WO2022185382A1 - 車輪用軸受装置 - Google Patents
車輪用軸受装置 Download PDFInfo
- Publication number
- WO2022185382A1 WO2022185382A1 PCT/JP2021/007738 JP2021007738W WO2022185382A1 WO 2022185382 A1 WO2022185382 A1 WO 2022185382A1 JP 2021007738 W JP2021007738 W JP 2021007738W WO 2022185382 A1 WO2022185382 A1 WO 2022185382A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- raceway surface
- balls
- axial
- axial position
- mounting flange
- Prior art date
Links
- 230000002093 peripheral effect Effects 0.000 description 8
- 230000007423 decrease Effects 0.000 description 5
- 238000007373 indentation Methods 0.000 description 4
- 229910000975 Carbon steel Inorganic materials 0.000 description 3
- 239000010962 carbon steel Substances 0.000 description 3
- 238000007789 sealing Methods 0.000 description 3
- 238000013459 approach Methods 0.000 description 2
- 230000006866 deterioration Effects 0.000 description 2
- 239000000725 suspension Substances 0.000 description 2
- 229910000831 Steel Inorganic materials 0.000 description 1
- 230000002159 abnormal effect Effects 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 239000000314 lubricant Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 239000011347 resin Substances 0.000 description 1
- 229920005989 resin Polymers 0.000 description 1
- 238000005096 rolling process Methods 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
Images
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
- B60B27/00—Hubs
- B60B27/0005—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
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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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/58—Raceways; Race rings
- F16C33/583—Details of specific parts of races
- F16C33/585—Details of specific parts of races of raceways, e.g. ribs to guide the rollers
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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
- B60B27/0094—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
- 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 a wheel bearing device.
- a wheel bearing device called a hub unit is used to rotatably support a wheel with respect to an automobile body.
- a double-row angular contact ball bearing may be employed in this wheel bearing device.
- the wheel bearing device has an inner member having a wheel mounting flange on one axial side, an outer member, and a plurality of balls arranged in a double row and interposed between the two members.
- the plurality of balls includes a plurality of first balls arranged in a row on one side in the axial direction of the double rows and a plurality of second balls arranged in a row on the other side in the axial direction. Reference 1).
- the contact angle of the first ball and the contact angle of the second ball are set to the same value. Therefore, when a moment load as described above acts on the inner member, the contact angle of the first ball becomes relatively larger than the contact angle of the second ball. When the contact angle of the first ball becomes larger, the allowable load in the radial direction by the first ball is relatively reduced, and the concentration of the load on the first ball promotes the occurrence of dents on the raceway surface on one side in the axial direction. will be made.
- Indentation on the raceway surface causes abnormal noise and peeling of the raceway surface. Therefore, it is desirable to take measures to suppress the occurrence of such indentations as described above.
- a wheel bearing device comprises an inner member having a wheel mounting flange on one axial side and a double-row inner raceway surface on the other axial side; a first inner raceway surface on one axial side of the double-row inner raceway surfaces; and a first inner raceway surface on one axial side of the double-row outer raceway surfaces.
- a plurality of first balls interposed between one outer raceway surface, a second inner raceway surface on the other side in the axial direction among the double-row inner raceway surfaces, and one of the double-row outer raceway surfaces.
- FIG. 1 is a cross-sectional view of a wheel bearing device.
- FIG. 2 is a diagram of the vehicle body mounting flange viewed along the central axis from the vehicle inner side.
- FIG. 3 is a cross-sectional view of a main part of the bearing device.
- FIG. 4 is a cross-sectional view of the wheel bearing device 10 for explaining a case where the lower side of the wheel collides with a curbstone.
- a wheel bearing device includes an inner member having a wheel mounting flange on one axial side and a double-row inner raceway surface on the other axial side; An outer member having opposing double-row outer raceway surfaces, a first inner raceway surface on one side of the double-row inner raceway surfaces in the axial direction, and one of the double-row outer raceway surfaces in the axial direction.
- a contact angle of the plurality of first balls is smaller than a contact angle of the plurality of second balls.
- the contact angle of the first ball may increase. Since the contact angle is smaller than the contact angles of the plurality of second balls, it is possible to suppress an increase in the difference between the contact angle of the first ball and the contact angle of the second ball. As a result, it is possible to suppress the relative decrease in the allowable load in the radial direction due to the plurality of first balls, suppress the concentration of the load on the first ball, and suppress the first inner raceway surface and the first outer raceway surface. It is possible to suppress the occurrence of indentations in the
- the pitch diameter of the plurality of first balls is larger than the pitch diameter of the plurality of second balls.
- the allowable load for the load can be increased, and the occurrence of dents on the first inner raceway surface and the first outer raceway surface can be effectively suppressed.
- the contact angles of the plurality of first balls are reduced, the allowable load for the axial load is lowered, and there is a possibility that the service life of the bearing under normal use will be shortened. Therefore, the service life of the plurality of first balls, the first outer raceway surface, and the first inner raceway surface as a bearing is shorter than the service life of the plurality of second balls, the second outer raceway surface, and the second inner raceway surface.
- the pitch circle diameter of the plurality of first balls is made larger than the pitch diameter of the plurality of second balls, and the allowable load for the load acting on the plurality of first balls is increased. It is possible to compensate for the relative reduction in life of the plurality of first balls, the first outer raceway surface, and the first inner raceway surface. As a result, it is possible to suppress the deterioration of the life of the wheel bearing device 10 as a whole.
- the axial position of the intersection of the first line of action of the load acting on the plurality of first balls and the second line of action of the load acting on the plurality of second balls is It is preferably located on one axial side of the axial center between the axial position of the bottom of the first outer raceway surface and the axial position of the bottom of the second outer raceway surface.
- a first line of action of the load acting on the plurality of first balls forms a contact angle of the plurality of first balls with a plane perpendicular to the center axis of the wheel bearing device.
- the second line of action of the load acting on the plurality of second balls forms a contact angle of the plurality of second balls with a plane perpendicular to the central axis of the wheel bearing device. Therefore, the axial position of the intersection of the first line of action and the second line of action is the axial position between the axial position of the bottom of the first outer raceway surface and the axial position of the bottom of the second outer raceway surface.
- the contact angle of the plurality of first balls is set smaller than the contact angle of the plurality of second balls by locating them on one side of the center in the axial direction.
- the outer member has a vehicle body mounting flange on its outer periphery for mounting the outer member to the vehicle body, and the axial position of the center of the vehicle body mounting flange in the axial direction is the second position. It is preferably closer to the axial position of the bottom of the first outer raceway surface than to the axial position of the bottom of the outer raceway surface.
- the axial position of the vehicle body mounting flange and the axial position of the wheel mounting flange to which the load is applied are compared to the case where the vehicle body mounting flange is provided at the other axial end of the outer member. becomes closer.
- the outer member has a vehicle body mounting flange on its outer periphery for mounting the outer member to the vehicle body, and the axial position of the center of the vehicle body mounting flange in the axial direction is the first outer raceway. It may be positioned on one axial side of the axial center between the axial position of the bottom of the surface and the axial position of the bottom of the second outer raceway surface. Also in this case, the axial position of the vehicle body mounting flange and the axial position of the wheel mounting flange to which the load is applied are different compared to the case where the vehicle body mounting flange is provided at the other axial end of the outer member. get closer.
- the axial position of the intersection point is located on one axial side of the axial position of the axial center portion of the vehicle body mounting flange.
- the axial position of the intersection approaches the axial center of the vehicle body mounting flange and the axial center. Therefore, the load transmitted to the outer member via both balls can be borne near the center of the bearing and the vehicle body mounting flange of the outer member. As a result, it is possible to prevent the load generated by the lower side of the wheel from colliding with the curbstone from being biased in the axial direction and borne by the outer member. can be done.
- FIG. 1 is a cross-sectional view of the wheel bearing device 10.
- FIG. A wheel bearing device 10 (hereinafter also simply referred to as a bearing device 10) is a bearing device used in a vehicle such as an automobile, and is also called a hub unit.
- the bearing device 10 rotatably supports the wheel with respect to a suspension device provided on the vehicle body of the automobile.
- the bearing device 10 includes an outer ring 11 (outer member), an inner shaft 12 (inner member), a plurality of balls 13, a retainer 14, and seal members 15 and 16.
- the outer ring 11 and the inner shaft 12 are arranged concentrically.
- the inner shaft 12 is rotatable with respect to the outer ring 11 around the central axis C1. That is, the outer ring 11 is a fixed ring, and the inner shaft 12 is a rotating ring (rotating shaft).
- the direction along the central axis C1 is called “axial direction”.
- the axial direction also includes a direction parallel to the central axis C1.
- the vehicle outer side is referred to as one axial direction side
- the vehicle inner side is referred to as the other axial direction side.
- a direction orthogonal to the axial direction is called a “radial direction”.
- the direction in which the inner shaft 12 rotates around the central axis C1 is called “circumferential direction”.
- the bearing device 10 can rotatably support an inner shaft 12 to which wheels and brake discs (not shown) are rotatably fixed with respect to the vehicle body.
- the outer ring 11 is made of carbon steel for machine structural use or the like.
- the outer ring 11 has a cylindrical shape and has a vehicle body mounting flange 11b on an outer peripheral surface 11a.
- the vehicle body mounting flange 11b is a member for mounting the outer ring 11 to the vehicle body.
- FIG. 2 is a view of the vehicle body mounting flange 11b viewed from the vehicle inner side along the central axis C1.
- the vehicle body mounting flange 11b has a plurality of protrusions 11b1 provided along the circumferential direction.
- a plurality of protrusions 11b1 (four in the example shown) protrude from the outer peripheral surface 11a.
- Each protrusion 11b1 has a through hole 11b2 parallel to the central axis C1.
- a bolt for fixing the outer ring 11 to a suspension device on the vehicle body side is inserted through the through hole 11b2.
- the plurality of protrusions 11b1 are provided symmetrically in the vertical direction, but may be provided at regular intervals in the circumferential direction. Also, the number of projecting portions 11b1 may be greater or less.
- a double-row outer raceway surface 17 is provided on the inner peripheral surface of the outer ring 11 .
- the double-row outer raceway surface 17 includes a first outer raceway surface 17a and a second outer raceway surface 17b.
- the first outer raceway surface 17a is provided on one axial side of the second outer raceway surface 17b.
- the outer diameter of the first outer raceway surface 17a is larger than the outer diameter of the second outer raceway surface 17b.
- the inner shaft 12 is made of carbon steel for mechanical structure or the like.
- the inner shaft 12 has a shaft member 18 and an inner ring 19 .
- the shaft member 18 has a body portion 18a extending along the axial direction and a wheel mounting flange 18b projecting radially outward from the body portion 18a.
- the body portion 18a and the wheel mounting flange 18b are integral.
- the wheel mounting flange 18b is provided on one axial side of the body portion 18a. Wheels and brake discs (not shown) are attached to the wheel attachment flanges 18b.
- the inner ring 19 is an annular member made of carbon steel for machine structural use or the like.
- the inner ring 19 is fixed to the other axial end of the shaft member 18 .
- a small-diameter portion 18c having an outer diameter smaller than that of the other portion of the main body portion 18a is provided on the other side of the shaft member 18 in the axial direction.
- the inner ring 19 is press-fitted into the small-diameter portion 18c from the other side in the axial direction and fitted to the outer peripheral surface of the small-diameter portion 18c.
- An end portion 18d on the other side in the axial direction of the shaft member 18 is crimped by being plastically deformed radially outward. The inner ring 19 is thereby fixed to the shaft member 18 .
- a double-row inner raceway surface 20 is provided on the outer peripheral surface of the inner shaft 12 .
- the double-row inner raceway surface 20 includes a first inner raceway surface 20a and a second inner raceway surface 20b.
- the first inner raceway surface 20 a is provided on the outer peripheral surface of the body portion 18 a of the shaft member 18 .
- the first inner raceway surface 20a faces the first outer raceway surface 17a.
- the second inner raceway surface 20 b is provided on the outer peripheral surface of the inner ring 19 .
- the second inner raceway surface 20b faces the second outer raceway surface 17b. Therefore, the first inner raceway surface 20a is provided on one axial side of the second inner raceway surface 20b.
- the plurality of balls 13 are balls formed of bearing steel or the like.
- the plurality of balls 13 includes a plurality of first balls 13a and a plurality of second balls 13b.
- the plurality of first balls 13a are interposed between the first outer raceway surface 17a and the first inner raceway surface 20a.
- the plurality of second balls 13b are interposed between the second outer raceway surface 17b and the second inner raceway surface 20b.
- the diameter of the plurality of first balls 13a and the diameter of the plurality of second balls 13b are the same.
- the plurality of balls 13 are in point contact with the outer raceway surfaces 17a, b and the inner raceway surfaces 20a, 20b with a predetermined contact angle. That is, the bearing device 10 includes a double-row angular contact ball bearing, and the outer ring 11 and the inner shaft 12 each form a bearing ring.
- the retainer 14 is an annular member made of resin.
- the retainer 14 holds a plurality of balls 13 in each row at predetermined intervals in the circumferential direction.
- the seal member 15 is attached between the one axial end of the outer ring 11 and the body portion 18a.
- the seal member 16 is attached between the other axial end of the outer ring 11 and the inner ring 19 .
- the sealing members 15 and 16 serve to prevent foreign matter such as muddy water from entering the annular space formed between the outer ring 11 and the inner shaft 12, and seal the annular space so that the lubricant does not leak out. have.
- FIG. 3 is a cross-sectional view of the main part of the bearing device 10. As shown in FIG. As shown in FIG. 3, the pitch diameter D1 of the plurality of first balls 13a is larger than the pitch diameter D2 of the plurality of second balls 13b.
- the contact angle ⁇ a of the plurality of first balls 13a is 30 degrees, and the contact angle ⁇ b of the plurality of second balls 13b is 40 degrees.
- the contact angle ⁇ a of the plurality of first balls 13a is smaller than the contact angle ⁇ b of the plurality of second balls 13b.
- the contact angle ⁇ a of the plurality of first balls 13a is set within a range of 25 to 35 degrees. Further, the contact angle ⁇ b of the plurality of second balls 13b is set within the range of 35 to 45 degrees.
- the contact angle of the ball 13 is the angle formed by a plane (radial plane) perpendicular to the central axis C1 and the line of action of the resultant force transmitted to the ball 13 by the outer ring 11 and the inner shaft 12 .
- a first line of action L1 of the load acting on the first ball 13a includes a contact portion 31 of the first ball 13a with the first outer raceway surface 17a, a contact portion 32 of the first ball 13a with the first inner raceway surface 20a, and a contact portion 32 of the first ball 13a with the first inner raceway surface 20a. It is a straight line passing through the center 33 of one ball 13a.
- the contact angle ⁇ a of the first ball 13a is the angle between the first line of action L1 and a straight line L2 passing through the center 33 of the first ball 13a and orthogonal to the central axis C1.
- the second line of action L3 of the load acting on the second ball 13b includes a contact portion 41 of the second ball 13b with the second outer raceway surface 17b, a contact portion 42 of the second ball 13b with the second inner raceway surface 20b, and a straight line passing through the center 43 of the second ball 13b.
- the contact angle ⁇ b of the second ball 13b is the angle between the second line of action L3 and a straight line L4 passing through the center 43 of the second ball 13b and orthogonal to the central axis C1.
- the axial position of the intersection point P1 between the first line of action L1 and the second line of action L3 is the axial position of the first outer raceway surface 17a and the axial position of the second outer raceway surface 17b. It is located on one side in the axial direction of the center. More specifically, the straight line L2 passes through the bottom portion 51 of the first outer raceway surface 17a. Also, the straight line L4 passes through the bottom portion 52 of the second outer raceway surface 17b.
- the axial centerline LC is orthogonal to the central axis C1 and positioned at the axial center between the straight lines L2 and L4. The intersection point P1 is located on one axial side of the axial centerline LC.
- the axial position of the intersection point P1 is on one axial side of the axial center between the axial position of the bottom portion 51 of the first outer raceway surface 17a and the axial position of the bottom portion 52 of the second outer raceway surface 17b. To position.
- the axial position of the vehicle body mounting flange 11b of this embodiment is positioned between the straight line L2 and the straight line L4. More specifically, the straight line LF indicating the axial center of the vehicle body mounting flange 11b is a straight line that is perpendicular to the center axis C1 and passes through the axial center of the vehicle body mounting flange 11b.
- the straight line LF is located on one axial side of the axial centerline LC. Therefore, the axial position of the axial center of the vehicle body mounting flange 11b is located from the axial center between the axial position of the bottom portion 51 of the first outer raceway surface 17a and the axial position of the bottom portion 52 of the second outer raceway surface 17b.
- the axial position of the axial center of the vehicle body mounting flange 11b is closer to the axial position of the bottom portion 51 of the first outer raceway surface 17a than the axial position of the bottom portion 52 of the second outer raceway surface 17b.
- the axial position of the intersection point P1 is located on one axial side of the straight line LF. Therefore, the axial position of the intersection point P1 is located on one axial side of the axial position of the axial center of the vehicle body mounting flange 11b.
- FIG. 4 is a cross-sectional view of the wheel bearing device 10 for explaining a case where the lower side of the wheel collides with a curbstone.
- an excessive moment load acts on the inner shaft 12 in the direction indicated by the arrow Y1 via the wheel mounting flange 18b.
- a large load acts on the first ball 13a1 positioned below the central axis C1 among the plurality of first balls 13a.
- the contact angle ⁇ a of the first ball 13a1 temporarily increases.
- the contact angle ⁇ b of the second ball 13b1 positioned below the central axis C1 among the plurality of second balls 13b temporarily decreases.
- the contact angle ⁇ a of the plurality of first balls 13a is smaller than the contact angle ⁇ b of the plurality of second balls 13b, so that the lower side of the wheel W collides with the curb and the first ball 13a1 Even if the contact angle ⁇ a of the first ball 13a temporarily increases, it is possible to suppress an increase in the difference between the contact angle ⁇ a of the first ball 13a and the contact angle ⁇ b of the second ball 13b. As a result, it is possible to suppress the relative decrease in the allowable load in the radial direction by the plurality of first balls 13a, suppress the concentration of the load on the first balls 13a, and suppress the first inner raceway surface 20a and the first inner raceway surface 20a. It is possible to suppress the occurrence of dents on the outer raceway surface 17a.
- the contact angle ⁇ a of the plurality of first balls 13a is made smaller than the contact angle ⁇ b of the plurality of second balls 13b, so that the plurality of first balls 13a and the first outer raceway surface 17a contact each other. and the first inner raceway surface 20a, the temperature rise of the entire wheel bearing device 10 is suppressed, and the rotational torque can be reduced.
- the pitch diameter D1 of the plurality of first balls 13a is larger than the pitch diameter D2 of the plurality of second balls 13b.
- the load acting on the plurality of second balls 13b can be made larger than the allowable load. Thereby, it is possible to effectively suppress the occurrence of dents on the first inner raceway surface 20a and the first outer raceway surface 17a. Also, if the contact angle ⁇ a of the plurality of first balls 13a is reduced, the allowable load for the axial load is lowered, and there is a possibility that the service life of the bearing under normal use will be shortened.
- the service life of the plurality of first balls 13a and raceway surfaces 17a and 20a as a bearing may be shorter than the service life of the plurality of second balls 13b and raceway surfaces 17b and 20b.
- the pitch diameter D1 of the plurality of first balls 13a is made larger than the pitch diameter D2 of the plurality of second balls 13b, and the allowable load for the load acting on the plurality of first balls 13a is is increased, it is possible to compensate for the relative decrease in life of the plurality of first balls 13a and the raceway surfaces 17a, 20a caused by the change in the contact angle ⁇ a. As a result, it is possible to suppress the deterioration of the life of the wheel bearing device 10 as a whole.
- the axial position (the straight line LF) of the axial center of the vehicle body mounting flange 11b is the axial position of the bottom portion 51 of the first outer raceway surface 17a and the bottom portion 52 of the second outer raceway surface 17b. It is positioned on one side in the axial direction of the center in the axial direction with respect to the axial position.
- the axial position (line LF) of the axial center of the vehicle body mounting flange 11b is closer to the axial position of the bottom portion 51 of the first outer raceway surface 17a than the axial position of the bottom portion 52 of the second outer raceway surface 17b. It is located close to
- the axial position of the vehicle body mounting flange 11b and the axial position of the wheel mounting flange 18b to which the load is applied are compared with the case where the vehicle body mounting flange 11b is provided at the vehicle inner side end of the outer ring 11, for example. and become closer. Therefore, it is possible to reduce the moment load acting on the entire bearing device 10 via the wheel mounting flange 18b when the lower side of the wheel W collides with the curbstone. As a result, it is possible to more effectively suppress the occurrence of dents on the first inner raceway surface 20a and the first outer raceway surface 17a.
- the intersection point P1 and the vehicle body mounting flange 11b can be provided close to each other in the axial direction.
- the load transmitted from the inner shaft 12 to the outer ring 11 via the balls 13 is borne at a position near the vehicle body mounting flange 11b on the outer ring 11 except when the lower side of the wheel W collides with the curbstone. can be done. Therefore, the load transmitted from the inner shaft 12 to the outer ring 11 via the two balls 13 can be appropriately borne except when the lower side of the wheel W collides with a curbstone.
- the axial position of the intersection point P1 is located on one side in the axial direction of the axial position (line LF) of the axial center of the vehicle body mounting flange 11b, the lower side of the wheel W is positioned on the curb.
- the contact angle ⁇ a of the first ball 13a1 temporarily increases, the axial position of the intersection point P1 approaches the straight line LF and the axial centerline LC. Therefore, the load transmitted to the outer ring 11 via the two balls 13a and 13b can be borne by the vehicle body mounting flange 11b of the outer ring 11 and the vicinity of the axial centerline LC.
- the axial position of the axial center of the vehicle body mounting flange 11b is the same as the axial position of the bottom portion 51 of the first outer raceway surface 17a and the axial position of the bottom portion 52 of the second outer raceway surface 17b.
- the axial position of the axial center of the vehicle body mounting flange 11b is the axial position of the bottom portion 51 of the first outer raceway surface 17a and the axial position of the second outer raceway surface 17a. It may be positioned on the other side in the axial direction of the axial center of the bottom portion 52 of the outer raceway surface 17b.
- the axial position of the intersection point P1 is located on one side of the axial center of the vehicle body mounting flange 11b in the axial direction, but the axial position of the intersection point P1 is It may be located on the other side in the axial direction of the axial position of the center of the vehicle body mounting flange 11b. In other words, the axial position of the center of the vehicle body mounting flange 11b in the axial direction may be located on one axial side of the axial position of the intersection point P1.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Rolling Contact Bearings (AREA)
Abstract
Description
上記車輪用軸受装置は、軸方向一方側に車輪取付フランジを有する内方部材と、外方部材と、複列に配置されて両部材に介在する複数の玉とを有する。複数の玉は、複列のうちの軸方向一方側の列に配置される複数の第1玉と、軸方向他方側の列に配置される複数の第2玉と、を含む(例えば、特許文献1参照)。
[実施形態の概要]
(1)実施形態である車輪用軸受装置は、軸方向一方側に車輪取付フランジを有するとともに軸方向他方側に複列の内側軌道面を有する内方部材と、前記複列の内側軌道面に対向する複列の外側軌道面を有する外方部材と、前記複列の内側軌道面のうちの軸方向一方側の第1内側軌道面と、前記複列の外側軌道面のうちの軸方向一方側の第1外側軌道面と、の間に介在する複数の第1玉と、前記複列の内側軌道面のうちの軸方向他方側の第2内側軌道面と、前記複列の外側軌道面のうちの軸方向他方側の第2外側軌道面と、の間に介在する複数の第2玉と、を備え、前記複数の第1玉と前記複数の第2玉とは同じ直径であり、前記複数の第1玉の接触角が、前記複数の第2玉の接触角よりも小さい。
また、複数の第1玉の接触角を小さくすれば、アキシャル荷重に対する許容負荷が低下し通常の使用による軸受としての寿命が低下するおそれがある。よって、複数の第1玉、第1外側軌道面、及び第1内側軌道面の軸受としての寿命が、複数の第2玉、第2外側軌道面、及び第2内側軌道面の寿命よりも低下するおそれがある。
この点、複数の第1玉のピッチ円直径を、複数の第2玉のピッチ円直径よりも大きくし、複数の第1玉に作用する荷重に対する許容負荷を大きくしたので、接触角の変更によって生じる複数の第1玉、第1外側軌道面、及び第1内側軌道面の相対的な寿命低下を補完することができる。この結果、車輪用軸受装置10全体としての寿命低下を抑制することができる。
複数の第1玉に作用する荷重の第1作用線は、車輪用軸受装置の中心軸に垂直な平面との間で複数の第1玉の接触角を成す。また、前記複数の第2玉に作用する荷重の第2作用線は、車輪用軸受装置の中心軸に垂直な平面との間で複数の第2玉の接触角を成す。よって、第1作用線と第2作用線との交点の軸方向位置が、前記第1外側軌道面の底部の軸方向位置と、前記第2外側軌道面の底部の軸方向位置との軸方向中心よりも軸方向一方側に位置するようにすることで、複数の第1玉の接触角は、複数の第2玉の接触角よりも小さく設定される。
この場合、例えば、車体取付フランジを外方部材の軸方向他方側の端部に設けた場合と比較して、車体取付フランジの軸方向位置と、荷重が与えられる車輪取付フランジの軸方向位置とがより近くなる。よって、車輪の側面下側が縁石に衝突したときに車輪取付フランジを介して車輪用軸受装置全体に作用するモーメント荷重を低減することができ、第1内側軌道面及び第1外側軌道面に圧痕が生じるのをより効果的に抑制することができる。
この場合も、車体取付フランジを外方部材の軸方向他方側の端部に設けた場合と比較して、車体取付フランジの軸方向位置と、荷重が与えられる車輪取付フランジの軸方向位置とがより近くなる。よって、車輪の側面下側が縁石に衝突したときに車輪取付フランジを介して車輪用軸受装置全体に作用するモーメント荷重を低減することができ、第1内側軌道面及び第1外側軌道面に圧痕が生じるのをより効果的に抑制することができる。
この場合、車輪の側面下側が縁石に衝突し、第1玉の接触角が一時的に大きくなったときに、交点の軸方向位置が車体取付フランジの軸方向中央及び前記軸方向中心に近づく。よって、両玉を介して外方部材に伝わる荷重を、外方部材における車体取付フランジ及び軸受中心近傍で負担することができる。この結果、車輪の側面下側が縁石に衝突したことで生じる荷重が軸方向に偏って外方部材に負担されるのを抑制することができ、外方部材11に伝わる荷重を適切に負担することができる。
以下、好ましい実施形態について図面を参照しつつ説明する。
〔軸受装置の全体構成〕
図2に示すように車体取付フランジ11bは、周方向に沿って設けられた複数の突起部11b1を有する。複数の突起部11b1(図例では4つ)は、外周面11aから突出している。
各突起部11b1は、中心軸C1に平行な貫通孔11b2を有する。貫通孔11b2には、外輪11を車体側の懸架装置に固定するためのボルトが挿通される。
なお、本実施形態では、複数の突起部11b1は、上下方向に対象となるように設けられているが、周方向に等間隔で設けられていてもよい。また、突起部11b1の個数は、より多数であってもよいし、より少なくてもよい。
軸部材18の軸方向他方側には、本体部18aの他の部分よりも外径が小さい小径部18cが設けられる。内輪19は、小径部18cに軸方向他方側から圧入され、小径部18cの外周面に嵌合されている。軸部材18の軸方向他方側の端部18dは径方向外方へ塑性変形させることにより、かしめられている。これによって、内輪19は軸部材18に固定されている。
第1内側軌道面20aは、軸部材18の本体部18aの外周面に設けられている。第1内側軌道面20aは、第1外側軌道面17aに対向している。
第2内側軌道面20bは、内輪19の外周面に設けられている。第2内側軌道面20bは、第2外側軌道面17bに対向している。
よって、第1内側軌道面20aは、第2内側軌道面20bよりも、軸方向一方側に設けられている。
複数の第1玉13aは、第1外側軌道面17aと、第1内側軌道面20aとの間に介在する。
複数の第2玉13bは、第2外側軌道面17bと、第2内側軌道面20bとの間に介在する。
複数の第1玉13aの直径と、複数の第2玉13bの直径とは、同じである。
シール部材15は、外輪11の軸方向一方側の端部と本体部18aとの間に取り付けられている。シール部材16は、外輪11の軸方向他方側の端部と内輪19との間に取り付けられている。シール部材15、16は、外輪11と内軸12との間に形成される環状空間に泥水等の異物が浸入するのを防ぎ、かつ環状空間内の潤滑剤が漏出しないように封止する役割を有している。
図3に示すように、複数の第1玉13aのピッチ円直径D1は、複数の第2玉13bのピッチ円直径D2よりも大きい。
なお、複数の第1玉13aの接触角θaは、25~35度の範囲で設定される。また、複数の第2玉13bの接触角θbは、35~45度の範囲で設定される。
ここで、玉13の接触角とは、中心軸C1に垂直な平面(ラジアル平面)と、外輪11及び内軸12によって玉13へ伝えられる力の合力の作用線と、がなす角度である。
第1玉13aに作用する荷重の第1作用線L1は、第1玉13aにおける第1外側軌道面17aに対する接触部分31、第1玉13aにおける第1内側軌道面20aに対する接触部分32、及び第1玉13aの中心33を通過する直線である。
第1玉13aの接触角θaは、第1作用線L1と、第1玉13aの中心33を通過しかつ中心軸C1と直交する直線L2とが成す角度である。
また、第2玉13bに作用する荷重の第2作用線L3は、第2玉13bにおける第2外側軌道面17bに対する接触部分41、第2玉13bにおける第2内側軌道面20bに対する接触部分42、及び第2玉13bの中心43を通過する直線である。
第2玉13bの接触角θbは、第2作用線L3と、第2玉13bの中心43を通過しかつ中心軸C1と直交する直線L4とが成す角度である。
より具体的に、直線L2は、第1外側軌道面17aの底部51を通過している。また、直線L4は、第2外側軌道面17bの底部52を通過している。
図3中、軸方向中心線LCは、中心軸C1に直交するとともに、直線L2と直線L4との軸方向中心に位置する。交点P1は、軸方向中心線LCよりも軸方向一方側に位置する。
よって、交点P1の軸方向位置は、第1外側軌道面17aの底部51の軸方向位置と、第2外側軌道面17bの底部52の軸方向位置との軸方向中心よりも軸方向一方側に位置する。
より詳細に、車体取付フランジ11bの軸方向中央を示す直線LFは、中心軸C1に直交するとともに、車体取付フランジ11bの軸方向中央を通過する直線である。直線LFは、軸方向中心線LCよりも軸方向一方側に位置する。
よって、車体取付フランジ11bの軸方向中央の軸方向位置は、第1外側軌道面17aの底部51の軸方向位置と、第2外側軌道面17bの底部52の軸方向位置との軸方向中心よりも軸方向一方側に位置する。
言い換えると、車体取付フランジ11bの軸方向中央の軸方向位置は、第2外側軌道面17bの底部52の軸方向位置よりも、第1外側軌道面17aの底部51の軸方向位置に近い位置である。
よって、交点P1の軸方向位置は、車体取付フランジ11bの軸方向中央の軸方向位置よりも軸方向一方側に位置する。
図4は、車輪の側面下側が縁石に衝突した場合を説明するための車輪用軸受装置10の断面図である。
例えば、車輪Wの側面下側が縁石に衝突したとする。すると、内軸12には、車輪取付フランジ18bを介して矢印Y1に示す方向に過大なモーメント荷重が作用する。
このような過大なモーメント荷重が内軸12に作用すると、複数の第1玉13aのうち、中心軸C1よりも下方に位置する第1玉13a1に大きく荷重が作用する。
これにより、第1内側軌道面20a及び第1外側軌道面17aに圧痕が生じるのを効果的に抑制することができる。
また、複数の第1玉13aの接触角θaを小さくすれば、アキシャル荷重に対する許容負荷が低下し通常の使用による軸受としての寿命が低下するおそれがある。
よって、複数の第1玉13a及び軌道面17a、20aの軸受としての寿命が、複数の第2玉13b及び軌道面17b、20bの寿命よりも低下するおそれがある。
この点、本実施形態では、複数の第1玉13aのピッチ円直径D1を、複数の第2玉13bのピッチ円直径D2よりも大きくし、複数の第1玉13aに作用する荷重に対する許容負荷を大きくしたので、接触角θaの変更によって生じる複数の第1玉13a及び軌道面17a、20aの相対的な寿命低下を補完することができる。この結果、車輪用軸受装置10全体としての寿命低下を抑制することができる。
言い換えると、車体取付フランジ11bの軸方向中央の軸方向位置(直線LF)が、第2外側軌道面17bの底部52の軸方向位置よりも、第1外側軌道面17aの底部51の軸方向位置に近い位置である。
今回開示した実施形態はすべての点で例示であって制限的なものではない。
例えば、本実施形態では、車体取付フランジ11bの軸方向中央の軸方向位置が、第1外側軌道面17aの底部51の軸方向位置と、第2外側軌道面17bの底部52の軸方向位置との軸方向中心よりも軸方向一方側に位置する場合を例示したが、車体取付フランジ11bの軸方向中央の軸方向位置は、第1外側軌道面17aの底部51の軸方向位置と、第2外側軌道面17bの底部52の軸方向位置との軸方向中心の軸方向他方側に位置していてもよい。
11 外輪
11a 外周面
11b 車体取付フランジ
11b1 突起部
11b2 貫通孔
12 内軸
13 玉
13a,13a1 第1玉
13b,13b1,13b2 第2玉
14 保持器
15 シール部材
16 シール部材
17 外側軌道面
17a 第1外側軌道面
17b 第2外側軌道面
18 軸部材
18a 本体部
18b 車輪取付フランジ
18c 小径部
18d 端部
19 内輪
20 内側軌道面
20a 第1内側軌道面
20b 第2内側軌道面
31 接触部分
32 接触部分
33 中心
41 接触部分
42 接触部分
43 中心
51 底部
52 底部
C1 中心軸
D1 ピッチ円直径
D2 ピッチ円直径
L1 第1作用線
L2 直線
L3 第2作用線
L4 直線
LC 軸方向中心線
LF 直線
P1 交点
W 車輪
Y1 矢印
Y2 矢印
θa 接触角
θb 接触角
Claims (6)
- 軸方向一方側に車輪取付フランジを有するとともに軸方向他方側に複列の内側軌道面を有する内方部材と、
前記複列の内側軌道面に対向する複列の外側軌道面を有する外方部材と、
前記複列の内側軌道面のうちの軸方向一方側の第1内側軌道面と、前記複列の外側軌道面のうちの軸方向一方側の第1外側軌道面と、の間に介在する複数の第1玉と、
前記複列の内側軌道面のうちの軸方向他方側の第2内側軌道面と、前記複列の外側軌道面のうちの軸方向他方側の第2外側軌道面と、の間に介在する複数の第2玉と、を備え、
前記複数の第1玉と前記複数の第2玉とは同じ直径であり、
前記複数の第1玉の接触角が、前記複数の第2玉の接触角よりも小さい
車輪用軸受装置。 - 前記複数の第1玉のピッチ円直径が、前記複数の第2玉のピッチ円直径よりも大きい
請求項1に記載の車輪用軸受装置。 - 前記複数の第1玉に作用する荷重の第1作用線と前記複数の第2玉に作用する荷重の第2作用線との交点の軸方向位置が、前記第1外側軌道面の底部の軸方向位置と、前記第2外側軌道面の底部の軸方向位置との軸方向中心よりも軸方向一方側に位置する
請求項1又は請求項2に記載の車輪用軸受装置。 - 前記外方部材は、前記外方部材が車体に取り付けられるための車体取付フランジを外周に有し、
前記車体取付フランジの軸方向中央の軸方向位置が、前記第2外側軌道面の底部の軸方向位置よりも、前記第1外側軌道面の底部の軸方向位置に近い位置である
請求項3に記載の車輪用軸受装置。 - 前記外方部材は、前記外方部材が車体に取り付けられるための車体取付フランジを外周に有し、
前記車体取付フランジの軸方向中央の軸方向位置は、前記第1外側軌道面の底部の軸方向位置と、前記第2外側軌道面の底部の軸方向位置との軸方向中心よりも軸方向一方側に位置する
請求項3に記載の車輪用軸受装置。 - 前記交点の軸方向位置は、前記車体取付フランジの軸方向中央部の軸方向位置よりも軸方向一方側に位置する
請求項4又は請求項5に記載の車輪用軸受装置。
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JP2000161368A (ja) * | 1998-11-27 | 2000-06-13 | Koyo Seiko Co Ltd | ホイール用軸受 |
JP2004345439A (ja) * | 2003-05-21 | 2004-12-09 | Honda Motor Co Ltd | 車輪支持用ハブユニット |
JP2013177913A (ja) * | 2012-02-28 | 2013-09-09 | Nsk Ltd | 車輪用複列アンギュラ型玉軸受 |
JP2017128236A (ja) * | 2016-01-20 | 2017-07-27 | Ntn株式会社 | 車輪用軸受装置 |
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JP2000161368A (ja) * | 1998-11-27 | 2000-06-13 | Koyo Seiko Co Ltd | ホイール用軸受 |
JP2004345439A (ja) * | 2003-05-21 | 2004-12-09 | Honda Motor Co Ltd | 車輪支持用ハブユニット |
JP2013177913A (ja) * | 2012-02-28 | 2013-09-09 | Nsk Ltd | 車輪用複列アンギュラ型玉軸受 |
JP2017128236A (ja) * | 2016-01-20 | 2017-07-27 | Ntn株式会社 | 車輪用軸受装置 |
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