WO2009150935A1 - 保持器、深溝玉軸受、およびシール付軸受 - Google Patents
保持器、深溝玉軸受、およびシール付軸受 Download PDFInfo
- Publication number
- WO2009150935A1 WO2009150935A1 PCT/JP2009/059558 JP2009059558W WO2009150935A1 WO 2009150935 A1 WO2009150935 A1 WO 2009150935A1 JP 2009059558 W JP2009059558 W JP 2009059558W WO 2009150935 A1 WO2009150935 A1 WO 2009150935A1
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- WIPO (PCT)
- Prior art keywords
- ball
- seal
- bearing
- contact
- cage
- Prior art date
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Classifications
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- 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
- F16C33/72—Sealings
- F16C33/76—Sealings of ball or roller bearings
- F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
- F16C33/784—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race
- F16C33/7843—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race with a single annular sealing disc
- F16C33/7853—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race with a single annular sealing disc with one or more sealing lips to contact the inner race
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- 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
- F16C33/38—Ball cages
- F16C33/3887—Details of individual pockets, e.g. shape or ball 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
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/38—Ball cages
- F16C33/42—Ball cages made from wire or sheet metal strips
- F16C33/422—Ball cages made from wire or sheet metal strips made from sheet metal
- F16C33/427—Ball cages made from wire or sheet metal strips made from sheet metal from two parts, e.g. ribbon cages with two corrugated annular parts
-
- 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
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- 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
- F16C33/72—Sealings
- F16C33/76—Sealings of ball or roller bearings
- F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
- F16C33/7816—Details of the sealing or parts thereof, e.g. geometry, material
- F16C33/782—Details of the sealing or parts thereof, e.g. geometry, material of the sealing region
- F16C33/7823—Details of the sealing or parts thereof, e.g. geometry, material of the sealing region of sealing lips
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
- F16C19/04—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly
- F16C19/06—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly with a single row or balls
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- 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 cage, a deep groove ball bearing, and a bearing with a seal.
- the bearing deep groove ball
- the bearing includes an outer ring 2 having an arcuate outer raceway surface 1 formed on the inner periphery and an arcuate inner raceway surface 3 facing the outer raceway surface 1 on the outer periphery.
- each annular holding plate 7 includes the hemispherical bulging portion 6 disposed along the circumferential direction and a flat portion 8 between adjacent hemispherical bulging portions 6.
- the flat portions 8 and 8 are overlapped, and the flat portions 8 and 8 are connected via a fixing tool 9 such as a rivet.
- a fixing tool 9 such as a rivet
- Patent Document 1 the lubrication state between the cage and the ball is improved (Patent Document 1), or the lubricating oil is actively supplied and discharged to improve the fluidity of the lubricating oil in the bearing. (Patent Document 2) and the like.
- Patent Document 1 The device described in Patent Document 1 is provided with an auxiliary concave portion on the inner peripheral side of the pocket, and this auxiliary concave portion functions as a lubricant reservoir for storing the lubricant. This improves the amount of lubricant retained in the pocket and improves the lubrication state between the cage and the ball.
- Patent Document 2 also has a recess formed on the inner peripheral surface of the pocket.
- the recesses communicate with the bearing space side between the outer ring and the cage and the bearing space side between the inner ring and the cage to form a groove-shaped lubricating oil path.
- a conventional bearing used in an automobile transmission is a bearing with a seal having a contact-type seal member that seals a bearing space formed between inner and outer rings thereof, whereby foreign matter enters the bearing. Is preventing.
- Patent Document 3 When the bearing space is sealed with such a contact-type seal member, foreign matter can be prevented from entering the bearing. However, since the seal torque is large, it is a problem in promoting the fuel saving of the automobile. In such a bearing with a seal, one having a reduced seal torque has been proposed (for example, Patent Document 3). In the one disclosed in Patent Document 3, shot peeling is applied to the surface where the seal lip portion is in sliding contact, for example, the inner wall surface of the seal groove of the bearing rotating ring, and the maximum roughness Ry of the contact surface is reduced to 2.5 ⁇ m or less. ing. Thereby, the seal torque is reduced.
- assistant recessed part becomes a lubricant pool, and a lubricant stores oil in this auxiliary
- the thing of patent document 2 does not reduce the resistance at the time of a lubricant passing a minute gap. That is, in this type of bearing, it has been impossible to achieve both a reduction in resistance when the lubricant passes and a reduction in the amount of oil film sheared when the ball moves. For this reason, conventionally, even if a recess is formed on the inner diameter surface of the pocket, torque reduction cannot be achieved.
- reducing the surface roughness of the contact surface and reducing the seal torque has a limit in the torque reduction effect. If a non-contact seal is used, the seal torque can be reduced to zero, but reducing the seal gap to such an extent that foreign materials such as gear wear powder can be prevented from entering due to assembly errors, processing errors, thermal expansion differences, etc. It is difficult to realize.
- the present invention is capable of achieving a torque reduction, a deep groove ball bearing using such a cage, and further preventing foreign matter from entering the bearing and sufficiently reducing the sealing torque.
- a sealed bearing is provided.
- the cage of the present invention is a combination of two annular holding plates having hemispherical bulging portions arranged at predetermined intervals along the circumferential direction, and the ball is placed at the opposing hemispherical bulging portions.
- a ball bearing retainer in which a pocket to be held is formed, wherein a ball non-contact portion is provided on a ball-facing surface of the pocket, and a contact area with the ball in the pocket is determined as a ball when no ball non-contact portion is provided.
- the contact area is reduced by 15% to 30%.
- retainer will fall when the area to reduce is larger than 30%, the upper limit was made 30%. If the area to be reduced is smaller than 15%, the torque cannot be reduced sufficiently (about 50%).
- the resistance when the lubricant passes through the pocket can be reduced by providing the ball non-contact portion on the ball facing surface. Further, by providing the ball non-contact portion, the amount of oil film formed between the ball and the pocket can be reduced. In this case, if the ball non-contact portion is too small, the amount of oil film to be sheared is small and torque reduction cannot be achieved. On the other hand, if the ball non-contact portion is too large, the amount of oil film formed between the ball and the pocket becomes too small, thereby impairing smooth rolling of the ball. Therefore, by setting the range of the non-ball contact portion as in the present invention, it is possible to achieve both the resistance when the lubricant passes through the pocket and the reduction in the amount of oil film to be sheared.
- a concave portion recessed toward the anti-ball side is provided on the ball facing surface, and this concave portion serves as the ball non-contact portion,
- a slit may be provided in the hemispherical bulge portion, and the slit may be used as the non-ball contact portion.
- the ball non-contact portion is preferably arranged on the bearing outer diameter side with respect to the pitch circle of the ball.
- the deep groove ball bearing of the present invention includes an outer ring having an outer race surface formed on the inner periphery, an inner ring having an inner race surface formed on the outer periphery, and a plurality of balls that roll between the inner race surface and the outer race surface. And the retainer disposed between the inner ring and the outer ring.
- the seal member includes a seal member that is a contact seal that has a base end fixed to one of the race rings and a seal lip portion that contacts the other race ring, and at least the seal lip portion
- the material of the tip of this is a high-abrasion material that wears to become a non-contact seal or a light contact that can be regarded as zero contact pressure when the bearing is used in a rotating state.
- the cage according to the present invention is used as the cage.
- the “high wear material” referred to in this specification indicates a material that is easily worn.
- the seal member that was a contact type at the beginning of the operation is worn early, for example, after the start of operation. It changes to a non-contact type seal member.
- the contact is light enough that the contact pressure can be regarded as zero due to wear.
- the seal member may have the entire or tip of the seal lip portion as a high wear material portion which is a material that easily wears against other portions of the seal member. Since the material that can provide appropriate high wear is limited, it may not be preferable to make the entire seal member highly wearable, but the entire seal lip or only the tip is made of a different material to make it highly wearable. This makes it possible to obtain a preferable high wear property.
- the high wear material may be a rubber material, that is, a high wear rubber material, or may be a resin material.
- the high wear material may be a solid lubricant, non-woven fabric, hard steel, or the like.
- the shape of the sealing member may be an axial contact type or a radial contact type.
- the seal lip portion may have a shape that makes contact in the axial direction with respect to the inner surface of the seal groove formed in the opposed raceway ring. Moreover, it is good also as a shape which a seal lip part contacts in a radial direction with respect to the raceway which opposes.
- the seal member may be provided with an adsorption preventing means for preventing the seal member from adsorbing to the other end of the track.
- the adsorption preventing means is, for example, a ventilation slit provided at the tip of the seal member.
- the seal member When a contact-type seal member is provided, the seal member may be attracted to the race and the torque may increase due to a decrease in bearing internal pressure.
- the present invention uses a high wear material, an adsorbing action occurs like a general contact seal until the seal member is worn.
- the cage of the present invention by setting the range of the non-ball contact portion, it is possible to achieve both the resistance when the lubricant passes through the pocket and the reduction in the amount of oil film to be sheared.
- the ball non-contact portion can be reliably formed by providing a concave portion recessed toward the opposite ball side or a slit on the ball facing surface. If the ball non-contact portion is disposed on the bearing outer diameter side with respect to the pitch circle of the ball, the shear resistance at the position where the peripheral speed is high can be reduced, and the torque can be more stably reduced.
- the overall shape is relatively simple, and it can be reliably formed regardless of whether it is made of metal or resin. Also, as a molding method, if it is made of metal, it can be molded by pressing or casting, and if it is made of resin, it can be molded by injection molding. It can be molded by the method, and the cost can be reduced.
- the seal member that was a contact type at the beginning of operation is changed to a non-contact type seal member at an early stage after the start of operation due to wear, for example.
- the contact is light enough that the contact pressure can be regarded as zero due to wear. For this reason, the seal torque can be sufficiently reduced.
- a minute gap serving as an optimal non-contact seal gap is formed between the seal lip portion and the rotating wheel, or light contact as described above is achieved. Therefore, although the lubricating oil can pass through, it is possible to prevent the entry of foreign matters having a large particle size that affect the bearing life. As a result, it is possible to prevent foreign matter from entering the bearing and sufficiently reduce the sealing torque.
- an anti-adsorption means such as the slit, adsorption until the seal member is worn is prevented, and an increase in torque is avoided.
- retainer is shown and it is the principal part simplification figure of the 3rd modification of a holder
- retainer is shown and it is the principal part simplification figure of the 4th modification of a holder
- retainer is shown and it is the principal part simplification figure of the 5th modification of a holder
- FIG. 1 shows a bearing (deep groove ball bearing) using the cage (ball bearing cage) of the first embodiment.
- This ball bearing includes an outer ring 12 having an arc-shaped outer raceway surface (rolling surface) 11 formed on the inner periphery, and an arc-shaped inner raceway surface (rolling surface) 13 facing the outer raceway surface 11 on the outer periphery.
- the seal members 17 and 17 are mounted on the axial end portions.
- this bearing can be called a bearing with a seal, and is used for an automobile transmission or the like.
- the inner ring 14 and the outer ring 12 are track rings.
- grease is initially sealed in the bearing.
- This rolling bearing is an inner ring rotating type in which the inner ring 14 is a rotating ring and the outer ring 12 is a fixed ring.
- the outer ring 12, the inner ring 14, and the ball 16 are made of, for example, high carbon chrome bearing steel such as SUJ2, and the cage 15 is a pressed product of, for example, cold rolled steel (JIS standard SPCC) or the like. It is.
- the cage 15 is formed by combining two annular holding plates 27 ⁇ / b> A and 27 ⁇ / b> B having hemispherical bulging portions 26 disposed at predetermined intervals along the circumferential direction. . That is, each annular holding plate 27A, 27B includes a hemispherical bulging portion 26 disposed along the circumferential direction, and a flat portion 28 between adjacent hemispherical bulging portions 26.
- each hemispherical bulge part 26 opposes and the ring-shaped ball fitting part (pocket) 30 is formed.
- a ball non-contact portion 31 is provided on the ball facing surface of the pocket 30.
- the contact area with the ball 16 in the pocket 30 is reduced by 15% to 30% than the contact area with the ball 16 when the ball non-contact portion 31 is not provided.
- a rectangular convex portion 32 protruding to the antiball side on the antiball-facing surface a rectangular concave portion 33 recessed to the antiball side is provided on the ball facing surface. 31 is formed.
- the convex part 32 various things are employable as shown in FIG.
- the shape A shown in FIG. 4A has a circumferential length L of LA and a width dimension W of WA.
- 4B has a circumferential length L that is shorter than LA, and a width dimension W that is the same as WA.
- the shape C shown in FIG. 4C is an LC having a circumferential length L that is the same as that of LB, and a width dimension W of which is larger than WA.
- a shape D shown in FIG. 4D has an LD having the same circumferential length L as LA and a width WD having the same width WD as WA.
- the circumferential length L is the same LE as the LB, and the width dimension W is the same WE as the WA.
- the shape F shown in FIG. 4F has a circumferential length L that is the same as LB, and a width dimension W that is the same as WA.
- the shape A shown in FIG. 4A, the shape B shown in FIG. 4B, and the shape F shown in FIG. 4F are such that the center line O of the convex portion 32 coincides with the pitch circle PCD of the ball 16,
- the part 32 is disposed on the pitch circle PCD.
- the center line O of the convex portion 32 is shifted to the bearing outer diameter side from the pitch circle PCD of the ball 16. .
- the deviation is slight in the shape C shown in FIG. 4C, but the deviation is large between the shape D shown in FIG. 4D and the shape E shown in FIG. 4E, and one long side is the pitch circle of the ball 16. It matches the PCD.
- the ball non-contact part 31 of the concave part 33 formed thereby.
- the pocket 30 only needs to be reduced by 15% to 30% from the contact area with the ball 16 when the ball non-contact portion 31 is not provided.
- the convex part 32 even if it is a rectangle (rectangular) whose rotation direction dimension is long with respect to the radial direction dimension, conversely, even if it is a rectangle (rectangle) whose radial direction dimension is long with respect to the rotation direction dimension,
- the rotation direction dimension and the radial direction dimension may be the same square. Further, it may be oval or elliptical instead of rectangular. Even in such an elliptical shape, the rotational dimension may be longer than the radial dimension, or conversely, the radial dimension may be longer than the rotational dimension. Furthermore, it may be circular.
- the seal member 17 includes a cored bar 18 and a covering part (elastic member) 19 made of a synthetic resin, a rubber material or the like that covers the cored bar 18. And an outer peripheral part is fixed by the fitting state in the seal attachment groove
- a seal groove 21 formed of a circumferential groove is formed at a position corresponding to the inner peripheral portion of each seal member 17.
- the tip of the seal lip portion 17 a formed at the inner peripheral end of the seal member 17 is in sliding contact with the inner surface of the seal structure 21 of the inner ring 14.
- the seal lip portion 17a has two axial lip portions 17aa and 17ab that are bifurcated.
- the first axial lip portion 17aa extends inward of the bearing and makes axial contact with the inner wall surface of the seal structure 21 of the inner ring 14.
- the second axial lip portion 17ab extends outside the bearing and makes axial contact with the outer wall surface of the seal groove 21 of the inner ring 14.
- the seal lip portion 17a is formed as a part of the elastic member 19, but at least a portion including the two axial lip portions 17aa and 17ab including the distal end portion is a high wear material portion 19b made of a material that easily wears. ing. That is, the elastic member 19 of the seal member 17 is composed of a main body portion 19a that covers the metal core 18, and a high wear material portion 19b that is provided continuously with the main body portion 19a. In this case, the high wear material portion 19b is made of a high wear rubber material, and the main body portion 19a is made of a normal rubber material.
- the entire sealing member 17 is formed by vulcanization molding of a rubber material, and the cored bar 18 is bonded to the elastic member 19 during the vulcanization molding.
- the type of the high wear rubber material constituting the high wear material portion 19b is selected depending on the compatibility with the operating temperature and the lubricating oil.
- the ball non-contact portion 31 by providing the ball non-contact portion 31 on the ball facing surface, the resistance when the lubricant passes through the pocket can be reduced. Further, since the ball non-contact portion 31 is provided, the amount of oil film formed between the ball 16 and the pocket 30 can be reduced. In this case, if the ball non-contact portion is too small, the amount of oil film to be sheared is small and torque reduction cannot be achieved. On the other hand, if the ball non-contact portion 31 is too large, the amount of oil film formed between the ball 16 and the pocket 30 becomes too small, and smooth rolling of the ball 16 is impaired.
- the range of the ball non-contact portion 31 as in the present invention, it is possible to achieve both the resistance when the lubricant passes through the pocket and the reduction in the amount of oil film to be sheared. For this reason, torque can be reduced, and if a bearing using this ball bearing retainer is used in an automobile, it is possible to improve the fuel consumption and to perform an environment-friendly operation.
- the ball non-contact portion 31 can be reliably formed by providing a concave portion 33 that is recessed toward the opposite ball side on the ball facing surface. If the ball non-contact portion 31 is arranged on the outer diameter side of the pitch circle of the ball 16, shear resistance at a position with a high peripheral speed can be reduced, and torque can be reduced more stably. .
- the tip of the seal lip portion 17a of the seal member 17 that is in sliding contact with the seal groove 21 of the inner ring 14 that is the rotating shaft is made of a highly wearable material (high wear rubber material). Since the wear material portion 19b is used, the seal member 17 which was a contact type in the initial stage of operation is enlarged in FIG. 6 at an early stage (several hours after the start of operation) after the start of operation due to wear of the high wear material portion 19b. As shown in the figure, the seal torque can be sufficiently reduced in place of the non-contact type seal member 17. For example, after the start of operation, it becomes non-contact within 60 minutes under oil bath or absolutely dry conditions.
- the wear of the high wear material portion 19b forms a minute gap that provides an optimum labyrinth between the seal lip portion 17a of the seal member 17 and the seal groove 21 of the inner ring 14, so that the lubricating oil can pass therethrough.
- the wear of the high wear material portion 19b does not necessarily occur until it becomes non-contact, and may be wear that makes a light contact that can be regarded as zero in practical use.
- the seal member 17 may be provided with an adsorption preventing means such as a slit 50 for ventilation.
- the adsorption preventing means is means for preventing the seal member 17 from being adsorbed by the inner ring 14 due to a reduction in the internal pressure of the bearing.
- the axial lip portions 17aa and 17ab of the seal member 17 are in contact with the inner ends of the seal grooves 21 at the tips of the axial lip portions 17aa and 17ab and are in a state of ventilation in the bearing space.
- a slit 50 is provided.
- the slit 50 is provided in several places in the circumferential direction, for example, two places.
- the seal member 17 is formed on the inner surface of the seal groove 21 of the inner ring 14 in order to reduce the bearing internal pressure until the high wear material portion 19b is worn. Adsorption is prevented and an increase in torque due to adsorption is avoided.
- the ball bearing (deep groove ball bearing) shown in FIG. 7 omits the point that it does not have the seal member 17, the seal mounting groove 20 in which the seal member 17 is mounted, and the seal groove 21 in which the lip portion 17a of the seal member 17 contacts. 1 is the same as the ball bearing (deep groove ball bearing) shown in FIG.
- FIG. 8 shows a bearing (deep groove ball bearing) using the ball bearing cage of the second embodiment.
- the cage 15 is provided with a slit 35 in the hemispherical bulging portion 26, and the slit 35 serves as a ball non-contact portion 31.
- the slit 35 in this case has a rectangular shape and is disposed on the pitch circle PCD whose center line O ⁇ b> 1 coincides with the pitch circle PCD of the ball 16.
- the slit 35 is a rectangle (rectangular) whose rotational direction dimension is longer than the radial dimension
- the slit 35 is rotated even if it is a rectangle (rectangular) whose radial direction dimension is longer than the rotational direction dimension.
- the directional dimension and the radial dimension may be the same square. Further, it may be oval or elliptical instead of rectangular. Even in such an elliptical shape, the rotational dimension may be longer than the radial dimension, or conversely, the radial dimension may be longer than the rotational dimension. Furthermore, it may be circular.
- the slit 35 may be arranged on the pitch circle PCD of the ball 16 or on the outer diameter side of the pitch circle PCD. Good. The amount of deviation in this case can also be set arbitrarily. That is, the ball non-contact portion 31 formed by the slit 35 may be any one that reduces the contact area with the ball 16 in the pocket 30 when the ball non-contact portion 31 is not provided by 15% to 30%. Since the other structure of the bearing shown in FIG. 9 is the same as that of the bearing shown in FIG.
- the ball non-contact portion 31 is formed by the slit 35
- the resistance when the lubricant passes through the pocket can be reduced, and the ball 16 and the pocket 30 can be reduced.
- the amount of oil film formed between the two can be reduced.
- the cage shown in FIG. 8 has the same operational effects as the cage shown in FIG.
- the slit 35 is provided, unlike the case where the convex portion 32 is provided, the size of the cage 15 in the bearing axial direction is not increased, and the size reduction can be achieved. That is, the torque can be reduced while maintaining the same dimensions as those of the conventional cage that does not have the ball non-contact portion 31.
- the ball bearing (deep groove ball bearing) shown in FIG. 10 omits the point that it does not have the seal member 17, the seal mounting groove 20 in which the seal member 17 is mounted, and the seal groove 21 in which the lip portion 17a of the seal member 17 contacts. This is the same as the ball bearing (deep groove ball bearing) shown in FIG. For this reason, even if it is a ball bearing (deep groove ball bearing) shown in FIG. 10, there exists an effect other than the effect by the ball bearing (deep groove ball bearing) shown in FIG.
- the cage 15 is a metal cage by press working in each of the above embodiments, but may be molded by casting. Moreover, it may be by shaving or by electric discharge machining (including wire cutting).
- the electric discharge machining is a machining method in which a part of the surface of the workpiece is removed by an arc discharge repeated at a short cycle between the electrode and the workpiece.
- Wire cutting is a kind of electric discharge machining, which is a method of applying a tension to a wire and processing a metal material using electric discharge.
- the cage 15 is not limited to a metal cage, and may be a synthetic resin molded product.
- resin material of the resin cage those conventionally used for this type of cage, for example, polyphenylene sulfide resin (hereinafter referred to as PPS resin) or polyamide 46 (PA46) are used.
- PPS resin polyphenylene sulfide resin
- PA46 polyamide 46
- those that require long-term heat resistance in the higher temperature range for example, about 200 ° C.
- PI resin polyimide resin
- PAI resin PAI resin
- PEEK resin polyether ether ketone resin
- This resin cage can be molded by, for example, injection molding. Moreover, you may shape
- the ball non-contact portion 31 when the ball non-contact portion 31 is provided, as shown in FIG. 1, a rectangular convex portion 32 that protrudes toward the anti-ball side is formed on the anti-ball facing surface, so that A rectangular concave portion 33 that is recessed toward the ball side may be provided, and the concave portion 33 may be used as the ball non-contact portion 31. Further, a slit 35 may be provided, and the ball 35 may be used as the non-ball contact portion 31. For this reason, even if it is a resin cage, there exists an effect similar to a metal cage as shown in FIG.
- the seal lip portion 17a of the seal member 17 has one radial lip portion 17ac that extends toward the inner diameter side and comes into radial contact with the seal groove 21 of the inner ring 14.
- At least the tip end portion of the seal lip portion 17a having the radial lip portion 17ac is a high wear material portion 19b made of an easily wearable material, the high wear material portion 19b is made of a high wear rubber material, and others
- the configuration is the same as that of the seal member 17 shown in FIG. 5A.
- the seal lip portion 17 a of the seal member 17 has only one axial lip portion 17 aa extending inward of the bearing and in axial contact with the inner wall surface of the seal groove 21 of the inner ring 14.
- the portion 19b including at least the tip portion of the seal lip portion 17a including the axial lip portion 17aa is a high wear material portion made of a material that easily wears, or the high wear material portion 19b is made of a high wear rubber material.
- the configuration is the same as that of the seal member 17 shown in FIG. 5A.
- the ball non-contact portion 31 extends along the rotation direction. Although arranged, it may be inclined with respect to the rotation direction. Further, the formed ball non-contact portion 31 is not limited to one for the hemispherical bulge portion 26, and two or more ball non-contact portions 31 are provided in each hemispherical bulge portion 26. Also good. In this case, a plurality may be arranged along the circumferential direction or a plurality may be arranged along the radial direction.
- each corner portion may be rounded or not rounded.
- the protrusion amount (depth of the recessed part 33) of the convex part 32 shall be 40% or less of the annular holding plates 27A and 27B. That is, when it exceeds 40%, the protruding amount of the convex portion 32 becomes too large, and it may be difficult to mount the seal member or may be enlarged.
- Example 1 Torque generated by producing cages (metal cages: pressed products) of shapes A, B, C, D, E, and F shown in FIG. 4 and using them to assemble the ball bearing shown in FIG. was measured. The results are shown in Table 1 below.
- the standard product is a conventional product in which the ball non-contact portion 31 is not formed.
- 1.6 ⁇ 9.0 in the shape A indicates that the dimension W is 1.6 mm and the circumferential length L is 9.0 mm.
- 1.6 ⁇ 5.5 in the shape B indicates that the dimension W is 1.6 mm and the circumferential length L is 5.5 mm.
- 2.6 ⁇ 5.5 in the shape C indicates that the dimension W is 2.6 mm and the circumferential length L is 5.5 mm.
- * 1 in the shape D indicates that the shape A is shifted from the PCD to the outer diameter side by 0.8 mm.
- * 2 in the shape D indicates that the shape B is shifted from the PCD to the outer diameter side by 0.8 mm.
- the columns from shape A to shape F in the contact area of the steel balls and the cage indicate the ratio (%) when the area of the standard product is 100%.
- the outer diameter of the outer ring 12 is 72.0 mm
- the inner diameter of the outer ring 12 is 60.2 mm
- the outer diameter of the inner ring 14 is 47.0 mm
- the inner diameter of the inner ring 14 is A ball (steel ball) 16 having an outer diameter of 11.1 mm was 35.0 mm.
- FIG. 13 shows a graph showing changes in torque when the contact area is changed and when the contact area is shifted from the PCD to the outer diameter side.
- the torque could be reduced by about 50% by reducing the contact area by 15%.
- the torque could be reduced by about 60% by reducing the contact area by 30% and by shifting 0.8 mm from the PCD to the outer diameter side.
- Example 2 As shown in FIG. 9, a cage having a slit 35 (metal cage: pressed product) was manufactured, and the ball bearing shown in FIG. 8 was assembled using this to measure the generated torque. In this case, the contact area was reduced by 30% compared to the standard product (the cage without the slit 35). As in Example 1, a rotational speed of 4000 r / min was applied with a radial load of 500 N applied. A part was immersed in a 30 ° C. lubricating oil (Toyota genuine ATF T-4). In this case, the torque was reduced by about 40%. That is, the standard product was 0.152 Nm, and the cage having the slit 35 was 0.093 Nm.
- the outer diameter of the outer ring 12 is 72.0 mm
- the inner diameter of the outer ring 12 is 60.2 mm
- the outer diameter of the inner ring 14 is 47.0 mm
- the inner diameter of the inner ring 14 is A ball (steel ball) 16 having an outer diameter of 11.1 mm was used.
- the same size was used.
- Comparative Example 1 instead of the convex portion 32 and the slit 35, a metal cage in which the bearing inner diameter and the bearing outer diameter side of the hemispherical bulging portion 26 are cut is manufactured, and the ball bearing shown in FIG.
- the torque to be measured was measured.
- the contact area was reduced by 25% compared to the standard product (the cage without the slit 35).
- the measurement conditions were the same as in the previous example. In this case, the torque was reduced by about 11%. That is, the standard product was 0.152 Nm, and the cage with the bearing inner and outer diameters cut was 0.135 Nm.
- Comparative Example 2 Further, a resin cage in which the bearing outer diameter side of the hemispherical bulging portion 26 was cut was manufactured, and the ball bearing shown in FIG. 8 was assembled using this to measure the generated torque.
- the resin material of the cage was PA66, and the contact area was reduced by 30% compared to the standard product.
- the measurement conditions were the same as in the previous example. In this case, the torque was reduced by about 18%. That is, the standard product was 0.152 Nm, and the cage with the bearing inner and outer diameters cut was 0.124 Nm.
- FIG. 14 is a graph showing the test results comparing the rotational torque of the sealed bearing of this embodiment with that of a conventional sealed bearing.
- rotational torque is reduced significantly.
- the cause of the rotational torque includes the resistance by grease, (cage shear resistance + rolling resistance), and seal torque as shown in FIG. 14B. This is due to the fact that the seal torque factor is eliminated in the sealed bearings.
- the bearing may be an inner ring rotation type rolling bearing or an outer ring rotation type rolling bearing.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Rolling Contact Bearings (AREA)
- Sealing Of Bearings (AREA)
Abstract
Description
図4に示す形状A、B、C、D、E、Fの保持器(金属製保持器:プレス加工品)を製作して、これらを用いて図1に示す玉軸受を組立て、発生するトルクを測定した。その結果を次の表1に示す。表1において標準品とは、ボール非接触部31が形成されていない従来品である。
図9に示すように、スリット35を有する保持器(金属製保持器:プレス加工品)を製作して、これを用いて図8に示す玉軸受を組立て、発生するトルクを測定した。この場合、接触面積を標準品(スリット35を有さない保持器)よりも30%低減させた。前記実施例1と同様、500Nのラジアル荷重を付与した状態で、4000r/minの回転速度を与えた。30℃の潤滑油(トヨタ純正ATF T-4)に一部を浸漬させた。この場合、約40%のトルク低減となった。すなわち、標準品が0.152Nmであり、スリット35を有する保持器では0.093Nmとなった。また、軸受としては、外輪12の外径寸法が72.0mmであり、外輪12の内径寸法が60.2mmであり、内輪14の外径寸法が47.0mmであり、内輪14の内径寸法が35.0mmであり、ボール(鋼球)16の外径寸法が11.1mmのものを用いた。なお、後述する比較例1、2においても、同一サイズのものを用いた。
凸部32やスリット35に代えて、半球状膨出部26の軸受内径及び軸受外径側をカットした金属製保持器を製作して、これを用いて図8に示す玉軸受を組立て、発生するトルクを測定した。接触面積を標準品(スリット35を有さない保持器)よりも25%低減させた。測定条件は前記実施例と同様とした。この場合、約11%のトルク低減となった。すなわち、標準品が0.152Nmであり、軸受内径及び軸受外径側をカットした保持器では0.135Nmとなった。
また、半球状膨出部26の軸受外径側をカットした樹脂製保持器を製作して、これを用いて図8に示す玉軸受を組立て、発生するトルクを測定した。この場合、保持器の樹脂材料はPA66であり、接触面積を標準品よりも30%低減させた。測定条件は前記実施例と同様とした。この場合、約18%のトルク低減となった。すなわち、標準品が0.152Nmであり、軸受内径及び軸受外径側をカットした保持器では0.124Nmとなった。
図14は、この実施形態のシール付き軸受の回転トルクを、従来のシール付き軸受と比較した試験結果をグラフで示したものである。図14Aに示すように、従来品に比べて、実施形態のシール付き軸受では、回転トルクが大幅に低減されている。その理由は、回転トルクの要因の内訳として、図14Bに示すように、従来品では、グリースによる抵抗、(保持器せん断抵抗+転がり抵抗)、およびシールトルクが挙げられるのに対して、実施形態のシール付き軸受ではシールトルクの要因が排除されることによる。
14 内輪
15 保持器
16 ボール
17 シール部材
17a シールリップ部
20 シール取付溝
21 シール溝
26 半球状膨出部
27A,27B 環状保持板
27A,27B 環状保持板
30 ポケット
31 ボール非接触部
33 凹部
35 スリット
Claims (16)
- 円周方向に沿って所定間隔で配設された半球状膨出部を有する2枚の環状保持板が組み合わされてなり、対向する半球状膨出部にてボールを保持するポケットが形成される保持器であって、
ポケットのボール対向面にボール非接触部を設け、このポケットにおけるボールとの接触面積を、ボール非接触部を設けないときのボールとの接触面積よりも15%~30%低減させたことを特徴とする保持器。 - 半球状膨出部において、ボール対向面に反ボール側へ凹む凹部を設け、この凹部をもって前記ボール非接触部としたことを特徴とする請求項1に記載の保持器。
- 半球状膨出部においてスリットを設け、このスリットをもって前記ボール非接触部としたことを特徴とする請求項1に記載の保持器。
- ボール非接触部を、ボールのピッチ円よりも軸受外径側に配置したことを特徴とする請求項1~請求項3のいずれか1に記載の保持器。
- 金属製であってプレス加工に成型されてなることを特徴とする請求項1~請求項4のいずれか1に記載の保持器。
- 金属製であって鋳造にて成型されてなることを特徴とする請求項1~請求項4のいずれか1に記載の保持器。
- 削り加工にて成型されてなることを特徴とする請求項1~請求項4のいずれか1に記載の保持器。
- 樹脂製であって射出成型にて成型されてなることを特徴とする請求項1~請求項4のいずれか1に記載の保持器。
- 内周に外側軌道面が形成された外輪と、外周に内側軌道面が形成された内輪と、内側軌道面と外側軌道面との間を転動する複数のボールと、内輪と外輪との間に配置された請求項1~請求項8のいずれか1項に記載の保持器を備えたことを特徴とする深溝玉軸受。
- 一対の軌道輪の対向する軌道面間に、保持器を介して保持される複数の転動体が介在し、前記一対の軌道輪間に形成される軸受空間を密封するシール部材を備えたシール付き軸受において、
前記シール部材は、基端がいずれか一方の軌道輪に固定され、シールリップ部が他方の軌道輪に接する接触シールであって、少なくともシールリップ部の先端の材質が、軸受を回転状態で使用することで、摩耗して非接触シールとなるかまたは接触圧が零と見なせる程度の軽接触となる高摩耗材であり、かつ前記保持器に、前記請求項1~請求項8のいずれか1項に記載の保持器を用いることを特徴とすることを特徴とするシール付き軸受。 - 前記シール部材は、シールリップ部の全体または先端を、このシール部材の他の部分に対して摩耗の生じ易い材質である高摩耗材部としたことを特徴とする請求項10に記載のシール付き軸受。
- 前記高摩耗材をゴム材としたことを特徴とする請求項10又は請求項11に記載のシール付き軸受
- 前記高摩耗材を樹脂材としたことを特徴とする請求項10又は請求項11に記載のシール付き軸受。
- 前記シール部材のシールリップ部を、対向する軌道輪に形成されたシール溝の内面に対してアキシアル方向に接触する形状としたことを特徴とする請求項10~請求項13のいずれか1項に記載のシール付き軸受。
- 前記シール部材のシールリップ部を、対向する軌道輪に対してラジアル方向に接触する形状としたことを特徴とする請求項10~請求項13のいずれか1項に記載のシール付き軸受。
- 前記シール部材に、このシール部材が前記他方の軌道輪に吸着することを防止する吸着防止手段を設けたことを特徴とする請求項10~請求項15のいずれか1項に記載のシール付き軸受。
Priority Applications (6)
Application Number | Priority Date | Filing Date | Title |
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CN200980122270.7A CN102066786B (zh) | 2008-06-13 | 2009-05-26 | 保持器、深沟球轴承及带密封件轴承 |
BRPI0915147A BRPI0915147B8 (pt) | 2008-06-13 | 2009-05-26 | Retentor, mancal de esfera com sulco profundo e mancal vedado |
US12/993,520 US8727631B2 (en) | 2008-06-13 | 2009-05-26 | Retainer, deep groove ball bearing, and bearing with seal |
EP17153050.4A EP3179122B1 (en) | 2008-06-13 | 2009-05-26 | Two-piece ball bearing retainer, deep groove ball bearing, and ball bearing with retainer and seal |
BR122019024860-5A BR122019024860B1 (pt) | 2008-06-13 | 2009-05-26 | retentor, mancal de esfera de sulco profundo e mancal vedado |
EP09762365.6A EP2287481B1 (en) | 2008-06-13 | 2009-05-26 | Retainer, deep groove ball bearing, and bearing with seal |
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JP2008155909A JP5602345B2 (ja) | 2008-06-13 | 2008-06-13 | 保持器および深溝玉軸受 |
JP2008-155909 | 2008-06-13 | ||
JP2008-178620 | 2008-07-09 | ||
JP2008178620A JP5455334B2 (ja) | 2008-07-09 | 2008-07-09 | シール付き軸受 |
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US (1) | US8727631B2 (ja) |
EP (2) | EP2287481B1 (ja) |
CN (1) | CN102066786B (ja) |
BR (2) | BR122019024860B1 (ja) |
WO (1) | WO2009150935A1 (ja) |
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WO2013002115A1 (ja) * | 2011-06-27 | 2013-01-03 | Ntn株式会社 | 転がり軸受 |
US9115762B2 (en) | 2011-06-27 | 2015-08-25 | Ntn Corporation | Rolling bearing |
JP2013036493A (ja) * | 2011-08-04 | 2013-02-21 | Ntn Corp | 転がり軸受 |
JP2015059617A (ja) * | 2013-09-19 | 2015-03-30 | Ntn株式会社 | 玉軸受用波形保持器および玉軸受 |
JP2014194281A (ja) * | 2014-06-11 | 2014-10-09 | Ntn Corp | 転がり軸受 |
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CN102066786B (zh) | 2015-04-22 |
EP2287481A4 (en) | 2015-04-22 |
BRPI0915147A2 (pt) | 2016-06-21 |
BRPI0915147A8 (pt) | 2019-12-24 |
CN102066786A (zh) | 2011-05-18 |
BR122019024860B1 (pt) | 2021-05-11 |
US20110069918A1 (en) | 2011-03-24 |
EP2287481A1 (en) | 2011-02-23 |
EP2287481B1 (en) | 2017-02-08 |
BRPI0915147B1 (pt) | 2020-09-15 |
US8727631B2 (en) | 2014-05-20 |
BRPI0915147B8 (pt) | 2021-11-09 |
EP3179122A1 (en) | 2017-06-14 |
EP3179122B1 (en) | 2020-02-12 |
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