WO2004022992A1 - 車輪支持用転がり軸受ユニット - Google Patents
車輪支持用転がり軸受ユニット Download PDFInfo
- Publication number
- WO2004022992A1 WO2004022992A1 PCT/JP2003/011113 JP0311113W WO2004022992A1 WO 2004022992 A1 WO2004022992 A1 WO 2004022992A1 JP 0311113 W JP0311113 W JP 0311113W WO 2004022992 A1 WO2004022992 A1 WO 2004022992A1
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- WO
- WIPO (PCT)
- Prior art keywords
- raceway
- bearing unit
- rolling bearing
- ring
- seal
- Prior art date
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C43/00—Assembling bearings
- F16C43/04—Assembling rolling-contact bearings
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
- B60B27/00—Hubs
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
- B60B35/00—Axle units; Parts thereof ; Arrangements for lubrication of axles
- B60B35/12—Torque-transmitting axles
- B60B35/18—Arrangement of bearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/02—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
-
- 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
- F16C25/00—Bearings for exclusively rotary movement adjustable for wear or play
- F16C25/06—Ball or roller bearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- 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
-
- 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
- F16C19/185—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 with two raceways provided integrally on a part other than a race ring, e.g. a shaft or housing
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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
- F16C19/186—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 with three raceways provided integrally on parts other than race rings, e.g. third generation hubs
-
- 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
-
- 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
Definitions
- the present invention relates to an improvement in a wheel supporting rolling bearing unit for rotatably supporting wheels on a suspension system of a vehicle (automobile).
- Japanese Patent Application Laid-Open No. 2001-221432 describes a structure as shown in FIGS. First of all,
- a wheel 1 constituting a wheel is rotatably supported on an end of an axle 3 constituting a suspension device by a rolling bearing unit 2 for supporting a wheel. That is, the inner races 5, which are stationary raceways, constituting the wheel supporting rolling bearing unit 2, are externally fitted to the support shaft 4 fixed to the end of the axle 3, and the inner race 5, 5 is fixed.
- the wheel 1 is fixedly connected to a hub 7, which is a rotating raceway, constituting the wheel supporting rolling unit 2 by a plurality of studs 8, 8 and nuts 9, 9.
- the inner circumferential surface of the hub 7 is formed with double-row outer raceways 10a and 10b, each of which is a rotating raceway surface, and the outer circumferential surface is formed with a mounting flange 11 respectively.
- the wheel 1 is mounted on one side of the mounting flange 11 (the outer side in the illustrated example, the left side in FIGS. 10 to 11) together with the drum 12 for constituting the braking device.
- Each of the outer ring raceways 10a, 10b and the inner ring raceways 13, 13 formed on the outer peripheral surface of each of the inner races 5, 5 are stationary raceway surfaces.
- a plurality of balls 14 and 14 are provided so as to roll freely while being held by retainers 15 and 15 respectively.
- the hub 7 is rotatably mounted around each of the inner races 5, 5 with radial load and thrust. The load is supported freely.
- sinorelle rings 16 a, 16 b, and the balls 14, 14 are respectively provided.
- the outer end of the hub 7 (the term “outside in the axial direction” refers to the outside in the width direction when assembled to the vehicle. Similarly, the center side in the width direction is referred to as "in”. The same applies to the entire specification). Closed by cap 17.
- the support shaft 4 having the inner rings 5, 5 fitted externally is fixed to the axle 3, and the mounting flange 1 of the hub 7 is fixed.
- a drum drum for braking is constructed by combining the drum 12 of these with a wheel cylinder and a shoe (not shown) supported on a backing plate 18 fixed to the end of the axle 3. At the time of braking, a pair of shoes provided on the inner diameter side of the drum 12 are pressed against the inner peripheral surface of the drum 12.
- a hub 7a which is a rotating raceway
- an outer race 19 which is a stationary raceway
- balls 14 and 14 It is rotatably supported.
- double-row outer raceways 10 a and 10 b each of which is a stationary raceway surface, are provided on the inner peripheral surface of the outer race 19, and a rotating raceway surface is formed on the outer peripheral surface of the hub 7 a.
- Certain first and second inner raceways 20 and 21 are provided, respectively.
- the hub 7a is formed by combining a hub body 22 as a main shaft member and an inner ring 23.
- the mounting flange 11 a for supporting the wheel is provided at the outer end of the outer peripheral surface of the hub body 22, the first inner raceway 20 is also provided at the intermediate portion, and the portion near the inner end of the intermediate portion is also provided.
- a small-diameter step portion 24 having a smaller diameter than the portion where the first inner raceway 20 is formed is provided.
- the inner ring 23 provided with the second inner ring raceway 21 having an arc-shaped cross section on the outer peripheral surface is fitted on the small-diameter stepped portion 24.
- the inner end surface of the inner ring 23 is pressed down by a caulking portion 25 formed by plastically deforming the inner end portion of the hub body 22 radially outward, and the inner ring 23 is attached to the hub body 22. It is fixed for. Furthermore, seal rings 16 c and 16 d are provided between the inner peripheral surface of both ends of the outer ring 19, the outer peripheral surface of the intermediate portion of the hub 7 a, and the outer peripheral surface of the inner end of the inner ring 23, respectively. The space provided with the balls 14 and 14 between the inner peripheral surface of the outer ring 19 and the outer peripheral surface of the hub 7a is isolated from the external space.
- the first inner raceway 20 is formed directly on the outer peripheral surface of the intermediate portion of the hub body 22.
- the first inner ring raceway 20 is connected to the center of the hub body 22 as in the structure shown in FIG. Rigidity is lower than when formed directly on the outer peripheral surface of the part.
- Hei 8-3-193979 by mixing plastic particles impregnated with a lubricant into a rubber composition constituting a seal material, a sliding contact portion between the seal material and a mating surface is formed. There is known a technique for reducing the sliding resistance.
- Japanese Patent Application Laid-Open No. H08-3193979 discloses that the above rubber composition is applied to a rolling bearing unit for supporting wheels to obtain a high-performance structure as a whole. There is no description.
- the rolling bearing unit for supporting a wheel which is the object of the present invention, even if the rotational torque is reduced, in order to secure the steering stability, to secure the support rigidity of the wheel, and to ensure the durability of the rolling bearing unit.
- it is necessary to increase the rigidity of the rolling bearing unit to secure the support rigidity but simply increase the preload applied to each rolling element in order to increase the rigidity. Then, the rolling resistance of each of the rolling elements increases, and the rotation torque cannot be reduced.
- the sliding resistance of the seal ring is merely considered to be low, it is not possible to sufficiently prevent foreign substances from entering the internal space of the rolling bearing unit, and the durability cannot be sufficiently secured. .
- the rolling bearing unit for supporting a wheel according to the present invention was invented in view of such circumstances, and realizes a structure having high rigidity, excellent durability, and low rotational torque.
- the rolling bearing unit for supporting a wheel includes a stationary-side bearing ring, a rotating-side bearing ring, and a plurality of balls, as in the above-described conventionally known wheel-supporting rolling bearing unit. And a seal ring.
- the stationary raceway is supported and fixed to the suspension device in use.
- the rotating raceway supports and fixes the wheel in use.
- each of the balls is provided between the stationary raceway surface and the rotating raceway surface which are present on the peripheral surfaces of the stationary raceway ring and the rotating raceway ring facing each other and each have an arc-shaped cross section. Have been killed.
- one of the stationary-side bearing ring and the rotating-side bearing ring which is located radially inward includes a main shaft member and an inner ring.
- the main shaft member is formed on the stationary side raceway surface or the rotation side raceway surface directly formed at the axially intermediate portion of the outer peripheral surface.
- a small-diameter step portion formed at one axial end of the outer peripheral surface.
- the inner ring has a stationary inner raceway surface or a rotation-side raceway surface formed with a second inner raceway on its outer peripheral surface, and is fitted and fixed to the small-diameter stepped portion.
- each of the two seal rings has two or three seal lips, each of which is made of an elastic material, and which has a front end edge slidably in contact with a mating surface.
- the axial load for applying a preload to each of the balls is 1.9 to 4.9 kN.
- the stiffness coefficient is 0.09 or more.
- the sum of the above two seal rings is 0.06 to 0.4 ⁇ ⁇ ⁇ .
- the torque required for relative rotation of the stationary raceway ring and the rotating raceway ring at 20 Omin- 1 (200 rotations per minute) based on the rolling resistance of each ball is 0.15 to 0.45 N ⁇ m.
- the rigidity coefficient described in this specification is the rigidity R CkN ⁇ m / deg of the wheel supporting rolling bearing unit, and the radial dynamic load rating C of the wheel supporting rolling bearing unit. r [N] (R / C r).
- the rigidity R in this case is the above-mentioned two races when a moment load is applied to the rotating race while the stationary race constituting the rolling bearing unit for wheel support is fixed. It is expressed in terms of the inclination angle, and is measured, for example, as shown in FIG. FIG. 12 shows a state where the rigidity R of the rolling bearing unit 2a for wheel support shown in FIG. 11 is measured.
- the outer race 19, which is the stationary raceway, is fixed to the upper surface of the fixed base 26, and the mounting flange 11a of the hub 7a, which is the rotating raceway, is attached to the base end of the lever plate 27 (The left end of 2). Then, a load is applied to the upper surface of the lever plate 27, for example, at a portion separated by a distance L corresponding to the rotation radius of the tire from the rotation center of the hub 7a, and is applied to the hub 7a via the lever plate 27.
- the 1.5 kN'm mode Load is applied to the upper surface of the lever plate 27, for example, at a portion separated by a distance L corresponding to the rotation radius of the tire from the rotation center of the hub 7a, and is applied to the hub 7a via the lever plate 27.
- the inclination angle is determined by the inclination of the mounting surface 29 of the mounting flange 1 1a with respect to the upper surface 28 of the fixed base 26. Measure as angle [ deg ]. Then, the rigidity R [kNm / deg] is obtained by dividing the moment load (1.5 kN'm) by the inclination angle. Further, the rigidity coefficient is obtained by dividing the rigidity R by the radial dynamic load rating Cr [N] of the wheel supporting rolling bearing unit 2a.
- the rotating torque can be sufficiently reduced while securing the required rigidity and durability.
- the axial load for applying a preload to each ball is restricted to the range of 1.96 to 4.9 kN, so that the rotational torque is reduced while securing rigidity and durability. Can be achieved. If the axial load is less than 1.96 kN, the preload is insufficient, the rigidity of the wheel supporting rolling bearing unit is insufficient, and the vehicle incorporating the wheel supporting rolling bearing unit is required. Steering stability deteriorates.
- the axial load exceeds 4.9 kN
- the preload becomes excessive (the contact pressure at the rolling contact portion becomes too high), and the wheel supporting rolls
- the rolling resistance (rotation torque) of the bearing unit is too large.
- the amount of heat generated at the rolling contact portion becomes excessively large, so that the temperature inside the wheel supporting rolling bearing unit increases significantly, and the grease sealed therein easily deteriorates early.
- the durability of the wheel supporting rolling bearing unit is reduced.
- the rolling fatigue life of the stationary raceway surface, the rotating raceway surface, and the rolling surface of each ball is reduced, and the rolling shaft for supporting the wheel is also seen from this surface.
- the durability of the receiving unit decreases.
- the axial load for applying a preload to each ball is restricted to the range of 1.96 to 4.9 kN, so that the rigidity and Rotational torque can be reduced while ensuring durability.
- the rigidity coefficient is set to 0.09 or more, the rigidity of the rolling bearing unit for supporting the wheel is secured, and the operation of the vehicle incorporating the rolling bearing unit for supporting the wheel is controlled. Longitudinal stability can be ensured. Conversely, if the stiffness coefficient is less than 0.09, the steering stability deteriorates.
- the rigidity coefficient is preferably as high as possible from the viewpoint of ensuring steering stability, and thus no upper limit is particularly defined. It doesn't matter how high it is if you meet other requirements.
- generally considered methods include increasing the value of preload or increasing the pitch circle diameter of balls or the pitch in the axial direction of balls arranged in multiple rows. It is possible to do.
- the rolling bearing unit for supporting the wheel is made of a general steel material (the outer ring and the hapter are made of S53C, and the inner ring and the ball are made of SUJ2)
- the upper limit of the rigidity coefficient is 0.1. It will be about 8.
- a part (for example, a ball) or all of the components of the rolling bearing unit for supporting the wheel is made of ceramic, the above-mentioned rigidity can be obtained without increasing the preload.
- the coefficient can be increased. Therefore, in this case, it is conceivable to increase the stiffness coefficient beyond 0.18.
- the torque required for relatively rotating the stationary raceway ring and the rotating raceway ring at 20 O mirf 1 based on the friction between each of the seal lips provided on each of the two seal rings and the mating surface is described. Since the thickness is set to 0.06 to 0.4 N ⁇ m, the rotational torque can be sufficiently reduced while ensuring the durability of the rolling bearing unit for supporting the wheel.
- the sum of the rotational resistances of the two seal rings is independent of the structure of the seal rings. It was found that the suitability of the sealing performance could be determined by the size. Of course, a small difference between the rotational resistance of a pair of seal rings is important from the viewpoint of securing the sealing performance of a seal ring having a low rotational resistance. From this aspect, it is necessary to ensure that the rotational resistance of the seal ring with the lower rotational resistance is not less than 0.3 N ⁇ m. The rotational resistance of the seal ring with low rotational resistance is maintained at 0.03 N ⁇ m or more, and the total rotational resistance of the pair of seal rings is 0.06 N.m. It was also found that the above required seal performance could be obtained.
- the rolling bearing unit for supporting a wheel since the above-mentioned torque is ensured to be not less than 0.06 N-m, the surface of the sliding contact portion between the tip of each seal lip constituting the both seal rings and the opposite surface. A sufficient pressure can be ensured, and the sealing performance of the two seal rings can be sufficiently ensured. As a result, foreign matters such as muddy water can be effectively prevented from entering the inside of the wheel supporting rolling bearing unit, and the durability of the wheel supporting rolling bearing unit can be ensured. Conversely, as the torque is reduced to less than 0.06 Nm, the surface pressure of the sliding contact between the tip of each seal lip of the both seal rings and the mating surface can be reduced to prevent the foreign matter from entering. The function becomes insufficient, and the durability of the above-mentioned wheel support and rolling bearing unit decreases.
- the stationary raceway ring and the rotating raceway ring are relatively rotated at 200 min " 1 based on the friction between each seal lip and the mating surface.
- the required torque is restricted to the range of 0.06 to 0.4 N ⁇ m, so that the rotation torque can be reduced while ensuring durability.
- the torque required for relative rotation between the stationary raceway ring and the rotating raceway ring at 20 Omin- 1 based on the rolling resistance of each ball is 0.15 to 0.45 N'm.
- the running torque of the wheel supporting rolling unit as a whole can be suppressed to a sufficiently low level (0.85 N ⁇ m or less) while ensuring steering stability and durability. If the torque is low enough to be less than 0.15Nm, the preload must be considerably reduced, and as described above, the rigidity of the rolling bearing unit for supporting the wheel is insufficient, and the wheel support is insufficient. Driving stability of vehicles incorporating rolling bearing units is reduced.
- the torque required to relatively rotate the stationary side raceway and the rotating side raceway at 20 Omirf 1 based on the rolling resistance of each ball described above. Is regulated to the range of 0.15 to 0.45 N ⁇ m, so that the steering torque can be reduced while ensuring the steering stability and durability.
- FIG. 1 is a cross-sectional view showing a first example of a structure to which the present invention is applied.
- FIG. 2 is a cross-sectional view showing the second example
- FIG. 3 is a cross-sectional view showing the third example
- FIG. 4 is a partial cross-sectional view showing a first example of a specific structure of a seal ring applicable to the present invention.
- FIG. 5 is a partial cross-sectional view showing the second example
- FIG. 6 is a partial cross-sectional view showing the third example
- FIG. 7 is a partial cross-sectional view showing the fourth example
- FIG. 8 is a partial sectional view showing the fifth example
- FIG. 9 is a partial cross-sectional view showing an example of a structure capable of reducing sliding resistance.
- FIG. 10 is a diagram showing a first example of a conventionally known wheel-supporting rolling bearing unit assembled to a suspension device. It is a sectional view shown in a state,
- FIG. 11 is a cross-sectional view showing the second example
- FIG. 12 is a cross-sectional view showing a state in which the rigidity of the wheel supporting rolling bearing unit is measured.
- the present invention is also applicable to the structure shown in FIGS. 10 to 11 described above, the first and second examples described below apply the present invention to driving wheels (FR wheels, rear wheels, FF vehicles). It shows the case where the present invention is applied to a rolling bearing unit for supporting wheels to rotatably support the front wheels (all wheels of 4WD vehicles).
- the present invention relates to a wheel supporting roller for a driving wheel. It is particularly important as a bearing unit. The reason for this is that, as shown in Figs.
- a hub 7 b as a rotating raceway ring is provided on the inner diameter side of an outer race 19 as a stationary raceway ring. It is supported rotatably by a plurality of balls 14, 14.
- a spline hole 30 for inserting a spline shaft (not shown) attached to the constant velocity joint is formed in the center of the hap body 22 a as a main shaft member that constitutes the hub 7 b. ing. Further, the inner end surface of the inner ring 23 externally fitted to the small-diameter step portion 24 formed at the inner end of the hub body 22a is plastically deformed radially outward at the inner end of the hub body 22a.
- the inner ring 23 is fixed to the hub body 22a by being held down by the caulking portion 25, thereby forming the hub 7b.
- a seal ring 16c, 16c is provided between the inner peripheral surface of both ends of the outer ring 19, the outer peripheral surface of the intermediate portion of the hub body 22a, and the outer peripheral surface of the inner end of the inner ring 23, respectively.
- the space provided with the balls 14 and 14 and the outer space are interposed between the inner peripheral surface of the outer ring 19 and the outer peripheral surface of the hap 7b by providing d.
- the axial load for applying preload to 14 and 14 shall be 1.96 to 4.9 kN.
- the torque (rolling resistance) required to rotate the hub 7b at 20 Omin- 1 inside the outer ring 19 is 0.15 to 0.45 N'm.
- the rigidity coefficient is set to 0.09 or more.
- the total of the rotational resistance (torque) of the two seal rings 16c and 16d is restricted to a range of 0.06 to 0.4Nm.
- the sealing rings 16c and 16d prevent foreign matter such as muddy water from entering the space where the balls 14 and 14 are installed.
- the structure of other parts is This is the same as the structure shown in FIG.
- the small-diameter step portion 24 provided at the inner end of the hub main body 22 b serving as the main shaft member is externally fitted and rotated together with the hub main body 22 b.
- the inner end surface of the inner race 23 constituting the hub 7c which is the side raceway, protrudes inward from the inner end surface of the hub body 22b.
- the outer end surface of the constant velocity joint (not shown) abuts on the inner end surface of the inner ring 23 in a state where the inner ring 23 is mounted on the vehicle, thereby preventing the inner ring 23 from falling off the small diameter step portion 24.
- the axial load for applying the preload is adjusted by the torque for tightening the nut screwed to the outer end of the spline shaft (not shown).
- Other configurations are the same as those of the first example shown in FIG. 1 described above.
- the present invention is applied to a case where the present invention is applied to a rolling bearing unit for rotatably supporting a driven wheel as shown in FIG. Is shown.
- the structure shown in FIG. 10 described above fixes a pair of inner rings 5 and 5 by a nut 6 screwed to the outer end of the support shaft 4
- the present embodiment employs a support which is a main shaft member.
- the first inner raceway 20 is formed directly in the middle of the shaft 4a, and the outer end of the support shaft 4a is plastically deformed radially outward.
- the inner ring 5 is fixed to the support shaft 4a by holding down the end face.
- the axial load for applying the preload is adjusted by the load at the time of processing the caulking portion 25.
- the structure of other portions is the same as the structure shown in the above-described first example and FIG. Next, five examples of the specific structure of the seal ring applicable to the present invention will be described with reference to FIGS. Of these, the four examples shown in FIGS. 4 to 7 are the first to third examples of the wheel supporting rolling unit shown in FIGS. 1 to 3 and the structure of FIG. This shows a structure that can be used as rings 16b and 16d. The following description will be made by taking as an example a case where the present invention is applied to the structures shown in FIGS.
- the first example shown in FIG. 4 is composed of an outer-diameter-side seal ring 31 fixed inside and fitted to the inner end of an outer ring 19 (FIGS. 1-2), and an inner ring 23 (FIGS. 1-2).
- This is a combination seal ring that combines an inner diameter seal ring 32 that is externally fitted and fixed to the end, and has a total of three seal lips, two on the inner diameter side and one on the outer diameter side.
- the inner ring is fixed to the inner end of the outer ring 19 (FIGS. 1-2).
- This is a combination seal ring combining a seal ring 33 and a slinger 34 fixed to the inner end of the inner ring 23 (Figs. 1-2) .
- the seal ring 33 has three seal lips. .
- the seal ring 35a that locks on the inner peripheral surface of the inner end of the outer ring 19 (FIGS. 1-2) and the inner ring 23 (FIGS. 1-2)
- This is a combination seal ring that combines a seal ring 35b that locks on the outer peripheral surface of the inner end.
- a total of three seal lips are provided, two on the outer ring 19 and two on the inner ring 23, and one on the inner ring 23. .
- Fig. 7 shows two seals provided on a seal ring 36 fitted inside the inner end of the outer ring 19 (Figs. 1-2). ) Is to be in sliding contact with the outer peripheral surface at the inner end.
- the seal ring 36 shown in FIG. 7 can also be used to close the outer end opening side of the space where the ball is installed.
- the seal ring 37 shown in FIG. 8 is an outer end of the outer ring 19 (FIGS. 1-2) or an inner end of the hub 7 (FIG. 3). ), 22b (Fig. 2), and a structure that can be used as a seal ring provided between the support shaft 4a (Fig. 3) and the outer peripheral surface of the intermediate portion.
- the seal ring 37 is provided with three seal lips on a core metal which is internally fixed to the outer end of the outer ring 19, and the leading edge of each seal lip is attached to a mounting flange 1 la ( The inner surface of FIGS. 1 and 2) or a curved surface portion connecting the inner surface and the outer peripheral surfaces of the hub bodies 22a and 22b can be slidably contacted.
- a pair of seal rings selected from those shown in FIGS. 4 to 8 are used to form the outer ring 1 9 (FIGS. 1 and 2) constituting the wheel supporting rolling unit shown in FIGS. 1 to 3 described above.
- the total rotational resistance of the two seal rings is restricted to a range of 0.06 to 0.4 Nm by, for example, a method described later.
- the rotational resistance of the seal ring having the lower rotational resistance is reduced by, for example, a method to be described later, and is kept at not less than 0.3 N'm.
- a method for reducing the torque required for the relative rotation between the seal ring and the mating member includes, for example, the following (1) to ( There are methods such as 4), and these can be used alone or in any combination.
- the rigidity of the seal lip decreases, the contact surface pressure of the sliding contact portion between the leading edge of the seal lip and the mating surface decreases, and the torque can be reduced.
- the seal lip forms a labyrinth seal with the mating surface. Then, the frictional resistance of the seal lip becomes zero.
- a lubricant is impregnated into a rubber composition constituting a sealing material as described in the above-mentioned Japanese Patent Application Laid-Open No. H08-319379. What mixed the fine plastic particles can also be adopted.
- the cross-sectional shape according to the prior invention disclosed in Japanese Patent Application No. 2002-71338 can be considered.
- the structure according to the prior invention is such that the thickness of the middle seal lip 38b of the three seal lips 38a, 38b, 38c is changed from the base end to the middle. And gradually increase from the middle to the tip. Also, the thickness of the seal lip 38 b is maximized at a part of the portion near the front end.
- the thickness of the base end of the seal lip 38 b is denoted by di
- the thickness of the minimum thickness portion where the thickness is minimized at the intermediate portion is denoted by d 2
- c ⁇ be a shape that satisfies 0.1 S 2 ⁇ 0.5 S 2 . Examples>
- each seal ring was assembled into a wheel-supporting rolling unit shown in FIG. 1 or 3 and subjected to a muddy water intrusion test.
- a muddy water penetration test the process of pouring muddy water at a rate of 300 Occ / min into the above-described seal ring installation portion and rotating the seal ring and the member having the mating surface relative to each other for 17 hours was continued. Thereafter, the process of stopping rotation and injecting muddy water for 3 hours and drying was defined as one cycle, and 20 cycles were performed for each sample.
- Lubrication of the rolling bearing unit for wheel support is performed by filling grease with a viscosity of loxi cr 6 '4 x 10 — 6 m 2 (104 cSt) under an environment of 20 ° C.
- the hub 7b (or 7) was rotated at 20 O min- 1 .
- Table 1 shows the results of the experiment performed under such conditions.
- the circled numbers refer to the drawing numbers describing the seal rings. Is represented. For example, 4 indicates the seal ring shown in FIG. 4, and 8 indicates the sinner ring shown in FIG. 8, respectively. Also, 4 + ⁇ indicates that the seal ring shown in FIG. 4 and the seal ring shown in FIG. 8 are combined. In addition, ⁇ xj '' indicates that a large amount of muddy water has entered the grease-filled interior space, ⁇ ⁇ '' indicates that a small amount of muddy water has entered, and ⁇ ⁇ '' indicates that no intrusion of muddy water has been observed. Respectively. From the results of such experiments, it can be seen that muddy water can be prevented regardless of the combination of the seal rings with any structure if the seal torque is 0.06 ⁇ ⁇ m or more.
- Tables 2 to 5 are based on the second to fifth experiments conducted by incorporating the seal ring shown in Fig. 5 and the seal ring shown in Fig. 8 into the rolling bearing unit for wheel support shown in Fig. 5. It will be described with reference to FIG. In Tables 2 to 5 shown below,
- Table 2 shows the results of a second experiment conducted to find out the influence of the sealing torque on the rotation torque and durability of the entire rolling bearing unit. This experiment was performed at a rotational speed of 200 min- 1 .
- Table 3 shows the results of a third experiment conducted to determine the effect of the axial load (preload) force on the stiffness and durability of the rolling bearing unit.
- Table 4 shows the results of a fourth experiment performed to determine the effect of the rolling resistance on the stiffness and durability of the rolling bearing unit. This experiment was performed at a rotation speed of 20 Omin " 1 .
- Table 5 shows the results of a fifth experiment performed to determine the effect of the rigidity coefficient on the rigidity of the rolling bearing unit.
- the figure shows the results of an experiment conducted to find out the effect on the rotational torque of the whole unit. This experiment was performed at a rotation speed of SO Omin- 1 .
- Table 7 below shows four examples of specifications of the rolling bearing unit for wheel support that belongs to the technical scope of the present invention.
- the ball diameter is the diameter of each ball
- PCD is the pitch circle diameter of the ball row of each ball
- the inter-row distance is the pitch in the axial direction of the rows of balls arranged in multiple rows.
- the distance between the centers of the balls) and the contact angle represent the contact angles between each ball and the inner and outer raceways.
- Table 8 below shows the effect of the contact angle on the stiffness coefficient. From Table 8, it can be seen that the rigidity coefficient decreases as the contact angle decreases.
- the rolling bearing unit for supporting a wheel according to the present invention is configured and operates as described above, the rotational torque of the haptic that rotates together with the wheel is reduced while ensuring rigidity and durability, thereby improving steering stability and acceleration. It can contribute to improving the running performance of vehicles, mainly performance and fuel efficiency.
- the rolling resistance of the rolling bearing unit for supporting a wheel having the structure shown in FIGS. 1 to 3 was about 1.5 N.m.
- the rolling resistance of the wheel supporting rolling bearing unit of the present invention is in the range of 0.21 to 0.85 N ⁇ m. In other words, the rotational resistance has been reduced by more than 43% compared to the past.
- the fuel consumption fuel consumption rate
- the use of the wheel-supporting rolling bearing cutout of the present invention allows fuel to be consumed in one year. 4 3 to 86 L can be saved. If, for example, 100,000 such vehicles are to be driven in Japan, the fuel that can be saved in one year will be 43.000 to 800.000 L. In addition, it can be said that industrial utilization is extremely high because fuel efficiency can be improved without any other problems.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Rolling Contact Bearings (AREA)
Abstract
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US10/526,549 US7338212B2 (en) | 2002-09-06 | 2003-08-29 | Wheel supporting rolling bearing unit |
JP2004534125A JPWO2004022992A1 (ja) | 2002-09-06 | 2003-08-29 | 車輪支持用転がり軸受ユニット |
EP03794151A EP1548307A4 (en) | 2002-09-06 | 2003-08-29 | ROLLER BEARING UNIT FOR SUPPORT WHEEL |
AU2003261852A AU2003261852A1 (en) | 2002-09-06 | 2003-08-29 | Rolling bearing unit for supporting wheel |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2002261194 | 2002-09-06 | ||
JP2002-261194 | 2002-09-06 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2004022992A1 true WO2004022992A1 (ja) | 2004-03-18 |
Family
ID=31973118
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2003/011113 WO2004022992A1 (ja) | 2002-09-06 | 2003-08-29 | 車輪支持用転がり軸受ユニット |
Country Status (7)
Country | Link |
---|---|
US (1) | US7338212B2 (ja) |
EP (1) | EP1548307A4 (ja) |
JP (1) | JPWO2004022992A1 (ja) |
KR (1) | KR100642588B1 (ja) |
CN (1) | CN100540928C (ja) |
AU (1) | AU2003261852A1 (ja) |
WO (1) | WO2004022992A1 (ja) |
Cited By (7)
Publication number | Priority date | Publication date | Assignee | Title |
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JP2005291457A (ja) * | 2004-04-05 | 2005-10-20 | Nsk Ltd | 玉軸受ユニット |
JP2006317008A (ja) * | 2006-07-28 | 2006-11-24 | Ntn Corp | 車輪用軸受装置 |
WO2007037477A1 (ja) * | 2005-09-30 | 2007-04-05 | Ntn Corporation | 車輪用軸受装置 |
WO2007049437A1 (ja) * | 2005-10-27 | 2007-05-03 | Ntn Corporation | 車輪用軸受装置 |
JP2007113719A (ja) * | 2005-10-21 | 2007-05-10 | Ntn Corp | 車輪用軸受装置 |
JP2007113718A (ja) * | 2005-10-21 | 2007-05-10 | Ntn Corp | 車輪用軸受装置 |
US7614796B2 (en) | 2005-05-12 | 2009-11-10 | Ntn Corporation | Wheel support bearing assembly |
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US7901141B2 (en) * | 2005-02-14 | 2011-03-08 | Nsk Ltd. | Hub unit bearing |
JP2007120594A (ja) * | 2005-10-27 | 2007-05-17 | Ntn Corp | 車輪用軸受装置 |
US7422373B2 (en) * | 2006-08-22 | 2008-09-09 | Emerson Power Transmission Manufacturing | Spherical roller bearing sealing assembly |
DE602007012991D1 (de) | 2007-01-04 | 2011-04-21 | Skf Ab | Dichtungsanordnung zwischen einem Gleichlaufgelenk und einer Nabenlagereinheit eines Kraftfahrzeugrades |
KR20080067088A (ko) * | 2007-01-15 | 2008-07-18 | 주식회사 일진글로벌 | 비대칭 휠 베어링 조립체 |
WO2008120694A1 (ja) * | 2007-03-29 | 2008-10-09 | Jtekt Corporation | 回転速度検出装置およびそれを用いた転がり軸受装置 |
US8845203B2 (en) * | 2008-11-06 | 2014-09-30 | Kyklos Bearing International, Inc. | Wheel bearing assembly |
JP5476173B2 (ja) | 2010-03-19 | 2014-04-23 | Ntn株式会社 | 車輪用軸受装置 |
DE102010064672B3 (de) * | 2010-08-13 | 2019-10-10 | Schaeffler Technologies AG & Co. KG | Dichtungsanordnung zur Abdichtung eines Radlagers |
JP5964120B2 (ja) * | 2012-04-13 | 2016-08-03 | Ntn株式会社 | 車輪用軸受の密封装置 |
US9435436B2 (en) * | 2013-03-15 | 2016-09-06 | Frank Majerik | Purgeable labyrinth axle/hub seal |
CN104121283A (zh) * | 2014-06-25 | 2014-10-29 | 芜湖众绅机械制造有限公司 | 非驱动轮用轮毂轴承单元 |
DE102016211196A1 (de) * | 2016-06-22 | 2017-12-28 | Aktiebolaget Skf | Wälzlagereinheit |
US10087985B2 (en) * | 2016-09-29 | 2018-10-02 | Jtekt Corporation | Rolling device for vehicle |
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- 2003-08-29 CN CNB038209950A patent/CN100540928C/zh not_active Expired - Fee Related
- 2003-08-29 JP JP2004534125A patent/JPWO2004022992A1/ja active Pending
- 2003-08-29 WO PCT/JP2003/011113 patent/WO2004022992A1/ja active Application Filing
- 2003-08-29 KR KR1020057003795A patent/KR100642588B1/ko not_active IP Right Cessation
- 2003-08-29 EP EP03794151A patent/EP1548307A4/en not_active Ceased
- 2003-08-29 US US10/526,549 patent/US7338212B2/en not_active Expired - Fee Related
- 2003-08-29 AU AU2003261852A patent/AU2003261852A1/en not_active Abandoned
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Cited By (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2005291457A (ja) * | 2004-04-05 | 2005-10-20 | Nsk Ltd | 玉軸受ユニット |
US7614796B2 (en) | 2005-05-12 | 2009-11-10 | Ntn Corporation | Wheel support bearing assembly |
US7901143B2 (en) | 2005-05-12 | 2011-03-08 | Ntn Corporation | Wheel support bearing assembly |
US8092095B2 (en) | 2005-05-12 | 2012-01-10 | Ntn Corporation | Wheel support bearing assembly |
WO2007037477A1 (ja) * | 2005-09-30 | 2007-04-05 | Ntn Corporation | 車輪用軸受装置 |
US8840313B2 (en) | 2005-09-30 | 2014-09-23 | Ntn Corporation | Bearing apparatus for a wheel of vehicle |
JP2007113719A (ja) * | 2005-10-21 | 2007-05-10 | Ntn Corp | 車輪用軸受装置 |
JP2007113718A (ja) * | 2005-10-21 | 2007-05-10 | Ntn Corp | 車輪用軸受装置 |
WO2007049437A1 (ja) * | 2005-10-27 | 2007-05-03 | Ntn Corporation | 車輪用軸受装置 |
US7832941B2 (en) | 2005-10-27 | 2010-11-16 | Ntn Corporation | Bearing apparatus for a wheel of vehicle |
JP2006317008A (ja) * | 2006-07-28 | 2006-11-24 | Ntn Corp | 車輪用軸受装置 |
Also Published As
Publication number | Publication date |
---|---|
KR100642588B1 (ko) | 2006-11-10 |
US7338212B2 (en) | 2008-03-04 |
CN1678837A (zh) | 2005-10-05 |
KR20050057194A (ko) | 2005-06-16 |
EP1548307A4 (en) | 2007-07-04 |
JPWO2004022992A1 (ja) | 2005-12-22 |
AU2003261852A1 (en) | 2004-03-29 |
EP1548307A1 (en) | 2005-06-29 |
CN100540928C (zh) | 2009-09-16 |
US20060165331A1 (en) | 2006-07-27 |
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