- the window angle was set to 55 ° or more in order to ensure good contact with the rollers, and the window angle was set to 80 ° or less. This is because there is a risk that smooth rotation may not be obtained even with a resin material having an insulative property.
- the window angle is 25 ° to 50 ° in a normal cage.
- the invention of claim 3 is the tapered roller bearing of claim 1 or 2, wherein the retainer is made of engineering plastic having excellent mechanical strength, oil resistance and heat resistance.
- the retainer is made of engineering plastic having excellent mechanical strength, oil resistance and heat resistance.
- Engineering '' plastics include general-purpose engineering '' plastics and super engineering ⁇ ⁇ ⁇ ⁇ ⁇ plastics. The following are representative examples, but these are examples of engineering plastics, and engineering plastics are not limited to the following.
- PC Polycarbonate
- PA6 Polyamide 6
- PA 66 Polyamide 66
- POM Polyacetal
- m-PPE Modified polyphenylene ether
- PBT Polybutylene terephthalate
- GF- ⁇ ⁇ GF reinforced polyethylene terephthalate
- U HMW- ⁇ ⁇ ultra-high molecular weight polyethylene
- roller coefficient r of the tapered roller bearing By setting the roller coefficient r of the tapered roller bearing to r> 0.94, not only the load capacity is increased but also the maximum surface pressure on the raceway surface can be reduced, so that extremely short It is possible to prevent surface-originated peeling over the life.
- FIG. 1A is a cross-sectional view of the tapered roller bearing of the present invention
- FIG. 1B is a longitudinal cross-sectional view of the same.
- FIG. 2 is a partially enlarged cross-sectional view of a tapered roller bearing having a lower window angle.
- FIG. 3 is a partially enlarged sectional view of a tapered roller bearing having an upper limit of the window angle.
- Figure 4 shows the results of the bearing life test.
- FIG. 5 is a partial sectional view of a tapered roller bearing according to a modification of the present invention.
- FIG. 6 is a cross-sectional view of a column of the cage of FIG.
- FIG. 7 is a cross-sectional view of a general automobile transmission.
- FIG. 8 is a cross-sectional view of a conventional tapered roller bearing in which a cage is moved toward the outer ring.
- FIG. 9 is a partially enlarged cross-sectional view of another conventional tapered roller bearing. BEST MODE FOR CARRYING OUT THE INVENTION
- the tapered roller bearing 1 of the embodiment shown in FIGS. 1 (A) and 1 (B) has a conical raceway surface 2a, a small flange portion 2b on the small diameter side of the raceway surface 2a, and a large flange portion on the large diameter side.
- the tapered roller bearing ⁇ has a roller coefficient r> 0.94.
- the retainer 5 is formed integrally with a super engineering plastic such as PPS, PEEK, PA, PPA, PAI, etc., and has a small-diameter annular portion 5a, a large-diameter annular portion 5, and a small-diameter annular portion.
- a plurality of pillars 5c are provided to connect 5a and the large-diameter annular portion 5b in the axial direction.
- the window angle 0 of the column surface 5d is such that the lower limit window angle 0min is 55 ° as shown in Fig. 2 and the upper limit window angle 0max is 80 as shown in Fig. 3. It is.
- the window angle is as large as about 50 ° for a typical tapered roller bearing with a cage, as shown in Fig. 9, where the cage is separated from the outer ring.
- the reason why the lower limit of the window angle 0 min is set to 55 ° or more is to ensure a good contact state with the rollers. If the window angle is less than 55 °, the contact state with the rollers becomes worse. In other words, if the window angle is 55 ° or more, it is possible to secure r> 0.94 and secure a good contact state while securing the cage strength.
- the reason why the upper limit window angle 0max is set to 80 ° or less is that if it is larger than this, the pressing force in the radial direction increases, and there is a risk that smooth rotation cannot be obtained even with a self-lubricating resin material. Because it occurs.
- Figure 4 shows the results of the bearing life test.
- ⁇ Comparative Example 1 J '' in the ⁇ Bearing '' column is a typical conventional tapered roller bearing in which the cage and outer ring are separated
- ⁇ Example 1 '' is a conventional tapered roller bearing of the present invention.
- a ⁇ Example 2 '' in which the roller coefficient r is r> 0.94 and the window angle is in the range of 55 to 80 °. It is a tapered roller bearing of the invention.
- the test was performed under severe lubrication and overload conditions.
- Example 1 has a service life that is at least twice as long as “Comparative Example”. Further, the bearing of “Example 2” has a roller coefficient of 0.96, which is the same as that of “Example 1,” but the service life is about five times or more that of “Example 1.”
- FIGS. Figure shown here is a tapered roller bearing 1
- a protrusion 5f is formed on the outer diameter surface of the column 5c of FIG. 5 so as to project toward the outer raceway surface side. Others are the same as the above-mentioned cage 5.
- the projecting portion 5f has an arc-shaped cross-sectional profile in the transverse direction of the column portion 5c.
- the arcuate curvature radius R 2 is the outer ring raceway surface radius R, are smaller form.
- the good wedge oil film is formed between the protruding portions 5 f and the outer ring raceway surface, preferably the radius of curvature R 2 of the protrusions 70-9 0% radius outer ring raceway surface It is good to form it. If it is less than 70%, the opening angle of the wedge-shaped oil slick is too large, and the dynamic pressure is rather reduced. On the other hand, if it exceeds 90%, the entrance angle of the wedge-shaped oil film becomes too small, and the dynamic pressure similarly decreases. Further, the width W 2 of the projecting portion 5 f is desirably formed to have a more than 50% of the width of the pillar portion 5 c (W 2 ⁇ 0. 5 ⁇ ⁇ ⁇ ⁇ ).
- the outer ring raceway surface radius R so is continuously changed to the small-diameter side from the large ⁇ IJ, I size of the large diameter side annular section 5 b to match therewith also the radius of curvature R 2 of the projecting portion 5 f continuously to vary from the radius of curvature R 2 to a small radius of curvature R 2 of the small diameter side annular section 5 a.
- the tapered roller bearing 1 in FIGS. 5 and 6 is configured as described above, when the bearing 1 starts rotating and the retainer 5 starts rotating, the outer ring raceway surface and the protrusion 5 f of the retainer 5 A wedge-shaped oil film is formed between them. Since this wedge-shaped oil film generates a dynamic pressure approximately proportional to the rotation speed of the bearing 1, even if the pitch circle diameter (PCD) of the cage 5 is made larger than before, and it is close to the outer ring raceway surface, 1 can be rotated without causing significant wear or loss of torque, and the number of rollers can be increased without difficulty.
- PCD pitch circle diameter
- a super engineering plastic such as PPS, PE EK, PA, PPA, or PAI was used as a material for the retainer.
- these resin materials or other engineering materials may be used to increase the strength. It is also possible to use a material obtained by blending glass fiber, carbon fiber, or the like with the ring plastic.
- the tapered roller bearing 1 according to the present invention can be used not only for being incorporated in a transmission of an automobile but also for an application other than a differential of an automobile or a gear device for an automobile.
Abstract
Description
Claims
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US10/581,338 US7789570B2 (en) | 2003-12-02 | 2004-11-30 | Tapered roller bearing |
EP04799961.0A EP1698789B1 (en) | 2003-12-02 | 2004-11-30 | Tapered roller bearing |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2003-403438 | 2003-12-02 | ||
JP2003403438 | 2003-12-02 | ||
JP2004198708A JP2005188738A (ja) | 2003-12-02 | 2004-07-05 | 円すいころ軸受 |
JP2004-198708 | 2004-07-05 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2005054697A1 true WO2005054697A1 (ja) | 2005-06-16 |
Family
ID=34656200
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2004/018113 WO2005054697A1 (ja) | 2003-12-02 | 2004-11-30 | 円すいころ軸受 |
Country Status (4)
Country | Link |
---|---|
US (1) | US7789570B2 (ja) |
EP (1) | EP1698789B1 (ja) |
JP (1) | JP2005188738A (ja) |
WO (1) | WO2005054697A1 (ja) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102007013482A1 (de) * | 2007-03-21 | 2008-10-09 | Ab Skf | Kegelrollenlager |
Families Citing this family (46)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2005111446A1 (ja) * | 2004-05-13 | 2005-11-24 | Ntn Corporation | 円すいころ軸受 |
JP2006022935A (ja) | 2004-07-05 | 2006-01-26 | Ntn Corp | 円すいころ軸受 |
JP4593208B2 (ja) * | 2004-09-01 | 2010-12-08 | Ntn株式会社 | 円すいころ軸受 |
JP2007024170A (ja) * | 2005-07-15 | 2007-02-01 | Ntn Corp | ころ軸受 |
JP2007078047A (ja) * | 2005-09-13 | 2007-03-29 | Ntn Corp | 円錐ころ軸受およびこれを備えた車輪用軸受装置 |
JP4717574B2 (ja) * | 2005-09-26 | 2011-07-06 | Ntn株式会社 | 円すいころ軸受 |
JP2007120648A (ja) * | 2005-10-28 | 2007-05-17 | Ntn Corp | 円すいころ軸受 |
JP5031219B2 (ja) * | 2005-10-19 | 2012-09-19 | Ntn株式会社 | 円すいころ軸受 |
JP4987277B2 (ja) * | 2005-10-20 | 2012-07-25 | Ntn株式会社 | デファレンシャル用円すいころ軸受 |
JP4975293B2 (ja) * | 2005-10-07 | 2012-07-11 | Ntn株式会社 | 円錐ころ軸受 |
JP4987281B2 (ja) * | 2005-10-25 | 2012-07-25 | Ntn株式会社 | 円すいころ軸受 |
JP4975294B2 (ja) * | 2005-10-07 | 2012-07-11 | Ntn株式会社 | 円錐ころ軸受 |
JP4987280B2 (ja) * | 2005-10-25 | 2012-07-25 | Ntn株式会社 | 円すいころ軸受 |
JP4994630B2 (ja) * | 2005-10-07 | 2012-08-08 | Ntn株式会社 | 円錐ころ軸受 |
JP2007120575A (ja) * | 2005-10-26 | 2007-05-17 | Ntn Corp | 円すいころ軸受 |
WO2007032470A1 (ja) * | 2005-09-16 | 2007-03-22 | Ntn Corporation | 円錐ころ軸受 |
JP5031220B2 (ja) * | 2005-10-19 | 2012-09-19 | Ntn株式会社 | 円すいころ軸受 |
JP4987278B2 (ja) * | 2005-10-20 | 2012-07-25 | Ntn株式会社 | トランスミッション用円すいころ軸受 |
JP4994637B2 (ja) * | 2005-10-28 | 2012-08-08 | Ntn株式会社 | ころ軸受 |
JP2007127220A (ja) * | 2005-11-04 | 2007-05-24 | Ntn Corp | トランスミッション用円すいころ軸受 |
JP2007127219A (ja) * | 2005-11-04 | 2007-05-24 | Ntn Corp | デファレンシャル用円すいころ軸受 |
JP4994643B2 (ja) * | 2005-11-11 | 2012-08-08 | Ntn株式会社 | 円すいころ軸受 |
JP4994636B2 (ja) * | 2005-10-27 | 2012-08-08 | Ntn株式会社 | 円すいころ軸受 |
JP2007127218A (ja) * | 2005-11-04 | 2007-05-24 | Ntn Corp | 円すいころ軸受 |
JP4994638B2 (ja) * | 2005-10-28 | 2012-08-08 | Ntn株式会社 | 円すいころ軸受 |
JP2007127217A (ja) * | 2005-11-04 | 2007-05-24 | Ntn Corp | 円すいころ軸受 |
WO2007046263A1 (ja) * | 2005-10-19 | 2007-04-26 | Ntn Corporation | ころ軸受 |
JP5008856B2 (ja) * | 2005-10-28 | 2012-08-22 | Ntn株式会社 | 円すいころ軸受 |
JP2007120577A (ja) * | 2005-10-26 | 2007-05-17 | Ntn Corp | 円すいころ軸受 |
JP4920236B2 (ja) * | 2005-10-19 | 2012-04-18 | Ntn株式会社 | 円すいころ軸受 |
JP5005209B2 (ja) * | 2005-11-11 | 2012-08-22 | Ntn株式会社 | 円すいころ軸受 |
JP4920238B2 (ja) | 2005-10-25 | 2012-04-18 | Ntn株式会社 | 円すいころ軸受 |
JP5005207B2 (ja) * | 2005-10-26 | 2012-08-22 | Ntn株式会社 | 円すいころ軸受 |
DE112007000532T5 (de) | 2006-03-08 | 2009-01-15 | Ntn Corporation | Lagervorrichtung für ein Fahrzeugrad |
JP2008008374A (ja) * | 2006-06-28 | 2008-01-17 | Ntn Corp | 車輪用軸受装置 |
DE102006021544B4 (de) * | 2006-05-08 | 2010-03-25 | Ab Skf | Wälzlager |
JP5340561B2 (ja) * | 2007-06-15 | 2013-11-13 | Ntn株式会社 | 円すいころ軸受 |
US8616776B2 (en) * | 2008-06-17 | 2013-12-31 | Jtekt Corporation | Cylindrical roller bearing |
US20100108932A1 (en) * | 2008-10-31 | 2010-05-06 | Bauer Robert R | Bearing assembly and a method for controlling fluid flow within a conduit |
US8356945B2 (en) * | 2009-11-24 | 2013-01-22 | Amsted Rail Company, Inc. | Railway car roller bearing |
DE102010023521A1 (de) * | 2010-06-11 | 2011-12-15 | Aktiebolaget Skf | Käfig für ein Wälzlager und Schrägkugellager |
JP5466100B2 (ja) * | 2010-06-30 | 2014-04-09 | Ntn株式会社 | 円すいころ軸受 |
JP5731914B2 (ja) * | 2011-06-17 | 2015-06-10 | Ntn株式会社 | 二つ割り保持器及び二つ割りころ軸受 |
JP2012107765A (ja) * | 2012-03-12 | 2012-06-07 | Ntn Corp | 円すいころ軸受 |
JP6798780B2 (ja) | 2015-01-28 | 2020-12-09 | Ntn株式会社 | 円すいころ軸受 |
DK3548760T3 (en) | 2016-12-01 | 2022-10-03 | Timken Co | Bearing assembly and bearing cage |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS6479419A (en) * | 1987-06-04 | 1989-03-24 | Nippon Seiko Kk | Plastic retainer for bearing |
JPH11210765A (ja) * | 1998-01-26 | 1999-08-03 | Ntn Corp | デファレンシャルギヤのピニオン軸支持用円すいころ軸受 |
JP2000240661A (ja) * | 1999-02-24 | 2000-09-05 | Ntn Corp | 保持器付きころ |
JP2002195255A (ja) * | 2000-12-28 | 2002-07-10 | Nsk Ltd | 転がり軸受 |
JP2003028165A (ja) * | 2001-07-17 | 2003-01-29 | Nsk Ltd | ころ軸受装置 |
JP2003166543A (ja) * | 2001-11-30 | 2003-06-13 | Nsk Ltd | 転がり軸受 |
Family Cites Families (18)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1426578A (en) * | 1922-08-22 | Chables i | ||
US2016526A (en) * | 1934-05-22 | 1935-10-08 | Miller S Tyson | Roller bearing |
US2231350A (en) * | 1940-06-17 | 1941-02-11 | Timken Roller Bearing Co | Roller bearing |
DE2121679C2 (de) * | 1971-03-03 | 1983-09-15 | INA Wälzlager Schaeffler KG, 8522 Herzogenaurach | Aus Stegen und Stirnringen bestehender Radialkäfig für zylindrische Wälzkörper |
US5590225A (en) | 1987-06-04 | 1996-12-31 | Nippon Seiko Kabushiki Kaisha | Plastic holder for bearing |
US4874260A (en) * | 1988-03-21 | 1989-10-17 | The Torrington Company | Cage outer diameter profile |
DE4133443C2 (de) * | 1991-10-09 | 1995-07-13 | Schaeffler Waelzlager Kg | Käfig für vollrollige Wälzlager |
US5352047A (en) * | 1992-07-13 | 1994-10-04 | Rexnord Corporation | Snap-tab roller bearing case |
DE4442404C2 (de) * | 1994-11-30 | 1999-07-01 | Schaeffler Waelzlager Ohg | Verdrehsicherung für einen Kunststoffkäfig eines Freilaufs |
DE29504069U1 (de) * | 1995-03-09 | 1995-04-27 | Skf Gmbh | Taschenkäfig für Rollenlager |
JP3305591B2 (ja) * | 1996-09-26 | 2002-07-22 | 富士機工株式会社 | ステアリングコラム用軸受 |
US6102579A (en) * | 1997-01-10 | 2000-08-15 | The Torrington Company | Cage or set of rollers for roller bearings |
US6086261A (en) | 1998-01-14 | 2000-07-11 | Ntn Corporation | Tapered roller bearing |
DE19807160B4 (de) * | 1998-02-20 | 2006-11-02 | Skf Gmbh | Verfahren zur Herstellung eines Blechkäfigs und danach hergestellter Blechkäfig |
JP3811575B2 (ja) * | 1998-10-29 | 2006-08-23 | 株式会社ジェイテクト | 軸受用保持器 |
JP4618915B2 (ja) * | 2001-03-14 | 2011-01-26 | Ntn株式会社 | 総ころ軸受およびこれを用いた遊星歯車減速装置 |
US6857785B2 (en) * | 2001-03-27 | 2005-02-22 | Ntn Corporation | Caged roller assembly and reduction gear unit using the same |
JP2003314542A (ja) * | 2002-04-16 | 2003-11-06 | Nsk Ltd | 円すいころ軸受 |
-
2004
- 2004-07-05 JP JP2004198708A patent/JP2005188738A/ja active Pending
- 2004-11-30 WO PCT/JP2004/018113 patent/WO2005054697A1/ja active Application Filing
- 2004-11-30 US US10/581,338 patent/US7789570B2/en not_active Expired - Fee Related
- 2004-11-30 EP EP04799961.0A patent/EP1698789B1/en not_active Expired - Fee Related
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS6479419A (en) * | 1987-06-04 | 1989-03-24 | Nippon Seiko Kk | Plastic retainer for bearing |
JPH11210765A (ja) * | 1998-01-26 | 1999-08-03 | Ntn Corp | デファレンシャルギヤのピニオン軸支持用円すいころ軸受 |
JP2000240661A (ja) * | 1999-02-24 | 2000-09-05 | Ntn Corp | 保持器付きころ |
JP2002195255A (ja) * | 2000-12-28 | 2002-07-10 | Nsk Ltd | 転がり軸受 |
JP2003028165A (ja) * | 2001-07-17 | 2003-01-29 | Nsk Ltd | ころ軸受装置 |
JP2003166543A (ja) * | 2001-11-30 | 2003-06-13 | Nsk Ltd | 転がり軸受 |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102007013482A1 (de) * | 2007-03-21 | 2008-10-09 | Ab Skf | Kegelrollenlager |
Also Published As
Publication number | Publication date |
---|---|
US7789570B2 (en) | 2010-09-07 |
JP2005188738A (ja) | 2005-07-14 |
US20070280574A1 (en) | 2007-12-06 |
EP1698789A4 (en) | 2011-07-27 |
EP1698789B1 (en) | 2017-04-12 |
EP1698789A1 (en) | 2006-09-06 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
WO2005054697A1 (ja) | 円すいころ軸受 | |
EP1746298B1 (en) | Tapered roller bearing | |
EP1614914B1 (en) | Tapered roller bearing | |
JP5005209B2 (ja) | 円すいころ軸受 | |
US8123414B2 (en) | Tapered roller bearing | |
JP4975293B2 (ja) | 円錐ころ軸受 | |
CN100485207C (zh) | 锥形滚柱轴承 | |
JP2006022821A (ja) | 円すいころ軸受 | |
JP2007120577A (ja) | 円すいころ軸受 | |
JP4987278B2 (ja) | トランスミッション用円すいころ軸受 | |
JP2006022824A (ja) | デファレンシャル用円すいころ軸受 | |
JP2006022822A (ja) | 円すいころ軸受 | |
JP2007127220A (ja) | トランスミッション用円すいころ軸受 | |
JP2006022823A (ja) | トランスミッション用円すいころ軸受 | |
JP5031219B2 (ja) | 円すいころ軸受 | |
JP4994643B2 (ja) | 円すいころ軸受 | |
JP4994637B2 (ja) | ころ軸受 | |
JP2005351472A (ja) | 円すいころ軸受 | |
JP2007127219A (ja) | デファレンシャル用円すいころ軸受 | |
JP5031220B2 (ja) | 円すいころ軸受 | |
JP2007120575A (ja) | 円すいころ軸受 | |
JP4994636B2 (ja) | 円すいころ軸受 | |
JP2007085526A (ja) | 円すいころ軸受 | |
JP2007120648A (ja) | 円すいころ軸受 |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AK | Designated states |
Kind code of ref document: A1 Designated state(s): AE AG AL AM AT AU AZ BA BB BG BR BW BY BZ CA CH CN CO CR CU CZ DE DK DM DZ EC EE EG ES FI GB GD GE GH GM HR HU ID IL IN IS KE KG KP KR KZ LC LK LR LS LT LU LV MA MD MG MK MN MW MX MZ NA NI NO NZ OM PG PH PL PT RO RU SC SD SE SG SK SL SY TJ TM TN TR TT TZ UA UG US UZ VC VN YU ZA ZM ZW |
|
AL | Designated countries for regional patents |
Kind code of ref document: A1 Designated state(s): BW GH GM KE LS MW MZ NA SD SL SZ TZ UG ZM ZW AM AZ BY KG KZ MD RU TJ TM AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LU MC NL PL PT RO SE SI SK TR BF BJ CF CG CI CM GA GN GQ GW ML MR NE SN TD TG |
|
NENP | Non-entry into the national phase |
Ref country code: DE |
|
WWW | Wipo information: withdrawn in national office |
Ref document number: DE |
|
REEP | Request for entry into the european phase |
Ref document number: 2004799961 Country of ref document: EP |
|
WWE | Wipo information: entry into national phase |
Ref document number: 2004799961 Country of ref document: EP |
|
WWP | Wipo information: published in national office |
Ref document number: 2004799961 Country of ref document: EP |
|
WWE | Wipo information: entry into national phase |
Ref document number: 10581338 Country of ref document: US |
|
WWP | Wipo information: published in national office |
Ref document number: 10581338 Country of ref document: US |