WO2005093273A1 - 自動調心ころ軸受 - Google Patents
自動調心ころ軸受 Download PDFInfo
- Publication number
- WO2005093273A1 WO2005093273A1 PCT/JP2005/006529 JP2005006529W WO2005093273A1 WO 2005093273 A1 WO2005093273 A1 WO 2005093273A1 JP 2005006529 W JP2005006529 W JP 2005006529W WO 2005093273 A1 WO2005093273 A1 WO 2005093273A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- outer ring
- roller bearing
- view
- flange
- self
- 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
- F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
- F16C23/06—Ball or roller bearings
- F16C23/08—Ball or roller bearings self-adjusting
- F16C23/082—Ball or roller bearings self-adjusting by means of at least one substantially spherical surface
- F16C23/086—Ball or roller bearings self-adjusting by means of at least one substantially spherical surface forming a track for 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
- 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
- F16C33/4682—Details of individual pockets, e.g. shape or roller retaining means of the end walls, e.g. interaction with the end faces of the rollers
-
- 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
- F16C33/54—Cages for rollers or needles made from wire, strips, or sheet metal
- F16C33/542—Cages for rollers or needles made from wire, strips, or sheet metal made from sheet metal
- F16C33/543—Cages for rollers or needles made from wire, strips, or sheet metal made from sheet metal from a single part
-
- 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
- F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
- F16C33/6681—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
- 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
- F16C19/38—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 two or more rows of rollers
-
- 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
- F16C33/48—Cages for rollers or needles for multiple rows of rollers or needles
- F16C33/485—Cages for rollers or needles for multiple rows of rollers or needles with two or more juxtaposed cages joined together or interacting with each other
Definitions
- the present invention relates to a self-aligning roller bearing that is incorporated in various types of machinery and supports a relatively heavy rotating shaft.
- FIG. 10 is a cross-sectional view of a conventional spherical roller bearing.
- Fig. 11A is an enlarged cross-sectional view of the cage shown in Fig. 10 (cross-sectional view along the line XIa-XIa in Fig. 13).
- Fig. 11B is a circle of Fig. 11A. It is an expanded sectional view of the part b enclosed with.
- FIG. 12A is a view of the arrow XII in FIG. 11A
- FIG. 12 1 is an enlarged view of a portion C surrounded by a circle in FIG. 12 ⁇ .
- FIG. 13 is a view of the arrow XIII in FIG. 11A.
- the S spherical roller bearing holds an outer ring 1, an inner ring 2, two rows of spherical rollers 3, 3 arranged between these outer and inner rings, and spherical rollers 3, 3, It is composed of cages 4 and 4.
- the outer race 1 has a single arc-shaped raceway surface 5 on the inner periphery.
- the inner race 2 has an inner periphery fixed to a rotating shaft (not shown), and two arc-shaped race surfaces 6, 6 facing the race surface 5 of the outer race 1 on its outer periphery. It is formed at a predetermined interval in the center. ,
- the retainer 4 includes an extending portion 7 extending substantially in the axial direction of the spherical roller 3, an extending portion 8 extending radially inward on the outside in the axial direction, and a flange 9 extending radially outward in the central portion in the bearing axial direction. (Central part) and are integrated.
- a pair of protrusions 10, 10 are formed on one side surface of the flange 9 so as to be circumferentially separated from each other.
- the pair of projections 10, 10 have their tip end surfaces at the head of one spherical roller 3, that is, at the end face inside the bearing of the spherical roller 3, preferably at the portion from the center of the end face to the bearing outer ring side
- the attitude of the spherical roller 3 is controlled to prevent the skew of the spherical roller 3.
- the protruding portion 10 is formed by press working by pressing from the back side.
- Dmin indicates the minimum inner diameter of the outer ring
- Dmax indicates the maximum outer diameter of the flange 9.
- FIG. 20 is a cross-sectional view of a conventional spherical roller bearing.
- FIG. 21 is an enlarged cross-sectional view of the cage shown in FIG. 20 (cross-sectional view taken along line XXI—; XI in FIG. 24).
- FIG. 22A is an enlarged sectional view of a portion XXIIa surrounded by a circle in FIG. 21.
- FIG. 22B is an enlarged sectional view in which these flanges are arranged to face each other as shown in FIG. .
- FIG. 23A is an arrow view of arrow XXIIIa in FIG. 21, and FIG. 23B is an enlarged view of a portion b surrounded by a circle in FIG. 23A.
- FIG. 24 is a view of the arrow XXIV in FIG. 21.
- the spherical roller bearings shown in FIGS. 20 to 24 have the same basic structure as those shown in FIGS. 10 to 13 described above, and only the differences will be described.
- lubrication is performed through an oil hole 12 drilled in the center of the outer ring 1 in the radial direction to lubricate the bearing.
- the "circulation refueling method" is adopted.
- a recess 11 is provided on the back side of the projection 10 formed by press working. As shown in FIG. 22B, the lubricant can flow from the oil hole 12 of the outer ring 1 between the pair of recesses 11 1, 11. However, the pair of recesses 11 and 11 do not penetrate from the outer diameter side to the inner diameter side.
- the present invention has been made in view of the above-described circumstances, and when a spherical roller is to be skewed, the attitude of the spherical roller is controlled more stably, skew is reliably prevented, and a bearing is provided. It is an object of the present invention to provide a self-aligning roller bearing that can reduce heat generation and wear during rotation and extend the life.
- a self-aligning roller bearing capable of performing the above-described operations.
- a self-aligning roller bearing according to a first aspect of the present invention includes: an outer ring having an arc-shaped orbit on an inner periphery;
- An inner ring having a raceway surface arranged on the outer periphery so as to face the inner raceway surface of the outer ring; two rows of spherical rollers interposed between the inner raceway surface of the outer ring and the outer raceway surface of the inner ring;
- a spherical roller bearing consisting of a cage that holds a row of spherical rollers and
- the flange of the cage is provided with a large-area protrusion on the head side of the spherical roller.
- the protrusion is formed by press working.
- the protrusion is formed in a petal shape protruding to the outer diameter side by punching the material into a petal shape at the time of press punching. .
- the cage when the flange maximum diameter of the cage is larger than the minimum inner diameter of the outer ring, the cage partially covers the flange maximum diameter portion.
- it is formed in a shaved shape.
- a self-aligning roller bearing includes: an outer race having an arc-shaped orbit on an inner periphery;
- An inner ring having a raceway surface arranged on the outer periphery so as to face the inner raceway surface of the outer ring
- the flange of the retainer has a protrusion on the head side of the spherical roller
- the concave portion formed on the back surface of the projection communicates with the oil hole of the outer ring, and penetrates from the outer diameter side to the inner diameter side.
- the protrusion or the recess is formed by press working.
- the flange of the cage is provided with the projection having a large area on the head side of the spherical roller, the flange comes into sliding contact (contact) with the head of the spherical roller.
- the posture of the spherical roller can be controlled more stably, thereby preventing the skew reliably and generating heat during bearing rotation. Wear can be reduced and the service life can be extended.
- the recess formed on the rear surface of the protrusion communicates with the oil hole of the outer ring and penetrates from the outer diameter side to the inner diameter side, it is supplied from the oil hole of the outer ring.
- the lubricant can be stably supplied to the raceway surface of the inner ring through the penetrating portion of the recess, thereby further improving lubrication performance and reducing heat generation and wear during bearing rotation.
- the service life can be extended.
- FIG. 1 is a cross-sectional view of a spherical roller bearing according to a first embodiment of the present invention.
- Fig. 2A is an enlarged cross-sectional view of the cage shown in Fig. 1 (a cross-sectional view along the line IIa-IIa in Fig. 3B).
- Fig. 2B is a circled part b in Fig. 2A.
- It is an expanded sectional view of. 3A is a view of arrow IIIa in FIG. 2A
- FIG. 3B is a view of arrow II lb in FIG. 2A
- FIG. 3C is a circle of FIG. 3A.
- FIG. 4 is a schematic view of the cage shown in FIG.
- FIG. 5 is a cross-sectional view of a spherical roller bearing according to a second embodiment of the present invention.
- Fig. 6A is an enlarged cross-sectional view of the cage shown in Fig. 5 (cross-sectional view along the line VIa- VIa in Fig. 7B), and Fig. 6B is a circled part b in Fig. 6A.
- It is an expanded sectional view of. 7A is a view of arrow VIIa of FIG. 6A
- FIG. 7B is a view of arrow VI lb of FIG. 6A
- FIG. 7C is a circle of FIG. 7A.
- FIG. 8 is a schematic diagram of a blank press-cut shape of the cage.
- FIG. 9 is a schematic diagram of the cage shown in FIG.
- FIG. 10 is a cross-sectional view of a conventional spherical roller bearing.
- Fig. 11A is an enlarged cross-sectional view of the cage shown in Fig. 10 (cross-sectional view along line XIa-XIa in Fig. 13).
- Fig. 11B is circled in Fig. 11A. It is an expanded sectional view of the part b. .
- FIG. 12A is a view on arrow XII of FIG. 11A
- FIG. 12B is an enlarged view of a portion c surrounded by a circle in FIG. 12A.
- FIG. 13 is a view of arrow XIII in FIG. 11A.
- FIG. 14 is a sectional view of a spherical roller bearing according to a third embodiment of the present invention.
- FIG. 15 is an enlarged cross-sectional view (a cross-sectional view taken along line XV-XV in FIG. 18) of the cage shown in FIG.
- FIG. 16A is an enlarged sectional view of a portion XVIa surrounded by a circle in FIG. 15>
- FIG. 16B is an enlarged sectional view in which flanges are arranged to face each other as shown in FIG.
- FIG. 17A is an arrow view of arrow XVIIa in FIG. 15
- FIG. 17B is an enlarged cross-sectional view in which flanges are arranged to face each other as shown in FIG. 14, and
- FIG. 17 is an enlarged view of a portion c surrounded by a circle of 17 A.
- FIG. 18 is a view of the arrow XVIII in FIG.
- FIG. 19 is a cross-sectional view (a cross-sectional view along the line XIX—XIX of FIG. 18) of the spherical roller bearing according to the third embodiment of the present invention.
- FIG. 20 is a cross-sectional view of a conventional spherical roller bearing.
- FIG. 21 is an enlarged cross-sectional view of the cage shown in FIG. 20 (cross-sectional view along the line XXI—XXI in FIG. 24).
- FIG. 22A is an enlarged sectional view of a part XXIIa surrounded by a circle in FIG. 21, and FIG. 22B is an enlarged sectional view in which these flanges are arranged to face each other as shown in FIG.
- FIG. 23A is a view of arrow XXIIIa in FIG. 21 and FIG. FIG. 3 is an enlarged view of a portion b surrounded by a circle A.
- FIG. 24 is a view of the arrow XXIV in FIG. 21. BEST MODE FOR CARRYING OUT THE INVENTION
- FIG. 1 is a cross-sectional view of a spherical roller bearing according to a first embodiment of the present invention.
- Fig. 2A is an enlarged cross-sectional view of the cage shown in Fig. 1 (a cross-sectional view along the line IIa-IIa in Fig. 3B).
- Fig. 2B is a circled part b in Fig. 2A.
- It is an expanded sectional view of. 3A is a view of arrow I lia in FIG. 2A
- FIG. 3B is a view of arrow II lb in FIG. 2A
- FIG. 3C is a circle of FIG. 3A. It is an enlarged view of the part c.
- FIG. 4 is a schematic view of the cage shown in FIG.
- the self-aligning roller bearing includes an outer ring 1, an inner ring 2, two rows of spherical rollers 3, 3 arranged between the outer and inner rings, and a cage 4 for holding the spherical rollers 3, 3. , 4 and.
- the outer race 1 has a single arc-shaped raceway surface 5 on the inner periphery.
- the inner race 2 has an inner periphery fixed to a rotating shaft (not shown), and two arc-shaped race surfaces 6, 6 facing the race surface 5 of the outer race 1 on its outer periphery. It is formed at a predetermined interval in the center.
- Two rows of spherical rollers 3, 3 are interposed between the raceway surface 5 of the outer ring 1 and the raceway surfaces 6, 6 of the inner ring 2, respectively. These two rows of spherical rollers 3, 3 are held by cages 4, 4, respectively.
- Each retainer 4 has an extension 7 extending substantially in the axial direction of the spherical roller 3, an extension 8 extending radially inward on the outside in the axial direction, and extending radially outward in a central portion in the bearing axial direction. It has a flange 9 (center) and.
- the maximum diameter Dmax of the flange 9 is larger than that of the conventional technique as shown in FIG.
- the maximum diameter Dm'ax of the flange 9 may be larger than the minimum inner diameter Dmin of the outer ring 1.
- one protrusion 20 per spherical roller having a large area is provided on one side of the increased diameter flange 9 in the circumferential direction. It is formed so as to extend.
- the protruding portion 20 having a large area has a tip end surface at the head of one spherical roller 3 (in the present specification, the head of the spherical roller 3 refers to the inner end surface of the spherical roller 3 in the bearing).
- the spherical roller 3 skews during rotation by controlling the attitude of the spherical roller 3 when the spherical roller 3 skews during rotation. Has been prevented. '
- the projecting portion 20 having a large area is formed by press working from the back side thereof.
- the flange 9 of the cage 4 has a large-area protrusion 20 near the head of the spherical roller 3, the sliding portion (contact) with the head of the spherical roller 3 increases.
- the posture of the spherical roller 3 can be controlled more stably, thereby reliably preventing skew and reducing heat generation and wear during bearing rotation. As a result, the service life can be extended.
- the maximum diameter Dmax of the flange 9 of the cage 4 must be basically smaller than the minimum inner diameter Dmin of the outer ring 1 in terms of bearing assembly.
- the maximum diameter Dmax of the flange 9 is larger than the minimum diameter Dmin of the outer ring 1.
- the maximum diameter portion of the flange 9 is partly cut away, that is, for example, two truncated projections that are diametrically opposed are notched at the tops, and the truncated projections 120 a, 12 0b, these truncated notches 1 2 0a, 1 If the distance L between the tops of 20 b is less than the minimum inner diameter Dmin of the outer ring 1 (L ⁇ Dmin), it is possible to assemble the bearing at right angles.
- the symmetrical position of only one protrusion 20 or two protrusions facing in the? G direction may be reduced. Even if the outer ring 1 is not deformed as described above, if the outer ring 1 is elastically deformed, it is possible to assemble the bearing at right angles.
- FIG. 5 is a sectional view of a spherical roller bearing according to a second embodiment of the present invention.
- Fig. 6A is an enlarged cross-sectional view of the cage shown in Fig. 5 (cross-sectional view along the line Via-Via in Fig. 7B), and Fig. 6B is a part b encircled in Fig. 6A.
- It is an expanded sectional view of. 7A is a view of arrow VI la in FIG. 6A
- FIG. 7B is a view of arrow VI lb in FIG. 6A
- FIG. 7C is a circle in FIG. 7A.
- FIG. 8 is a schematic diagram of a blank press-cut shape of the cage.
- FIG. 9 is a schematic diagram of the cage shown in FIG.
- This embodiment has the same basic structure as the above-described first embodiment, and only different points will be described.
- the protrusions 20 are formed in a petal shape protruding toward the outer diameter side by punching the material into a petal shape during press punching. As a result, the pressed surface can be reduced, and the pressing force can be reduced.
- the protrusion 20 has a petal shape protruding toward the outer diameter side.
- the maximum diameter Dma of the flange 9 is larger than the minimum inner diameter Dmin of the outer ring 1. I have. That is, the maximum diameter of the protrusion 20 is larger than that of the first embodiment.
- the bearing is assembled by partially shaving the maximum diameter portion of the flange 9 as shown in FIG.
- the top of each of the two protrusions is shaved to form truncated protrusions 120a and 120b, and the distance L between the tops of these truncated cutouts 120a and 120b is defined as the outer ring 1 of If the minimum inner diameter is less than Dmin (L ⁇ Dmin), it is possible to assemble the bearing at right angles. Note that, depending on the size, it is only necessary to cut off only one protrusion 20 or the symmetrical position of the pair of protrusions 20 facing in the radial direction.
- the flange 9 of the cage 4 is provided with the projection 20 having a large area on the head side of the spherical roller 3, and the maximum diameter of the projection 20 is
- the force that is larger than that of the first embodiment increases the portion that slides or touches the head of the spherical roller 3, and when the spherical roller 3 is skewed, the attitude of the spherical roller 3 Can be more stably controlled, thereby reliably preventing skew, reducing heat generation and wear during bearing rotation, and extending the life.
- FIG. 14 is a sectional view of a spherical roller bearing according to a third embodiment of the present invention.
- FIG. 15 is an enlarged cross-sectional view (a cross-sectional view taken along line XV-XV in FIG. 18) of the cage shown in FIG.
- FIG. 16A is an enlarged sectional view of a portion XVIa surrounded by a circle in FIG. 15, and FIG. 16B is an enlarged sectional view in which flanges are arranged to face each other as shown in FIG.
- FIG. 17A is an arrow view of arrow XVIIa in FIG. 15, and FIG. 17B is an enlarged sectional view in which the flanges are arranged to face each other as shown in FIG. C is an enlarged view of a portion c surrounded by a circle in FIG. 17A.
- FIG. 18 is a view of the arrow XVIII in FIG. 15.
- FIG. 19 is a cross-sectional view (a cross-sectional view along the line XIX—XIX of FIG. 18) of the spherical roller bearing according to the third embodiment of the present invention.
- This embodiment has the same basic structure as the above-described first embodiment, and only different points will be described.
- an oil hole 1 2 is formed in the center of the outer ring 1 in a radial direction in order to lubricate the bearing.
- the “circulation refueling method” is used for refueling.
- a pair of projections 30 having a large area are formed so as to be circumferentially separated from each other.
- a recess 31 is provided on the back side of the projection 30 formed by press working. As shown in FIG. 19, between the pair of recesses 31, 31, the lubricant can flow from the oil hole 12 of the outer ring 1.
- the pair of recesses 31 and 31 penetrate from the outer diameter side to the inner diameter side.
- the pair of recesses 31, 31 formed on the back surface of the projection 30 communicate with the oil hole 12 of the outer ring 1 and also, from the outer diameter side to the inner diameter side.
- the lubricant supplied from the oil hole 12 of the outer ring 1 can be stably supplied to the raceway surface of the inner ring 2 through the pair of recesses 31 and 31.
- lubrication performance can be further improved, heat generation and wear during bearing rotation can be reduced, and the life can be extended.
- the surface area of the projection 30 is larger than that of the related art (FIG. 20, etc.). . Therefore, since the flange 9 of the cage 4 is provided with a large-area projection 30 on the head side of the spherical roller 3, the portion that comes into contact with or comes into contact with the head of the spherical roller 3 increases. When the spherical roller 3 is about to skew, the attitude of the spherical roller 3 can be controlled more stably, thereby reliably preventing skew and reducing heat generation and wear during bearing rotation. As a result, the service life can be extended.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Rolling Contact Bearings (AREA)
- Support Of The Bearing (AREA)
Abstract
Description
Claims
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2006511612A JPWO2005093273A1 (ja) | 2004-03-26 | 2005-03-28 | 自動調心ころ軸受 |
EP05727503A EP1741944A1 (en) | 2004-03-26 | 2005-03-28 | Self-aligning roller bearing |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2004-092988 | 2004-03-26 | ||
JP2004092988 | 2004-03-26 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2005093273A1 true WO2005093273A1 (ja) | 2005-10-06 |
Family
ID=35056258
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2005/006529 WO2005093273A1 (ja) | 2004-03-26 | 2005-03-28 | 自動調心ころ軸受 |
Country Status (4)
Country | Link |
---|---|
EP (1) | EP1741944A1 (ja) |
JP (1) | JPWO2005093273A1 (ja) |
CN (1) | CN1938525A (ja) |
WO (1) | WO2005093273A1 (ja) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2010007979A1 (ja) * | 2008-07-18 | 2010-01-21 | Ntn株式会社 | 打抜き保持器、自動調心ころ軸受、及び打抜き保持器の製造方法 |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US9033585B2 (en) * | 2013-05-07 | 2015-05-19 | Baldor Electric Company | Spherical roller bearing cage with inward flange turned radially outward |
WO2015070146A1 (en) * | 2013-11-11 | 2015-05-14 | The Timken Company | Bearing cage and assembly with lubrication stimulant |
JP2018179078A (ja) * | 2017-04-07 | 2018-11-15 | 株式会社ジェイテクト | 自動調心ころ軸受 |
DE102019204973A1 (de) * | 2019-04-08 | 2020-10-08 | Aktiebolaget Skf | Pendelrollenlager |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH02180314A (ja) * | 1988-11-14 | 1990-07-13 | Skf:Ab | ころ軸受用保持器 |
JPH034019A (ja) * | 1989-05-20 | 1991-01-10 | Skf Gmbh | 複列自動調心ころ軸受 |
JPH08296653A (ja) | 1995-04-26 | 1996-11-12 | Nippon Seiko Kk | 保持器付自動調心ころ軸受 |
JPH09166144A (ja) * | 1996-11-08 | 1997-06-24 | Koyo Seiko Co Ltd | ころ軸受用保持器の製作方法 |
JP2000081036A (ja) * | 1998-09-07 | 2000-03-21 | Nippon Seiko Kk | 自動調心ころ軸受 |
-
2005
- 2005-03-28 WO PCT/JP2005/006529 patent/WO2005093273A1/ja active Application Filing
- 2005-03-28 CN CNA2005800097862A patent/CN1938525A/zh active Pending
- 2005-03-28 EP EP05727503A patent/EP1741944A1/en not_active Withdrawn
- 2005-03-28 JP JP2006511612A patent/JPWO2005093273A1/ja not_active Withdrawn
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH02180314A (ja) * | 1988-11-14 | 1990-07-13 | Skf:Ab | ころ軸受用保持器 |
JPH034019A (ja) * | 1989-05-20 | 1991-01-10 | Skf Gmbh | 複列自動調心ころ軸受 |
JPH08296653A (ja) | 1995-04-26 | 1996-11-12 | Nippon Seiko Kk | 保持器付自動調心ころ軸受 |
JPH09166144A (ja) * | 1996-11-08 | 1997-06-24 | Koyo Seiko Co Ltd | ころ軸受用保持器の製作方法 |
JP2000081036A (ja) * | 1998-09-07 | 2000-03-21 | Nippon Seiko Kk | 自動調心ころ軸受 |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2010007979A1 (ja) * | 2008-07-18 | 2010-01-21 | Ntn株式会社 | 打抜き保持器、自動調心ころ軸受、及び打抜き保持器の製造方法 |
Also Published As
Publication number | Publication date |
---|---|
EP1741944A1 (en) | 2007-01-10 |
JPWO2005093273A1 (ja) | 2008-02-14 |
CN1938525A (zh) | 2007-03-28 |
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