WO2003074890A1 - Unite palier a roulement pour le support d'une roue - Google Patents

Unite palier a roulement pour le support d'une roue Download PDF

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Publication number
WO2003074890A1
WO2003074890A1 PCT/JP2003/002370 JP0302370W WO03074890A1 WO 2003074890 A1 WO2003074890 A1 WO 2003074890A1 JP 0302370 W JP0302370 W JP 0302370W WO 03074890 A1 WO03074890 A1 WO 03074890A1
Authority
WO
WIPO (PCT)
Prior art keywords
rolling bearing
bearing unit
seal
wheel
raceway
Prior art date
Application number
PCT/JP2003/002370
Other languages
English (en)
Japanese (ja)
Inventor
Junshi Sakamoto
Original Assignee
Nsk Ltd.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Nsk Ltd. filed Critical Nsk Ltd.
Priority to AU2003211541A priority Critical patent/AU2003211541A1/en
Publication of WO2003074890A1 publication Critical patent/WO2003074890A1/fr

Links

Classifications

    • 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
    • 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
    • B60B27/00—Hubs
    • B60B27/0005—Hubs with ball bearings
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B27/00—Hubs
    • B60B27/0078—Hubs characterised by the fixation of bearings
    • B60B27/0084—Hubs characterised by the fixation of bearings caulking to fix inner race
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B27/00—Hubs
    • B60B27/0094—Hubs one or more of the bearing races are formed by the hub
    • 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
    • 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
    • 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 rolling bearing unit for supporting a wheel for rotatably supporting a wheel with respect to a suspension system of an automobile. Background technology
  • FIGS. 11 Japanese Patent Application Laid-Open No. 2001-221234 discloses a structure as shown in FIGS. First, the structure of the first example shown in FIG. 11 will be described.
  • a wheel 1 constituting a wheel is rotatably supported on an end of an axle 3 constituting a suspension 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 fixed by the nut 6.
  • the wheel 1 is fixedly connected to a hub 7, which is a rotating raceway, constituting the wheel supporting rolling bearing unit 2 by a plurality of studs 8, 8 and nuts 9, 9.
  • double-row outer ring raceways 10a and 10b are formed, and on the outer peripheral surface, a mounting flange 11 is formed.
  • the above-mentioned wheel 1 is provided with the above-mentioned studs 8 and 8 and nuts 9 and 9 on one side (the outer side in the illustrated example) of the above-mentioned mounting flange 11 together with the drum 12 and the drum for constituting the braking device. Due to this, the connection is fixed.
  • Seal rings 16a and 16b are provided between the inner peripheral surfaces at both ends of the hub 7 and the outer peripheral surfaces at the ends of the inner rings 5 and 5, respectively. It blocks the space with 14 and the outside space.
  • the outer end of the hub 7 (the term “outside in the axial direction” refers to the outer side 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 throughout the present specification.) Closed by cap 17.
  • the support shaft 4 having the inner rings 5 and 5 externally fixed thereto is fixed to the axle 3 and the mounting flange 1 of the hub 7 is fixed.
  • a drum drum for braking is configured 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 is pressed against the inner peripheral surface of the drum 12.
  • a hub 7a as a rotating raceway is provided on the inner diameter side of an outer ring 19 as a stationary raceway, and a plurality of balls each being a rolling element. It is supported rotatably by 14 and 14.
  • the double-row outer raceways 10a and 10b are rotated on the inner circumferential surface of the outer race 19, respectively, on the outer circumferential surface of the hub 7a.
  • First and second inner raceways 20 and 21 which are side raceway surfaces are provided, respectively.
  • the hub 7a is formed by combining a hub body 22 and an inner ring 23.
  • the mounting flange 11 a for supporting the wheel is also provided, the first inner raceway 20 is also provided at the intermediate portion, and the inner end track is also provided at the intermediate portion.
  • the small-diameter step portions 24 each having a smaller diameter than the portion where the first inner ring raceway 20 is formed are 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 externally fitted to the small-diameter stepped portion 24.
  • the inner end surface of the inner ring 23 is suppressed 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. On the other hand, it is fixed. Further, seal rings 16c and 16d are provided between inner peripheral surfaces of both ends of the outer ring 19, an outer peripheral surface of an intermediate portion of the hub 7a, and an outer peripheral surface of an inner end of the inner ring 23, respectively. The balls 14 and 14 are set between the inner peripheral surface of the outer ring 19 and the outer peripheral surface of the hub 7a. It shields the girder space from the outside space.
  • seal rings 16a, 16b (or 1a) are used to close the openings at both ends of the internal space where the balls 14, 14 are installed. Due to the existence of 6c, 16d), it is inevitable that the torque required for rotating the hub 7 (or 7a) (rotational resistance of the rolling bearing unit for wheel support) increases. As a result, the driving performance of the vehicle incorporating the above-mentioned rolling bearing unit for supporting the wheel, particularly the acceleration performance and the fuel consumption performance, is deteriorated. Therefore, in response to the recent trend of energy saving, improvement is desired. I have.
  • the rolling bearing unit for supporting wheels of the present invention has been invented in view of such circumstances. Disclosure of the invention
  • the rolling bearing unit for supporting a wheel according to the present invention includes a stationary bearing ring, a rotating bearing ring, and a plurality of balls, as in the above-described conventionally known rolling bearing unit for supporting a wheel. And a seal ring.
  • the stationary race is supported and fixed to the suspension device in use.
  • the rotating raceway rings support and fix the wheels in use.
  • the balls are provided between the stationary raceway and the rotating raceway, each having an arc-shaped cross section, which are present on the peripheral surfaces of the stationary raceway and the rotating raceway facing each other. Have been killed.
  • the pair of seal rings close both end openings of the space in which the balls are installed between the opposing peripheral surfaces of the stationary raceway ring and the rotating raceway ring.
  • Each of the two seal rings has two to three seal lips, each of which is made of an elastic material.
  • the axial load for applying a preload to each of the balls is 0.49 to 2.94 kN (50 to 300 kgf).
  • the stationary raceway and the rotating raceway are relatively rotated at 20 Omin- 1 based on the rolling resistance of each ball.
  • the required torque (rolling resistance) is 0.12 to 0.23N • m.
  • the rigidity coefficient is 0.09 or more when the axial load is 1.96 kN.
  • the torque required to rotate the stationary raceway and the rotating raceway relative to each other at 20 Omin- 1 based on the friction between each seal lip and the mating surface is 0 in total for both seal rings. 06 ⁇ 0.4N'm.
  • the stiffness coefficient described in this specification is the stiffness R [kN ⁇ m / deg] of the wheel-supporting rolling bearing unit, and the radial dynamic load rating of the wheel-supporting rolling bearing unit. It is the ratio (RZC r) to C r [N].
  • the rigidity R in this case is the above-mentioned rigidity when the momentary load is applied to the rotating raceway while the stationary raceway constituting the wheel supporting rolling bearing unit is fixed. Raceway It is expressed by the angle of inclination, and is measured, for example, as shown in FIG. FIG. 13 shows a state where the rigidity R of the wheel supporting rolling bearing unit 2a shown in FIG. 12 is measured.
  • the outer ring 19, which is the stationary raceway, is fixed to the upper surface of the fixed base 37, and the base end of the lever plate 38 is attached to the mounting flange 11a of the hub 7a, which is the rotating raceway (Fig. 13). (The left end). Then, a load is applied to a portion of the upper surface of the lever plate 38, which is separated from the rotation center of the above-mentioned bracket 7a by a distance L corresponding to the rotation radius of the tire, and the hub 7a is provided via the lever plate 38. A moment load of 1.5 kN'm.
  • the inclination angle is determined by the inclination angle [deg] of the mounting surface 40 of the mounting flange 11a with respect to the upper surface 39 of the fixed base 37.
  • the rigidity R [kN-m / deg] is obtained by dividing the moment load (1.5 kN, m) by this inclination angle.
  • 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 the preload is 0.49 kN or more
  • the rolling resistance when this axial load is 1.96 kN is 0.12 Nm or more
  • the Oka IJ coefficient is 0.09 or more.
  • the axial load for applying the preload is 2.94 kN or less
  • the rolling resistance is 0.23 N ⁇ m or less
  • the total rotational resistance (torque) of a pair of seal rings is 0. . 4N'm or less, so the above-mentioned rotation torque can be reduced.
  • the rolling resistance cannot be suppressed to a low level (for example, 0.23 0 ⁇ ⁇ or less), and the rotational torque cannot be reduced.
  • the axial load is less than 0.49 kN, it becomes difficult to secure the rigidity of the wheel supporting rolling unit unit. As a result, steering stability decreases.
  • the rotational torque of the entire wheel supporting rolling unit can be reduced.
  • the total rotational resistance of the two seal rings is maintained at 0.06 ⁇ ⁇ ⁇ or more, the required sealing performance (mainly, muddy water resistance to prevent intrusion of muddy water) can be ensured.
  • the axial load for applying the preload is 0.49 to 2.94 kN, and the rolling resistance when this axial load is 1.96 kN is 0.12 to 0.23 Nm, Similarly, in the case of the rolling bearing unit for supporting a wheel of the present invention in which the rigidity coefficient is 0.09 or more and the rotational resistance of both seal rings is 0.06 to 0.4 Nm in total, rigidity and durability are secured. While reducing the rotational torque.
  • FIG. 1 is a sectional view showing a first example of a structure to which the present invention is applied.
  • FIG. 2 is a cross-sectional view showing a second example of the structure to which the present invention is applied.
  • FIG. 3 is a cross-sectional view showing a third example of the structure to which the present invention is applied.
  • 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 a second example of the specific structure of the seal ring applicable to the present invention.
  • FIG. 6 is a partial cross-sectional view showing a third example of the specific structure of the seal ring applicable to the present invention.
  • FIG. 7 is a partial sectional view showing a fourth example of the specific structure of the seal ring applicable to the present invention.
  • FIG. 8 is a partial cross-sectional view showing a fifth example of the specific structure of the seal ring applicable to the present invention.
  • FIG. 9 is a partial cross-sectional view showing a sixth example of the specific structure of the seal ring applicable to the present invention.
  • FIG. 10 is a partial sectional view showing a seventh example of the specific structure of the seal ring applicable to the present invention.
  • FIG. 11 is a cross-sectional view showing a first example of a conventionally known wheel-supporting rolling bearing unit when assembled to a suspension device.
  • FIG. 12 is a cross-sectional view showing a second example of a conventionally known rolling bearing unit for supporting a wheel.
  • FIG. 13 is a cross-sectional view showing a state in which the rigidity of the wheel supporting rolling bearing unit is measured.
  • a rolling bearing unit for supporting a wheel which is an object of the present invention.
  • the present invention is also applicable to the structure shown in FIGS. 11 and 12 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 a wheel for rotatably supporting the front wheel of the vehicle and all wheels of a 4WD vehicle).
  • the present invention is particularly important as a wheel supporting rolling bearing unit for driving wheels. The reason for this is shown in Figs. 11 and 12 above.
  • a rolling bearing unit for supporting wheels such as driven wheels (front wheels of FR vehicles, rear wheels of FF vehicles)
  • the raceway wheels located on the outer diameter side (Fig.
  • the seal ring (16a, 16d) on one end side is omitted by closing one end opening of the outer ring 19) with the cap 17 (Fig. 11), and only one seal ring that generates sliding resistance
  • two seal rings are required.
  • a plurality of hubs 7b which are rotating-side races, are provided on the inner diameter side of the outer race 19, which is a stationary-side race. It is rotatably supported by balls 14 and 14.
  • a spline hole 26 for inserting a spline shaft (not shown) attached to the constant velocity joint is formed in the center of the hub body 22a constituting the hub 7b.
  • 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 formed by plastically deforming the inner end of the hub body 22a radially outward.
  • the inner ring 23 is fixed to the hub main body 22a by being held down by the caulking portion 25, thereby forming the hub 7b.
  • Seal rings 16 c and 16 d are provided between the inner peripheral surfaces of both ends of the outer ring 19, the outer peripheral surface of the intermediate portion of the hub body 22 a, and the outer peripheral surface of the inner end of the inner ring 23, respectively. Between the inner peripheral surface of the outer ring 19 and the outer peripheral surface of the hub 7b, the space in which the balls 14, 14 are provided and the outer space are shut off.
  • the balls 14, 14 The axial load for applying a preload to 14 shall be 0.49 to 2.94 kN.
  • the torque (rolling resistance) required to rotate the hub 7b at 20 Omin- 1 inside the outer ring 19 is 0.12 to 0.23N '. m.
  • the stiffness coefficient when this axial load is 1.96 kN is set to 0.09 or more.
  • the total rotational resistance (torque) of the two seal rings 16c and 16d is restricted to a range of 0.06 to 0.4Nm.
  • the seal rings 16c and 16d The structure of the other parts is the same as the structure shown in FIG.
  • the hub 7c is formed together with the hub main body 2 2b by externally fitting the small-diameter step portion 24 provided at the inner end of the hub main body 22b.
  • the inner end surface of the inner ring 23 protrudes more inward than the inner end surface of the hub body 22 b.
  • 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 tightening torque of the nut screwed to the outer end of the spline shaft (not shown).
  • Other configurations are the same as those in 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. 11 described above.
  • a rolling bearing unit for rotatably supporting a driven wheel as shown in FIG. 11 described above.
  • the first inner ring raceway 20 is formed directly in the middle part, and the outer end surface of the inner ring 5 is held down by a caulking part 25 formed by plastically deforming the outer end of the support shaft 4a radially outward.
  • the inner ring 5 is fixed to the support shaft 4a.
  • the axial load for applying the preload is adjusted by the load at the time of processing the caulked portion 25.
  • the structure of the other parts is the same as that of the first example described above and the structure shown in FIG.
  • FIGS. 4 to 8 are the first to third examples of the wheel-supporting rolling unit shown in FIGS. 1 to 3 and the structures of FIGS.
  • the first example shown in FIG. 4 includes an outer-diameter-side seal ring 27 that is internally fitted and fixed to the inner end of an outer ring 19 (FIGS. 1 and 2), and an inner ring 23 (FIGS. 1 and 2).
  • This is a combination seal ring combining an inner diameter side seal ring 28 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.
  • FIG. 5 a second example shown in FIG. 5 is a seal ring 29 that is fitted and fixed to the inner end of the outer ring 19 (FIGS. 1 and 2), and an inner end of the inner ring 23 (FIGS. 1 and 2).
  • This is a combination seal ring in which a slinger 30 that is externally fitted and fixed to the seal ring is used. With book seal lip.
  • FIG. 7 shows a seal ring 33a which is locked to the inner peripheral surface of the inner end of the outer ring 19 (FIGS. 1 and 2), and an inner end of the inner ring 23 (FIGS. 1 and 2).
  • This is a combination seal ring combining the seal ring 33b which is locked to the outer peripheral surface.
  • a total of three seal lips are provided, two on the seal ring 33a locked on the outer ring 19 side and one on the seal ring 33b locked on the inner ring 23 side.
  • FIG. 8 shows the front edges of the two seal lips provided on the seal ring 34 fitted inside the inner end of the outer ring 19 (FIGS. 1 and 2), and the inner end of the inner ring 23 (FIGS. 1 and 2). This is to make sliding contact with the outer peripheral surface.
  • Figs. 9 and 10 show the inner peripheral surface of the outer end of the outer ring 19 (Figs. 1-2) and the outer peripheral surface of the intermediate part of the hub bodies 22a (Fig. 1) and 22b (Fig.
  • the figure shows a structure that can be used as a sealing provided between them.
  • the seal ring 35 of the first example shown in FIG. 9 is provided with three seal lips on a core metal that can be fitted and fixed at the outer end of the outer ring 19. Can be slidably contacted with the inner surface of the mounting flange 11a (FIGS. 1 and 2) or a curved surface portion connecting the inner surface to the outer peripheral surfaces of the hub bodies 22a and 22b.
  • the middle seal lip 36 of the three seal lips provided on the seal ring 35a is connected to the hub body 22 by the girder spring 32a. a (Fig. 1) and 22b (Fig. 2).
  • a pair of seal rings selected from those shown in FIGS. 4 to 10 are used for the outer ring 19 (FIGS. 1 and 2) which constitutes the wheel supporting rolling bearing unit shown in FIGS. ,
  • Balls 14 and 14 are installed by assembling between the surface (Figs. Close the openings at both ends of the space. Then, regardless of which seal ring is combined, the total rotational resistance of both seal rings is restricted to the range of 0.06 to 0.4N'm. Also, ensure that the rotational resistance of the seal ring with the lower rotational resistance is at least 0.03 N 'm.
  • each seal ring was assembled into a wheel supporting rolling bearing unit shown in FIG. 1 or FIG. 3 and subjected to a muddy water intrusion test.
  • Lubrication of the wheel supporting rolling bearing Interview two Tsu DOO is performed by a viscosity encapsulating grease 10 X 10- 6 ⁇ 14X 10- 6 m 2 / s (10 ⁇ 14c S t), 20 ° C environment Below, the hub 7b (or 7) was rotated at 20 Omin " 1 .
  • Table 1 shows the results of the experiment performed under such conditions.
  • the circled numbers represent the drawing numbers describing the seal rings.
  • 4 indicates the seal ring shown in FIG. 4
  • 9 indicates the seal ring shown in FIG. 9, respectively.
  • 4 + ⁇ ⁇ ⁇ ⁇ ⁇ indicates that the seal ring shown in FIG. 4 and the seal ring shown in FIG. 9 are combined.
  • ⁇ XJ mark '' means that a large amount of muddy water has infiltrated the internal space filled with grease
  • ⁇ ⁇ '' means that a small amount of muddy water has entered
  • ⁇ ⁇ '' means that no infiltration of muddy water has been observed.
  • FIG. 1 Tables 2 to 5 show the results of the second to fifth experiments in which the seal ring shown in Fig. 4 and the seal ring shown in Fig. 9 were incorporated into the rolling bearing unit for wheel support shown in Fig. 4. It will be described with reference to FIG.
  • Table 2 shows the results of a second experiment conducted to find out the effect of the sealing torque on the rotation torque and durability of the entire rolling bearing unit. This experiment was performed at a rotation speed of 20 Omiir 1 .
  • Table 3 shows the results of a third experiment performed to determine the effect of the axial load (preload) on the stiffness of the rolling bearing unit and the overall rotational torque.
  • Table 4 shows the results of a fourth experiment performed to determine the effect of the rolling resistance on the rigidity of the rolling bearing unit and the overall rotational torque. This experiment was performed with an axial load (preload) of 1.96 kN (200 kgf) and a rotation speed of 20 Omin-.
  • Table 5 shows the results of a fifth experiment conducted to determine the effect of the rigidity coefficient on the rigidity of the rolling bearing unit. This experiment was performed with an axial load of 1.96 kN (20 Okgf) applied.
  • Table 6 shows the results of an experiment conducted to find out the effect of the sealing torque and the rolling resistance on the rotation torque of the rolling bearing unit as a whole.
  • an axial load of 1.96 kN (200 kgf) was applied, and the rotation speed was 20 O min-.
  • the rolling bearing unit for supporting a wheel according to the present invention is configured and operates as described above, the steering torque and the rotating torque of the hub that rotates with the wheel are reduced while maintaining the steering stability and durability, thereby improving the acceleration performance. However, it can contribute to the improvement of the running performance of vehicles mainly on fuel efficiency.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rolling Contact Bearings (AREA)
  • Mounting Of Bearings Or Others (AREA)
  • Sealing Of Bearings (AREA)
  • Support Of The Bearing (AREA)

Abstract

L'invention concerne une unité palier à roulement pour le support d'une roue. Les deux ouvertures d'extrémité d'un espace dans lequel sont installées les billes (14) et (14) sont fermées par des bagues d'étanchéité (16c) et (16d) munies de deux à trois lèvres d'étanchéité. Une résistance au roulement variant sur la base d'une précharge se limite à une gamme comprise entre 0,12 et 0,23 N·m. Le total des résistances au roulement des deux bagues d'étanchéité (16c) et (16d) sur la base du frottement des lèvres d'étanchéité sur leurs surfaces de contact se limite à une gamme comprise entre 0,06 et 0,4 N·m. Pour accroître les rendements de déplacement d'un véhicule comprenant principalement un rendement d'accélération et un rendement de consommation de carburant, on peut réduire le couple d'un moyeu qui tourne conjointement avec la roue, tout en assurant une stabilité de direction.
PCT/JP2003/002370 2002-03-01 2003-02-28 Unite palier a roulement pour le support d'une roue WO2003074890A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU2003211541A AU2003211541A1 (en) 2002-03-01 2003-02-28 Rolling bearing unit for supporting wheel

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2002055660A JP2005299685A (ja) 2002-03-01 2002-03-01 車輪支持用転がり軸受ユニット
JP2002-55660 2002-03-01

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WO2003074890A1 true WO2003074890A1 (fr) 2003-09-12

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AU (1) AU2003211541A1 (fr)
WO (1) WO2003074890A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1548307A1 (fr) * 2002-09-06 2005-06-29 Nsk Ltd., Unite de roulement con ue pour soutenir une roue
US9751361B2 (en) 2012-04-13 2017-09-05 Ntn Corporation Seal device for a wheel bearing

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5376288B2 (ja) * 2008-08-25 2013-12-25 Ｎｔｎ株式会社 可変バルブタイミング装置
JP5354186B2 (ja) * 2008-07-09 2013-11-27 Ｎｔｎ株式会社 減速装置
WO2010004880A1 (fr) * 2008-07-09 2010-01-14 Ntn株式会社 Démultiplicateur et dispositif de distribution à soupape variable l'utilisant

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH07113418A (ja) * 1993-10-18 1995-05-02 Toyota Motor Corp 車両用軸受装置およびその製造方法
JPH1123598A (ja) * 1997-06-27 1999-01-29 Nippon Seiko Kk 回転速度検出器を備えた軸受
JP2001121904A (ja) * 1999-10-27 2001-05-08 Ntn Corp 車輪軸受装置

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH07113418A (ja) * 1993-10-18 1995-05-02 Toyota Motor Corp 車両用軸受装置およびその製造方法
JPH1123598A (ja) * 1997-06-27 1999-01-29 Nippon Seiko Kk 回転速度検出器を備えた軸受
JP2001121904A (ja) * 1999-10-27 2001-05-08 Ntn Corp 車輪軸受装置

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1548307A1 (fr) * 2002-09-06 2005-06-29 Nsk Ltd., Unite de roulement con ue pour soutenir une roue
EP1548307A4 (fr) * 2002-09-06 2007-07-04 Nsk Ltd Unite de roulement con ue pour soutenir une roue
US7338212B2 (en) 2002-09-06 2008-03-04 Nsk, Ltd. Wheel supporting rolling bearing unit
US9751361B2 (en) 2012-04-13 2017-09-05 Ntn Corporation Seal device for a wheel bearing

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AU2003211541A1 (en) 2003-09-16

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