WO2015050143A1 - 複列円すいころ軸受ユニットおよびその製造方法 - Google Patents

複列円すいころ軸受ユニットおよびその製造方法 Download PDF

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Publication number
WO2015050143A1
WO2015050143A1 PCT/JP2014/076215 JP2014076215W WO2015050143A1 WO 2015050143 A1 WO2015050143 A1 WO 2015050143A1 JP 2014076215 W JP2014076215 W JP 2014076215W WO 2015050143 A1 WO2015050143 A1 WO 2015050143A1
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WIPO (PCT)
Prior art keywords
inner ring
shaft member
fitted
raceway
peripheral surface
Prior art date
Legal status (The legal status 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 status listed.)
Ceased
Application number
PCT/JP2014/076215
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English (en)
French (fr)
Japanese (ja)
Inventor
信行 萩原
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
NSK Ltd
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 CN201480048779.2A priority Critical patent/CN105518321B/zh
Priority to US15/026,800 priority patent/US9581192B2/en
Priority to EP14850592.8A priority patent/EP3054184B1/en
Publication of WO2015050143A1 publication Critical patent/WO2015050143A1/ja
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
    • F16C19/38—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers
    • F16C19/383—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
    • F16C19/385—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings
    • F16C19/386—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings in O-arrangement
    • 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
    • B60B27/001—Hubs with roller-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
    • 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
    • B60B35/00—Axle units; Parts thereof ; Arrangements for lubrication of axles
    • B60B35/02—Dead axles, i.e. not transmitting torque
    • 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
    • F16C33/34—Rollers; Needles
    • F16C33/36—Rollers; Needles with bearing-surfaces other than cylindrical, e.g. tapered; with grooves in the bearing surfaces
    • F16C33/366—Tapered rollers, i.e. rollers generally shaped as truncated cones
    • 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
    • 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
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
    • F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
    • F16C35/063—Fixing them on the shaft
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B2380/00—Bearings
    • B60B2380/10—Type
    • B60B2380/14—Roller bearings
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B2380/00—Bearings
    • B60B2380/60—Rolling elements
    • B60B2380/64—Specific shape
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B2380/00—Bearings
    • B60B2380/70—Arrangements
    • B60B2380/73—Double track
    • 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
    • F16C2226/00—Joining parts; Fastening; Assembling or mounting parts
    • F16C2226/10—Force connections, e.g. clamping
    • F16C2226/12—Force connections, e.g. clamping by press-fit, e.g. plug-in
    • 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
    • F16C2226/00—Joining parts; Fastening; Assembling or mounting parts
    • F16C2226/50—Positive connections
    • F16C2226/52—Positive connections with plastic deformation, e.g. caulking or staking
    • 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
    • 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
    • F16C2326/20—Land vehicles
    • 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
    • F16C33/60—Raceways; Race rings divided or split, e.g. comprising two juxtaposed rings

Definitions

  • the present invention relates to a double row tapered roller bearing unit used for rotatably supporting a wheel with respect to a suspension device in a relatively heavy automobile such as a light truck and a large passenger car, and a method for manufacturing the same.
  • FIG. 9 shows a double-row tapered roller bearing unit used for rotationally supporting a drive wheel with respect to a suspension device in a relatively heavy automobile such as a light truck or a large passenger car.
  • This double-row tapered roller bearing unit includes an outer ring 1 that is an outer diameter side race ring member, a hub 2 that is an inner diameter side race ring member, and a plurality of tapered rollers 3.
  • the outer ring 1 includes double-row outer ring raceways 4 and 5 on the inner peripheral surface, and stationary flanges 6 on the outer peripheral surface for coupling and fixing to the knuckle of the suspension device.
  • the first outer ring raceway 4 located on the axially inner side which is one side in the axial direction and the second outer ring raceway 5 located on the outer side in the axial direction which is the other side in the axial direction Is formed by a partial conical surface inclined in a direction in which the diameter increases toward the direction away from each other.
  • “inside” in the axial direction means the center side in the width direction of the vehicle in the assembled state in the automobile, and is the right side in FIGS.
  • outside in the axial direction refers to the outside in the width direction of the vehicle, which is the left side of FIGS. 1 and 9 and the lower side of FIGS. 3 and 8.
  • the hub 2 is disposed concentrically with the outer ring 1 on the inner diameter side of the outer ring 1.
  • the hub 2 includes a plurality of rows of inner ring raceways 7 and 8 at the inner peripheral portion and the intermediate portion of the outer peripheral surface, and a portion projecting in the axial direction from the inner diameter side of the outer ring 1 at a portion closer to the outer end in the axial direction.
  • Rotation side flanges 9 for supporting and fixing each of them.
  • the first inner ring raceway 7 located on the inner side in the axial direction and the second inner ring raceway 8 located on the outer side in the axial direction have a larger diameter in the direction away from each other in the axial direction. It consists of a partial conical surface inclined in the direction.
  • the hub 2 includes an annular first inner ring 10 having a first inner ring raceway 7 formed on the outer peripheral surface, an annular second inner ring 11 having a second inner ring raceway 8 formed on the outer peripheral surface, and a rotation side flange 9.
  • the first inner ring raceway 7 (second inner ring raceway 8) is provided with a small flange portion provided at the small diameter end portion and a large diameter side end portion of the outer peripheral surface of the first inner ring 10 (second inner ring 11). It is provided between the buttocks.
  • the second inner ring 11 is externally fitted by an interference fit into the axially outer half of a cylindrical fitting surface portion 13 provided from the axially inner end portion to the intermediate portion of the outer peripheral surface of the hub body 12 by press fitting. .
  • the first inner ring 10 is externally fitted to the inner half of the fitting surface portion 13 in the axial direction by press-fitting.
  • the large-diameter side end surface of the first inner ring 10 is restrained by a caulking portion 15 formed by plastically deforming a cylindrical portion 14 provided at the axially inner end portion of the hub body 12 radially outward. ing.
  • first inner ring 10 and the second inner ring 11 are sandwiched from both sides in the axial direction by the step surface 16 and the caulking portion 15 existing at the axially outer end portion of the fitting surface portion 13 with respect to the hub body 12. Bonding is fixed.
  • a plurality of tapered rollers 3 are held by a cage 17 between the first outer ring raceway 4 and the first inner ring raceway 7 and between the second outer ring raceway 5 and the second inner ring raceway 8, respectively. It is arranged to roll freely in the state. Between the inner peripheral surface of the inner end portion in the axial direction of the outer ring 1 and the outer peripheral surface of the end portion on the large diameter side of the first inner ring 10 and the inner peripheral surface of the outer end portion in the axial direction of the outer ring 1 and the end portion on the large diameter side of the second inner ring 11. A combination seal ring 18 is assembled between each outer peripheral surface, and both axial ends of the cylindrical space in which the tapered rollers 3 are installed are closed. A spline hole 19 is provided at the center of the hub body 12 in the radial direction for inserting the tip of the drive shaft into spline engagement.
  • the first inner ring 10 When the hub 2 is assembled, as the caulking portion 15 is formed, the first inner ring 10 is elastically deformed so that the large-diameter end thereof is elastically larger than the small-diameter end. Along with this, the inclination angle of the first inner ring raceway 7 changes. Therefore, as described in Japanese Patent No. 4019548, the inclination of the first inner ring raceway 7 in the state before the caulking portion 15 is formed in consideration of the change in the inclination angle of the first inner ring raceway 7. It is necessary to adjust the angle. If such an adjustment is not made, the contact state between the rolling surface of the tapered roller 3 and the respective raceways 4, 5, 7, and 8 becomes irregular, and it is difficult to ensure the durability of the double-row tapered roller bearing unit.
  • the inclination angle of the first inner ring raceway 7 refers to the inclination angle of the first inner ring raceway 7 with respect to the central axis of the first inner ring 10.
  • the inclination angle of the second inner ring raceway 8 refers to the inclination angle of the second inner ring raceway 8 with respect to the central axis of the second inner ring 11.
  • an object of the present invention is to provide a structure of a double row tapered roller bearing unit capable of further improving durability and a manufacturing method for realizing such a double row tapered roller. Yes.
  • the double row tapered roller bearing unit of the present invention is An outer-diameter-side track ring member having a first outer ring raceway and a second outer ring raceway, each of which is constituted by a partial conical surface inclined in a direction in which the diameter increases in a direction away from each other with respect to the axial direction on the inner peripheral surface;
  • An inner diameter side race ring member having a first inner ring raceway and a second outer ring raceway, each formed by a partial conical surface inclined in a direction in which the diameter increases in a direction away from each other with respect to the axial direction on the outer peripheral surface;
  • a plurality of tapered rollers each provided between the first outer ring raceway and the first inner ring raceway and between the second outer ring raceway and the second inner ring raceway;
  • the inner diameter side race ring member includes a first inner ring having a first inner ring raceway formed on an outer peripheral surface, a second inner ring having a second inner ring raceway formed on
  • the second inner ring is externally fitted to the shaft member by press fitting, and the large-diameter side end surface of the first inner ring is suppressed by a caulking portion formed by plastic deformation at one axial end portion of the shaft member.
  • the first inner ring and the second inner ring are configured by being coupled and fixed to the shaft member.
  • the relationship is: ⁇ 1 + ⁇ a ( ⁇ X 1 ) + ⁇
  • the inner diameter of the first inner ring before the first inner ring is fitted onto the shaft member by press fitting, and the inner diameter of the second inner ring before the second inner ring is fitted onto the shaft member by press fitting.
  • a step is provided between a portion where the first inner ring is fitted and a portion where the second inner ring is fitted, and the first inner ring of the outer peripheral surface of the shaft member.
  • the outer diameter of the portion where the second inner ring is fitted to the shaft member before the first inner ring is fitted onto the shaft member is the portion of the outer peripheral surface of the shaft member where the second inner ring is fitted.
  • the outer diameter of the shaft member is larger than that before the second inner ring is externally fitted to the shaft member.
  • a spacer is sandwiched between the small-diameter side end surface of the first inner ring and the small-diameter side end surface of the second inner ring around the stepped portion. Moreover, it is preferable that the specifications of the first inner ring and the second inner ring are substantially equal.
  • a portion on which the first inner ring is fitted and a portion on which the second inner ring is fitted are configured by a single cylindrical surface that is continuous with each other.
  • the inner diameter dimension of the first inner ring in a state before the outer fitting is fitted by press-fitting is smaller than the inner diameter dimension of the second inner ring before the second inner ring is fitted on the shaft member by the press-fitting.
  • the first inner ring has an R chamfered portion at a continuous portion between the inner peripheral surface and the large-diameter end surface
  • the second inner ring has an R chamfered portion where the radius of curvature is larger than the radius of curvature of the R chamfered portion of the first inner ring, or an axial width dimension and a radial width dimension at a continuous portion between the inner peripheral surface and the large-diameter side end surface.
  • the shaft member has a rotation side flange for supporting and fixing the wheel at a portion adjacent to the other side in the axial direction of the portion where the second inner ring is fitted on the outer peripheral surface, and the second inner ring A cross-sectional arc shape that smoothly exists between the outer peripheral surface of the shaft member and the axial one side surface of the rotation side flange, which exists at a position facing the R chamfered portion or the C chamfered portion.
  • the corner R portion is a cross-sectional arc shape that smoothly exists between the outer peripheral surface of the shaft member and the axial one side surface of the rotation side flange, which exists at a position facing the R chamfered portion or the C chamfered portion.
  • the method for producing a double row tapered roller bearing unit of the present invention is a method for producing a double row tapered roller bearing unit having the above-described configuration, An inclination angle ⁇ 1 of the first inner ring raceway in a state before the first inner ring is fitted onto the shaft member by press fitting; An inclination angle ⁇ 2 of the second inner ring raceway in a state before the second inner ring is fitted over the shaft member by press fitting; A tilt angle reduction amount ⁇ a of the first inner ring raceway that is generated when the first inner ring is fitted onto the shaft member by press fitting; A tilt angle reduction amount ⁇ b of the second inner ring raceway that is generated when the second inner ring is fitted on the shaft member by press fitting; By adjusting the amount of increase ⁇ k of the inclination angle of the first inner ring race that is caused by forming the caulking portion, The inclination angle ⁇ 1 of the first inner ring raceway and the inclination angle ⁇ 2 of the second inner ring race in
  • the tilt angle reduction amount ⁇ a is adjusted by adjusting the press-fit allowance ⁇ X 1 of the first inner ring with respect to the shaft member, and the press-fit allowance ⁇ X 2 of the second inner ring with respect to the shaft member is set.
  • the inclination angle reduction amount ⁇ b can be adjusted.
  • the inner diameter of the first inner ring before the first inner ring is fitted onto the shaft member by press fitting, and the inner diameter of the second inner ring before the second inner ring is fitted onto the shaft member by press fitting.
  • a step is provided between a portion where the first inner ring is fitted and a portion where the second inner ring is fitted, and the first inner ring of the outer peripheral surface of the shaft member is The outer diameter of the part to be externally fitted before the first inner ring is externally fitted to the shaft member by press-fitting, the part of the outer peripheral surface of the shaft member to which the second inner ring is externally fitted, The press-fitting allowances ⁇ X 1 and ⁇ X 2 are respectively adjusted to be larger than the outer diameter dimension in a state before the second inner ring is externally fitted to the shaft member.
  • a spacer is sandwiched between the small-diameter side end face of the first inner ring and the small-diameter side end face of the second inner ring around the step portion.
  • the specifications of the first inner ring and the second inner ring are substantially equal.
  • a portion where the first inner ring is fitted and a portion where the second inner ring is fitted are a single cylindrical surface which is continuous with each other,
  • the inner diameter of the first inner ring before the first inner ring is fitted onto the shaft member by press fitting, and the inner diameter of the second inner ring before the second inner ring is fitted onto the shaft member by press fitting.
  • the press-fitting allowances ⁇ X 1 and ⁇ X 2 are respectively adjusted to be smaller.
  • an R chamfered portion is provided at a continuous portion between the inner peripheral surface of the first inner ring and the large-diameter end surface, and a first portion is provided at the continuous portion between the inner peripheral surface of the second inner ring and the large-diameter end surface.
  • a rotation side flange for supporting and fixing the wheel is provided in a portion adjacent to the other side in the axial direction of the portion fitting the second inner ring, and the R chamfered portion of the second inner ring Or the corner
  • angular area R of the circular arc section which exists in the position which opposes a C chamfering part, and makes these surfaces smoothly continue in the continuous part of the outer peripheral surface of the said shaft member and the axial direction one side surface of the said rotation side flange.
  • FIG. 1 is a cross-sectional view showing a first example of an embodiment of the present invention with some components omitted.
  • FIG. 2 is an enlarged view of part a in FIG.
  • FIG. 3 is a diagram showing a hub assembly method in the order of steps.
  • FIG. 4A is a diagram showing a change in the inclination angle of the first inner ring raceway caused by the assembly of the hub
  • FIG. 4B is a line showing a change in the inclination angle of the second inner ring raceway.
  • FIG. FIG. 5 is a diagram showing the relationship between the press-fitting allowance of the first inner ring and the second inner ring and the amount of decrease in the inclination angle of the first inner ring raceway and the second inner ring raceway.
  • FIG. 6 is a diagram showing the relationship between the press-fit allowance of the first inner ring and the second inner ring, the amount of decrease in the inclination angle of the first inner ring track and the second inner ring track, and the amount of increase in the inclination angle of the first inner ring track.
  • FIG. 7 is a diagram showing the relationship between the press-fitting allowance of the first inner ring and the second inner ring, the inclination angle of the first inner ring raceway and the second inner ring raceway after press fitting, and the amount of increase in the inclination angle of the first inner ring raceway is there.
  • FIG. 7 is a diagram showing the relationship between the press-fitting allowance of the first inner ring and the second inner ring, the inclination angle of the first inner ring raceway and the second inner ring raceway after press fitting, and the amount of increase in the inclination angle of the first inner ring raceway is there.
  • FIG. 8 is a cross-sectional view showing the first inner ring, the second inner ring, and the hub body before being combined with each other, showing a second example of the embodiment of the present invention.
  • FIG. 9 is a sectional view showing an example of a conventional double-row tapered roller bearing unit for supporting a wheel.
  • the double-row tapered roller bearing unit for wheel support which is the object of this example, includes an outer ring 1, a hub 2a, and a plurality of tapered rollers 3, as in the conventional structure shown in FIG.
  • FIG. 1 shows the wheel support double-row tapered roller bearing unit according to the present embodiment.
  • the outer ring 1, a plurality of tapered rollers 3, a pair of cages 17 and a pair of combination seal rings 18 are part of the components. Is shown in a state where is omitted.
  • the outer ring 1 includes double row outer ring raceways 4 and 5 formed on the inner peripheral surface, and a stationary side flange 6 formed on the outer peripheral surface and coupled and fixed to the knuckle of the suspension device.
  • the first outer ring raceway 4 positioned on the inner side in the axial direction and the second outer ring raceway 5 positioned on the outer side in the axial direction increase in diameter toward the direction away from each other in the axial direction. It is comprised by the partial conical surface inclined in the direction which becomes.
  • the hub 2a is disposed concentrically with the outer ring 1 on the inner diameter side of the outer ring 1.
  • the hub 2a protrudes in the axial direction from the inner diameter side of the outer ring 1 at a portion closer to the outer end in the axial direction and the double-row inner ring raceways 7 and 8 formed respectively at the inner end and the intermediate portion of the outer peripheral surface.
  • a rotation-side flange 9 for supporting and fixing the wheel.
  • the first inner ring raceway 7 located on the inner side in the axial direction and the second inner ring raceway 8 located on the outer side in the axial direction have larger diameters as they go away from each other in the axial direction. It is comprised by the partial conical surface inclined in the direction which becomes.
  • the hub 2a includes an annular first inner ring 10 having a first inner ring raceway 7 formed on an outer peripheral surface, an annular second inner ring 11 having a second inner ring raceway 8 formed on an outer peripheral surface, and an annular shape used for preload adjustment.
  • the first inner ring raceway 7 (second inner ring raceway 8) is provided with a small flange portion provided at the small diameter end portion and a large diameter side end portion of the outer peripheral surface of the first inner ring 10 (second inner ring 11). It is provided in the part between the buttocks.
  • the second inner ring 11 is externally fitted with an interference fit by press-fitting into the outer half in the axial direction of a cylindrical fitting surface portion 13a provided from the inner end in the axial direction of the outer peripheral surface of the hub body 12a to the intermediate portion. It is fitted.
  • the first inner ring 10 is externally fitted with an interference fit by being press-fitted into the inner half of the fitting surface portion 13a in the axial direction.
  • the spacer 20 is sandwiched between the small diameter side end surface of the first inner ring 10 and the small diameter side end surface of the second inner ring 11.
  • the large-diameter side end face of the first inner ring 10 is held down by a caulking portion 15 formed by plastically deforming a cylindrical portion 14 provided at an axially inner end portion of the hub body 12a radially outward. . Accordingly, the first inner ring 10 and the second inner ring 11 and the spacer 20 are sandwiched from both sides in the axial direction by the step surface 16 and the caulking portion 15 existing at the outer end in the axial direction of the fitting surface portion 13a. It is fixedly coupled to 12a.
  • a plurality of tapered rollers 3 are held by a cage 17 between the first outer ring raceway 4 and the first inner ring raceway 7 and between the second outer ring raceway 5 and the second inner ring raceway 8, respectively. It is provided so that it can roll freely. Between the inner peripheral surface of the inner end portion in the axial direction of the outer ring 1 and the outer peripheral surface of the end portion on the large diameter side of the first inner ring 10 and the inner peripheral surface of the outer end portion in the axial direction of the outer ring 1 and the end portion on the large diameter side of the second inner ring 11. A combination seal ring 18 is assembled between each outer peripheral surface, and both axial ends of the cylindrical space in which the tapered rollers 3 are installed are closed. A spline hole 19 is provided at the center of the hub body 12 in the radial direction for inserting the tip of the drive shaft into spline engagement.
  • FIG. 3 (A) to 3 (F) show an assembling method of the hub 2a constituting the wheel bearing rolling bearing unit of this example in the order of steps.
  • the second inner ring 11 shown in FIG. 3A is connected to the axially outer end of the fitting surface portion 13a of the hub body 12a as shown in FIG. It fits by press-fitting from the inner side.
  • FIG. 3 (C) around the stepped portion 21 provided in the intermediate portion in the axial direction which is a portion adjacent to the inner side in the axial direction of the second inner ring 11 in the fitting surface portion 13a.
  • the seat 20 is externally fitted with a gap fit.
  • FIG. 3 (E) the first inner ring 10 shown in FIG.
  • 3 (D) is an axial inner end that is a portion adjacent to the inner side in the axial direction of the spacer 20 in the fitting surface portion 13a.
  • the outer portion is fitted with an interference fit.
  • FIG. 3 (F) a portion of the cylindrical portion 14 provided at the axially inner end portion of the hub body 12a that protrudes inward in the axial direction from the first inner ring 10 is plasticized toward the outer diameter side.
  • the caulking portion 15 is formed, and the caulking portion 15 suppresses the large-diameter side end surface (the axial inner end surface) of the first inner ring 10.
  • the relationship with the inclination angle ⁇ 1 of the first inner ring raceway 7 after the outer fitting is ⁇ 1 > ⁇ 1 as shown in the left half of FIG.
  • the relationship with the inclination angle ⁇ 2 of the second inner ring raceway 8 after the outer fitting is ⁇ 2 > ⁇ 2 as shown in FIG.
  • the press-fit allowance ⁇ X 1 (or ⁇ X 2 ) of the first inner ring 10 (or the second inner ring 11) with respect to the fitting surface portion 13a The relationship is specifically obtained by experiment or elastic FEM analysis, and is almost a straight line (proportional relationship) as shown in FIG.
  • the inclination angle of the first inner ring raceway 7 increases as the large diameter side end portion of the first inner ring 10 is elastically deformed in the diameter increasing direction. That is, the relationship between the inclination angle ⁇ 1 of the first inner ring raceway 7 before the caulking portion 15 is formed and the inclination angle ⁇ 1 of the first inner ring raceway 7 after the caulking portion 15 is formed is shown in FIG. As shown in the right half of (B), ⁇ 1 ⁇ 1 .
  • the inclination angle ⁇ 1 of the first inner ring raceway 7 and the second inner ring raceway in the state where the hub 2a is assembled that is, in the state where the caulking portion 15 is formed.
  • ⁇ 1 + ⁇ a ( ⁇ X 1 ) + ⁇ 2 ⁇ b ( ⁇ X 2 ) ⁇ k (4)
  • the first inner ring 10 and the second inner ring 11 are made of a material and in a state (free state) before the first inner ring 10 and the second inner ring 11 are fitted onto the fitting surface portion 13a by press fitting.
  • the specifications such as the shape and dimensions are substantially the same except for inevitable manufacturing errors.
  • the axial inner portion fitted around the first inner ring 10 the large diameter portion outside diameter in the state before fitted by press-fitting the first inner ring 10 is by D 1 22
  • the axially outer portion where the second inner ring 11 is externally fitted is a small diameter portion 23 whose outer diameter dimension is D 2 ( ⁇ D 1 ) before the second inner ring 11 is externally fitted by press-fitting.
  • ⁇ X 2 D 2 ⁇ d 2 of 10 within the range of the expression (6) ( ⁇ X 1 > ⁇ X 2 ).
  • the tilt angle decrease amount ⁇ a ( ⁇ X 1 ) is made larger than the tilt angle decrease amount ⁇ b ( ⁇ X 2 ) ( ⁇ a ( ⁇ X 1 )> ⁇ b ( ⁇ X 2 )), and the tilt angle decrease amount is increased.
  • ⁇ a ( ⁇ X 1), ⁇ b ( ⁇ X 2) the difference between ⁇ a ( ⁇ X 1) - ⁇ b and ([Delta] X 2), and a tilt angle increase amount .delta..theta k, by substantially equal, (5 ) Is satisfied.
  • the first inner ring 10 and the second inner ring 11 are substantially the same in terms of material, shape, dimensions, and the like. For this reason, it is easy to ensure quality and productivity and reduce costs based on the fact that a device for finishing grinding can be used in common for the first inner ring raceway 7 and the second inner ring raceway 8. Further, the spacer 20 is sandwiched between the small-diameter side end surface of the first inner ring 10 and the small-diameter side end surface of the second inner ring 11, and the portion of the fitting surface portion 13a located on the inner diameter side of the spacer 20 is A stepped portion 21 is provided. For this reason, it is possible to prevent the first inner ring 10 or the second inner ring 11 from being externally fitted to the step portion 21 and to prevent adverse effects such as variations in the press-fitting allowance ⁇ X 1 or ⁇ X 2. .
  • the present invention can also be applied to a double-row tapered roller bearing unit for supporting a wheel for a driven wheel or a double-row tapered roller bearing unit other than for supporting a wheel.
  • the present invention can also be applied to a double-row tapered roller bearing unit in which the outer diameter side race ring member rotates in use and the inner diameter side race ring member does not rotate.
  • the inclination angle ⁇ 2 of the track can be made different from each other, and the appropriate range of the inclination angle ⁇ 1 of the first inner ring track and the inclination angle ⁇ 2 of the second inner ring track in the state after the caulking portion is formed.
  • the appropriate range can be different from each other.
  • FIG. 8 shows a second example of the embodiment of the present invention.
  • the radially inner end portion (step surface 16) of the inner side surface of the rotation side flange 9 and the fitting surface portion 13 The radius of curvature of the corner R portion 24a existing in the continuous portion is larger than the radius of curvature of the corner R portion 24 of the hub body 12a according to the first example of the embodiment.
  • the radius of curvature of the R chamfered portion 26a that is located at the continuous portion between the inner peripheral surface of the second inner ring 11a and the large-diameter side end surface that is disposed at a position facing the corner R portion 24a is also the same as that of the embodiment. It is larger than the radius of curvature of the R chamfered portion 26 of the second inner ring 11 in the first example. This prevents the R chamfered portion 26 a from interfering with the corner R portion 24 a and preventing the large-diameter side end surface of the second inner ring 11 a from coming into contact with the stepped surface 16.
  • the radius of curvature of the R chamfered portion 26a of the second inner ring 11a is larger than the radius of curvature of the R chamfered portion 25 existing at the continuous portion between the inner peripheral surface of the first inner ring 10 and the large diameter side end surface. It is getting bigger. That is, at least in this respect, the specifications of the first inner ring 10 and the specifications of the second inner ring 11a are different from each other.
  • the portion of the fitting surface portion 13 that externally fits the first inner ring 10 and the portion that externally fits the second inner ring 11a are mutually connected.
  • the inner diameter dimension d 1 in the state before the outer fitting by the interference fit.
  • the inclination angle reduction amount ⁇ a ( ⁇ X 1 ) of the first inner ring raceway 7 is larger than the inclination angle reduction amount ⁇ b ( ⁇ X 2 ) of the second inner ring raceway 8 ( ⁇ a ( ⁇ X 1 )> ⁇ b ( with [Delta] X 2) and), these inclination angles decrease ⁇ a ( ⁇ X 1), ⁇ b ( ⁇ X 2) the difference between ⁇ a ( ⁇ X 1) and - ⁇ b ( ⁇ X 2), the inclination angle increases the amount .delta..theta By making k substantially equal, the relationship of equation (5) is satisfied.
  • the fitting surface portion 13 is a single cylindrical surface, and a step portion serving as a stress concentration source is provided at the axial intermediate portion of the fitting surface portion 13. Therefore, as compared with the case of the first example of the embodiment, it is easy to design to ensure the strength of the hub main body 12b, and it is easy to ensure the productivity of the hub main body 12b and reduce the cost. Other configurations and operations are the same as those of the first example of the embodiment.
  • the R chamfered portion 26a of the second inner ring 11a can be changed to a C chamfered portion.
  • the axial width dimension and the radial width dimension of the C chamfered portion are set to the curvature radius of the R chamfered portion 25 of the first inner ring 10 (the curvature of the R chamfered portion 26 of the second inner ring 11 of the first example of the embodiment).
  • the radius of curvature of the corner R portion 24a existing at the base portion of the rotation side flange 9 can be increased correspondingly, and the strength of the base portion can be improved.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rolling Contact Bearings (AREA)
  • Mounting Of Bearings Or Others (AREA)
PCT/JP2014/076215 2013-10-04 2014-09-30 複列円すいころ軸受ユニットおよびその製造方法 Ceased WO2015050143A1 (ja)

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CN201480048779.2A CN105518321B (zh) 2013-10-04 2014-09-30 双列圆锥滚子轴承单元及其制造方法
US15/026,800 US9581192B2 (en) 2013-10-04 2014-09-30 Double-row tapered roller bearing unit and method for manufacturing same
EP14850592.8A EP3054184B1 (en) 2013-10-04 2014-09-30 Double-row tapered roller bearing unit and method of manufacturing the bearing unit

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JP2013-209026 2013-10-04
JP2013209026A JP6183127B2 (ja) 2013-10-04 2013-10-04 複列円すいころ軸受ユニット及びその製造方法

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CN115091281A (zh) * 2022-07-14 2022-09-23 浙江晟禧精密机械科技有限公司 一种汽车轮毂轴承小内圈的加工系统及其加工方法
CN119333471A (zh) * 2024-12-20 2025-01-21 人本股份有限公司 非对称免维护轮毂轴承及其加工方法

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JP2019019870A (ja) * 2017-07-14 2019-02-07 株式会社ジェイテクト 車輪用軸受装置及び密封装置
JP7172407B2 (ja) * 2018-10-09 2022-11-16 日本精工株式会社 車輪支持用転がり軸受ユニット
CN117817460B (zh) * 2024-02-21 2024-05-31 肥城市华源机械有限公司 一种轴承配件打磨器

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EP3054184A4 (en) 2017-02-08
CN105518321A (zh) 2016-04-20
EP3054184B1 (en) 2018-11-07
CN105518321B (zh) 2017-10-03
JP2015072057A (ja) 2015-04-16
US9581192B2 (en) 2017-02-28
US20160245334A1 (en) 2016-08-25
JP6183127B2 (ja) 2017-08-23
EP3054184A1 (en) 2016-08-10

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