JP3622458B2 - Rolling bearing unit for wheel support - Google Patents

Rolling bearing unit for wheel support Download PDF

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Publication number
JP3622458B2
JP3622458B2 JP32105597A JP32105597A JP3622458B2 JP 3622458 B2 JP3622458 B2 JP 3622458B2 JP 32105597 A JP32105597 A JP 32105597A JP 32105597 A JP32105597 A JP 32105597A JP 3622458 B2 JP3622458 B2 JP 3622458B2
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Japan
Prior art keywords
ring
caulking
hub
cylindrical
peripheral
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JP32105597A
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Japanese (ja)
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JPH11129703A (en
Inventor
善久 大貫
裕也 宮崎
孝史 桑野
弘幸 沢井
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日本精工株式会社
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Priority to JP23279897 priority Critical
Priority to JP9-232798 priority
Application filed by 日本精工株式会社 filed Critical 日本精工株式会社
Priority to JP32105597A priority patent/JP3622458B2/en
Priority claimed from EP03004632A external-priority patent/EP1314903B1/en
Publication of JPH11129703A publication Critical patent/JPH11129703A/en
Publication of JP3622458B2 publication Critical patent/JP3622458B2/en
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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
    • B60B27/0078—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
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21J—FORGING; HAMMERING; PRESSING METAL; RIVETING; FORGE FURNACES
    • B21J9/00—Forging presses
    • B21J9/02—Special design or construction
    • B21J9/025—Special design or construction with rolling or wobbling dies
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21K—MAKING FORGED OR PRESSED METAL PRODUCTS, e.g. HORSE-SHOES, RIVETS, BOLTS OR WHEELS
    • B21K25/00—Uniting components to form integral members, e.g. turbine wheels and shafts, caulks with inserts, with or without shaping of the components

Description

[0001]
BACKGROUND OF THE INVENTION
The wheel support rolling bearing unit according to the present invention is used for rotatably supporting the wheel of an automobile with respect to a suspension device.
[0002]
[Prior art]
The wheels of the automobile are supported on the suspension device by a rolling bearing unit for supporting the wheels. FIG. 17 shows a first example of a wheel bearing rolling bearing unit that has been widely used in the past. This wheel supporting rolling bearing unit 1 isCorresponding to the inner member according to claim 1,A hub 2, an inner ring 3, an outer ring 4, and a plurality of rolling elements 5 and 5 are provided. Out of these, the outer end of the outer peripheral surface of the hub 2 (outside means the side that is outward in the width direction when assembled to the automobile, and is the left side of each figure excluding FIGS. 4 to 6. The first flange 6 for supporting the wheel is formed on the side closer to the center is called the inner side, and is the right side of each figure except FIGS. A first inner ring raceway 7 is formed on the outer peripheral surface of the intermediate portion of the hub 2, and a step portion 8 having a smaller outer diameter is formed on the inner end portion.
[0003]
The step 8 is fitted with the inner ring 3 having a second inner ring raceway 9 formed on the outer peripheral surface thereof. Further, a male screw portion 10 is formed at the inner end portion of the hub 2, and a tip portion of the male screw portion 10 is projected inward from the inner end surface of the inner ring 3. The inner ring 3 is clamped and fixed to a predetermined position of the hub 2 by sandwiching the inner ring 3 between a nut 11 screwed into the male threaded portion 10 and a stepped surface 12 of the stepped portion 8. . A locking recess 14 is formed on the outer peripheral surface of the distal end portion of the male screw portion 10. Then, after tightening the nut 11 with a predetermined torque, a portion of the nut 11 that matches the locking recess 14 is caulked inward in the diametrical direction, thereby preventing the nut 11 from loosening. Yes.
[0004]
A first outer ring raceway 15 that faces the first inner ring raceway 7 and a second outer ring raceway 16 that faces the second inner ring raceway 9 are formed on the inner peripheral surface of the outer ring 4. . A plurality of rolling elements 5 and 5 are provided between the first and second inner ring raceways 7 and 9 and the first and second outer ring raceways 15 and 16, respectively. In the illustrated example, balls are used as the rolling elements 5 and 5. However, in the case of a rolling bearing unit for automobiles that is heavy in weight, tapered rollers may be used as these rolling elements.
[0005]
In order to assemble the wheel bearing rolling bearing unit 1 as described above to an automobile, the outer ring 4 is fixed to the suspension device by the second flange 17 formed on the outer peripheral surface of the outer ring 4, and the first flange 6 Secure the wheels to the As a result, this wheel can be rotatably supported with respect to the suspension device.
[0006]
US Pat. No. 5,490,732 describes a wheel bearing rolling bearing unit 1 having a structure as shown in FIG. In the case of the second example of this conventional structure, the first inner ring 41 and the second inner ring 3 are fitted on the outer peripheral surface of the hub 18 provided with the first flange 6 on the outer peripheral surface. A caulking portion 19 is formed by bending a portion of the inner end portion of the hub 18 that protrudes inward from the inner end surface of the second inner ring 3 outward in the diametrical direction, and the caulking portion 19 and the hub 18 are formed. The first and second inner rings 41 and 3 are sandwiched between the stepped surface 12a provided at the base of the first flange 6 at the outer peripheral surface of the intermediate portion. That is, the caulking portion 19 is formed by caulking and expanding the cylindrical portion formed at the inner end portion of the hub 18 inwardly from the second inner ring 3 in the diametrical direction. 19, the first and second inner rings 41 and 3 are pressed against the step surface 12a.
[0007]
[Problems to be solved by the invention]
In the case of the first example of the conventional structure shown in FIG. 17, it is necessary to perform the operation of forming the locking recess 14 at the tip of the male screw 10 and the operation of caulking a part of the nut 11 inward in the diameter direction. Become. For this reason, the parts manufacturing work and assembling work of the wheel bearing rolling bearing unit 1 become troublesome, and the cost increases.
[0008]
Further, in the case of the structure of the second example shown in FIG. 18, it is necessary to form a caulking portion 19 on the hub 18 for connecting and fixing the first and second inner rings 41 and 3 to the hub 18. . Therefore, the hub 18 needs to be made of a material capable of forming the caulking portion 19. In the case of the structure of the second example shown in FIG. 18, the hub 18 itself is not provided with an inner ring raceway, and the first and second inner rings 41, 3 externally fitted to the hub 18 are provided on the outer peripheral surfaces. Since the second inner ring raceways 7 and 9 are provided, carbon steel having a carbon content of less than 0.45 wt%, which can easily form the caulking portion 19 as the material of the hub 18, can be used. However, with the processing of the caulking portion 19 as described above, a large load is applied to the second inner ring 3 fitted on the hub 18. For this reason, the second inner ring 3 may be deformed, and the (positive or negative) internal clearance of the rolling bearing unit may deviate from a desired value. When the internal gap deviates from an appropriate value, the rolling fatigue life of the second inner ring raceway 9 formed on the outer peripheral surface of the second inner ring 3 is reduced.
[0009]
Such inconvenience is a structure in which the structure shown in FIG. 17 and the structure shown in FIG. 18 are combined and the hub 2 is provided with the first flange 6 and the first inner ring raceway 7, and the inner ring 3 is connected to the hub. This also occurs in the case of a structure that is coupled and fixed with the caulking portion 19 to 2. Further, when such a structure is adopted, the hub 2 is made of carbon steel having a carbon content of less than 0.45% by weight, like the hub 18 having the conventional structure shown in FIG. The hardness of one inner ring raceway 7 portion cannot be sufficiently increased, and sufficient durability cannot be ensured.
In view of such circumstances, the present invention was invented to provide a rolling bearing unit for supporting a wheel that is low in cost and has sufficient durability.
[0010]
[Means for Solving the Problems]
The wheel support rolling bearing unit of the present invention includes inner members (2b, 2c, 2c, 2c, 1c) each formed with a first flange (6) on the outer peripheral surface of one end and a first inner ring raceway (7) on the outer peripheral surface of the intermediate portion. 51) and a stepped portion (8) having a smaller outer diameter than the portion where the first inner ring raceway (7) is formed, which is formed at the other end of the inner member (2b, 2c, 51). A second inner ring raceway (9) is formed on the outer peripheral surface and the inner ring (3) is externally fitted to the stepped portion (8), and the inner ring is opposed to the first inner ring raceway (7). An outer ring (4) formed with one outer ring raceway (15) and a second outer ring raceway (16) facing the second inner ring raceway (9), and a second flange (17) on the outer peripheral surface, respectively. There are not a plurality of each between the first and second inner ring raceways (7, 9) and the first and second outer ring raceways (15, 16). And provided with rolling elements (5) provided, and at the other end of the inner member (2b, 2c, 51), at least a portion protruding from the inner ring (3) externally fitted to the stepped portion (8) is diametrically The inner ring (3) fitted to the stepped portion (8) is pressed against the stepped surface (12) of the stepped portion (8) by the crimped portions (19, 19a) formed by caulking outward. The inner ring (3) externally fitted to the step (8) is coupled and fixed to the inner member (2b, 2c, 51).
In particular, in the rolling bearing unit for supporting a wheel of the present invention, the inner member (2b, 2c, 51) includes the stepped portion (12) including at least a step surface (12) which is an abutting surface of the inner ring (3). 8) From the one end portion of the first inner ring raceway (7) portionA side surface portion of the base end portion of the first flange (6)Are hardened continuously by quenching treatment, and at least the other end portion of the inner member (2b, 2c, 51) protrudes from the inner ring (3) without being subjected to the quenching treatment. I'm leaving.
[0011]
Preferably, at least at the corners of the stepped portion, the cross-sectional shape is preferably a quarter of a circle on the continuous portion of the cylindrical outer peripheral surface on which the inner ring is fitted and fixed and the stepped surface that abuts the end surface of the inner ring. An arcuate curved surface portion (corner R portion) is formed. And the curvature radius of the cross section of this curved surface part is regulated to the range of 2.5 ± 1.5 mm.
[0012]
[0013]
[0014]
[Action]
The action of rotatably supporting the wheel with respect to the suspension device by the wheel supporting rolling bearing unit of the present invention configured as described above is the same as that of the conventionally known wheel supporting rolling bearing unit.
In particular, in the case of the rolling bearing unit for supporting a wheel according to the present invention, the cost can be reduced while ensuring sufficient durability.
[0015]
[0016]
or,Inner ringIs made of high carbon steel such as bearing steel and hardened to the core,Caulking partEven when a large load is applied to the inner ring as a result of this processing, deformation of the inner ring can be prevented and the (positive or negative) internal gap of the rolling bearing unit can be prevented from deviating from a desired value. That is,Inner memberA portion protruding from the inner ring at the other end of theProvided on this inner memberWhen the caulking part is formed by caulking the cylindrical part,Inner memberIt is necessary to apply a large load directed outward in the diametrical direction to a portion protruding from the inner ring or the cylindrical portion at the other end. As a result, a large surface pressure acts on the inner peripheral surface and the end surface of the inner ring in association with the forming operation of the caulking portion. Therefore, if the hardness of the inner ring is low, the inner ring is deformed by the surface pressure, and the internal clearance of the rolling bearing unit deviates from a desired value. On the other hand, when the inner ring is made of high carbon steel such as bearing steel and is hardened and hardened to the core, the hardness of the inner ring is sufficiently high. The internal gap can be kept at a desired value by preventing deformation. or,secondIt is possible to prevent the diameter of the inner ring raceway from changing and the shape accuracy (roundness, cross-sectional shape) from deteriorating, thereby preventing the rolling fatigue life of the second inner ring raceway from being lowered.
[0017]
still,Inner memberThe carbon content in the carbon steel constituting the steel is 0.45 to 1.10% by weight.Inner memberIf the hardness of the part protruding from the inner ring at the other end of the cylinder or the cylindrical part formed at the other end is Hv 200 to 300 before caulking,firstTo ensure the hardness of the inner ring raceway part and the aboveInner memberIt is possible to sufficiently perform the caulking and expanding operation of the portion protruding from the inner ring at the other end of the inner ring or the cylindrical portion. still,Inner memberIf the carbon content in the carbon steel constituting the steel is 0.45 to 0.60% by weight, annealing may not be performed after forging. In addition, the cooling rate is simply controlled after forging, and the aboveInner memberThe hardness of the part which protruded from the inner ring | wheel at the other end part or the said cylindrical part can be set to Hv200-300. On the contrary,Inner memberWhen the carbon content in the carbon steel constituting is 0.60 to 1.10% by weight, annealing is performed after forging.
[0018]
[0019]
DETAILED DESCRIPTION OF THE INVENTION
1-4,The present inventionThe 1st example of this embodiment is shown. The wheel support rolling bearing unit 1a of this example isIt corresponds to the inner member recited in claim 1.A hub 2b, an inner ring 3, an outer ring 4, and a plurality of rolling elements 5, 5 are provided. Of these, a first flange 6 for supporting the wheel is formed in a portion near the outer end of the outer peripheral surface of the hub 2b. Further, a first inner ring raceway 7 is formed on the outer peripheral surface of the intermediate part of the first inner ring member 2b, and a step part 8 having a smaller outer diameter is formed on the inner end part. Such a hub 2b is integrally formed by forging a carbon steel material having a carbon content of 0.45 to 1.10% by weight.
[0020]
Further, a part of the outer peripheral surface of such a hub 2b shown by an oblique lattice in FIG. 1, that is, the first inner ring raceway 7 part and the base end of the first flange 6 are shown.Part sideThe portion and the base half of the step portion 8 (from the step surface 12 which is the butting surface of the inner ring 3 to a part of the cylindrical outer peripheral surface which is the fitting portion of the inner ring 3) are induction-hardened, Quenching treatment such as carburizing quenching and laser quenching is performed to increase the hardness of the portion to about Hv550 to 900. Of the above quenching processes, the induction quenching process is most preferable because the process cost is low. On the other hand, since the carburizing quenching process needs to perform a charcoal-proof plating process on the part which is not hardened, processing cost increases. Also, laser quenching increases equipment costs.
[0021]
Of the portions subjected to the quenching treatment indicated by the oblique lattice, the first inner ring raceway 7 portion receives a large surface pressure based on the contact with the rolling surface of the rolling element 5, so that it rolls. Harden to ensure fatigue life. Also, the base end of the first flange 6Part sideThe portion is cured to prevent the base end portion from being deformed regardless of the moment load received from the first flange 6 to which the wheel is fixed. Further, of the base half portion of the step portion 8, a part of the outer peripheral surface portion of the step portion 8 is irrespective of the fitting pressure of the inner ring 3 and the radial load received by the inner ring 3 from the plurality of rolling elements 5. In order to prevent the outer peripheral surface of the step portion 8 from being deformed, and to prevent fretting wear from occurring on the outer peripheral surface of the step portion 8 which is a fitting portion with the inner ring 3. Harden. Further, the stepped surface 12 portion of the stepped portion 8 prevents the stepped surface 12 from being deformed regardless of the axial load applied to the inner ring 3 by the caulking operation described later. The stepped surface 12 that is a contact surface with the outer end surface is cured to prevent fretting wear from occurring. Further, the corner R portion which is a continuous portion between the outer peripheral surface of the step portion 8 and the step surface 12 is cured in order to prevent deformation due to stress concentration. In addition, Preferably, the curvature radius of the cross section of this corner R part is regulated in the range of 2.5 ± 1.5 mm. If the radius of curvature of this portion is less than 1 mm, there is a possibility that damage such as cracks may occur due to stress concentration. On the other hand, if the radius of curvature of the portion exceeds 4 mm, it easily interferes with the inner peripheral edge of the end of the inner ring 3, and the wheel bearing rolling bearing unit becomes difficult.
[0022]
Note that the axial position (point a in FIG. 1) of the inner end of the hardened hardened layer indicated by the oblique lattice is the axial position of the center of the plurality of rolling elements 5 arranged around the inner ring 3 (see FIG. 1). The position in the axial direction of the base end of the caulking portion 19 described later (the portion where the outer diameter of the caulking portion begins to become larger than the outer diameter of the step portion 8) (in FIG. 1). It is assumed that the outer side (the left side in FIG. 1) from the point (1). The reason for restricting the inner end position of the hardened hardening layer in this way is that the surface area of the hardened hardened layer present on the outer peripheral surface portion of the stepped portion 8 is made as wide as possible and the processing of the caulking portion 19 is facilitated. In addition, this is to prevent damage such as cracks from occurring in the caulking portion 19 based on the presence of the hardened and hardened layer. In addition, although the above-mentioned quench hardening layer may be discontinuously formed for every required part, like this example shown in FIG. 1, adjacent quench hardening layers are continuously connected. If formed, the strength and durability of the hub 2b can be improved.
[0023]
A cylindrical portion 20 for forming a caulking portion 19 for fixing the inner ring 3 is formed at the inner end portion of the hub 2b. In the example shown in the drawing, the thickness of the cylindrical portion 20 becomes smaller toward the leading edge in a state before the cylindrical portion 20 is caulked outward in the diameter direction shown in FIG. For this reason, in the case of the illustrated example, a tapered hole 21 is formed on the inner end surface of the hub 2b. The inner ring 3 is made of a high carbon steel such as a high carbon chromium bearing steel such as SUJ2, and is hardened and hardened to the core.
[0024]
The carbon content in the carbon steel constituting the hub 2b is 0.45 to 1.10% by weight as described above, and the hardness of the cylindrical portion 20 formed at least on the other end of the hub 2b is as follows. Before the caulking process shown in FIG. By satisfying such a condition, the required hardness (Hv 550 to 900) is ensured for the first inner ring raceway 7 portion, and the work of caulking and expanding the cylindrical portion 20 can be sufficiently performed. That is, when the cylindrical portion 20 is caulked and spread into the caulking portion 19, if the hardness of the cylindrical portion 20 exceeds Hv300, the formed caulking portion 19 may be cracked or insufficiently caulked. As a result, the caulking portion 19 and the inner ring 3 are not in close contact with each other, and the fastening force of the inner ring 3 to the hub 2b is reduced. In addition, the load required to form the caulking portion 19 becomes excessive, and it becomes easy to cause damage such as indentation on each raceway surface and the rolling elements 5 and 5 along with caulking work, and the dimensional accuracy of each portion deteriorates. Cause the possibility of Further, machining of the hub 2b becomes difficult. That is, the machining time becomes longer and the tool life is reduced, resulting in an increase in cost.
[0025]
If the carbon content in the carbon steel constituting the hub 2b exceeds 1.10% by weight, it becomes difficult to suppress the hardness of the cylindrical portion 20 to Hv300 or less. Therefore, in the carbon steel constituting the hub 2b, The upper limit of the carbon content was 1.10% by weight. On the other hand, if the hardness of the cylindrical portion 20 does not reach Hv200, the hardness of the caulking portion 19 formed by caulking the cylindrical portion 20 cannot be secured, and the fastening force of the inner ring 3 by the caulking portion 19 is also increased. Run short. If the carbon content in the carbon steel constituting the hub 2b does not reach 0.45% by weight, the hardness (Hv 550 to 900) required for the first inner ring raceway portion 7 cannot be secured, and this first Since the life of one inner ring raceway portion 7 is reduced, the lower limit of the carbon content in the carbon steel constituting the hub 2b is set to 0.45% by weight.
[0026]
The hub 2b is manufactured by forging a carbon steel having a carbon content of 0.45 to 1.10% by weight for the reasons described above. In the case of 0.60% by weight, it is not necessary to perform an annealing process after forging. That is, by simply controlling the cooling rate after forging, it is possible to keep at least the hardness of the cylindrical portion 20 in the range of Hv 200 to 300. Therefore, after the hub 2b is formed by forging, the work of processing the cylindrical portion 20 into the caulking portion 19 can be performed without performing an annealing process. The wheel-supporting rolling bearing having the caulking portion 19 is provided. Units can be built at low cost.
[0027]
On the other hand, when the carbon content in the carbon steel constituting the hub 2b is 0.60 to 1.10% by weight, the hub 2b needs to be annealed after being made by forging. is there. That is, even when the carbon content in the carbon steel is 0.60 to 1.10% by weight, the hardness of the cylindrical portion 20 is set to about Hv 200 to 300 by controlling the cooling rate after forging. Is possible. However, since the cooling rate needs to be considerably small (slow), it takes a long time and special equipment is also required. For this reason, it is preferable to perform annealing rather than controlling the cooling rate in terms of securing production efficiency and simplifying production equipment. Moreover, the one-time annealing improves the hardenability when quenching the necessary portion of the hub 2b. Therefore, after the hub 2b is made by forging, annealing is performed so that at least the hardness of the cylindrical portion 20 is about Hv 200 to 300. In the case where the carbon content in the carbon steel constituting the hub 2b is 0.60 to 1.10% by weight, the cooling rate after forging is not slowed down and the annealing treatment is not performed. The same problem as described above occurs when the content in the carbon steel exceeds 1.10% by weight. By the way, when the content in the carbon steel exceeds 1.10% by weight, the hardness of the cylindrical portion 20 is reduced to Hv300 or less even when the cooling rate after forging is slowed or annealing is performed. It becomes difficult to suppress.
[0028]
In order to squeeze the tip of the cylindrical portion 20 as described above in order to fix the inner ring 3 to the inner end of the hub 2b, the hub 2b is fixed so that it does not move in the axial direction. As shown in FIG. 2, the pressing die 22 is strongly pressed against the tip of the cylindrical portion 20. A frustoconical convex portion 23 that can be pushed into the inside of the cylindrical portion 20 is formed at the center of the front end surface (left end surface in FIG. 2) of the pressing die 22, and a circular arc section is formed around the convex portion 23. The concave portion 24 is formed so as to surround the entire circumference of the convex portion 23. The cross-sectional shape of the recess 24 and the outer diameter Rtwenty fourAnd depth Dtwenty fourWhen the cylindrical portion 20 is plastically deformed to form the caulking portion 19, a predetermined shape and size are applied while applying a compressive force to the metal (carbon steel) constituting the cylindrical portion 20. It restrict | limits so that the said crimping part 19 to have may be formed. That is, the cross-sectional shape of the concave portion 24 is such that the cross-sectional shape of the caulking portion 19 obtained by plastically deforming the distal end portion of the cylindrical portion 20 by the concave portion 24 has a thickness dimension as it goes from the proximal end portion toward the distal end portion. The composite curved surface has a curvature radius that becomes smaller toward the outer diameter side, so that the thickness dimension is abruptly reduced especially at the tip portion so as to gradually become smaller. Outer diameter Rtwenty fourIs the outer diameter R of the caulking portion 19 to be formed19Or the outer diameter R of the caulking portion 1919Slightly less than (Rtwenty four≦ R19)I have to. Furthermore, depth Dtwenty fourIn the state where the caulking portion 19 is formed by sandwiching the tip end portion of the cylindrical portion 20 between the inner peripheral surface and the inner end surface of the inner end portion of the inner ring 3, the tip end surface of the pressing die 22 and the inner ring 3 are formed. The gap 25 is restricted so as to remain between the inner end face and the inner end face.
[0029]
If the pressing die 22 having the convex portion 23 and the concave portion 24 having the shape and dimensions as described above is pressed against the tip portion of the cylindrical portion 20, the tip portion of the cylindrical portion 20 is caulked outward in the diametrical direction, The caulking portion 19 can be formed. The inner ring 3 can be clamped between the caulking portion 19 and the stepped surface 12 of the stepped portion 8 formed at the inner end of the hub 2b, and the inner ring 3 can be fixed to the hub 2b. In the case of the illustrated example, in the final stage of forming the caulking portion 19 by plastically deforming the inner end surface of the cylindrical portion 20, the inner surface of the concave portion 24 extends from the inner diameter surface of the caulking portion 19 to the outer diameter surface. Inward compression force acts. Therefore, it is possible to effectively prevent the occurrence of damage such as cracks on the outer peripheral edge of the caulking portion 19. Further, a curved surface portion 26 having an arcuate cross section is formed in the inner end opening peripheral edge portion of the inner ring 3 where the outer diameter surface of the base end portion of the caulking portion 19 abuts. Therefore, the radius of curvature of the base end portion of the caulking portion 19 is not reduced, and it is difficult to apply an excessive stress to the base end portion.
[0030]
As described above, in the case of the rolling bearing unit for supporting a wheel of the present invention, the hub 2b is made of carbon steel having a carbon content of 0.45 to 1.10% by weight, and the first inner ring raceway 7 is formed. Since the portion is hardened by the quenching process, the rolling fatigue life of the surface of the first inner ring raceway 7 can be sufficiently ensured regardless of the load repeatedly applied from the rolling elements 5 and 5. On the other hand, the cylindrical portion 20 is left raw without being quenched. For this reason, the force required to plastically deform the cylindrical portion 20 increases suddenly, or when the cylindrical portion 20 is plastically deformed, damage such as cracks is likely to occur in the cylindrical portion 20. Absent. Therefore, even when the hardness of the first inner ring raceway 7 portion is increased to secure the rolling fatigue life of the first inner ring raceway portion 7 as described above, the caulking for joining the hub 2b and the inner ring 3 is performed. The processing of the part 19 is not troublesome. Moreover, since the inner ring 3 is made of high carbon steel such as bearing steel and is hardened and hardened to the core, even if a large load is applied to the inner ring 3 due to the processing of the caulking portion 19, the inner ring 3 3 can be prevented and the internal clearance of the rolling bearing unit can be prevented from deviating from a desired value. Further, the diameter of the second inner ring raceway 9 formed on the outer peripheral surface of the inner ring 3 can be prevented from changing or the accuracy can be prevented, so that the rolling fatigue life of the second inner ring raceway 9 can be prevented from being lowered. .
[0031]
Furthermore, in the case of the illustrated example, since the thickness of the cylindrical portion 20 for forming the caulking portion 19 is made smaller toward the tip edge, the hub 2b has a carbon content of 0.45 to 1. Even when made of 10% by weight carbon steel, the force required to form the caulking portion 19 by plastically deforming the tip portion of the cylindrical portion 20 with the pressing die 22 as described above is increased. There is no. For this reason, damage such as cracks occurs in the caulking portion 19 due to the caulking work, or the diameter of the inner ring 3 affects the durability such as preload and rolling fatigue life of the inner ring 3 fixed by the caulking portion 19. It is possible to more reliably prevent the action of a force that changes so much that it exerts. In particular, in the illustrated example, compressive stress is applied to the distal end portion of the caulking portion 19 and the radius of curvature of the proximal end portion of the caulking portion 19 is increased, so that the caulking portion 19 can be more effectively prevented from being damaged. I can plan. The outer end opening of the space 27 provided with the rolling elements 5 and 5 is closed by the seal ring 28 and the inner end opening is closed by the lid 29, so that dust enters the space 27, or Lubricating oil is prevented from leaking from the space.
[0032]
Next, the appropriate values of the dimensions of each part in the case of realizing the structure as shown in FIGS. Note that this value is the inner diameter r of the inner ring 3 to be fixed to the hub 2b in the case of a wheel bearing rolling bearing unit incorporated in a general passenger car.Three Is about 20-60mm, and length dimension LThree Is about 15 to 40 mm, the material of the hub 2b is carbon steel with a carbon content of 0.45 to 1.10% by weight, and the material of the inner ring 3 is high carbon chromium bearing steel such as SUJ2. It is about the case.
First, the thickness dimension t of the tip of the cylindrical portion 20 before the caulking portion 19 is processed.20Is preferably in the range of 1.5 to 5 mm. Also, the thickness T of the base end portion of the cylindrical portion 2020Is preferably in the range of 5 to 10 mm. Thickness dimension t of the tip and base ends20And T20If this is regulated within this range, it is possible to prevent the caulking portion 19 from being damaged, such as a crack, and to secure the support rigidity of the inner ring 3 by the caulking portion 19.
That is, it is possible to effectively prevent the occurrence of the damage by thinning the tip portion of the cylindrical portion 20 where the amount of deformation increases and making the tip portion easily plastically deformable. Also, the base end portion of the cylindrical portion 20 that is used to hold the inner ring 3 toward the stepped surface 12 can be made thick so that the support strength of the inner ring 3 can be sufficiently secured.
[0033]
Also, the length L of the cylindrical portion 2020Is preferably about 8 to 20 mm. This length L20Is too small (L20<8 mm), the above-mentioned caulking portion 19 cannot be formed sufficiently, or damage such as a crack is likely to occur in a part of the caulking portion 19 at the time of formation. In contrast, the length dimension L20Is too large (L20> 20 mm), the length of the hollow portion existing at the inner end of the hub 2b becomes too long, and the strength of the hub 2b is reduced. Based on the radial load applied to the inner ring 3, the inner diameter of the hub 2b is reduced. The end portion is easily deformed. The operation of plastically deforming the cylindrical portion 20 restricted to the above dimensions to form the caulking portion 19 is preferably performed by forging or swing pressing.
[0034]
Further, the line of action of the load applied to the inner ring 3 from the plurality of rolling elements 5 (corresponding to the chain line α in FIG. 2 representing the contact angle of the rolling elements 5) is the inner peripheral surface of the inner ring 3 and the step portion 8. So that it does not pass through the crimping part 19. The reason for regulating in this way is to prevent the caulking portion 19 from being deformed or damaged by preventing the load from acting as a force that directly deforms the caulking portion 19 inward in the diameter direction.
[0035]
Next, the cross-sectional area S of the inner ring 3 that is closer to the outer side than the second inner ring raceway 9 (the AA line portion in FIG. 3).Three And the cross-sectional area S of the hub 2b at that portion.2bS in relation toThree <S2bAnd more preferably SThree ≦ 0.94S2bAnd The reason for restricting the cross-sectional areas of these parts in this way is to ensure the support strength of the inner ring 3 with respect to the hub 2b.
That is, the force (axial force) for pressing the inner ring 3 in the axial direction and preventing the rotation of the inner ring 3 in the state where the inner ring 3 is sandwiched between the caulking portion 19 and the stepped surface 12 is as described above. It is determined by the difference in strain amount in the axial direction of the hub 2b and the inner ring 3. That is, during the caulking process, the elastic deformation amount of the inner ring 3 is larger than the elastic deformation amount of the hub 2b. After the caulking process, the inner ring 3 and the hub 2b are elastically restored, and an axial force (axial force) is applied to the inner ring 3. Since the material constituting the inner ring 3 and the material constituting the hub 2b have substantially the same elastic modulus, as described above, SThree <S2bIf so, the amount of elastic deformation during caulking is larger in the inner ring 3 than in the hub 2b. Therefore, if the cross-sectional area of each part is regulated in this way, it is possible to effectively prevent the occurrence of so-called creep, in which the inner ring 3 continues to be applied to the inner ring 3 and the inner ring 3 rotates with respect to the hub 2b.
[0036]
Next, when the plurality of rolling elements 5 arranged around the inner ring 3 are balls, the distance L from the center O of the rolling element 5 to the inner end face of the inner ring 3 is as follows.O3Is the diameter D of the rolling element 5Five 0.75 times or more (LO3≧ 0.75DFive ) Is preferable. This distance LO3This is because the diameter of the second inner ring raceway 9 where the rolling contact surface of the rolling element 5 comes into contact with the caulking portion 19 is increased or the accuracy ( This is to prevent deterioration in roundness and cross-sectional shape. That is, this distance LO3Is too small, the base end portion of the caulking portion 19 is present on the inner diameter side portion of the second inner ring raceway 9, and the second inner ring raceway 9 is formed along with the forming operation of the caulking portion 19. There is a possibility that the diameter of the portion becomes so large that it cannot be ignored or the accuracy is deteriorated.
[0037]
Next, the outer diameter R of the caulking portion 19 described above.19Is the inner diameter r of the inner ring 3Three And the outer diameter R of the outer ring portion of the inner ring 3 that is out of the second inner ring raceway 9Three Therefore, it is preferable to regulate to the following range.
rThree +0.7 (RThree -RThree ) ≦ R19≦ rThree +1.3 (RThree -RThree )
Outer diameter R of the caulking portion 1919By limiting the range to this range, it is possible to prevent the caulking portion 19 from being damaged such as cracking and to secure the support strength of the inner ring 3 with respect to the hub 2b.
Outer diameter R19Is shifted in a direction larger than the above range, the damage is likely to occur. Conversely, the outer diameter R19Is shifted in a direction smaller than the above range, it is difficult to ensure the support strength.
[0038]
Further, the cross-sectional shape of the curved surface portion 26 is preferably regulated as follows. First, an inclined surface portion is provided near the starting point of the curved surface portion 26, and the angle θ at which the inclined surface portion is inclined with respect to the central axis of the inner ring 3.26Is 10 to 45 degrees. Further, the radius of curvature r of the portion where the inner peripheral surface of the inner ring 3 and the inclined surface portion are continuous is provided.26Is 2 to 8 mm. Further, the radius of curvature R of the portion where the inclined surface portion and the end surface of the inner ring 3 are continuous is provided.26Is 3 to 10 mm.
By restricting the cross-sectional shape of the curved surface portion 26 in this way, excessive stress is generated at the proximal end portion of the caulking portion 19 when the cylindrical portion 20 is plastically deformed to form the caulking portion 19. This prevents the damage to the base end portion.
[0039]
Moreover, it is preferable to perform the operation | work which plastically deforms the said cylindrical part 20 (caulking and expanding) and forms the said crimping part 19 using the rocking press apparatus 43 as shown in FIGS. The swing press device 43 includes a pressing die 22, a holding jig 44, and a holder 45. Of these, the holder 45 is formed in a bottomed cylindrical shape with a metal material having a sufficiently large rigidity, and the upper surface of the bottom portion 46 has a shape that allows the outer end portion of the hub 2b to be abutted without being rattled. . The holding jig 44 is formed as a whole by combining jig elements 47 and 47 each having a semicircular arc shape, and includes a cylindrical holding section 48 at the inner peripheral edge. . The outer peripheral edges of the jig elements 47 and 47 and the inner peripheral surface of the upper end opening of the holder 45 are tapered surfaces that are inclined in a direction in which the diameter increases toward the upper side. In the process of coupling and fixing the jig elements 47, 47 to the mounting portion 51 provided on the upper inner peripheral surface of the holder 45 with bolts (not shown) inserted through the through holes 49, 49, 47 is displaced inward in the diameter direction based on the engagement between the tapered surfaces. Then, the inner peripheral surface of the holding portion 48 of the holding jig 44 constituted by these jig elements 47 and 47 is strongly pressed against the outer peripheral surface of the inner ring 3. Due to such a configuration, the holding jig 44 can hold down the inner ring 3 sufficiently strongly even if the outer diameter of the inner ring 3 is deviated within the range of dimensional tolerance (50 μm).
[0040]
When the caulking portion 19 is formed by caulking the cylindrical portion 20, the pressing die 22 is swung and rotated while pressing the hub 2 b upward via the holder 45. That is, in a state where the central axis of the pressing die 22 and the central axis of the hub 2b are inclined by an angle θ, the pressing die 22 is rotated around the central axis of the hub 2b. When the caulking portion 19 is formed by such a rocking press, a part in the circumferential direction of the pressing die 22 presses the cylindrical portion 20, and the machining operation on the caulking portion 19 is a partial process. And continuously in the circumferential direction. For this reason, compared with the case where the said crimping part 19 is formed by general forging, the load added to the said cylindrical part 20 at the time of a process can be made small. The holding jig 44 prevents the hub 2b from swinging when the caulking portion 19 is processed by the pressing die 22, and the size and shape accuracy of each portion of the constituent elements such as the raceway surfaces and the rolling elements 5, 5 are deteriorated. To prevent it.
[0041]
The inclination angle (swinging angle) θ, the swinging rotational speed, the pressing load and the like of the pressing die 22 are determined in design according to the size and the like of the wheel support rolling bearing unit in which the caulking portion 19 is to be processed. However, for example, in the case of a general rolling bearing unit for supporting a wheel for a passenger car having the cylindrical portion 20 having the shape and size as described above, the following range is set. First, the inclination angle θ is preferably about 0.5 to 5.0 degrees. When the inclination angle θ is less than 0.5 degrees, the load required to plastically deform the cylindrical portion 20 to form the caulking portion 19 increases, and the dimensional accuracy and shape accuracy of each raceway surface and rolling element are increased. Deteriorates or indentation or the like is likely to occur. On the other hand, when the inclination angle θ exceeds 5 degrees, the hub 2b is shaken in the diameter direction when the cylindrical portion 20 is plastically deformed to form the caulking portion 19, and the hub 2b is swung by the restraining jig 44. 2b cannot be held sufficiently, and the dimensional accuracy and shape accuracy of each raceway surface and rolling element are deteriorated, and indentations and the like are liable to occur.
[0042]
In addition, the swinging rotation speed is 100 to 500 r.p.m. (min-1 ) Degree is preferred. When this rocking rotation speed is less than 100 r.p.m., the machining time becomes long. On the contrary, if it exceeds 500 r.p.m., the caulking portion 19 obtained is hardened due to work hardening, and damage such as cracking is likely to occur.
Further, the pressing load is preferably about 15 to 50 t. When the pressing load is less than 15 t, the cylindrical portion 20 cannot be sufficiently plastically deformed, and a good caulking portion 19 cannot be obtained, so that the coupling strength of the inner ring 3 to the hub 2b is insufficient. . On the other hand, when the pressing load exceeds 50 t, the dimensional accuracy and shape accuracy of each raceway surface and rolling element are deteriorated, and indentations and the like are liable to occur.
In addition, the effect | action and effect by forming the crimping part 19 with the above oscillating press apparatuses 43 are acquired irrespective of the kind of metal material which comprises the said hub 2b and the inner ring | wheel 3. FIG.
[0043]
Next, FIG.The present invention2 shows a second example of the embodiment. In this example, the present invention is applied to a wheel bearing rolling bearing unit with a rotation speed detection device for detecting the rotation speed of a wheel. For this reason, in the case of this example, a step portion 31 having a smaller diameter than the shoulder portion 30 of the inner ring 3 and projecting inward from the shoulder portion 30 is formed at the inner end portion of the inner ring 3. And the base end part (left end part of FIG. 7) of the tone wheel 32 which comprises a rotational speed detection apparatus is externally fixed to this shoulder part 30. As shown in FIG. A part of the tone wheel 32 abuts on the periphery of the base end portion (left end portion in FIG. 7) of the step portion 31 on the inner end face of the shoulder portion 30, and extends in the axial direction (left and right direction in FIG. 7). Positioning is planned. A synthetic resin or metal cover 33 is fitted and fixed to the inner end opening of the outer ring 4, and the sensor 34 embedded in the cover 33 is opposed to the tone wheel 32 to detect the rotational speed. Configure the device.
[0044]
In this example, the step portion 31 is formed at the inner end portion of the inner ring 3 as described above, and the step portion 31 is suppressed by the caulking portion 19 formed at the inner end portion of the hub 2b. The axial distance between the caulking portion 19 and the second inner ring raceway 9 formed on the outer peripheral surface of the inner ring 3 is increased by the amount of such stepped portion 31 formed. As a result, the dimensional change of the second inner ring raceway 9 due to the formation of the caulking portion 19 can be further suppressed. Furthermore, not only the second inner ring raceway 9 but also the shoulder 30 can be prevented from increasing in outer diameter. Therefore, when a seal ring or tone wheel is externally fitted to the shoulder portion 30 or a seal lip is slidably brought into contact with the outer peripheral surface of the shoulder portion 30, the function of the seal ring or tone wheel is prevented from being impaired. it can. In the case of this example as well, when the plurality of rolling elements 5 arranged around the inner ring 3 are balls, the distance L from the center O of the rolling element 5 to the inner end face of the second inner ring member 3.O3Is the diameter D of the rolling element 5Five 0.75 times or more (LO3≧ 0.75DFive ) Is preferable. Since the configuration and operation of the other parts are the same as in the case of the first example described above, the same parts are denoted by the same reference numerals, and redundant description is omitted. In the case of this example (and will be described below)Examples 3 to 5 and Reference Examples 1 to 6In the case of ()), the hardened and hardened portion of the hub is represented by a diagonal lattice.
[0045]
Next, FIG.The present invention3 shows a third example of the embodiment. In the first example and the second example described above, the hub 2b is rotatably provided inside the non-rotating outer ring 4, whereas in this example, the outer ring 4 side rotates. LikeA shaft member 51 corresponding to the inner member described in claim 1 and the inner ring 3 are arranged on the inner diameter side of the outer ring 4.ing. That is, in the case of this example, the outer ring 4 rotates together with the wheels. Since the rotation side and the stationary side are inward and outward in the diametrical direction, and the configuration and action other than that in which the inner and outer sides in the axial direction are partially reversed are the same as in the case of the first example described above. Equivalent parts are denoted by the same reference numerals, and redundant description is omitted.
[0046]
Next, FIG.The present invention4 shows a fourth example of the embodiment. In both the first and second examples described above and the third example described above, wheel support rolling for rotatably supporting driven wheels (front wheels of FR and RR vehicles, rear wheels of FF vehicles) that are not rotationally driven. Whereas the present invention is applied to the bearing unit, in this example, the drive wheels (the rear wheels of the FR and RR vehicles, the front wheels of the FF vehicle, and all the wheels of the 4WD vehicle) are supported rotatably. The present invention is applied to a rolling bearing unit for supporting a wheel.
[0047]
For this reason, in this example,Corresponds to the inner member,The hub 2c is formed in a cylindrical shape, and a female spline portion 35 is formed on the inner peripheral surface of the hub 2c. A drive shaft 37 attached to the constant velocity joint 36 and having a male spline portion formed on the outer peripheral surface is inserted into the female spline portion 35. On the other hand, the inner ring 3 is fitted on the step 8 formed on the outer peripheral surface of the inner end of the hub 2c, and a step 38 is formed near the inner end surface of the inner ring 3. The caulking portion 19 formed at the inner end portion of the hub 2c is caulked toward the step portion 38. In this state, the caulking portion 19 does not protrude inward from the inner end surface of the inner ring 3. Accordingly, the outer end surface of the main body portion 39 of the constant velocity joint 36 is in contact with the inner end surface of the inner ring 3. In this manner, with the outer end surface of the main body portion 39 in contact with the inner end surface of the inner ring 3, the nut 40 is screwed into a portion protruding from the outer end surface of the hub 2c at the distal end portion of the drive shaft 37. By further tightening, the inner ring 3 and the hub 2c are firmly held in the axial direction.
[0048]
In the structure of this example, when the plurality of rolling elements 5 arranged around the inner ring 3 are balls, it is preferable that the distance L from the center O of the rolling element 5 to the step surface of the step portion 38 is preferable.38, The diameter D of the rolling element 5Five 0.75 times or more (see Fig. 3)38≧ 0.75DFive ). Since the configuration and operation of the other parts are the same as in the case of the first example described above, the same parts are denoted by the same reference numerals, and redundant description is omitted.
[0049]
In the case of this example, since a hollow cylindrical member is used as the hub 2c, it may be difficult to make the cross-sectional area of the hub 2c larger than the cross-sectional area of the inner ring 3. However, in the structure of this example, since the inner ring 3 is strongly pressed against the stepped surface 12 of the hub 2c by the axial force based on the tightening of the nut 38 in the used state, the caulking portion is pressed from the inner ring 3 to the caulking portion 19. The force acting in the direction of loosening 19 is limited. Therefore, even if the relationship of the cross-sectional areas cannot be satisfied, the durability of the caulking portion 19 is not impaired.
[0050]
Next, FIG.The present inventionThe 5th example of embodiment of this is shown. In the case of this example, the caulking portion 19a formed at the inner end portion of the hub 2c is caulked toward the inner end surface of the inner ring 3, and the caulking portion 19a is axially inward from the inner end surface of the inner ring 3. Protruding. Further, an annular flat surface 42 is formed on the inner surface side of the caulking portion 19a, and the flat surface 42 is brought into contact with the outer end surface of the main body portion 39 of the constant velocity joint 36. The caulking portion 19a is raw carbon steel, but the flat surface 42 makes contact with the outer end surface of the main body portion 39 in a wide area. Therefore, the surface pressure applied to the contact portion even when the nut 40 is tightened. Is never extremely high. Therefore, it is possible to prevent the caulking portion 19a from sagging regardless of the use over a long period of time, and the caulking portion 19a may cause the nut 40 to loosen and the rolling elements 5 and 5 to rattle. Can be effectively prevented. Since the configuration and operation of the other parts are the same as in the case of the above-described fourth example, the same parts are denoted by the same reference numerals, and redundant description is omitted.
[0051]
Next, FIGS. 11 to 13 show the present invention.Reference examples of the present invention that are not includedThe first1-3An exampleYes.Mentioned aboveEmbodiment of the present inventionIn the case of the first to fifth examples, the quench hardening layer applied to the member forming the caulking portion 19 was continuously formed, whereasFirst to third examplesIn the case of an example, the said hardening hardening layer is formed discontinuously for every part especially required. That is, as shown in FIG.First reference exampleIn the case of the example, only the first inner ring raceway portion 7 and the step surface 12 and the corner R portion existing on the inner peripheral portion of the step surface 12 are shown in FIG.Second reference exampleIn the case of the example, only the first inner ring raceway 7 portion, the step surface 12, the corner R portion, and the base half outer peripheral surface of the step portion 8 are shown in FIG.Third reference exampleIn the case of the example, only the first inner ring raceway portion 7 and the base end portion of the first flange 6 and the stepped surface 12 and the outer peripheral surface of the base half portion of the corner R portion and the stepped portion 8 are respectively quenched and hardened. Forming a layer. However, as described above, the quenched and hardened layer is shown in FIGS. 1, 7, 8, 9, and 10, rather than being discontinuously formed at each necessary portion as described above.Embodiment of the present inventionAs in the first to fifth examples, it is possible to improve the strength and durability of the member to which the quenching and hardening layer is applied by continuously forming the adjacent hardening and hardening layers. The configuration and operation of the other parts are described above.Embodiment of the present inventionThis is the same as in the first example.
[0052]
Next, FIG.A fourth reference example of the present invention, which also departs from the present invention.An example is shown. BookreferenceThe wheel support rolling bearing unit of the example is formed with the first and second inner ring raceways 7 and 9 on the outer peripheral surfaces of the first and second inner rings 41 and 3 that are externally fitted to the step portion 8a of the hub 2d. doing. Each of the first and second inner rings 41 and 3 is made of a high carbon steel such as a high carbon chrome bearing steel such as SUJ2, and is hardened and hardened to the core. Further, the first and second inner rings 41 and 3 are formed at the base portion of the first flange 6 and the caulking portion 19 formed at the inner end portion of the hub 2d in a state of being fitted on the step portion 8a. It is sandwiched between the step surface 12.
[0053]
BookreferenceIn the example, the hub 2d can be made of carbon steel having a carbon content of less than 0.45% by weight. 14, the base end portion of the first flange 6, the base end portion of the step portion 8a including the step surface 12, and the outer peripheral surface of the step portion 8a. A portion other than the end portion is hardened to increase the hardness of the portion. However, at least the cylindrical portion 20 of the hub 2d, which is the portion that forms the caulking portion 19, is left without being subjected to the quenching process. The reason why the above-mentioned portions of the hub 2d are quenched and the reason for restricting the axial position (point a in FIG. 14) of the inner end of the quenched and hardened layer indicated by the oblique lattice is described above.Embodiment of the present inventionThis is the same as in the first example.
[0054]
Book configured as abovereferenceIn the case of the wheel support rolling bearing unit of the example, since the inner ring raceway is not provided in the hub 2d itself, it is easy to form the caulking portion 19 as the material of the hub 2d, and the carbon content is less than 0.45% by weight. Carbon steel can be used. However, the hub 2d has a hardened hardened layer formed in the portion shown by the oblique grid in FIG. Therefore, the strength and durability of the hub 2d can be ensured by preventing fretting wear from occurring in the portion where the hardened layer is formed or deformation of the portion where the hardened layer is formed. it can. On the other hand, since at least the cylindrical portion 20 provided in the hub 2d is not subjected to the quenching process and remains raw, the caulking portion for joining the hub 2d and the first and second inner rings 41, 3 is used. The processing of 19 is not troublesome and the caulking portion 19 is not damaged.
[0055]
Further, the second inner ring 3 fitted on the stepped portion 8a is made of high carbon steel such as bearing steel, and is hardened and hardened to the core. For this reason,Embodiment of the present inventionAs in the case of the inner ring 3 of the first example, even when a large load is applied to the second inner ring 3 due to the processing of the caulking portion 19 formed on the hub 2d, the deformation of the second inner ring 3 is prevented. Thus, the internal clearance of the rolling bearing unit can be prevented from deviating from a desired value. Further, the diameter of the second inner ring raceway 9 formed on the outer peripheral surface of the second inner ring 3 is prevented from changing or the accuracy is deteriorated, and the rolling fatigue life of the second inner ring raceway 9 is reduced. It can be prevented. BookreferenceIn the example, the hub 2d may be made of carbon steel having a carbon content of 0.45 to 1.10% by weight. In this case, the strength and durability of the hub 2d are further improved. The configuration and operation of the other parts are described above.Embodiment of the present inventionThis is the same as in the first example.
[0056]
BookreferenceExamples (and laterReference examples 5-6In the case of Example), the carbon content in the carbon steel constituting the hub 2d is restricted to a range of 0.20 to 1.10% by weight, and at least the hardness of the cylindrical portion 20 is Hv200 to 300. The hub 2d is manufactured by forging a carbon steel that satisfies such conditions. Further, when the carbon content in the carbon steel constituting the hub 2d is in the range of 0.20 to 0.60% by weight, after forging and before caulking the cylindrical portion 20, At least the cylindrical portion 20 is not annealed. On the other hand, when the carbon content in the carbon steel constituting the hub 2d is in the range of 0.60 to 1.10% by weight, after forging and before caulking and expanding the cylindrical portion 20 At least the cylindrical portion 20 is annealed. Regarding the hardness of the hub 2d and the necessity of annealing after the forging process,Embodiment of the present inventionThis is the same as in the first example.
[0057]
Next, FIGS.Reference examples 5 to 6 of the present invention that also depart from the present inventionAn exampleYes.These second5-6In the case of the example, the hardened hardened layer applied to the hub 2d is formed only in a portion that receives a particularly large load when the rolling bearing is used. That is, as shown in FIG.The fifth reference exampleIn the case of the example, only the base end portion of the step portion 8a including the step surface 12 is shown in FIG.Sixth reference exampleIn the case of the example, the hardened hardened layer is formed only on the base end portion of the stepped portion 8 a including the stepped surface 12 and the base end portion of the first flange 6, respectively. The configuration and operation of other parts are as described above.Fourth reference exampleThe same as in the example.
[0058]
Although not shown in the drawings, in each of the embodiments described above, each caulking portion 19 and the inner ring (second inner ring) 3 do not necessarily have to be in close contact with each other over the entire surface of the facing portion. Even if a gap exists in a part of the facing portion, the operation and effect of the present invention can be obtained in the same manner. Before the caulking portion 19 is formed, the cylindrical portion 20 has a hardness of about Hv 200 to 300. However, in the state where the cylindrical portion 20 is caulked and expanded to form the caulking portion 19, this caulking portion is formed by work hardening. The hardness of 19 becomes larger than Hv200-300.
[0059]
【The invention's effect】
Since the wheel-supporting rolling bearing unit of the present invention is configured and operates as described above, it is possible to realize a wheel-supporting rolling bearing unit having low cost and sufficient durability.
Further, as shown in the example in the figure, the shape of the cylindrical portion for forming the caulking portion is reduced toward the tip edge in a state before the cylindrical portion is caulked outward in the diametrical direction. It is possible to prevent the occurrence of damage such as cracks in the steel sheet, and to prevent the caulking portion from changing so that the diameter of the inner ring fixed to the hub becomes a problem in practice. Further, it is possible to reduce the possibility that the inner ring is damaged based on the fixing operation and to maintain the preload at an appropriate value, and to reduce the cost by reducing the number of parts, parts processing, and assembly man-hours.
[Brief description of the drawings]
FIG. 1 is a half sectional view showing a first example of an embodiment of the present invention.
FIG. 2 is a partially enlarged cross-sectional view showing a state in which the inner end of the hub is caulked to fix the inner ring during the manufacture of the structure of the first example.
FIG. 3 is a partially enlarged cross-sectional view showing a state before the inner end of the hub is caulked and spread.
4 is a cross-sectional view taken along line AA in FIG.
FIG. 5 is a longitudinal sectional view of a main part of a rocking press device.
FIG. 6 is a plan view of a holding jig incorporated in a rocking press device.
FIG. 7 is a half sectional view showing a second example of an embodiment of the present invention.
FIG. 8 is a half sectional view showing the third example.
FIG. 9 is a half sectional view showing the fourth example.
FIG. 10 is a half sectional view showing the fifth example.
FIG. 11First reference example of the present inventionThe half part sectional view showing an example.
FIG. 122The half part sectional view showing an example.
FIG. 133The half part sectional view showing an example.
FIG. 144The half part sectional view showing an example.
FIG. 155The half part sectional view showing an example.
FIG. 166The half part sectional view showing an example.
FIG. 17 is a half sectional view showing a first example of a conventional structure.
FIG. 18 is a sectional view showing the second example.
[Explanation of symbols]
1, 1a Wheel support hub unit
2, 2a, 2b, 2c, 2d hub
3 Inner ring (second inner ring)
4 outer ring
5 Rolling elements
6 First flange
7 First inner ring raceway
8, 8a Step
9 Second inner ring raceway
10 Male thread
11 Nut
12, 12a Step surface
13 Second inner ring member
14 Locking recess
15 First outer ring raceway
16 Second outer ring raceway
17 Second flange
18 Hub
19, 19a Caulking part
20 Cylindrical part
21 Tapered hole
22 stamping die
23 Convex
24 recess
25 Clearance
26 Curved surface
27 space
28 Seal ring
29 Lid
30 shoulder
31 steps
32 tone wheel
33 Cover
34 sensors
35 Female spline section
36 Constant Velocity Joint
37 Drive shaft
38 steps
39 Body part
40 nuts
41 First inner ring
42 flat surface
43 Oscillating press device
44 Holding jig
45 Holder
46 Bottom
47 Jig elements
48 restraining part
49 through hole
50 Mounting part
51 Shaft member

Claims (1)

  1. An inner member (2b, 2c, 51) formed with a first flange (6) on the outer peripheral surface of one end and a first inner ring raceway (7) on the outer peripheral surface of the intermediate portion, and the inner members (2b, 2c). 51), the step portion (8) having a smaller outer diameter than the portion where the first inner ring raceway (7) is formed, and the second inner ring raceway ( 9) and an outer ring (3) externally fitted to the step (8), a first outer ring raceway (15) facing the first inner ring raceway (7) on the inner peripheral surface, and the second A second outer ring raceway (16) facing the inner ring raceway (9), an outer ring (4) formed with a second flange (17) on the outer peripheral surface, and the first and second inner ring raceways ( 7, 9) and the first and second outer ring raceways (15, 16), and a plurality of rolling elements (5) each provided, A caulking portion (19, 19) formed by caulking and expanding a portion protruding from the inner ring (3) at least externally fitted to the stepped portion (8) at the other end of the member (2b, 2c, 51) radially outward. 19a), the inner ring (3) fitted on the stepped portion (8) is pressed against the stepped surface (12) of the stepped portion (8), and the inner ring (3) fitted on the stepped portion (8) is pressed. ) Is coupled and fixed to the inner member (2b, 2c, 51), and the inner member (2b, 2c, 51) is at least a step which is an abutting surface of the inner ring (3). From one end of the step (8) including the surface (12) to the side surface of the base end of the first flange (6) including the first inner ring raceway (7). It is hardened by quenching treatment and at least the inner member (2b, 2c, 51 Wheel supporting rolling bearing unit in the portion that protrudes from the inner ring (3), characterized in that was neat without being subjected to the quenching treatment in the other end portion.
JP32105597A 1997-08-28 1997-11-21 Rolling bearing unit for wheel support Expired - Lifetime JP3622458B2 (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
JP23279897 1997-08-28
JP9-232798 1997-08-28
JP32105597A JP3622458B2 (en) 1997-08-28 1997-11-21 Rolling bearing unit for wheel support

Applications Claiming Priority (14)

Application Number Priority Date Filing Date Title
JP32105597A JP3622458B2 (en) 1997-08-28 1997-11-21 Rolling bearing unit for wheel support
EP03004632A EP1314903B1 (en) 1997-01-17 1998-01-14 Bearing unit for vehicle wheel support
DE69831515T DE69831515T2 (en) 1997-01-17 1998-01-14 Bearing unit for a vehicle wheel suspension
EP98300221A EP0854303B1 (en) 1997-01-17 1998-01-14 Rolling bearing unit for supporting vehicle wheel
EP03001091A EP1319854B1 (en) 1997-01-17 1998-01-14 Bearing unit for vehicle wheel support
DE69819217T DE69819217T2 (en) 1997-01-17 1998-01-14 Rolling bearing unit for a vehicle wheel
DE69831102T DE69831102T2 (en) 1997-01-17 1998-01-14 Bearing unit for a vehicle wheel suspension
DE69831434T DE69831434T2 (en) 1997-01-17 1998-01-14 Bearing unit for a vehicle wheel suspension
EP03001090A EP1312821B1 (en) 1997-01-17 1998-01-14 Bearing unit for vehicle wheel support
US09/005,716 US6280096B1 (en) 1997-01-17 1998-01-16 Rolling bearing unit for supporting vehicle wheel
US09/641,863 US6422758B1 (en) 1997-01-17 2000-08-18 Rolling bearing unit for supporting vehicle wheel
US09/916,420 US6524011B2 (en) 1997-01-17 2001-07-27 Rolling bearing unit for supporting vehicle wheel
US10/113,879 US6672770B2 (en) 1997-01-17 2002-04-01 Rolling bearing unit for supporting vehicle wheel
US10/341,826 US6761486B2 (en) 1997-01-17 2003-01-14 Rolling bearing unit for supporting vehicle wheel

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Families Citing this family (64)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE60038092T2 (en) 1999-12-16 2009-02-19 Nsk Ltd. Roller carrier for wheel and manufacturing process
DE60020754T2 (en) 1999-12-20 2005-11-03 Nsk Ltd. Process for their production of a rolling bearing bearing unit
JP4581233B2 (en) * 1999-12-20 2010-11-17 日本精工株式会社 Rolling bearing unit for wheel support
JP4947166B2 (en) * 1999-12-20 2012-06-06 日本精工株式会社 Manufacturing method of wheel bearing rolling bearing unit
JP3979001B2 (en) * 2000-02-28 2007-09-19 株式会社ジェイテクト Hub unit for vehicles
JP2001347805A (en) 2000-04-05 2001-12-18 Nsk Ltd Axle unit for driving wheel
JP2002089572A (en) * 2000-07-10 2002-03-27 Koyo Seiko Co Ltd Bearing device
JP4193344B2 (en) 2000-08-22 2008-12-10 日本精工株式会社 Wheel drive unit
US6622377B1 (en) * 2000-10-24 2003-09-23 Delphi Technologies, Inc. Wheel bearing with separable inner race processing feature
JP4742478B2 (en) * 2000-11-20 2011-08-10 日本精工株式会社 Manufacturing method of wheel supporting hub unit and its manufacturing die
EP1375196B1 (en) * 2001-03-29 2011-04-27 NTN Corporation Bearing device for drive wheel
JP4682459B2 (en) * 2001-06-21 2011-05-11 日本精工株式会社 Manufacturing method of wheel bearing rolling bearing unit
DE60237669D1 (en) * 2001-12-21 2010-10-28 Ntn Toyo Bearing Co Ltd Bearing device for a drive wheel of a vehicle
US6736418B2 (en) * 2002-05-23 2004-05-18 Visteon Global Technologies, Inc. Vehicle wheel end having integrated knuckle and outer race
WO2004007219A1 (en) * 2002-07-15 2004-01-22 Nsk Ltd. Rolling bearing unit for supporting wheel
JP4506467B2 (en) 2003-02-20 2010-07-21 日本精工株式会社 Assist device for electric power steering device and electric power steering device
JP2005083513A (en) * 2003-09-10 2005-03-31 Ntn Corp Wheel bearing device
JP4471150B2 (en) 2003-11-05 2010-06-02 Ｎｔｎ株式会社 Wheel bearing device and manufacturing method thereof
JP4716481B2 (en) 2003-12-01 2011-07-06 Ｎｔｎ株式会社 Wheel bearing device
DE10359643A1 (en) * 2003-12-18 2005-07-28 Fag Kugelfischer Ag Outer ring of a wheel bearing
JP3974115B2 (en) 2004-03-10 2007-09-12 Ｎｔｎ株式会社 Wheel bearing device
JP2005256897A (en) 2004-03-10 2005-09-22 Ntn Corp Machine element and its manufacturing method
JP3917992B2 (en) 2004-08-03 2007-05-23 Ｎｔｎ株式会社 Wheel bearing device
JP4562025B2 (en) * 2004-08-16 2010-10-13 Ｎｔｎ株式会社 Wheel bearing device
US20070217728A1 (en) * 2004-09-30 2007-09-20 Shinichirou Kashiwagi Hub Unit, Rolling Bearing Assembly and Manufacture Method Thereof, as Well as Assembling Apparatus for Rolling Bearing Assebly and Assebly Method Thereof
US7883272B2 (en) 2004-10-08 2011-02-08 Ntn Corporation Wheel support bearing assembly
JP4715172B2 (en) * 2004-11-25 2011-07-06 株式会社ジェイテクト Bearing device assembling apparatus and assembling method thereof
JP3923986B2 (en) 2005-05-10 2007-06-06 Ｎｔｎ株式会社 Wheel bearing device
US7874734B2 (en) 2005-06-02 2011-01-25 Ntn Corporation Wheel support bearing assembly
JP2006336758A (en) * 2005-06-02 2006-12-14 Ntn Corp Bearing device for wheel
JP2006336756A (en) * 2005-06-02 2006-12-14 Ntn Corp Bearing device for wheel
JP2007024208A (en) * 2005-07-19 2007-02-01 Ntn Corp Bearing device for wheel
EP1908852B1 (en) 2005-07-20 2013-08-21 NTN Corporation Bearing device for wheel
JP2007038803A (en) * 2005-08-02 2007-02-15 Ntn Corp Bearing device for wheel
JP5105725B2 (en) * 2005-08-19 2012-12-26 Ｎｔｎ株式会社 Wheel bearing device
EP1944518B1 (en) 2005-09-30 2013-07-31 NTN Corporation Bearing device for wheel
JP2007113719A (en) * 2005-10-21 2007-05-10 Ntn Corp Bearing device for wheel
DE112006003288T5 (en) 2005-12-05 2008-12-11 Ntn Corporation Wheel bearing support assembly and method for its production
JP5040108B2 (en) * 2005-12-08 2012-10-03 日本精工株式会社 Manufacturing method of bearing ring member constituting rolling bearing unit for supporting wheel
JP5283315B2 (en) * 2006-01-12 2013-09-04 Ｎｔｎ株式会社 Wheel bearing device
JP5283316B2 (en) * 2006-01-19 2013-09-04 Ｎｔｎ株式会社 Manufacturing method of wheel bearing device
JP5283317B2 (en) * 2006-01-30 2013-09-04 Ｎｔｎ株式会社 Manufacturing method of wheel bearing device
JP5099872B2 (en) 2006-02-07 2012-12-19 Ｎｔｎ株式会社 Wheel bearing device
JP4936739B2 (en) * 2006-02-07 2012-05-23 Ｎｔｎ株式会社 Wheel bearing device
JP5099875B2 (en) * 2006-08-30 2012-12-19 Ｎｔｎ株式会社 Wheel bearing device
JP4607081B2 (en) * 2006-09-22 2011-01-05 Ｎｔｎ株式会社 Drive axle bearing device
JP2007062732A (en) * 2006-10-13 2007-03-15 Ntn Corp Bearing device for driving wheel
JP5278935B2 (en) 2006-11-14 2013-09-04 Ｎｔｎ株式会社 Wheel bearing device
JP4658028B2 (en) * 2006-12-18 2011-03-23 Ｎｔｎ株式会社 Manufacturing method of wheel bearing device
JP4573200B2 (en) * 2007-01-12 2010-11-04 Ｎｔｎ株式会社 Wheel bearing device
JP2008175262A (en) 2007-01-17 2008-07-31 Ntn Corp Wheel bearing device and its manufacturing method
JP2007271081A (en) * 2007-03-26 2007-10-18 Ntn Corp Wheel bearing device
JP4829170B2 (en) * 2007-04-26 2011-12-07 株式会社ジェイテクト Hub unit
JP2008302766A (en) * 2007-06-06 2008-12-18 Nsk Ltd Method for assembling hub unit bearing
JP4846672B2 (en) * 2007-08-03 2011-12-28 Ｎｔｎ株式会社 Axle bearing and wheel bearing device
JP5301175B2 (en) * 2008-02-29 2013-09-25 Ｎｔｎ株式会社 Drive wheel bearing device
JP2008221337A (en) * 2008-04-21 2008-09-25 Jtekt Corp Calking method of vehicular hub unit
JP2010089530A (en) * 2008-10-03 2010-04-22 Ntn Corp Wheel bearing apparatus
US20100210369A1 (en) * 2009-02-17 2010-08-19 Jtekt Corporation Wheel bearing device and manufacturing method therefor
JP5304742B2 (en) * 2010-07-26 2013-10-02 株式会社ジェイテクト Manufacturing method of hub unit
JP2013024393A (en) * 2011-07-26 2013-02-04 Ntn Corp Apparatus and method for attaching wheel bearing device
KR101338439B1 (en) * 2011-11-01 2013-12-10 주식회사 일진글로벌 Device and method for manufacturing wheel bearing device
JP6505961B2 (en) * 2013-04-11 2019-04-24 Ntn株式会社 Wheel bearing device
KR20190008881A (en) 2016-07-12 2019-01-25 닛본 세이고 가부시끼가이샤 Inspection device for rocking forging device, tool for inspection, inspection method, manufacturing device of bearing unit, and manufacturing method of bearing unit

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3636243C2 (en) * 1986-10-24 1989-10-19 Loehr & Bromkamp Gmbh, 6050 Offenbach, De
JPH0277303A (en) * 1988-09-14 1990-03-16 Fuji Heavy Ind Ltd Structure of wheel bearing section
JP2529597Y2 (en) * 1989-07-13 1997-03-19 日本精工株式会社 Bearing unit for wheels
JPH0399225U (en) * 1990-01-30 1991-10-16
JP2936657B2 (en) * 1990-06-26 1999-08-23 日本精工株式会社 Measurement method of heat treatment hardened layer depth
FR2666389B1 (en) * 1990-09-04 1992-10-23 Roulements Soc Nouvelle Process for producing a bearing collar and bearing assembly equipped with such a collar.
JPH0657324A (en) * 1992-08-10 1994-03-01 Nippon Seiko Kk Manufacture of bearing
IT1264059B (en) * 1993-02-09 1996-09-09 Skf Svenska Kullagerfab Ab Wheel hub group for a vehicle.
KR100211423B1 (en) * 1993-09-08 1999-08-02 스마 요시쓰기 Mechanical part having rolling elements
DE4339847C2 (en) * 1993-11-23 2000-09-14 Kugelfischer G Schaefer & Co Storage unit
IT235829Y1 (en) * 1995-04-06 2000-07-18 Skf Ind Spa Ball bearing for the wheel hub of a motor vehicle.
JPH09164803A (en) * 1995-12-15 1997-06-24 Nippon Seiko Kk Driving wheel supporting hub unit
JP3735926B2 (en) * 1995-12-15 2006-01-18 日本精工株式会社 Wheel support hub unit
JPH094642A (en) * 1996-07-10 1997-01-07 Nippon Seiko Kk Bearing unit for wheel
JPH1151064A (en) * 1997-08-07 1999-02-23 Ntn Corp Hub unit bearing

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