WO2010079734A1 - 車輪用軸受シールおよびこれを備えた車輪用軸受装置 - Google Patents
車輪用軸受シールおよびこれを備えた車輪用軸受装置 Download PDFInfo
- Publication number
- WO2010079734A1 WO2010079734A1 PCT/JP2010/000012 JP2010000012W WO2010079734A1 WO 2010079734 A1 WO2010079734 A1 WO 2010079734A1 JP 2010000012 W JP2010000012 W JP 2010000012W WO 2010079734 A1 WO2010079734 A1 WO 2010079734A1
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- WIPO (PCT)
- Prior art keywords
- seal
- slinger
- wheel bearing
- lip
- wheel
- 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
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/16—Sealings between relatively-moving surfaces
- F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
- F16J15/3248—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings provided with casings or supports
- F16J15/3252—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings provided with casings or supports with rigid casings or supports
- F16J15/3256—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings provided with casings or supports with rigid casings or supports comprising two casing or support elements, one attached to each surface, e.g. cartridge or cassette seals
- F16J15/3264—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings provided with casings or supports with rigid casings or supports comprising two casing or support elements, one attached to each surface, e.g. cartridge or cassette seals the elements being separable from each other
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
- B60B27/00—Hubs
- B60B27/0073—Hubs characterised by sealing means
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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
- 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
- F16C33/7869—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted with a cylindrical portion to the inner surface of the outer race and having a radial portion extending inward
- F16C33/7879—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted with a cylindrical portion to the inner surface of the outer race and having a radial portion extending inward with a further sealing ring
- F16C33/7883—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted with a cylindrical portion to the inner surface of the outer race and having a radial portion extending inward with a further sealing ring mounted to the inner race and of generally L-shape, the two sealing rings defining a sealing with box-shaped cross-section
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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
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/16—Sealings between relatively-moving surfaces
- F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
- F16J15/3268—Mounting of sealing rings
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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
- F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
- F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
- F16C19/181—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact
- F16C19/183—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles
- F16C19/184—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement
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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
- F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
- F16C2240/12—Force, load, stress, pressure
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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
- F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
- F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
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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
- F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
- F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
- F16C2240/60—Thickness, e.g. thickness of coatings
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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
- F16C2326/00—Articles relating to transporting
- F16C2326/01—Parts of vehicles in general
- F16C2326/02—Wheel hubs or castors
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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
- F16C41/00—Other accessories, e.g. devices integrated in the bearing not relating to the bearing function as such
- F16C41/007—Encoders, e.g. parts with a plurality of alternating magnetic poles
Definitions
- the present invention relates to a wheel bearing seal comprising a pack seal with improved muddy water resistance, and more specifically, to reduce the sliding resistance of the seal to reduce torque, and to separate the seal before sealing and before assembly.
- the present invention relates to a wheel bearing seal that is prevented and improved in reliability and a wheel bearing device including the same.
- a wheel bearing device for supporting a wheel of an automobile or the like supports a hub wheel for mounting a wheel rotatably via a double row rolling bearing, and includes a drive wheel and a driven wheel.
- an inner ring rotation method is generally used for driving wheels
- an inner ring rotation method and an outer ring rotation method are generally used for driven wheels.
- the wheel bearing device has a structure called a first generation in which a wheel bearing composed of a double row angular ball bearing or the like is fitted between a knuckle and a hub wheel constituting a suspension device.
- Second generation structure in which body mounting flange or wheel mounting flange is formed directly on the outer periphery of the member, third generation structure in which one inner rolling surface is directly formed on the outer periphery of the hub wheel, or hub wheel, etc. It is roughly classified into a fourth generation structure in which the inner rolling surface is directly formed on the outer periphery of the outer joint member of the speed universal joint.
- bearings are fitted with seals to prevent leakage of grease sealed inside the bearings and to prevent rainwater and dust from entering from the outside.
- the torque of bearings has been reduced to improve the fuel efficiency of automobiles.
- the rotational torque of the bearing portion the rotational torque of the seal is dominant. That is, the sliding resistance of the seal is larger than the rolling resistance, and the ratio of the sliding resistance of the seal to the rotational torque is high. Further reduction in torque is required for the seal of the wheel bearing device.
- the damage by seal failure occupies more than the original bearing life such as peeling. Therefore, the bearing life can be reliably improved by enhancing the sealing performance and durability of the seal.
- the seal 50 includes a slinger 51 and an annular seal plate 52 that are arranged to face each other.
- the slinger 51 is an inner ring (not shown) that is formed into a substantially L-shaped section by pressing from a steel plate having rust prevention ability such as an austenitic stainless steel plate (JIS standard SUS304 type). ) And a standing plate portion 51b extending radially outward from the cylindrical portion 51a.
- the seal plate 52 is formed in a substantially L-shaped cross section and is attached to an outer member (not shown) serving as a fixed member.
- the seal plate 52 includes a metal core 53 and a seal member 54 that is vulcanized and bonded to the metal core 53.
- the core metal 53 is formed by press working from a steel plate having an antirust function, such as an austenitic stainless steel plate, and a cylindrical portion 53a fitted in the end portion of the outer member, and a radial direction from the cylindrical portion 53a It consists of the standing board part 53b extended inward.
- the seal member 54 is made of an elastic member such as nitrile rubber, and has first and second side lips 54 a and 54 b that are in sliding contact with the standing plate portion 51 b of the slinger 51.
- the first and second side lips 54 a and 54 b are formed to be inclined from the standing plate portion 53 b of the core metal 53 toward the outer diameter side, and their tips are fixed to the standing plate portion 51 b of the slinger 51 with a predetermined squeeze (contact It is in sliding contact with the load.
- a predetermined squeeze contact It is in sliding contact with the load.
- the sealing member 54 wraps around and adheres to the outer surface of the cylindrical portion 53a of the core metal 53 to improve airtightness, and wraps around and adheres to the inner edge of the standing plate portion 53b of the core metal 53, and A grease lip 54c protruding toward the cylindrical portion 51a side of the slinger 51 is formed.
- the grease lip 54 c has a predetermined pressing force with respect to the cylindrical portion 51 a of the slinger 51.
- the tension force P1 of the grease lip 54c contact load on the cylindrical portion 51a of the slinger 51
- the first side lip 54a and the first lip 54a The contact load P2 of the second side lip 54b (the total contact load of both side lips) is set to have the following relationship.
- the tension force P1 of the grease lip 54c is set to be greater than the contact load P2 of the first side lip 54a and the second side lip 54b, or the tension force P1 and the contact load P2 are equal.
- Such a contact load P2 between the first side lip 54a and the second side lip 54b is a force acting in a direction in which the seal plate 52 is to be separated from the slinger 51, and a pressing force P1 of the grease lip 54c. Is a force acting in a direction against the force to be separated, and by setting as in the above relational expression, the seal plate 52 in a single state before the seal 50 is mounted on the bearing. And the slinger 51 can be prevented from separating.
- seal plate 52 and the slinger 51 can be unitized and assembled to the bearing, it is not necessary to separately assemble them and the assembling property of the seal 50 to the bearing can be improved.
- the tension force P1 of the grease lip 54c is set to be larger than the contact load P2 of the first side lip 54a and the second side lip 54b.
- the present invention has been made in view of such conventional problems, and reduces the sliding resistance of the seal to reduce the torque, and also prevents the separation of the seal alone and the seal before assembly to improve reliability.
- An object of the present invention is to provide an improved wheel bearing seal and a wheel bearing device including the same.
- the invention according to claim 1 of the present invention includes an outer member in which a double row outer rolling surface is integrally formed on the inner periphery, and a double row rolling member on the outer member. It is inserted through a moving body and attached to an opening of an annular space formed between an inner member having a double row inner rolling surface facing the outer row rolling surface of the double row on the outer periphery.
- the slinger is formed in a substantially L-shaped cross section, and is outside the end of the inner member.
- the contact loads of the first and second side lips are F1 and F2, and the grease lip Is set such that F1 + F2 ⁇ 1.5 ⁇ F3.
- the seal is composed of a composite seal composed of an annular seal plate and a slinger, which are mounted on the opening of the annular space formed between the outer member and the inner member, and are arranged to face each other.
- the plate includes a metal core press-fitted into the inner periphery of the end of the outer member, and a seal member integrally joined to the metal core by vulcanization adhesion, and the seal member is inclined radially outward.
- the first and second side lips that extend and the grease lip that extends while inclining toward the inner side of the bearing are integrally formed, and the slinger is formed in a substantially L-shaped cross section, and is press-fitted into the outer periphery of the end of the inner member.
- the grease lip is in sliding contact with the part via a predetermined radial shimiro
- the relationship is set so that F1 + F2 ⁇ 1.5 ⁇ F3 when the contact loads of the first and second side lips are F1 and F2 and the tension force of the grease lip is F3. Therefore, it is possible to provide a wheel bearing seal with improved reliability by reducing the sliding resistance of the seal to reduce torque and preventing separation of the seal alone and before assembly. .
- the end surface on the outer diameter side of the seal plate and the end surface of the standing plate portion of the slinger are set to be flush with each other, and the width dimension of the seal plate is If it is set to be larger than the width dimension of the slinger, the seal plate and the slinger can be simultaneously press-fitted into the outer member and the inner ring in a state in which a predetermined scissors are maintained at the time of seal assembly.
- a gap can be secured between the adjacent slinger, and the first and second seals located at the lower part can be secured by their own weight. It is possible to prevent the side lip 2 from being excessively deformed and to prevent the grease lip from falling off from the cylindrical portion of the slinger and separating them, thereby improving the reliability of the seal quality.
- a magnetic encoder is integrally joined to the side surface of the standing plate portion of the slinger by vulcanization adhesion, and the magnetic encoder is mixed with magnetic powder in the elastomer, and the circumferential direction, etc. If the magnetic poles N and S are alternately magnetized, and the end face on the outer diameter side of the seal plate and the end face of the magnetic encoder are set to be flush with each other, a predetermined squeeze is maintained during seal assembly. In this state, the seal plate and the slinger can be simultaneously pressed into the outer member and the inner ring, and the air gap with the rotation speed sensor can be set with high accuracy.
- the seal plate when the seal plate is set to have a width dimension larger than a width dimension of the slinger including the magnetic encoder, the seal plates are adjacent when stacked. A gap can be secured between the slinger including the magnetic encoder, the first side lip and the second side lip of the seal located below can be prevented from being excessively deformed by its own weight, and the grease lip is a cylinder of the slinger. It is possible to prevent the two parts from being separated from each other.
- the thickness of the first side lip on the radially outer side of the first and second side lips is larger than the thickness of the second side lip. If the thickness is set, the contact load of the first side lip becomes larger than the contact load of the second side lip, and the muddy water resistance of the seal can be improved and the overall sliding resistance can be reduced. It is possible to reduce the torque and reduce the torque.
- a straight portion is provided between the first and second side lips, and the distance between the lips of the first and second side lips is maximum. If each lip is set so as not to interfere with each other when it is deformed, the deformation of one lip can be independently deformed without affecting the other.
- the seal member is made of synthetic rubber and the temperature TR10 of the seal member is set to ⁇ 35 ° C. or lower, the lip followability can be maintained even in a low temperature atmosphere. And can exhibit muddy water resistance.
- innumerable dimples are formed on the surface of the slinger in the range of Rz2 to 4 in surface roughness, and each lip is pre-applied with grease.
- An oil film can be easily formed at the contact portion between the lip and the slinger, reducing the sliding resistance of the seal, reducing the torque and reducing the lip wear.
- the vehicle body mounting flange for being attached to the knuckle is integrally formed on the outer periphery, and the double-row outer rolling surface is integrally formed on the inner periphery.
- An outer member a wheel mounting flange for mounting a wheel at one end, and an inner rolling surface facing one of the outer rolling surfaces of the double row on the outer periphery, and an axis from the inner rolling surface Hub wheel formed with a small-diameter step portion extending in the direction, and an inner ring fitted inside the small-diameter step portion of the hub wheel and having an inner rolling surface facing the other of the outer rolling surfaces of the double row on the outer periphery
- An inner member a double row rolling element that is rotatably accommodated between the rolling surfaces of the inner member and the outer member via a cage, and the outer member and the inner member.
- a wheel bearing device having a seal attached to an opening of an annular space formed between The seal of the inner side of the seal, consisting of a wheel bearing seal as claimed in any one claims 1 to 9.
- the inner ring is press-fitted and fixed to the hub ring, and the inner ring is immovable after assembly.
- the effect of the present invention that the seal can be assembled by simultaneously press-fitting the seal plate and the slinger into the outer member and the inner ring while maintaining the above can be exhibited.
- the wheel bearing seal according to the present invention includes an outer member in which a double row outer rolling surface is integrally formed on the inner periphery, and the outer member is inserted into the outer member via a double row rolling element.
- the seal plate includes a core bar press-fitted into the inner periphery of the end portion of the outer member, and a seal member integrally joined to the core bar by vulcanization adhesion.
- the seal member integrally includes first and second side lips extending obliquely outward in the radial direction and a grease lip extending inclined toward the inner side of the bearing, and the slinger has a substantially L-shaped cross section. And a cylindrical portion that is press-fitted into the outer periphery of the end portion of the inner member. A standing plate portion extending radially outward from the cylindrical portion, and the first and second side lips are slidably contacted with the standing plate portion via a predetermined axial squeeze, and the green portion is connected to the cylindrical portion.
- (A) is a longitudinal cross-sectional view which shows 3rd Embodiment of the wheel bearing apparatus which concerns on this invention.
- (B) is an enlarged view showing a single seal of (a). It is a longitudinal cross-sectional view which shows 4th Embodiment of the wheel bearing apparatus which concerns on this invention. It is a longitudinal cross-sectional view which shows the conventional seal
- It is composed of a composite type seal composed of an annular seal plate and a slinger, which are attached to an opening of an annular space formed between the inner members having double row inner rolling surfaces.
- the seal plate includes a core bar that is press-fitted into the inner periphery of the end portion of the outer member, and a seal member that is integrally joined to the core bar by vulcanization adhesion.
- the first and second side lips extending obliquely and the grease lip extending inclined toward the bearing inward side are integrally formed, and the slinger is formed in a substantially L-shaped cross section.
- the first and second side lips are slidably contacted with the upright plate portion via a predetermined axial nip, and the grease lip is slid with the cylindrical portion via a predetermined radial nip.
- the end surface on the outer diameter side of the seal plate and the end surface of the standing plate portion of the slinger are set flush with each other, and the width dimension of the seal plate is the width dimension of the slinger Set so that the contact load of the first and second side lips is F1 and F2, and the tension force of the grease lip is F3, so that the relation of F1 + F2 ⁇ 1.5 ⁇ F3 is established.
- the grease lip does not fall off the cylindrical portion of the slinger. Arrangement Is placed.
- FIG. 1 is a longitudinal sectional view showing a first embodiment of a wheel bearing according to the present invention
- FIG. 2 is an enlarged view showing a seal according to the present invention
- FIG. 3 is an explanation showing an operation of the seal of FIG.
- FIGS. 4 and 4 are explanatory views showing the laminated state of the seal of FIG. 2
- FIG. 5 is an enlarged view showing a modification of the seal of FIG.
- the side closer to the outside of the vehicle in the state assembled to the vehicle is referred to as an outer side (left side in FIG. 1)
- the side closer to the center is referred to as an inner side (right side in FIG.
- the wheel bearing 1 is used in a wheel bearing device and is referred to as a first generation.
- the wheel bearing 1 is an outer member 2 in which double rows of outer rolling surfaces 2a, 2a are integrally formed on the inner periphery, and the above-mentioned compound on the outer periphery.
- a pair of inner rings 3 and 3 formed with an inner rolling surface 3a opposite to the outer rolling surfaces 2a and 2a of the row, and double row rolling elements (balls) 4 and 4 accommodated between the rolling surfaces;
- the holders 5 and 5 that hold the rolling elements 4 and 4 so as to freely roll, and the seals attached to the openings of the annular space formed between the outer member 2 and the pair of inner rings 3 and 3. 6 and 7.
- the outer member 2 is made of high carbon chromium bearing steel such as SUJ2 (JIS G 4805) or carburized steel. In the case of high carbon chromium bearing steel, it is quenched at 820 to 860 ° C., then tempered at 160 to 200 ° C., and hardened to the core in the range of 58 to 64 HRC. In the case of carburized steel, the surface is hardened in the range of 58 to 64 HRC.
- the inner ring 3 is also made of high carbon chrome bearing steel such as SUJ2 or carburized steel, like the outer member 2, and in the case of high carbon chrome bearing steel, the core is hardened in the range of 58 to 64 HRC and carburized steel. In this case, the surface is cured in the range of 58 to 64 HRC.
- the rolling element 4 is made of a high carbon chrome bearing steel such as SUJ2, and is hardened in the range of 58 to 64 HRC to the core portion by quenching.
- This wheel bearing 1 is set in a state where the small diameter side (front side) end faces 3b and 3b of the pair of inner rings 3 and 3 are abutted, and constitutes a so-called back-to-back type double row angular ball bearing. . Further, the seals 6 and 7 prevent leakage of the lubricating grease sealed inside the bearing and intrusion of rainwater, dust, and the like from the outside into the bearing.
- the seal 6 on the outer side of the seals 6, 7 is a cored bar 8 press-fitted through a predetermined shimiro to the inner periphery of the outer side end portion of the outer member 2 serving as a fixed side member. It is composed of an integrated seal composed of a joined seal member 9.
- the inner-side seal 7 is composed of a composite seal composed of an annular seal plate 10 and a slinger 11 arranged so as to face each other, a so-called pack seal.
- the seal plate 10 includes a cored bar 12 attached to the outer member 2 and a seal member 13 joined to the cored bar 12 by vulcanization adhesion.
- the core metal 12 is formed by pressing from a steel plate having rust prevention ability such as an austenitic stainless steel plate (JIS standard SUS304 type) or a rust-proof cold rolled steel plate (JIS standard SPCC type).
- a cylindrical fitting portion 12a that is formed in a substantially L-shaped cross section, is press-fitted into the outer member 2, has a slightly reduced diameter at the end, and is formed radially inward from the fitting portion 12a. And an inner diameter portion 12b.
- the seal member 13 is made of a synthetic rubber such as NBR (acrylonitrile-butadiene rubber), and extends first and second side lips 13a and 13b extending obliquely outward in the radial direction and inclined inward of the bearing. And a grease lip 13c. And it goes around from the outer surface of the end part of the fitting part 12a of the metal core 12 to the inner edge of the inner diameter part 12b, and it is aiming at airtight improvement.
- the material of the seal member 13 includes, for example, HNBR (hydrogenated acrylonitrile-butadiene rubber), EPM, EPDM (ethylene / propylene rubber), etc., which have excellent heat resistance, heat resistance and chemical resistance. Examples thereof include ACM (polyacrylic rubber), FKM (fluororubber), and silicon rubber, which are excellent in properties.
- the slinger 11 has a substantially L-shaped cross section, and includes a cylindrical portion 11a that is press-fitted into the outer diameter of the inner ring 3, and a standing plate portion 11b that extends radially outward from the cylindrical portion 11a.
- the first and second side lips 13a, 13b of the seal member 13 are slidably contacted with the upright plate portion 11b via a predetermined axial shimiro (contact load), and the grease lip 13c is predetermined with the cylindrical portion 11a.
- the standing plate portion 11b of the slinger 11 is opposed to the seal plate 10 through a slight radial clearance to form a labyrinth seal 14.
- the end surface on the inner side of the seal plate 10 and the end surface of the standing plate portion 11b of the slinger 11 are set to be flush with each other, and the width dimension W1 of the seal plate 10 is set larger than the width dimension W2 of the slinger 11. (W1> W2).
- the first and second side lips 13a and 13b of the seal 7 located below due to its own weight can be prevented from being excessively deformed, and the grease lip 13c is detached from the cylindrical portion 11a of the slinger 11 and separated from each other. Can be prevented, and the reliability of the quality of the seal 7 can be improved.
- the contact load of the first and second side lips 13a and 13b and the tension force of the grease lip 13c are set to have a predetermined relationship. That is, when the contact loads of the first and second side lips 13a and 13b are F1 and F2, and the tension force of the grease lip 13c is F3, the sum of the contact loads F1 and F2 of the two side lips 13a and 13b. Is set to be smaller than 1.5 times the tension force F3 of the grease lip 13c (F1 + F2 ⁇ 1.5 ⁇ F3).
- the tension force (center of shimeshiro) F3 of the grease lip 13c is 12N
- the sum of the contact loads (center of shimeshiro) F1 and F2 of the first and second side lips 13a and 13b is set to 18N or less. Has been.
- each lip is arranged so that the grease lip 13c does not fall off the cylindrical portion 11a of the slinger 11 even in such a state.
- a seal 15 shown in FIG. 5 is a modification of the seal 7 described above.
- the shape of the seal 15 is basically the same as that of the seal 7, but the thickness of the first and second side lips 13a and 13b and the distance between ships are defined.
- the thickness L1 of the first side lip 13a is set to be thicker than the thickness L2 of the second side lip 13b (L1> L2).
- the straight portions 16 are provided between the lips so that when the lips are deformed, they are set so as not to interfere with each other and the deformation of one lip is independently deformed without affecting the other. .
- the contact load of the first side lip 13a becomes larger than the contact load of the second side lip 13b, the muddy water resistance of the seal 15 can be improved, and the overall sliding resistance is reduced. Lower torque can be achieved.
- the temperature TR10 (an index representing the elasticity of rubber) indicating a low temperature elastic recovery rate of 10% of the sealing member 13 made of synthetic rubber is set to ⁇ 35 ° C. or lower.
- FIG. 6 is a longitudinal sectional view showing a second embodiment of the wheel bearing according to the present invention
- FIG. 7 is an enlarged view showing the seal according to the present invention
- FIG. 8 shows a laminated state of the seal of FIG. It is explanatory drawing. Note that the same parts and parts as those in the above-described embodiment (FIG. 1) or parts and parts having the same functions are denoted by the same reference numerals and detailed description thereof is omitted.
- the wheel bearing 17 is referred to as a second generation, and has a vehicle body mounting flange 18b integrally attached to a knuckle (not shown) on the outer periphery, and double row outer rolling surfaces 18a, 18a on the inner periphery.
- An outer member 18 formed integrally, a pair of inner rings 3, 3 having an outer periphery formed with an inner rolling surface 3a opposite to the double row outer rolling surfaces 18a, 18a, and between both rolling surfaces Formed between the accommodated double-row rolling elements 4, 4, the cages 5, 5 that hold these rolling elements 4, 4, and the outer member 18 and the pair of inner rings 3, 3.
- seals 19 and 20 attached to the openings of the annular space.
- the outer member 18 is formed of medium and high carbon steel containing 0.40 to 0.80 wt% of carbon such as S53C, and at least the double row outer rolling surfaces 18a and 18a are hardened in the range of 58 to 64 HRC by induction hardening. Has been processed.
- seals 19 and 20 basically differ only in the presence or absence of a magnetic encoder, only the inner seal 20 will be described, and the outer seal 19 is omitted here.
- the seal 20 is constituted by a so-called pack seal composed of an annular seal plate 21 and a slinger 11 'arranged to face each other.
- the seal plate 21 includes a cored bar 22 attached to the outer member 18 and a seal member 23 integrally joined to the cored bar 22 by vulcanization adhesion.
- the cored bar 22 is formed by pressing a steel plate having rust prevention ability such as an austenitic stainless steel plate (JIS standard SUS304 type) or a rust-proof cold rolled steel plate (JIS standard SPCC type).
- a cylindrical fitting portion 22a that is formed in a substantially L-shaped cross section, is press-fitted into the outer member 18, has a slightly reduced diameter at the end, and is formed radially inward from the fitting portion 22a. And an inner diameter portion 22b.
- the seal member 23 is made of a synthetic rubber such as NBR, and has first and second side lips 23a and 23b extending inclined outward in the radial direction, and a grease lip 23c extending inclined inward of the bearing. is doing. And it goes around and fixes from the outer surface of the end part of the fitting part 22a of the metal core 22 to the inner edge of the inner diameter part 22b, and the airtightness is improved.
- the first and second side lips 23a and 23b of the seal member 23 are slidably contacted with the standing plate portion 11b 'of the slinger 11' via a predetermined axial squeeze (contact load), and the grease lip 23c is a cylindrical portion. 11a 'is slidably contacted via a predetermined radial shimiro.
- the magnetic encoder 24 is integrally joined to the side surface of the upright plate portion 11b 'by vulcanization bonding or the like. This magnetic encoder 24 is a rotary encoder for detecting the rotational speed of a wheel by mixing magnetic powder such as ferrite in an elastomer such as rubber and magnetizing the magnetic poles N and S alternately in the circumferential direction. Yes.
- the end face on the inner side of the seal plate 21 and the end face of the magnetic encoder 24 are set to be flush with each other, and a tongue piece 25 protruding inward of the bearing is formed on the inner diameter portion of the core metal 23.
- the width dimension W3 of 21 is set larger than the width dimension W4 of the slinger 11 ′ including the magnetic encoder 24 (W3> W4).
- countless dimples are formed on the surface of the slinger 11 'by shot peening or the like, and grease is applied to each lip in advance.
- the unevenness of the dimple is set in the range of Rz2 to 4 in terms of surface roughness.
- Rz refers to the ten-point average roughness of the JIS roughness shape parameter (JIS B0601-1994).
- dimples are formed on the surface of the slinger 11 ', but dimples may be formed on the surface of each lip by blending synthetic rubber or the like.
- FIG. 9A is a longitudinal sectional view showing a third embodiment of the wheel bearing device according to the present invention
- FIG. 9B is an enlarged view showing a single seal of FIG.
- symbol is attached
- This wheel bearing device is called a second generation of the outer ring rotating type on the driven wheel side, and has a wheel mounting flange 26 for mounting a wheel (not shown) on the outer periphery, and a double row outer side on the inner periphery.
- the outer member 27 is formed of medium and high carbon steel containing 0.40 to 0.80 wt% of carbon such as S53C, and at least the double row outer rolling surfaces 27a and 27a are hardened in the range of 58 to 64HRC by induction hardening. Has been processed.
- the seal 19 is composed of a pack seal made up of an annular seal plate 21 and a slinger 11 that are arranged to face each other.
- the seal plate 21 includes a cored bar 22 attached to the outer member 27 and a seal member 23 integrally joined to the cored bar 22 by vulcanization adhesion.
- the seal member 23 is made of a synthetic rubber such as NBR, extends in a radially outward direction, and is slidably contacted with the standing plate portion 11b of the slinger 11 via a predetermined axial shimiro. Lips 23a and 23b, and a grease lip 23c extending obliquely inwardly of the bearing and slidably contacted with the cylindrical portion 11a via a predetermined radial shimiro.
- the end surface on the inner side of the seal plate 21 and the side surface of the standing plate portion 11 b of the slinger 11 are set to be flush with each other, and a tongue piece 25 that protrudes inward of the bearing is formed on the inner diameter portion of the core metal 23.
- the width dimension W5 of the seal plate 21 is set to be larger than the width dimension W6 of the slinger 11 (W5> W6). Accordingly, the seal plate 21 and the slinger 11 can be simultaneously press-fitted into the outer member 27 and the inner ring 3 while maintaining a predetermined squeeze at the time of seal assembly.
- the contact loads F1, F2 and the grease of the first and second side lips 23a, 23b are caused by the centrifugal force accompanying the rotation of the outer member 27.
- the tension force F3 of the slip 23c decreases, the sum of the contact loads F1, F2 of the two side lips 23a, 23b is more than 1.5 times the tension force F3 of the grease lip 23c, as in the above-described embodiment. It is set to be small (F1 + F2 ⁇ 1.5 ⁇ F3).
- FIG. 10 is a longitudinal sectional view showing a fourth embodiment of the wheel bearing device according to the present invention.
- symbol is attached
- This wheel bearing device is called the third generation on the driven wheel side, and includes an inner member 30 comprising a hub wheel 29 and an inner ring 3 fixed to the hub wheel 29, and a plurality of rows of inner members 30. And an outer member 31 inserted through the rolling elements 4 and 4.
- the hub wheel 29 integrally has a wheel mounting flange 26 at an end portion on the outer side, one (outer side) inner rolling surface 29a on the outer periphery, and a small-diameter step portion extending in the axial direction from the inner rolling surface 29a. 29b is formed.
- the inner ring 3 is formed with the other (inner side) inner raceway surface 3a on the outer periphery, and is press-fitted into the small-diameter step portion 29b of the hub wheel 29 via a predetermined shishiro, and the end portion of the small-diameter step portion 29b is radially outward. It is fixed in the axial direction in a state where a predetermined bearing preload is applied by a caulking portion 29c formed by plastic deformation in the direction.
- the hub wheel 29 is formed of medium and high carbon steel containing carbon of 0.40 to 0.80 wt% such as S53C, and includes a wheel mounting flange 26 that serves as a seal land portion of an outer side seal 32 described later, including an inner rolling surface 29a.
- the surface is hardened in the range of 58 to 64 HRC by induction hardening from the inner side base portion 26b to the small diameter step portion 29b.
- the outer member 31 integrally has a vehicle body mounting flange 31b to be attached to a knuckle (not shown) constituting a suspension device on the outer periphery, and the inner rolling surfaces 29a, 3a of the inner member 30 on the inner periphery. Opposing double-row outer rolling surfaces 31a, 31a are integrally formed. Between these rolling surfaces 31a, 29a and 31a, 3a, double-row rolling elements 4, 4 are accommodated via a cage 5 so as to roll freely.
- This outer member 31 is made of medium-high carbon steel containing 0.40 to 0.80 wt% of carbon such as S53C, and at least the double row outer rolling surfaces 31a and 31a have a surface in the range of 58 to 64 HRC by induction hardening. It has been cured.
- seals 32 and 20 are attached to the opening of the annular space formed between the outer member 31 and the inner member 30, and leakage of the lubricating grease sealed inside the bearing to the outside and from the outside It prevents rainwater and dust from entering the bearing.
- the seal 32 on the outer side of the seals 32 and 20 includes a core metal 33 press-fitted to the inner periphery of the outer end portion of the outer member 31 through a predetermined shimiro, and a seal member joined to the core metal 33. 34 and an integral seal.
- the seal member 34 is made of a synthetic rubber such as NBR, and is integrally joined to the cored bar 33 by vulcanization adhesion, and is formed with a side lip 34a and a dust lip 34b that are formed to incline radially outward, and on the inner side of the bearing.
- a grease lip 34c formed in an inclined manner is integrally provided.
- the base 26b on the inner side of the wheel mounting flange 26 is formed in a curved surface having an arc-shaped cross section, and the side lip 34a and the dust lip 34b are slidably contacted with the base 26b with a predetermined squeeze, and the grease lip 34c has a predetermined diameter. It is slidably contacted through a direction shimoshiro.
- the material of the seal member 34 is, for example, HNBR, EPDM (ethylene-propylene rubber) having excellent heat resistance, ACM, FKM, or silicon having excellent heat resistance and chemical resistance. A rubber etc. can be illustrated.
- the inner seal 20 is composed of a pack seal composed of the annular seal plate 21 and the slinger 11 ′ arranged to face each other.
- the seal plate 21 includes a cored bar 22 attached to the outer member 31 and a seal member 23 integrally joined to the cored bar 22 by vulcanization adhesion.
- the width dimension W3 of the seal plate 21 is set larger than the width dimension W4 of the slinger 11 ′ including the magnetic encoder 24, and the contact loads of the first and second side lips 23a, 23b are set to F1 and F2. Since the total sum is set to be smaller than 1.5 times the force F3 of the grease lip 23c, the sliding resistance of the seal 20 is reduced to reduce torque, and the seal 20 alone and before assembly. Separation of the seal 20 can be prevented.
- the inner ring 3 is assembled to the hub ring 29 and simultaneously fixed in the axial direction by the crimping portion 29c.
- the seal 20 can be assembled by pressing the seal plate 21 and the slinger 11 'into the outer member 31 and the inner ring 3 at the same time while preventing separation before assembly and maintaining a predetermined level. Is big.
- the wheel bearing seal according to the present invention can be applied to the wheel bearing device of the first to third generation structure regardless of the driving wheel side or the driven wheel side.
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Abstract
Description
図1は、本発明に係る車輪用軸受の第1の実施形態を示す縦断面図、図2は、本発明に係るシールを示す拡大図、図3は、図2のシールの作用を示す説明図、図4は、図2のシールの積層状態を示す説明図、図5は、図2のシールの変形例を示す拡大図である。なお、以下の説明では、車両に組み付けた状態で車両の外側寄りとなる側をアウター側(図1の左側)、中央寄り側をインナー側(図1の右側)という。
2、18、27、31 外方部材
2a、18a、27a、31a 外側転走面
3 内輪
3a、29a 内側転走面
3b 小径側端面
4 転動体
5 保持器
6、7、15、19、20、32 シール
8、12、22、33 芯金
9、13、23、34 シール部材
10、21 シール板
11、11’ スリンガ
11a、11a’ 円筒部
11b、11b’ 立板部
12a、22a 嵌合部
12b、22b 内径部
13a、23a 第1のサイドリップ
13b、23b 第2のサイドリップ
13c、23c、34c グリースリップ
14 ラビリンスシール
16 ストレート部
18b、31b 車体取付フランジ
24 磁気エンコーダ
25 舌片
26 車輪取付フランジ
26a ハブボルト
26b 基部
28 シールド
29 ハブ輪
29b 小径段部
29c 加締部
30 内方部材
34a サイドリップ
34b ダストリップ
50 シール
51 スリンガ
51a、53a 円筒部
51b、53b 立板部
52 シール板
53 芯金
54 シール部材
54a 第1のサイドリップ
54b 第2のサイドリップ
54c グリースリップ
F1 第1のサイドリップの接触荷重
F2 第2のサイドリップの接触荷重
F3 グリースリップの緊迫力
L1 第1のサイドリップの厚さ
L2 第2のサイドリップの厚さ
L リップ間距離
W1、W3、W5 シール板の幅寸法
W2、W4、W6 スリンガの幅寸法
ΔW スリンガの間隙
P1 グリースリップの緊迫力
P2 サイドリップの接触荷重
Claims (10)
- 内周に複列の外側転走面が一体に形成された外方部材と、この外方部材に複列の転動体を介して内挿され、外周に前記複列の外側転走面に対向する複列の内側転走面を有する内方部材との間に形成された環状空間の開口部に装着され、互いに対向配置された環状のシール板とスリンガとからなる複合型のシールで構成され、
前記シール板が、前記外方部材の端部内周に圧入される芯金と、この芯金に加硫接着により一体に接合されたシール部材とを備え、このシール部材が、径方向外方に傾斜して延びる第1および第2のサイドリップと、軸受内方側に傾斜して延びるグリースリップとを一体に有すると共に、
前記スリンガが断面略L字状に形成され、前記内方部材の端部外周に圧入される円筒部と、この円筒部から径方向外方に延びる立板部とを有し、この立板部に前記第1および第2のサイドリップが所定の軸方向シメシロを介して摺接され、前記円筒部に前記グリースリップが所定の径方向シメシロを介して摺接された車輪用軸受シールにおいて、
前記第1および第2のサイドリップの接触荷重をF1、F2とし、前記グリースリップの緊迫力をF3とした時、F1+F2≦1.5×F3の関係になるように設定されていることを特徴とする車輪用軸受シール。 - 前記シールが、単体の状態で前記第1および第2のサイドリップの接触荷重の反力で前記スリンガが移動しても、前記グリースリップが前記スリンガの円筒部から脱落しないように配置されている請求項1に記載の車輪用軸受シール。
- 前記シール板の外径側の端面と前記スリンガの立板部の端面とが面一に設定されると共に、前記シール板の幅寸法が、前記スリンガの幅寸法よりも大きく設定されている請求項1または2に記載の車輪用軸受シール。
- 前記スリンガの立板部の側面に磁気エンコーダが加硫接着で一体に接合され、この磁気エンコーダがエラストマに磁性体粉が混入され、周方向等配で交互に磁極N、Sが着磁されると共に、前記シール板の外径側の端面と前記磁気エンコーダの端面とが面一に設定されている請求項1乃至3に記載の車輪用軸受シール。
- シール板の幅寸法が、前記磁気エンコーダを含む前記スリンガの幅寸法よりも大きく設定されている請求項4に記載の車輪用軸受シール。
- 前記第1および第2のサイドリップのうち径方向外方側の第1のサイドリップの厚さが、前記第2のサイドリップの厚さよりも肉厚に設定されている請求項1乃至5いずれかに記載の車輪用軸受シール。
- 前記第1および第2のサイドリップの間にストレート部が設けられると共に、当該第1および第2のサイドリップのリップ間距離が、最大シメシロで各リップが変形した際に互いに干渉しないように設定されている請求項1乃至6いずれかに記載の車輪用軸受シール。
- 前記シール部材が合成ゴムからなり、このシール部材の温度TR10が-35℃以下に設定されている請求項1乃至7いずれかに記載の車輪用軸受シール。
- 前記スリンガの表面に表面粗さでRz2~4の範囲にディンプルが無数に形成されると共に、前記リップに予めグリースが塗布されている請求項1乃至8いずれかに記載された車輪用軸受シール。
- 外周にナックルに取り付けられるための車体取付フランジを一体に有し、内周に複列の外側転走面が一体に形成された外方部材と、
一端部に車輪を取り付けるための車輪取付フランジを一体に有し、外周に前記複列の外側転走面の一方に対向する内側転走面と、この内側転走面から軸方向に延びる小径段部が形成されたハブ輪、およびこのハブ輪の小径段部に内嵌され、外周に前記複列の外側転走面の他方に対向する内側転走面が形成された内輪からなる内方部材と、
この内方部材と前記外方部材の両転走面間に保持器を介して転動自在に収容された複列の転動体と、
前記外方部材と内方部材との間に形成された環状空間の開口部に装着されたシールとを備えた車輪用軸受装置において、
前記シールのうちインナー側のシールが、前記請求項1乃至9いずれかに記載された車輪用軸受シールからなることを特徴とする車輪用軸受装置。
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DE112010000730T DE112010000730T5 (de) | 2009-01-07 | 2010-01-05 | Radlagerdichtung und mit der Radlagerdichtung versehene Radlagervorrichtung |
CN2010800095266A CN102333969B (zh) | 2009-01-07 | 2010-01-05 | 车轮轴承密封件以及设置有该密封件的车轮轴承装置 |
US13/177,596 US8267591B2 (en) | 2009-01-07 | 2011-07-07 | Wheel bearing seal and a wheel bearing apparatus provided with the wheel bearing seal |
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DE102005020653A1 (de) * | 2005-05-03 | 2006-11-09 | Schaeffler Kg | Abgedichtetes Radialwälzlager, insbesondere Radlager eines Kraftfahrzeuges |
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JP2008261463A (ja) | 2007-04-13 | 2008-10-30 | Ntn Corp | 回転速度検出装置付き車輪用軸受装置 |
JP2008261461A (ja) | 2007-04-13 | 2008-10-30 | Ntn Corp | 回転速度検出装置付き車輪用軸受装置 |
JP2008261462A (ja) | 2007-04-13 | 2008-10-30 | Ntn Corp | 回転速度検出装置付き車輪用軸受装置 |
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2010
- 2010-01-05 DE DE112010000730T patent/DE112010000730T5/de active Pending
- 2010-01-05 WO PCT/JP2010/000012 patent/WO2010079734A1/ja active Application Filing
- 2010-01-05 CN CN2010800095266A patent/CN102333969B/zh active Active
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2011
- 2011-07-07 US US13/177,596 patent/US8267591B2/en active Active
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US9090122B2 (en) | 2010-11-02 | 2015-07-28 | Ntn Corporation | Wheel bearing apparatus for a vehicle |
US9623703B2 (en) | 2012-02-07 | 2017-04-18 | Ntn Corporation | Wheel bearing apparatus for a vehicle |
US20210355995A1 (en) * | 2018-11-12 | 2021-11-18 | Nok Corporation | Sealing device and method for applying grease thereto |
US11927218B2 (en) * | 2018-11-12 | 2024-03-12 | Nok Corporation | Sealing device and method for applying grease thereto |
Also Published As
Publication number | Publication date |
---|---|
CN102333969A (zh) | 2012-01-25 |
DE112010000730T5 (de) | 2012-08-09 |
US8267591B2 (en) | 2012-09-18 |
CN102333969B (zh) | 2013-10-16 |
US20110262069A1 (en) | 2011-10-27 |
JP2010159791A (ja) | 2010-07-22 |
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