WO2010047213A1 - 転がり軸受および回転軸支持構造 - Google Patents
転がり軸受および回転軸支持構造 Download PDFInfo
- Publication number
- WO2010047213A1 WO2010047213A1 PCT/JP2009/067059 JP2009067059W WO2010047213A1 WO 2010047213 A1 WO2010047213 A1 WO 2010047213A1 JP 2009067059 W JP2009067059 W JP 2009067059W WO 2010047213 A1 WO2010047213 A1 WO 2010047213A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- outer ring
- rolling bearing
- resin retaining
- ring
- outer diameter
- Prior art date
Links
Images
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
- F16C33/58—Raceways; Race rings
- F16C33/60—Raceways; Race rings divided or split, e.g. comprising two juxtaposed 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
- F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
- F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
- F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
- F16C35/07—Fixing them on the shaft or housing with interposition of an element
- F16C35/077—Fixing them on the shaft or housing with interposition of an element between housing and outer race ring
-
- 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
- F16C43/00—Assembling bearings
- F16C43/04—Assembling rolling-contact 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
- 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
- F16C19/44—Needle bearings
- F16C19/46—Needle bearings with one row or needles
- F16C19/466—Needle bearings with one row or needles comprising needle rollers and an outer ring, i.e. subunit without inner ring
Definitions
- the present invention relates to a rolling bearing and a rotating shaft support structure, and more particularly to a rolling bearing and a rotating shaft support structure used in an environment with a large temperature change.
- Needle bearings composed of an outer ring, needle rollers and a cage can receive a heavy load and have high rigidity despite a small bearing projection area. Therefore, taking advantage of such characteristics, it is effectively used as a bearing for supporting automobile parts, particularly a crankshaft of an automobile engine. Bearings for automobile engines are used in a wide range of temperature environments from cold times around -30 ° C to operating times around 150 ° C.
- FIG. 10 is a view of a conventional crankshaft support structure as seen from the direction of the rotation axis of the crankshaft.
- 11 is a cross-sectional view of a part of the crankshaft support structure shown in FIG. 10 taken along the IX-IX cross section in FIG.
- the rotation axis direction of the crankshaft is the front and back direction of the paper. From the viewpoint of easy understanding, FIG. 10 shows a state in which a part of the crankshaft support structure is disassembled.
- a crankshaft support structure 101 includes a crankshaft 102, a rolling bearing 103 that supports the crankshaft 102, and an engine block 104 to which the rolling bearing 103 is attached.
- the rolling bearing 103 includes an outer ring 106, a plurality of rollers 107, and a cage 108 that holds the plurality of rollers.
- the outer ring 106 can be divided into two divided outer ring parts 109a and 109b.
- the cage 108 can also be divided into two divided cage parts 110a and 110b.
- the engine block 104 can be divided into two divided engine block parts 105a and 105b.
- the rolling bearing 103 is attached to the engine block 104 by fastening the divided engine block parts 105a and 105b with bolts (not shown) with the rolling bearing 103 interposed therebetween.
- the radial clearance i.e., the radial gap is provided as shown by dimension X 1 in FIG. 11.
- the roller 107 can be smoothly rolled.
- interference Y 1 is provided, thereby, in the interference fit to the rolling bearing 103, to prevent creep of the outer ring 106.
- the radial gap and the tightening allowance are exaggerated and greatly illustrated from the viewpoint of easy understanding.
- an aluminum alloy is generally used from the viewpoint of weight reduction.
- steel is used for the material of the outer ring 106 of the crankshaft 102 and the rolling bearing 103 from the viewpoint of ensuring rigidity.
- crankshaft support structure 101 having the above-described configuration is used in various environments such as a high temperature environment and a low temperature environment.
- thermal expansion coefficients of the components that constitute the crankshaft support structure 101 are different, there is a possibility that the dimensions X 1 and interference Y 1 of the radial gap is not properly maintained.
- FIG. 12 is a cross-sectional view showing a part of the crankshaft support structure 101 in a high temperature environment, specifically, around 150 ° C., and corresponds to FIG.
- FIG. 13 is a cross-sectional view showing a part of the crankshaft support structure 101 in a low temperature environment, specifically, around ⁇ 30 ° C., and corresponds to FIG.
- FIG. 11 is a cross-sectional view showing a part of the crankshaft support structure 101 in a room temperature environment, specifically, around 20 ° C.
- the thermal expansion coefficient of the aluminum alloy that is the material of engine block 104 is larger than the thermal expansion coefficient of the steel that is the material of crankshaft 102 and outer ring 106. Therefore, in high temperature environments, it is necessary to configure to be able to ensure interference Y 2 in an appropriate amount. However, when configured in this manner, the interferences Y 1 and Y 3 become too large in a normal temperature environment and a low temperature environment, and the assemblability deteriorates. Further, there is a possibility that becomes also negative dimension X 3 of the radial gap in a low-temperature environment. Such a situation not only makes it difficult to start the engine including the crankshaft support structure 101, but also may cause seizure and galling.
- Patent Document 4 the noise and vibration of the rolling bearing 103 are reduced by an oil film formed by an oil seal.
- the oil seal is exposed to high-temperature engine oil for a long period of time, the sealing performance may be impaired. As a result, noise and vibration cannot be reduced.
- An object of the present invention is to provide a rolling bearing that has good productivity and ease of integration, can reduce noise and vibration, and can reduce seizure and galling.
- Another object of the present invention is to provide a rotating shaft support structure that has good bearing productivity and ease of assembly, reduces noise and vibration, and can reduce seizure and galling.
- the rolling bearing according to the present invention includes an outer ring formed by arranging a plurality of divided outer ring parts in the circumferential direction, a plurality of rollers rolling on the raceway surface of the outer ring, and a circumferential direction of the annular member so as to form a clearance. And a resin retaining ring that is disposed on the outer diameter side of the outer ring so as to be in contact with the outer ring and restricts the movement of the plurality of divided outer ring parts in the radial direction.
- the split outer ring part is arranged from the outer diameter side of the rotating shaft to form the outer ring, and the resin retaining ring having a shape in which one place in the circumferential direction of the annular member is cut so as to form a gap. It can be elastically deformed and arranged from the outer diameter side to incorporate a rolling bearing. If it does so, embedding property can be made favorable. In this case, the movement of the split outer ring part in the radial direction can be restricted by the resin retaining ring, and separation of the outer ring can be prevented. If it does so, since it does not give a special process to an outer ring
- the rolling bearing can improve the assemblability and productivity, reduce noise and vibration, and reduce seizure and galling.
- the outer diameter dimension of the resin retaining ring is larger than the outer diameter dimension of the outer ring.
- a resin retaining ring can be interposed between the outer ring and the housing or the like disposed on the outer diameter side of the outer ring at room temperature, preventing creep of the outer ring during rotation, Vibration can be further reduced.
- the relationship is 0 ⁇ D 1 ⁇ 0.4D 2 where the circumferential length of the gap is D 1 and the outer diameter of the outer ring is D 2 at room temperature.
- the cross section of the resin retaining ring when the resin retaining ring is cut in a direction perpendicular to the rotation axis is substantially C-shaped.
- the cross section when the resin retaining ring is cut in the circumferential direction is rectangular.
- a plurality of resin retaining rings are provided in the axial direction. By doing so, it is possible to more reliably prevent the outer ring from being separated.
- a groove portion recessed radially inward is provided on the outer diameter surface of the outer ring, and the resin retaining ring is disposed so as to be fitted into the groove portion.
- a rotating shaft support structure includes a rotating shaft, a rolling bearing described in any of the above-described embodiments that supports the rotating shaft, and a housing disposed on the outer diameter side of the rolling bearing.
- Such a rotating shaft support structure has good bearing productivity and ease of integration, and can reduce noise and vibration, and also can reduce seizure and galling.
- the linear expansion coefficient due to the heat of the resin retaining ring is larger than the linear expansion coefficient due to the heat of the housing, and the linear expansion coefficient due to the heat of the housing is larger than the linear expansion coefficient due to the heat of the rotating shaft and the outer ring.
- the rotating shaft and the outer ring are made of steel, and the housing is made of an aluminum alloy.
- the resin outer ring is formed in such a manner that the outer ring is formed by arranging the divided outer ring parts from the outer diameter side of the rotary shaft, and the annular member is cut at one circumferential direction so as to form a gap.
- the ring can be elastically deformed and arranged from the outer diameter side, and a rolling bearing can be incorporated. If it does so, embedding property can be made favorable. In this case, the movement of the split outer ring part in the radial direction can be restricted by the resin retaining ring, and separation of the outer ring can be prevented.
- the productivity and incorporation of the bearing are good, and noise and vibration can be reduced, and seizure and galling can be reduced.
- crankshaft support structure shown in FIG. 6 shows a part of crankshaft support structure shown in FIG. 6 in a high temperature environment. It is sectional drawing which shows a part of crankshaft support structure shown in FIG. 6 in a low temperature environment. It is a figure which shows a part of conventional crankshaft support structure. It is a figure which shows a part of crankshaft support structure shown in FIG. 10 in normal temperature environment. It is sectional drawing which shows a part of crankshaft support structure shown in FIG. 10 in a high temperature environment. It is sectional drawing which shows a part of crankshaft support structure shown in FIG. 10 in a low temperature environment.
- FIG. 1 is a view showing a resin retaining ring provided in a rolling bearing according to an embodiment of the present invention.
- FIG. 2 is an enlarged view of a part of the resin retaining ring shown in FIG. 1 as seen from the direction indicated by the arrow II in FIG.
- FIG. 1 is equivalent to the figure seen from the axial direction, ie, the rotating shaft direction of a rolling bearing, when arrange
- the resin retaining ring 11 a is made of resin and has a shape obtained by cutting one place in the circumferential direction of the annular member so as to form a gap 13. That is, the resin retaining ring 11a has two end portions 12a and 12b that face each other in the circumferential direction, and has a gap 13 between the end portions 12a and 12b. The ends 12a and 12b are not connected to each other. In a normal temperature state, here, 20 ° C., the end portions 12a and 12b are separated from each other.
- the shapes of the end portions 12a and 12b are shapes cut by a plane extending in the axial direction when arranged in a rolling bearing described later.
- the surfaces facing the end portions 12b and 12a are flat.
- the cross section when the resin retaining ring 11a is cut in the circumferential direction is rectangular.
- the resin retaining ring 11 a can be elastically deformed so as to widen the gap 13.
- the resin retaining ring 11a corresponds to the front and back direction of the paper surface here, but the cross section when cut in the direction perpendicular to the rotation axis is substantially C-shaped.
- the productivity of the resin retaining ring 11a can be improved.
- the resin retaining ring 11a having such a shape may be manufactured by first manufacturing an annular member made of resin and cutting one circumferential direction of the annular member so as to form a gap 13.
- it may be manufactured by injection molding or the like using a mold having an overall shape substantially C-shaped as shown in FIG.
- the resin retaining ring 11a having the above-described shape may be manufactured by bending a rod-shaped resin member into an annular shape.
- FIG. 3 is a view showing a rolling bearing 21 according to an embodiment of the present invention, which includes the resin retaining ring 11a shown in FIGS.
- FIG. 3 is a view seen from the direction of the rotation axis (not shown) of a rotation shaft such as a crankshaft supported by the rolling bearing 21.
- the state shown in FIG. 3 is a room temperature state, specifically, a state around 20 ° C. 4 is a cross-sectional view of the rolling bearing 21 shown in FIG. 3 taken along the line IV-IV in FIG.
- FIG. 5 is a view of the rolling bearing 21 shown in FIG. 3 as viewed from the direction of the arrow V in FIG.
- a rolling bearing 21 includes an outer ring 22, a plurality of rollers 23, a cage 24 that holds the rollers 23, and two resin stoppers disposed on the outer diameter side of the rolling bearing 21. Wheels 11a and 11b are provided. Since the resin retaining ring 11b has the same configuration as the resin retaining ring 11a, the description thereof is omitted.
- Roller 23 rolls on raceway surface 27 located on the inner diameter side of outer ring 22.
- the cage 24 has a plurality of pockets (not shown) for accommodating the plurality of rollers 23.
- the cage 24 for holding the rollers 23 is formed from two divided cage components 26a and 26b.
- Each of the divided cage parts 26a and 26b has a shape in which the annular cage 24 is cut along a plane including the rotation axis of the rolling bearing 21 and parallel to the rotation axis. That is, the cage 24 can be divided into two divided cage parts 26a and 26b, and is formed by arranging the divided cage parts 26a and 26b in the circumferential direction.
- Each split cage part 26a, 26b can hold the roller 23, respectively.
- the outer ring 22 is formed of two divided outer ring parts 25a and 25b.
- Each of the divided outer ring parts 25a and 25b has a shape obtained by cutting the annular outer ring 22 along a plane that includes the rotation axis of the rolling bearing 21 and is parallel to the rotation axis. That is, the outer ring 22 is divided into two divided outer ring parts 25a and 25b, and is formed by arranging the divided outer ring parts 25a and 25b in the circumferential direction.
- the split outer ring part 25a is provided with two grooves 29a and 29c that are recessed radially inward from the outer diameter surface 28a.
- the groove portions 29a and 29c are provided at different positions in the axial direction.
- the split outer ring part 25b is provided with two grooves 29b and 29d that are recessed radially inward from the outer diameter surface 28b.
- the groove parts 29a and 29b and the groove parts 29c and 29d are each formed in a ring shape.
- Such groove portions 29a to 29d are easily formed by cutting a part of the outer diameter surfaces 28a and 28b of the outer ring divided parts 25a and 25b.
- the resin retaining rings 11a and 11b are arranged on the outer diameter side of the outer ring 22 so as to be in contact with the outer ring 22, and restrict the movement of the plurality of divided outer ring parts 25a and 25b in the radial direction.
- the resin retaining ring 11a is disposed on the outer diameter side of the rolling bearing 21 so as to be fitted into the grooves 29a and 29b.
- the resin retaining ring 11b is disposed on the outer diameter side of the rolling bearing 21 so as to be fitted into the grooves 29c and 29d. That is, the resin retaining rings 11a and 11b are provided at different positions in the axial direction.
- the outer ring 22 By so doing, it is possible to prevent the outer ring 22 from being separated by restricting the radial movement of the divided outer ring parts 25a, 25b. In this case, separation of the outer ring 22 can be more reliably prevented by the two resin retaining rings 11a and 11b provided at different positions in the axial direction. Further, since it is arranged so as to fit into the grooves 29a to 29d, the movement of the resin retaining rings 11a, 11b in the axial direction is restricted, and the resin retaining rings 11a, 11b are more reliably secured to the outer diameter surface 28a of the outer ring 22. , 28b side. Further, as will be described later, the radial dimension of the rolling bearing 21 can be adjusted more appropriately by using the grooves 29a to 29d. That is, the amount of protrusion protruding in the radial direction from the outer diameter surfaces 28a and 28b can be adjusted by the depth of the grooves 29a to 29b, specifically, the amount of recess in the radial direction.
- the outer diameter dimensions of the resin retaining rings 11 a and 11 b are larger than the outer diameter dimension of the outer ring 22.
- the resin retaining rings 11a and 11b fitted in the groove portions 29a to 29d slightly protrude from the outer diameter surfaces 28a and 28b in the normal temperature state.
- the resin retaining rings 11a and 11b can be interposed between the outer ring 22 and a later-described housing or the like disposed on the outer diameter side of the outer ring 22 in a normal temperature state. While preventing creep, noise and vibration can be further reduced.
- FIG. 6 is a view of the crankshaft support structure including the rolling bearing 21 according to the embodiment of the present invention as seen from the direction of the rotation axis of the crankshaft. From the viewpoint of easy understanding, FIG. 6 shows a state in which a part of the crankshaft support structure is disassembled as in FIG. 10 described above.
- a crankshaft support structure 31 is disposed on a crankshaft 32 as a rotating shaft, the rolling bearing 21 configured as described above that supports the crankshaft 32, and the outer diameter side of the rolling bearing 21.
- an engine block 33 as a housing to which the rolling bearing 21 is attached.
- the engine block 33 can be divided into two divided engine block parts 34a and 34b divided in the circumferential direction.
- the rolling bearing 21 is attached to the engine block 33 by fastening the divided engine block parts 34 a and 34 b with bolts (not shown) with the rolling bearing 21 interposed therebetween.
- the crankshaft 32 and the outer ring 22 are made of steel, and the engine block 33 is made of an aluminum alloy.
- linear expansion coefficient due to the heat of the resin retaining rings 11a and 11b is larger than the linear expansion coefficient due to the heat of the engine block 33, and the linear expansion coefficient due to the heat of the engine block 33 is due to the heat of the crankshaft 32 and the outer ring. It is configured to be larger than the linear expansion coefficient.
- the split cage parts 26a and 26b holding the rollers 23 are arranged from the outer diameter side of the crankshaft 32.
- the divided outer ring parts 25a and 25b are arranged from the outer diameter side of the divided cage parts 26a and 26b.
- the resin retaining rings 11a and 11b are arranged using the elastic deformation of the resin retaining rings 11a and 11b from the outer diameter side of the divided outer ring parts 25a and 25b. In this case, it arrange
- each component of the rolling bearing 21 can be assembled from the outer diameter side of the crankshaft 32. If it does so, interference with the counterweight (not shown) etc. which are located in the axial direction of the crankshaft 32 can be prevented, and it can incorporate.
- the split resin retaining rings 11a and 11b can be arranged from the outer diameter side, the assemblability can be improved. That is, it is possible to prevent galling or the like that occurs when the annular member is press-fitted. Further, the resin retaining rings 11a and 11b can restrict the radial movement of the divided outer ring parts 25a and 25b and prevent the outer ring 22 from being separated.
- the resin retaining rings 11a and 11b are interposed between the engine block 33 and the outer ring 22 of the rolling bearing 21, the resin retaining rings 11a and 11b can absorb noise and vibration of the rolling bearing 21. it can. Therefore, noise and vibration can be reduced. Moreover, the radial dimension of the rolling bearing 21 can be adjusted by the resin retaining rings 11a and 11b, and the radial clearance and the tightening allowance can be appropriately maintained.
- a crankshaft 32 is disposed on the inner diameter side of the rolling bearing 21.
- a 1 of the radial clearance to adjust the resin retaining ring 11a, 11b the thickness of such.
- no fastening allowance is provided between the outer ring 22 and the engine block 33, and a fastening allowance is provided between the engine block 33 and the resin retaining rings 11a and 11b.
- the crankshaft 32, the outer ring 22, the engine block 33, and the resin retaining rings 11a and 11b each thermally expand radially outward.
- the clearance between the outer ring 22 and the engine block 33 is increased.
- the linear expansion coefficient due to the heat of the resin retaining rings 11a and 11b is larger than the linear expansion coefficient due to the heat of the engine block 33, the clearance between the outer ring 22 and the engine block 33 due to the thermal expansion of the resin retaining rings 11a and 11b. Can be filled.
- the crankshaft 32, the outer ring 22, the engine block 33, and the resin retaining rings 11a and 11b are each thermally contracted radially inward.
- the linear expansion coefficient due to heat of the engine block 33 is larger than the linear expansion coefficient due to heat of the outer ring 22, the clearance between the outer ring 22 and the engine block 33 is reduced.
- the thermal expansion coefficient of the resin retaining rings 11a and 11b is larger than the thermal expansion coefficient of the resin retaining rings 11a and 11b than the thermal expansion coefficient of the engine block 33, the resin shrinkage of the resin retaining rings 11a and 11b and the use of the grooves 29a to 29d
- the retaining rings 11a, 11b and the engine block 33 are not in contact with each other, and the outer ring 22 and the engine block 33 are in contact with each other, so that a gap can be eliminated. That is, the tightening allowance B 3 is provided between the outer ring 22 and the engine block 33.
- the dimensional A 3 of the radial clearance between the rollers 23 and the crankshaft 32 can be made proper.
- Table 1 shows the results of measuring the radial dimensions and the like in each environment in the crankshaft support structure 31 including the rolling bearing 21 having the above-described configuration.
- Table 2 shows the measurement results of the radial dimensions and the like in each environment in the crankshaft support structure including the conventional rolling bearing shown in FIG.
- the radial clearance is displaced between 0.002 mm and 0.050 mm in the conventional crankshaft support structure.
- the displacement is 0.002 mm to 0.015 mm, and the amount of displacement is small. Therefore, the amount of displacement of the radial gap can be reduced and kept properly, ensuring stable rotation of the crankshaft 32, and noise and vibration can be reduced.
- the tightening allowance in the conventional crankshaft support structure, if the allowance at 150 ° C. is secured, the allowance at ⁇ 30 ° C. increases to 0.045 mm.
- the resin retaining rings 11a and 11b disposed between the outer ring 22 and the engine block 33 are only secured by considering the tightening allowance at ⁇ 30 ° C. It's okay.
- the radial gap and the interference allowance can be made appropriate in each environment.
- such a rolling bearing 21 can improve the assemblability and productivity, reduce noise and vibration, and reduce seizure and galling.
- crankshaft support structure 31 has good productivity and ease of incorporation of the rolling bearing 21 and can reduce noise and vibration, and can reduce seizure and galling.
- the circumferential length of the gap 13 and D 1 when the outer diameter of the outer ring and D 2, 0 ⁇ preferably have a relationship of D 1 ⁇ 0.4D 2 (see FIG. 5) . By doing so, it is possible to more reliably prevent the outer ring 22 from being separated.
- the two resin retaining rings 11a and 11b are provided on the rolling bearing 21.
- the present invention is not limited to this, and only one resin retaining ring may be provided. Two or more resin retaining rings may be provided.
- the resin retaining rings 11a and 11b are provided so as to be fitted into the grooves 29a to 29d provided on the outer diameter surfaces 28a and 28b of the outer ring 22.
- the present invention is not limited to this.
- the groove portions 29a to 29d may not be provided on the surfaces 28a and 28b, and the resin retaining rings 11a and 11b may be fitted directly to the outer diameter surfaces 28a and 28b. By doing so, it is possible to prevent separation of the outer ring without special processing of the outer ring.
- groove portions 29a to 29d do not have to be configured in a ring shape, but are configured so that groove-shaped portions are formed at various locations in the circumferential direction, and a part of the resin retaining ring is fitted into the groove-shaped portions. Also good.
- the resin retaining rings 11a and 11b have a rectangular cross section, the shape is not limited to this, and may be a round hole shape or the like.
- the rolling bearing and the rotating shaft support structure according to the present invention are effectively used as automotive parts.
- 11a, 11b Resin retaining ring, 12a, 12b end, 13 clearance, 21 rolling bearing, 22 outer ring, 23 roller, 24 cage, 25a, 25b split outer ring part, 26a, 26b split cage part, 27 raceway surface, 28a , 28b outer diameter surface, 29a, 29b, 29c, 29d groove, 31 crankshaft support structure, 32 crankshaft, 33 engine block, 34a, 34b split engine block parts.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Rolling Contact Bearings (AREA)
- Mounting Of Bearings Or Others (AREA)
Abstract
Description
Claims (10)
- 複数の分割外輪部品を周方向に配置して形成される外輪と、
前記外輪の軌道面を転動する複数のころと、
すき間を形成するように環状部材の周方向の一箇所を切断した形状であって、前記外輪と接触するように前記外輪の外径側に配置され、前記複数の分割外輪部品の径方向の動きを規制する樹脂止め輪とを備える、転がり軸受。 - 常温状態において、前記外輪の外径側に前記樹脂止め輪が配置された際に、前記樹脂止め輪の外径寸法は、前記外輪の外径寸法よりも大きい、請求項1に記載の転がり軸受。
- 常温状態において、前記すき間の周方向の長さをD1とし、前記外輪の外径をD2とすると、0<D1≦0.4D2の関係を有する、請求項1に記載の転がり軸受。
- 回転軸線に垂直な方向に前記樹脂止め輪を切断した場合の前記樹脂止め輪の断面は、略C字状である、請求項1に記載の転がり軸受。
- 前記樹脂止め輪を周方向に切断した場合の断面は、矩形状である、請求項1に記載の転がり軸受。
- 前記樹脂止め輪は、軸方向に複数設けられている、請求項1に記載の転がり軸受。
- 前記外輪の外径面には、径方向内側に凹んだ溝部が設けられており、
前記樹脂止め輪は、前記溝部に嵌め込むように配置される、請求項1に記載の転がり軸受。 - 回転軸と、
請求項1に記載され、前記回転軸を支持する転がり軸受と、
前記転がり軸受の外径側に配置されるハウジングとを含む、回転軸支持構造。 - 前記樹脂止め輪の熱による線膨張係数は、前記ハウジングの熱による線膨張係数よりも大きく、
前記ハウジングの熱による線膨張係数は、前記回転軸および前記外輪の熱による線膨張係数よりも大きい、請求項8に記載の回転軸支持構造。 - 前記回転軸および前記外輪は、鋼製であり、
前記ハウジングは、アルミニウム合金製である、請求項8に記載の回転軸支持構造。
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE112009002563T DE112009002563T5 (de) | 2008-10-22 | 2009-09-30 | Wälzlager und Rotationswellen-Stützaufbau |
CN200980141598.3A CN102187106B (zh) | 2008-10-22 | 2009-09-30 | 滚动轴承及旋转轴支承结构 |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2008271661A JP5303240B2 (ja) | 2008-10-22 | 2008-10-22 | 転がり軸受および回転軸支持構造 |
JP2008-271661 | 2008-10-22 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2010047213A1 true WO2010047213A1 (ja) | 2010-04-29 |
Family
ID=42119257
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2009/067059 WO2010047213A1 (ja) | 2008-10-22 | 2009-09-30 | 転がり軸受および回転軸支持構造 |
Country Status (4)
Country | Link |
---|---|
JP (1) | JP5303240B2 (ja) |
CN (1) | CN102187106B (ja) |
DE (1) | DE112009002563T5 (ja) |
WO (1) | WO2010047213A1 (ja) |
Families Citing this family (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
ITTO20120918A1 (it) * | 2012-10-17 | 2014-04-18 | Skf Ab | Dispositivo anti-slittamento per un anello di un cuscinetto di rotolamento e cuscinetto equipaggiato con lo stesso |
CN102937138A (zh) * | 2012-10-30 | 2013-02-20 | 无锡风电设计研究院有限公司 | 支承式滚子结构的滚动轴承 |
CN103206461B (zh) * | 2013-03-21 | 2015-06-17 | 洛阳轴研科技股份有限公司 | 一种消除组配角接触球轴承高速所产生轴向热膨胀的方法 |
DE102013210693A1 (de) * | 2013-06-07 | 2014-12-11 | Schaeffler Technologies Gmbh & Co. Kg | Lageranordnung für zwei benachbarte Zahnräder, insbesondere für zwei Gangräder in einem Doppelkupplungsgetriebe |
DE102014209105B4 (de) * | 2014-05-14 | 2016-02-04 | Aktiebolaget Skf | Vorrichtung zur Demontage eines Lagerrings |
CN104265771B (zh) * | 2014-09-23 | 2017-02-15 | 徐州重型机械有限公司 | 一种轴承、滑轮总成、伸缩臂和起重机 |
US10523082B2 (en) * | 2016-04-21 | 2019-12-31 | Safran Electrical & Power | Bearing assembly for electrical generator |
DE102018127029A1 (de) * | 2018-10-30 | 2020-04-30 | Schaeffler Technologies AG & Co. KG | Akustikoptimierte Lagereinheit |
JP2020148316A (ja) * | 2019-03-15 | 2020-09-17 | Ntn株式会社 | 転がり軸受 |
CN113042764B (zh) * | 2021-03-30 | 2022-03-01 | 河南科技大学 | 自补偿机床主轴轴承热诱导预紧力的轴承隔圈及生产方法 |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH06109025A (ja) * | 1992-09-29 | 1994-04-19 | Ntn Corp | 割り型軸受 |
JPH07317778A (ja) * | 1994-05-31 | 1995-12-08 | Ntn Corp | 分割軸受の製造方法 |
Family Cites Families (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1920148A (en) | 1929-06-06 | 1933-07-25 | Soudure Electr Antogene Sa | Fusible electrode for electric welding |
JPH0681846A (ja) | 1992-08-31 | 1994-03-22 | Ntn Corp | 割り型軸受 |
JPH06229415A (ja) | 1993-01-29 | 1994-08-16 | Fuji Heavy Ind Ltd | 内燃機関のクランクシャフト軸受 |
-
2008
- 2008-10-22 JP JP2008271661A patent/JP5303240B2/ja not_active Expired - Fee Related
-
2009
- 2009-09-30 WO PCT/JP2009/067059 patent/WO2010047213A1/ja active Application Filing
- 2009-09-30 DE DE112009002563T patent/DE112009002563T5/de not_active Withdrawn
- 2009-09-30 CN CN200980141598.3A patent/CN102187106B/zh not_active Expired - Fee Related
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH06109025A (ja) * | 1992-09-29 | 1994-04-19 | Ntn Corp | 割り型軸受 |
JPH07317778A (ja) * | 1994-05-31 | 1995-12-08 | Ntn Corp | 分割軸受の製造方法 |
Also Published As
Publication number | Publication date |
---|---|
DE112009002563T5 (de) | 2012-06-28 |
JP5303240B2 (ja) | 2013-10-02 |
CN102187106A (zh) | 2011-09-14 |
CN102187106B (zh) | 2016-02-03 |
JP2010101364A (ja) | 2010-05-06 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
WO2010047213A1 (ja) | 転がり軸受および回転軸支持構造 | |
WO2009142172A1 (ja) | 二つ割り外輪、これを用いた二つ割り転がり軸受、転がり軸受の取付構造及び取付方法 | |
US20090080824A1 (en) | Bearing having thermal compensating capability | |
US20090126195A1 (en) | Roller bearing | |
US9726219B2 (en) | Thrust washer | |
EP2279352A1 (en) | Bearing device for supercharger | |
EP1696143B1 (en) | Double split bearing | |
JP2009008202A (ja) | 転がり軸受の固定構造 | |
JP2008095723A (ja) | 転がり軸受 | |
JP2010138753A (ja) | 過給機の軸受装置 | |
JP5762698B2 (ja) | 分割型ニードル軸受及び軸受装置 | |
US20100166350A1 (en) | Split-type sliding bearing for crankshaft in internal combustion engine and split-type sliding bearing device | |
JP2007092863A (ja) | 軸受装置 | |
JP2011252523A (ja) | 転がり軸受装置 | |
JP5049044B2 (ja) | 転がり軸受 | |
JP2008232309A (ja) | ころ軸受 | |
JP2007024143A (ja) | 割れ型転がり軸受 | |
JP5089572B2 (ja) | 内燃機関のクランク軸用分割型すべり軸受および分割型すべり軸受装置 | |
JP4788630B2 (ja) | 転がり軸受装置 | |
JPH11101128A (ja) | 過給機、その組立方法ならびに過給機に用いる軸受ユニット | |
JPH06109025A (ja) | 割り型軸受 | |
JP4480639B2 (ja) | 針状ころ軸受および外輪の製造方法 | |
JP2000291651A (ja) | 一方向クラッチ付き転がり軸受 | |
JP2014105733A (ja) | 転がり軸受 | |
JP5012265B2 (ja) | クランクシャフトの支持構造及びクランクシャフト用軸受 |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
WWE | Wipo information: entry into national phase |
Ref document number: 200980141598.3 Country of ref document: CN |
|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 09821911 Country of ref document: EP Kind code of ref document: A1 |
|
WWE | Wipo information: entry into national phase |
Ref document number: 797/MUMNP/2011 Country of ref document: IN |
|
WWE | Wipo information: entry into national phase |
Ref document number: 1120090025633 Country of ref document: DE |
|
122 | Ep: pct application non-entry in european phase |
Ref document number: 09821911 Country of ref document: EP Kind code of ref document: A1 |