WO2007132735A1 - 軸受装置 - Google Patents
軸受装置 Download PDFInfo
- Publication number
- WO2007132735A1 WO2007132735A1 PCT/JP2007/059680 JP2007059680W WO2007132735A1 WO 2007132735 A1 WO2007132735 A1 WO 2007132735A1 JP 2007059680 W JP2007059680 W JP 2007059680W WO 2007132735 A1 WO2007132735 A1 WO 2007132735A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- oil supply
- supply groove
- shaft member
- peripheral surface
- bearing device
- 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
- F16C33/02—Parts of sliding-contact bearings
- F16C33/04—Brasses; Bushes; Linings
- F16C33/06—Sliding surface mainly made of metal
- F16C33/10—Construction relative to lubrication
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C17/00—Sliding-contact bearings for exclusively rotary movement
- F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
-
- 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
- F16C33/02—Parts of sliding-contact bearings
- F16C33/04—Brasses; Bushes; Linings
- F16C33/06—Sliding surface mainly made of metal
- F16C33/10—Construction relative to lubrication
- F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
- F16C33/106—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid
- F16C33/1065—Grooves on a bearing surface for distributing or collecting the liquid
-
- 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
-
- 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
- F16C2240/90—Surface areas
-
- 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
- F16C2350/00—Machines or articles related to building
- F16C2350/26—Excavators
Definitions
- the present invention relates to a bearing device, and more particularly to a bearing device that is applied to various connecting parts in, for example, a construction civil machine and supports a shaft member so as to be relatively rotatable around its central axis. It is.
- a bearing device that supports a rod-shaped shaft member so as to be relatively rotatable around the center axis of the center axis is used.
- Such a bearing device has, for example, a cylindrical shape, and allows a shaft member to pass through a support hole formed therein to support the shaft member in a relatively rotatable manner.
- a thin oil film of lubricating oil supplied is formed between the outer peripheral surface of the shaft member and the inner peripheral surface of the support hole. That is, the shaft member rotates relatively through the oil film of the lubricating oil.
- the shaft member reciprocates at a predetermined angle at a low speed and with a high load.
- a large load is always applied in the sliding contact area (contact angle area) where the relative sliding speed with respect to the inner peripheral surface is extremely slow. Therefore, an oil film breakage locally occurs between the outer peripheral surface of the shaft member and the inner peripheral surface of the support hole, and seizure is likely to occur on the outer peripheral surface of the shaft member and the inner peripheral surface of the support hole.
- Patent Document 1 Japanese Patent Application Laid-Open No. 2004-84815
- the ratio of the area of the oil groove to the area of the inner peripheral surface of the support hole is 30% or more, and therefore, other than the oil groove in the support hole. That is, the ratio of the area of the sliding contact surface that is actually in contact with the outer peripheral surface of the shaft member becomes relatively small.
- the ratio of the area of the sliding contact surface becomes relatively small, the friction coefficient of the inner peripheral surface of the support hole will not be sufficiently small. If the friction coefficient is not sufficiently small, excessive torque is generated due to frictional resistance when the shaft member rotates relatively. For example, an unnecessarily large load is applied to the support member that supports the bearing device. This may cause damage to the support member and the like.
- improving the seizure resistance increases the friction coefficient, reducing the friction coefficient decreases the seizure resistance, and there is a contradictory relationship between the two.
- an object of the present invention is to provide a bearing device that can improve seizure resistance and friction coefficient that are in a mutually contradictory relationship.
- the bearing device allows the shaft member to pass through the formed support hole so that the shaft member can be relatively rotated around its central axis.
- an oil supply groove for supplying lubricating oil to the inner peripheral surface of the support hole slidingly contacting the shaft member when the shaft member rotates relatively is formed in a spiral shape.
- the ratio of the area of the oil supply groove portion to the area of the inner peripheral surface of the hole is 30% or less, and the distance in the central axis direction of the shaft member between the oil supply groove portions adjacent to each other on the inner peripheral surface of the support hole is The product of the distance in the circumferential direction is 50 mm 2 or more and 300 mm 2 or less.
- the bearing device according to claim 2 of the present invention is characterized in that, in claim 1 described above, the oil supply groove portion is formed as a multi-groove.
- the bearing device according to claim 3 of the present invention is the bearing device according to claim 1 or 2, wherein the oil supply groove portion has an inclination angle of 70 ° or more with respect to a central axis direction of the shaft member.
- the ratio of the area of the oil supply groove portion to the area of the inner peripheral surface of the support hole is 30% or less, and the shaft member between the oil supply groove portions adjacent to each other on the inner peripheral surface of the support hole is Since the product of the distance in the mandrel direction and the distance in the circumferential direction is 50 mm 2 or more and 300 mm 2 or less, it is possible to sufficiently secure the area of the portion other than the oil supply groove on the inner peripheral surface of the support hole. In addition, it is possible to stably supply the oil supply groove portion forces adjacent to each other and to prevent the occurrence of oil film breakage or the like. As a result, the seizure resistance can be ensured to be necessary and sufficient while the coefficient of friction is sufficiently small, and therefore the friction coefficient and seizure resistance, which are in a mutually contradictory relationship, are improved. It has the effect of being able to
- FIG. 1 is a longitudinal sectional view schematically showing the structure of a bearing device in an embodiment of the present invention.
- FIG. 2 is an enlarged cross-sectional view showing an enlarged end portion of the bearing device shown in FIG.
- FIG. 3 is an enlarged cross-sectional view showing an enlarged central portion of the periphery of the bearing device shown in FIG.
- FIG. 4 is an enlarged cross-sectional view showing the inner peripheral surface of the bearing device shown in FIG. 1 in an enlarged manner.
- FIG. 5 is a chart showing the friction coefficient when the ratio of the area of the oiling groove is changed.
- FIG. 6 is a chart showing changes in the friction coefficient and seizure surface pressure when the pressure receiving area is changed by changing the pitch between the oil supply grooves.
- FIG. 1 is a longitudinal sectional view schematically showing the structure of a bearing device according to an embodiment of the present invention.
- the bearing device illustrated here is a bush 10 applied to a connecting portion of a work machine that connects an arm and a packet mounted on an excavator that is a construction civil engineering machine.
- the bush 10 has a cylindrical shape and is not shown in the figure, but is fixedly supported on the inner periphery of the boss in a state of being press-fitted into a cylindrical boss fixedly supported at the tip of the arm. It is.
- the journal shaft 1 which is a rod-shaped shaft member, is passed through a support hole 11 formed inside.
- the journal shaft 1 has an outer diameter slightly smaller than the inner diameter (for example, 40 to 120 mm) of the support hole 11 and is fixedly supported between a pair of brackets of the packet, though not explicitly shown in the drawing.
- the journal shaft 1 rotates relative to the center of the axis about the central axis.
- the bush 10 supports the journal shaft 1 so as to be relatively rotatable about its central axis.
- the bush 10 supports the outer peripheral surface of the journal shaft 1.
- the inner peripheral surface of the hole 11 is in sliding contact.
- the bush 10 is made of a desired steel material standardized by JIS symbols, for example, high carbon steel or alloy steel.
- the surface hardness of the bush 10 may be 50 or more in terms of Rockwell hardness HRC, and is preferably 52 to 60 in terms of Rockwell hardness HRC.
- an inner tapered surface 12a and an outer tapered surface 12b are formed in the opening edge portion and the outer edge portion at both ends of the bush 10, respectively.
- the internal tapered surface 12a is formed to facilitate the insertion of the journal shaft 1.
- the outer tapered surface 12b is formed to facilitate press-fitting into the boss, and has a smaller gradient than the inner tapered surface 12a.
- a lubricating oil passage 13 is formed in the central portion of the outer peripheral surface of the bush 10 along the outer peripheral direction.
- Lubricating oil flow path 13 is a flow path for lubricating oil supplied to the inner peripheral surface of bush 10, and in this embodiment, for example, cutting
- the cross-sectional shape is formed in an arc shape by processing.
- a lubricating oil supply groove 15 and an oil supply groove 16 are formed on the inner peripheral surface of the bush 10 (support hole 11).
- the lubricating oil supply groove 15 is formed along the inner circumferential direction in a region corresponding to the lubricating oil flow path 13 in the central portion of the inner circumferential surface.
- the lubricating oil supply groove 15 communicates with the lubricating oil flow path 13 through the communication hole 14, and the groove width is slightly smaller than the lubricating oil flow path 13.
- the cross-sectional shape of the lubricating oil supply groove 15 is formed in an arc shape.
- the oil supply groove 16 is formed in a spiral shape from the lubricant supply groove 15 toward the opening edge portions at both ends. More specifically, the oil supply groove 16 is formed in a manner inclined at a predetermined angle with respect to the axial direction of the bush 10, that is, the central axis direction of the journal shaft 1.
- the oil supply groove 16 is formed as a multiple groove (for example, six grooves).
- the inclination angle ⁇ of the oil supply groove portion 16 is not particularly limited, but is preferably in the range of, for example, 70 ° to 80 °, and particularly preferably 75 °.
- the oil supply groove portion 16 supplies lubricating oil to the inner peripheral surface of the support hole 11.
- the oil supply groove portion 16 supplies the lubricating oil supplied to the lubricant oil supply groove portion 15 through the communication hole 14 to the support hole 11. It is intended to circulate and supply to the inner peripheral surface of the.
- the oil supply groove portion 16 is formed in an arc shape in cross section, and is smaller than the groove width of the lubricant oil supply groove portion 15. The groove width of the oil supply groove 16 will be described later.
- the inner peripheral surface of the bush 10 is subjected to a hardening treatment such as induction hardening after the oil supply groove portion 16 is formed.
- the ratio of the area of the oil supply groove portion 16 to the area of the inner peripheral surface of the support hole 11 (hereinafter also referred to as area ratio) is 30% or less, preferably 10% or more and 30%.
- the distance (a) in the central axis direction of the journal shaft 1 and the distance (c) in the circumferential direction between the oil supply groove portions 16 adjacent to each other on the inner peripheral surface of the support hole 11 are as follows.
- Product (a X c: hereinafter referred to as pressure receiving area) is 50 mm 2 or more and 300 mm 2 or less.
- FIG. 5 shows the friction coefficient when the ratio of the area of the oil supply groove is changed.
- the inner diameter of bush 10 is 70 mm. According to the figure, when the area ratio is 30% or less, the friction coefficient can be sufficiently reduced to 0.08 or less, whereas when the area ratio exceeds 30%, the friction coefficient can be increased. Understood.
- the area ratio is 30% or less and the pressure receiving area is 50 mm 2 or more and 300 mm 2 or less, the area other than the oil supply groove 16 on the inner peripheral surface of the support hole 11, that is, the journal shaft 1 It is possible to secure a sufficient area of the sliding contact surface that is actually in contact with the outer peripheral surface, and to suppress the occurrence of oil film breakage or the like by stably circulating and supplying the lubricating oil from the oil supply groove portions 16 adjacent to each other. As a result, the seizure resistance can be ensured to be necessary and sufficient while the coefficient of friction is sufficiently small. Therefore, with the above-mentioned bush 10, it is possible to improve the friction coefficient and seizure resistance, which are in a mutually contradictory relationship.
- FIG. 6 shows changes in the friction coefficient and seizure surface pressure when the pressure receiving area is changed by changing the pitch between the oil supply grooves.
- the inner diameter of the bush 10 was 70 mm
- the inclination angle ⁇ of the oil groove 16 was 75 °
- the area ratio of the oil groove 16 was 30% or less
- the swing angle of the bucket was 46 °.
- the seizure surface pressure was calculated as the load applied to the bush 10 divided by the projected area of the inner peripheral surface of the support hole 11.
- the seizing surface pressure can be ensured to a necessary and sufficient size while being small.
- the pressure receiving area is less than 50 mm 2, but seizure surface pressure becomes very large, the coefficient of friction resulting in large KuNatsu. More specifically, the friction coefficient becomes larger than 0.08.
- the friction coefficient is larger than 0.08, there is a possibility that the detent portion (such as a bracket) of the journal shaft 1 may be damaged.
- the pressure receiving area exceeds 300 mm 2
- the friction coefficient becomes sufficiently low casting, seizure surface pressure resulting in summer small. More specifically, the seizure surface pressure is 5k. becomes gZmm less than 2.
- the seizing surface pressure is less than 5 kgZmm 2 , seizing sites will occur under the working conditions of the construction machine.
- the groove width of the oil supply groove 16 is 3. Omm or less. Therefore, in the bush 10, the groove width of the oil supply groove portion 16 is preferably 3. Omm or less, particularly preferably 0.5 mm or more and 3. Omm or less. Thus, when the groove width of the oil supply groove portion 16 is 3. Omm or less, it is possible to ensure the seizure resistance to a necessary and sufficient level while keeping the friction coefficient sufficiently small.
- the oil supply groove portion 16 is formed as a multiple groove, but in the present invention, the oil supply groove portion may be formed as a single groove. Even with such a configuration, as long as the area ratio of the oil supply groove is in a specific range and the pressure receiving area is in a specific range, the same effects as those of the above-described embodiment can be achieved. Note that “between adjacent oil groove portions” when the oil groove portion is formed as a single groove means between adjacent oil groove portions in a predetermined region on the inner peripheral surface of the support hole.
- the cross-sectional shape of the oil supply groove portion 16 is an arc shape.
- the cross-sectional shape of the oil supply groove portion may be a triangular shape or a rectangular shape.
- the bush 10 applied to the connecting portion of the work machine that connects the arm and the packet provided to the excavator that is a construction civil engineering machine has been described as a bearing device.
- the bearing device in the present invention is not limited to the powerful bush 10 but can be applied to various connecting portions of various industrial machines.
- the bearing device according to the present invention is various in, for example, construction civil engineering machines. It is applied to the connecting portion and is useful for supporting the shaft member so as to be relatively rotatable about its central axis.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Oil, Petroleum & Natural Gas (AREA)
- Sliding-Contact Bearings (AREA)
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP07743115.3A EP2022993B1 (en) | 2006-05-17 | 2007-05-10 | Bearing unit |
CN2007800179363A CN101449069B (zh) | 2006-05-17 | 2007-05-10 | 轴承装置 |
US12/227,346 US8104966B2 (en) | 2006-05-17 | 2007-05-10 | Bearing device |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2006138069A JP2007309392A (ja) | 2006-05-17 | 2006-05-17 | 軸受装置 |
JP2006-138069 | 2006-05-17 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2007132735A1 true WO2007132735A1 (ja) | 2007-11-22 |
Family
ID=38693829
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2007/059680 WO2007132735A1 (ja) | 2006-05-17 | 2007-05-10 | 軸受装置 |
Country Status (6)
Country | Link |
---|---|
US (1) | US8104966B2 (ja) |
EP (1) | EP2022993B1 (ja) |
JP (1) | JP2007309392A (ja) |
KR (1) | KR20090025207A (ja) |
CN (1) | CN101449069B (ja) |
WO (1) | WO2007132735A1 (ja) |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2009024798A (ja) * | 2007-07-20 | 2009-02-05 | Hitachi Powdered Metals Co Ltd | すべり軸受 |
TWI425153B (zh) * | 2011-08-12 | 2014-02-01 | Topmag Technology Co Ltd | High lubrication performance of the bearing components |
CN107061498A (zh) * | 2017-02-27 | 2017-08-18 | 苏州市鑫渭机电修造有限公司 | 一种具有冷却功能的轴套 |
CN110608231A (zh) * | 2019-08-21 | 2019-12-24 | 嘉兴市中诚自润轴承有限公司 | 一种高承载耐磨衬套及其生产方法 |
DE102014201016B4 (de) | 2013-01-23 | 2022-07-14 | Kabushiki Kaisha Toyota Jidoshokki | Lager |
Families Citing this family (15)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP5455491B2 (ja) * | 2009-07-29 | 2014-03-26 | 大豊工業株式会社 | 軸受装置 |
US8075191B2 (en) | 2009-09-28 | 2011-12-13 | Honeywell International Inc. | Helical inner diameter groove journal bearing |
CN103511455A (zh) * | 2012-06-21 | 2014-01-15 | 襄阳汽车轴承股份有限公司 | 内径带螺旋槽的向心关节轴承 |
US8870461B2 (en) | 2012-11-14 | 2014-10-28 | Caterpiller Inc. | Bearing assembly |
FR2999671B1 (fr) * | 2012-12-13 | 2015-06-19 | Hydromecanique & Frottement | Organe de guidage sous forme d'une bague pour le montage avec frottement et avec capacite d'articulation et/ou de coulissement d'un element |
GB2508043B (en) | 2013-04-17 | 2015-07-22 | Messier Dowty Ltd | Dynamic bearing |
JP6193118B2 (ja) * | 2013-12-27 | 2017-09-06 | 三菱重工業株式会社 | 軸受装置及び粉砕装置 |
GB2527040B (en) * | 2014-06-09 | 2016-10-12 | Terex Gb Ltd | Liquid injection bush for rotary shafts |
JP6453029B2 (ja) * | 2014-10-10 | 2019-01-16 | 三菱日立パワーシステムズ株式会社 | 粉砕装置および粉砕装置の軸受部調整方法 |
JP6453028B2 (ja) * | 2014-10-10 | 2019-01-16 | 三菱日立パワーシステムズ株式会社 | 粉砕装置および粉砕装置の軸受用潤滑油置換方法 |
US9618039B2 (en) * | 2015-02-03 | 2017-04-11 | Caterpillar Inc. | Sleeve bearing with lubricant reservoirs |
CN106050922B (zh) * | 2016-07-04 | 2018-08-14 | 浙江大学 | 自循环式的滑动轴承 |
EP3712451A4 (en) * | 2017-11-15 | 2021-10-13 | Diamet Corporation | OIL IMPREGNATED SINTER BEARING AND PROCESS FOR THE PRODUCTION OF THE SAME |
US11396344B2 (en) * | 2018-10-26 | 2022-07-26 | Fox Factory, Inc. | Bushing bypass |
CN111042912A (zh) * | 2019-12-18 | 2020-04-21 | 马双斌 | 高性能长效增压器 |
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JP2004060757A (ja) * | 2002-07-29 | 2004-02-26 | Enomoto Co Ltd | 摺動用ブッシュ |
JP2004084815A (ja) | 2002-08-27 | 2004-03-18 | Komatsu Ltd | 軸受装置 |
JP2006009846A (ja) * | 2004-06-23 | 2006-01-12 | Hitachi Powdered Metals Co Ltd | 高荷重用すべり軸受 |
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US1961029A (en) * | 1931-08-18 | 1934-05-29 | Elek K Benedek | Self-cooling high pressure lubricant film bearing |
US2249843A (en) * | 1940-04-23 | 1941-07-22 | Maud Lois Marsland | Lubrication apparatus |
DE3600721A1 (de) * | 1986-01-13 | 1987-07-16 | Balcke Duerr Ag | Lageranordnung |
US4960202A (en) * | 1987-01-14 | 1990-10-02 | Ingersoll-Rand Company | Friction control for bearing surface of roller |
JP3185433B2 (ja) * | 1992-12-29 | 2001-07-09 | オイレス工業株式会社 | 内周面に固体潤滑剤を埋設固定した円筒状軸受 |
JP3599886B2 (ja) * | 1996-03-08 | 2004-12-08 | 日立粉末冶金株式会社 | 動圧スラスト多孔質軸受 |
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2006
- 2006-05-17 JP JP2006138069A patent/JP2007309392A/ja active Pending
-
2007
- 2007-05-10 KR KR1020087027401A patent/KR20090025207A/ko not_active Application Discontinuation
- 2007-05-10 CN CN2007800179363A patent/CN101449069B/zh not_active Expired - Fee Related
- 2007-05-10 WO PCT/JP2007/059680 patent/WO2007132735A1/ja active Application Filing
- 2007-05-10 EP EP07743115.3A patent/EP2022993B1/en not_active Expired - Fee Related
- 2007-05-10 US US12/227,346 patent/US8104966B2/en not_active Expired - Fee Related
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
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JP2004060757A (ja) * | 2002-07-29 | 2004-02-26 | Enomoto Co Ltd | 摺動用ブッシュ |
JP2004084815A (ja) | 2002-08-27 | 2004-03-18 | Komatsu Ltd | 軸受装置 |
JP2006009846A (ja) * | 2004-06-23 | 2006-01-12 | Hitachi Powdered Metals Co Ltd | 高荷重用すべり軸受 |
Non-Patent Citations (1)
Title |
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See also references of EP2022993A4 * |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2009024798A (ja) * | 2007-07-20 | 2009-02-05 | Hitachi Powdered Metals Co Ltd | すべり軸受 |
TWI425153B (zh) * | 2011-08-12 | 2014-02-01 | Topmag Technology Co Ltd | High lubrication performance of the bearing components |
DE102014201016B4 (de) | 2013-01-23 | 2022-07-14 | Kabushiki Kaisha Toyota Jidoshokki | Lager |
CN107061498A (zh) * | 2017-02-27 | 2017-08-18 | 苏州市鑫渭机电修造有限公司 | 一种具有冷却功能的轴套 |
CN110608231A (zh) * | 2019-08-21 | 2019-12-24 | 嘉兴市中诚自润轴承有限公司 | 一种高承载耐磨衬套及其生产方法 |
Also Published As
Publication number | Publication date |
---|---|
EP2022993A1 (en) | 2009-02-11 |
CN101449069A (zh) | 2009-06-03 |
EP2022993B1 (en) | 2013-08-21 |
CN101449069B (zh) | 2011-02-09 |
JP2007309392A (ja) | 2007-11-29 |
US8104966B2 (en) | 2012-01-31 |
US20090268996A1 (en) | 2009-10-29 |
EP2022993A4 (en) | 2012-03-07 |
KR20090025207A (ko) | 2009-03-10 |
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