JP4408251B2 - Bearing clearance measurement method for wheel bearing device - Google Patents

Description

  The present invention relates to a bearing clearance measuring method in a wheel bearing device for rotatably supporting a wheel of an automobile or the like.

  2. Description of the Related Art Conventionally, a wheel bearing device that rotatably supports a wheel of an automobile or the like is provided with a predetermined bearing preload in order to ensure a desired bearing rigidity. The management of the bearing preload amount is, for example, a so-called third generation, which includes a hub wheel integrally having a wheel mounting flange and an inner ring surface formed directly on the outer periphery, and an inner ring press-fitted into the hub wheel. In a wheel bearing device referred to as “a”, the abutment surface between the hub ring and the inner ring is accurately controlled, and when the hub ring and the outer joint member of the constant velocity universal joint are fastened by a fixing nut, the fixing nut The tightening torque (axial force) is set to a predetermined value.

  Naturally, the bearing preload amount affects the bearing life, but this bearing preload amount is greatly related to environmental problems such as safe driving of the vehicle and improvement of fuel consumption. That is, the bearing preload amount is proportional to the rotational torque of the bearing, and if the preload amount is reduced, the rotational torque can be reduced and the fuel consumption can be improved. On the other hand, the relationship between the bearing tilt angle, which is the main factor of bearing rigidity, and the bearing preload amount is inversely proportional, so if the preload amount is increased, the bearing stiffness improves and the bearing tilt angle decreases, which occurs when the vehicle turns. The inclination of the brake rotor can be suppressed. Therefore, by setting the preload amount of such a bearing optimally, it is possible to provide a wheel bearing device that is excellent not only in terms of bearing life but also in terms of vehicle safety and fuel efficiency.

A typical example of such a wheel bearing device will be described with reference to FIG. 1 showing a first embodiment of the present invention. In the following description, the side closer to the outer side of the vehicle when assembled to the vehicle is referred to as the outboard side (left side in the drawing), and the side closer to the center is referred to as the inboard side (right side in the drawing).
The wheel bearing device includes an inner member 1, an outer member 10, and double-row rolling elements (balls) 6, 6 accommodated between the members 1, 10 so as to roll freely. The inner member 1 includes a hub ring 2 and a separate inner ring 3 that is press-fitted into the hub ring 2.

  The hub wheel 2 is made of medium carbon steel containing 0.40 to 0.80 wt% of carbon such as S53C, and has a wheel mounting flange 4 for mounting a wheel (not shown) at the end on the outboard side. A hub bolt 5 for fixing a wheel (not shown) is implanted at a circumferentially equidistant position of the wheel mounting flange 4. Further, an inner rolling surface 2a and a cylindrical small-diameter step portion 2b extending in the axial direction from the inner rolling surface 2a are formed on the outer periphery of the hub wheel 2, and a serration (or spline) for torque transmission is formed on the inner periphery. ) 2c is formed.

  A hardened layer having a surface hardness of 58 to 64 HRC is formed by induction quenching from the seal land where the seal 8 on the outboard side of the hub wheel 2 is in sliding contact to the inner rolling surface 2a and the small diameter step 2b. ing. In addition, the edge part of the small diameter step part 2b is made into the unhardened part of the raw material surface hardness 25HRC or less after forging. On the other hand, the inner ring 3 has an inner rolling surface 3 a formed on the outer periphery, and is press-fitted into the small diameter step 2 b of the hub ring 2. The inner ring 3 is prevented from coming off in the axial direction with respect to the hub wheel 2 by a crimping part 2d formed by plastically deforming the end of the small diameter step part 2b radially outward. The inner ring 3 is made of high carbon chrome bearing steel such as SUJ2, and is hardened in the range of 58 to 64 HRC up to the core part by quenching.

  The outer member 10 is formed of medium carbon steel containing 0.40 to 0.80 wt% of carbon such as S53C, and integrally includes a vehicle body mounting flange 10b for mounting on a vehicle body (not shown) on the outer periphery. Double rows of outer rolling surfaces 10a and 10a are formed around the circumference. A hardened layer having a surface hardness in the range of 58 to 64 HRC is formed on the double row outer raceway surfaces 10a and 10a by induction hardening. And the double row rolling elements 6 and 6 are accommodated between each rolling surface 10a, 2a and 10a, 3a, and these double row rolling elements 6 and 6 are rollably hold | maintained by the holder | retainers 7 and 7. ing. Further, seals 8 and 9 are attached to both ends of the outer member 10 to prevent leakage of the lubricating grease sealed inside the bearing and intrusion of rainwater, dust and the like from the outside into the bearing.

  This type of wheel bearing device employs a so-called self-retaining structure in which the inner ring 3 is fixed by a crimping portion 2d formed by plastically deforming the end of the small-diameter stepped portion 2b of the hub wheel 2 radially outward. Therefore, it is not necessary to control the preload by tightening firmly with a nut or the like as in the prior art, so that the ease of incorporation into the vehicle can be simplified and the preload is maintained for a long time. be able to. However, this type of wheel bearing device has such a feature, but there is a risk that the bearing clearance may fluctuate due to deformation of the inner ring 3 due to caulking, or variations in caulking load. Without measuring the amount, it was not known whether the amount of preload was appropriate.

As a solution to such a problem, as shown in FIG. 11, a technique is known in which a preload setting is performed by measuring a torque by rotating a bearing during assembly of a wheel bearing device.
FIG. 11A is a schematic diagram showing a configuration of a preload monitoring device 51 attached to the wheel bearing device 50. The preload monitoring device 51 includes a gear 53 to which a rubber member that comes into contact with the outer peripheral surface on the inboard side of the vehicle body mounting flange 52a in the outer member 52, a drive gear 54 that meshes with the gear 53, and the drive A motor 55 that rotationally drives the gear 54, a torque detector 56 that includes a power meter that detects the rotational torque of the motor 55, and a determiner 57 that compares the detected rotational torque with a predetermined value set in advance. ing.

  In the preload monitoring device 51, the motor 55 is driven to rotate the outer member 52 through the gears 54 and 53, and the rotational torque of the outer member 52 is detected by the torque detector 56. Then, a preload amount is obtained based on the detected rotational torque, and when the preload amount reaches a predetermined value set in advance, that is, a preload amount suitable for the wheel bearing device 50, the swing type caulking device 58 is moved backward. Let Further, the rotational torque is monitored even after finishing the caulking process by the swing caulking device 58 to confirm that the preload amount is appropriate.

FIG. 11B is a graph showing changes in the position A and the rotational torque T (vertical axis) of the caulking die 58a in the swing type caulking device 58 with respect to the caulking processing time t (horizontal axis). When the caulking process is started by gradually lowering the position A of the caulking die 58a, a preload is applied to the wheel bearing device 50 from a certain time t0, and the rotational torque T starts to fluctuate. When the fluctuation range reaches a predetermined value Δ set in advance (t1), it is determined that a preload suitable for the wheel bearing device 50 has been applied, and the caulking process is terminated. Thereafter, the position A of the caulking die 58a is returned to the origin. With such a preload monitor device 51, the rotational torque can be measured by rotating the bearing during assembly of the wheel bearing device 50, and the preload amount can be set using this rotational torque as a medium.
JP 11-44319 A

  However, in such a conventional technique, the rotational torque of the bearing is dominated by the stirring resistance of the lubricating grease enclosed in the bearing and the rotational torque of the seals 59 and 60 attached to both ends of the outer member 52. It is difficult to measure the rotational torque of such a bearing and to manage the preload amount of the bearing accurately and stably using this rotational torque as a medium.

  The present invention has been made in view of such circumstances, so that the negative clearance can be managed by measuring the amount of end face movement of the outer member that is correlated with the axial clearance reduction amount of the bearing due to plastic coupling. An object of the present invention is to provide a bearing clearance measuring method for a wheel bearing device.

In order to achieve the object, the method invention according to claim 1 of the present invention includes an outer member integrally having a vehicle body mounting flange on the outer periphery, and a double row outer rolling surface formed on the inner periphery. A wheel mounting flange is integrally formed at one end, and an inner rolling surface facing one of the double row outer rolling surfaces and a small-diameter step portion extending in the axial direction from the inner rolling surface are formed on the outer periphery. A hub ring, an inner member that is an inner ring that is press-fitted into a small-diameter step portion of the hub ring, and has an inner rolling surface that is opposed to the other of the outer circumferential rolling surfaces of the double row ; The inner ring is axially formed by a crimping portion formed by plastically deforming the end of the small-diameter step portion of the hub wheel in a radial direction, including a double row rolling element that is rotatably accommodated between the outer members. in fixed bearing clearance measuring method for a wheel bearing device, when the press-fitting said annulus to said wheel hub, Once stopped press-fitting in the state of Kimagasei, actually measured axial dimension T0 the initial axial clearance δ0 between the reference surface of the inner wheel and the hub wheel in this state, the press-fitting is completed to continue the further press-fitting after the actually measured axial dimension T1 between the reference surface of the hub wheel and the inner wheel, the axial clearance .delta.1 with determined based formula .delta.1 = the δ0- (T0-T1) in this state, the inner member The end face movement amount is calculated from the difference in the end face position of the outer member measured before and after the plastic coupling of the outer member, and the end face movement amount of the outer member is set to the preset axial clearance reduction amount and the outer direction. By applying the relationship to the end face movement amount of the member, the axial clearance reduction amount Δδ of the bearing due to plastic coupling is obtained, and the axial clearance reduction amount Δδ of the bearing is measured before the inner member is plastically coupled. Reduced from the axial clearance δ1 And to determine the axial clearance δ of the bearing after the plastic binding by.

As described above, in the bearing clearance measuring method of the wheel bearing device in which the inner ring is fixed in the axial direction by the caulking portion formed by plastically deforming the end of the small-diameter step portion of the hub ring in the radial direction , when press-fitting the wheel, a gap is temporarily stopped press-fitting a positive state, actually measured axial dimension T0 the initial axial clearance δ0 between the reference surface of the hub wheel and the inner wheel in this state, and continue with the further press-fitting after the press-fitting Te is complete, the actually measured axial dimension T1 between the reference surface of the hub wheel and the inner wheel, determine based on the axial gap .delta.1 in this state equation δ1 = δ0- (T0-T1) , the inner The end face movement amount is calculated from the difference in the end face position of the outer member measured before and after the plastic coupling of the outer member, and the end face movement amount of the outer member is calculated from the preset axial clearance reduction amount of the bearing and the outside. By applying to the relational expression of the end face movement amount of the side member The axial clearance reduction amount Δδ of the bearing due to the plastic coupling is obtained, and the axial clearance reduction amount Δδ of the bearing is subtracted from the axial clearance δ1 measured before the inner member is plastically coupled. Since the axial clearance δ of the bearing is obtained, it is possible to measure the bearing clearance while managing the bearing clearance that fluctuates due to deformation of the inner ring due to caulking, or variations in the caulking load, etc. Even if the bearing clearance is negative, the bearing clearance can be set accurately and stably without using the rotational torque inherent in the dispersion factors, such as the stirring resistance of the lubricated grease and the seal squealing, as the medium. can do.

In the invention according to claim 2 , the movement amount of the end surface of the outer member is an axial dimension from the reference surface of the outer member to the reference surface of the hub wheel before and after plastic coupling of the inner member. Since the difference is used, the preload amount of the bearing can be accurately and stably managed as compared with the conventional bearing clearance measuring method using the rotational torque of the bearing as a medium.

According to a third aspect of the present invention, the position of the end face of the outer member is measured by placing the wheel bearing device in a vertical position so that the reference surface of the hub wheel contacts the surface plate. Therefore, the influence of the angular deflection of the bearing can be suppressed, and the axial position from the reference plane can be measured accurately and stably.

A bearing clearance measuring method for a wheel bearing device according to the present invention includes an outer member integrally having a vehicle body mounting flange on the outer periphery and a double row outer raceway formed on the inner periphery, and a wheel mounting on one end. A hub wheel having a flange integrally formed on the outer periphery thereof and formed with an inner rolling surface facing one of the double row outer rolling surfaces, and a small-diameter step portion extending in an axial direction from the inner rolling surface, and An inner member that is an inner ring that is press-fitted into a small-diameter step portion of the hub wheel and has an inner rolling surface that faces the other of the outer rolling surfaces of the double row on the outer periphery, and between the inner member and the outer member A wheel in which the inner ring is fixed in the axial direction by a caulking portion formed by plastically deforming the end portion of the small diameter step portion of the hub wheel in a radial direction. in the bearing clearance measuring method of use bearing device, when the press-fitting said annulus to said hub wheel, a gap is positive Once stopped pressed in a state, after the said in the state actually measured axial dimension T0 the initial axial clearance δ0 between the reference surface of the hub wheel and the inner wheel, press-fitting is completed to continue the further press-fitting, said hub actually measuring the axial dimension T1 between the reference surface of the wheel and the inner wheel, the axial clearance .delta.1 in this state with determined based formula .delta.1 = the δ0- (T0-T1), plastic coupling front and rear of the inner member The end face movement amount is calculated from the difference in the end face position of the outer member actually measured, and the end face movement amount of the outer member is calculated from the preset axial clearance reduction amount of the bearing and the end face movement of the outer member. The amount of axial clearance reduction Δδ of the bearing due to plastic coupling is obtained by applying to the relational expression of the quantity, and the amount of axial clearance reduction Δδ of this bearing is measured in the axial direction measured before plastically coupling the inner member. Subtract from clearance δ1 Since so as to obtain a more axial clearance of the plastic binding post of the bearing [delta], it is possible to measure the bearing clearance while managing bearing clearance varies with variations in deformation or caulking load of the inner ring by caulking The bearing clearance is accurate based on the measured values even if the bearing clearance is negative, without using the rotational torque inherent in the dispersion factors, such as the stirring resistance of the lubricating grease sealed inside the bearing and the seal squeezing, as the medium. And can be set stably.

  An outer member integrally having a vehicle body mounting flange on the outer periphery and a double row outer rolling surface formed on the inner periphery, and a double row inner rolling surface facing the outer surface of the double row on the outer periphery And an inner member integrally formed with one end of a wheel mounting flange and an inner ring externally fitted to the hub wheel. And a bearing clearance measuring method for a wheel bearing device including a double row rolling element housed so as to be freely rollable between the outer member and the outer member, the outer member measured before and after the plastic coupling of the inner member. By calculating the end face movement amount from the difference in the end face position, and applying the end face movement amount of the outer member to a preset relational expression of the axial clearance reduction amount of the bearing and the end face movement amount of the outer member, While obtaining the axial clearance reduction amount Δδ of the bearing due to plastic coupling, The axial clearance reduction amount Δδ of the bearing is subtracted from the axial clearance δ1 of the bearing actually measured before plastically coupling the inner member, thereby obtaining the axial clearance δ of the bearing after plastic coupling. .

Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.
FIG. 1 is a longitudinal sectional view showing a first embodiment of a wheel bearing device according to the present invention, FIG. 2 is an explanatory view showing a bearing clearance measuring method in an assembly process, and FIG. 3 is a caulking process of FIG. It is a longitudinal cross-sectional view which shows the front.

  As shown in FIG. 1, this wheel bearing device has a configuration called the third generation on the drive wheel side, and has been described with reference to FIG. 1 as an example of a conventional wheel bearing device. A detailed description of the configuration will be omitted, and only the characteristic part according to the present invention will be mainly described.

  First, in the assembly process of the wheel bearing device, as shown in FIG. 2A, the inner ring 3 is press-fitted into the small-diameter step portion 2 b of the hub ring 2, and the small end surface 11 of the inner ring 3 is the shoulder portion 12 of the hub ring 2. Stop immediately before coming into contact. That is, at this time, a predetermined distance S remains between the small end surface 11 of the inner ring 3 and the shoulder 12 of the hub ring 2, and the axial clearance of the bearing is positive. In this state, the axial dimension T0 from the reference surface 13 (large end surface) of the inner ring 3 to the reference surface 14 (flange side surface) of the hub wheel 2 is measured, and the axial direction of the outer member 10 relative to the inner member 1 is measured. The initial axial clearance δ0 of the bearing is measured from the amount of movement.

  Subsequently, as shown in FIG. 2B, the inner ring 3 is press-fitted until the small end surface 11 of the inner ring 3 abuts against the shoulder 12 of the hub ring 2, and the reference surface 13 of the hub ring 2 is referred to from the reference surface 13 of the inner ring 3. An axial dimension T1 up to 14 is measured. Then, the axial clearance δ1 of the bearing after the inner ring 3 is press-fitted into the hub wheel 2 is obtained from the equation δ1 = δ0− (T0−T1). Here, the reference surface 14 of the hub wheel 2 is not limited to the side surface of the wheel mounting flange 4 but may be the end surface of the hub wheel 2 on the outboard side.

  FIG. 3 shows the wheel bearing device before the caulking process in the wheel bearing device of FIG. 1, but the end face position of the outer member 10 after the inner ring 3 is press-fitted into the hub wheel 2 (before the caulking process). That is, the axial dimension L1 from the reference surface 16 of the outer member 10 to the reference surface 14 of the hub wheel 2 is measured. As shown in FIG. 5A, the measuring procedure is such that the reference surface 14 of the hub wheel 2 comes into contact with the surface plate B1 in which the recess 17 that accommodates the pilot portion 15 of the hub wheel 2 is formed. Place the bearing device. Then, the height from the reference surface 14 to the reference surface 16 of the outer member 10 is measured by a measuring instrument such as a dial gauge. In this way, since the wheel bearing device is placed in a vertical position so that the reference surface 14 of the hub wheel 2 is in contact with the surface plate B1, and measured by the measuring instrument, the influence of angular deflection of the bearing is suppressed. It is possible to measure the position in the axial direction from the reference plane with high accuracy and stability. As shown in FIG. 5B, the wheel bearing device is placed so that the end surface on the outboard side of the hub wheel 2 is in contact with the surface plate B2, and the reference of the outer member 10 from the surface plate B2. The height up to the surface 16 may be measured.

  Thereafter, caulking is performed, and similarly, the end face dimension L2 (see FIG. 1) of the outer member 10 after caulking is measured as described above (see FIG. 5A). And the end face movement amount ΔL of the outer member 10 before and after the caulking process can be obtained by ΔL = L1−L2. Here, the reference surface 14 of the hub wheel 2 is not limited to the side surface of the wheel mounting flange 4 but may be an end surface on the outboard side of the hub wheel 2 (see FIG. 5B).

  Here, it was found from experiments conducted by the present applicant that there is a high correlation between the axial clearance reduction amount Δδ of the bearing and the end face movement amount ΔL of the outer member. FIG. 4 is an example showing the relationship between the axial clearance reduction amount Δδ of the bearing and the end face movement amount ΔL of the outer member. These relationships are set as predetermined relational expressions in advance, and this relational expression is used. The bearing axial clearance reduction amount Δδ due to caulking was calculated. That is, based on the relational expression between the axial clearance reduction amount Δδ of the bearing and the end face movement amount ΔL of the outer member due to the caulking process, the axial clearance reduction amount Δδ of the bearing is calculated from the measured end face movement amount ΔL of the outer member. Was calculated. Further, the axial clearance (negative clearance) δ after caulking is obtained from the axial clearance reduction amount Δδ of the bearing and the axial clearance δ1 of the bearing after the inner ring 3 is press-fitted, that is, δ = δ1-Δδ. be able to.

  In this embodiment, the end face movement amount ΔL of the outer member 10 is such that the axial dimensions ΔL1 and ΔL2 from the reference surface 16 of the outer member 10 to the reference surface 14 of the hub wheel 2 before and after plastic coupling of the inner member 1 are set. Since the difference is used, the preload amount of the bearing can be accurately and stably managed as compared with the conventional bearing clearance measuring method using the rotational torque of the bearing as a medium.

  On the other hand, it has been found that there is a high correlation between the axial clearance δ of the bearing and the amount of preload of the bearing. Therefore, the preload amount of the bearing can be accurately obtained from the axial clearance δ of the bearing by using a relational expression between the preset axial clearance of the bearing and the preload amount of the bearing.

  Thus, in the present embodiment, the end face movement amount ΔL is calculated from the difference between the end face positions L1 and L2 of the outer member 10 measured before and after the plastic coupling of the inner member 1, and the end face of the outer member 10 is calculated. By applying the movement amount ΔL to a preset relational expression between the axial clearance reduction amount of the bearing and the end face movement amount of the outer member, the axial clearance reduction amount Δδ of the bearing due to the plastic coupling is obtained. By subtracting the axial clearance reduction amount Δδ from the axial clearance δ1 of the bearing actually measured before the inner member 1 is plastically coupled, the axial clearance δ of the bearing after plastic coupling, that is, δ = δ1−Δδ. Therefore, it is possible to accurately determine the bearing clearance based on the measured values without using as a medium the rotational torque inherent in the dispersion factors such as the stirring resistance of the lubricating grease sealed in the bearing and the seal squealing. It is possible to set a stable manner.

  Here, the third generation structure has been described in detail, but the bearing clearance measuring method in the wheel bearing device according to the present invention can also be applied to the fourth generation structure shown in FIG. In addition, the same site | part, the same component as the embodiment mentioned above, the part which has the same function, and a site | part are attached | subjected with the same code | symbol, and the overlapping description is abbreviate | omitted.

  In this wheel bearing device, a hub wheel 18, a double row rolling bearing 19, and a constant velocity universal joint 20 are configured as a unit. The double-row rolling bearing 19 includes an outer member 10, an inner member 21, and double-row rolling elements 6 and 6.

  The inner member 21 includes a hub wheel 18 and an outer joint member 22 to be described later that is fitted into the hub wheel 18. The hub wheel 18 is made of medium carbon steel containing 0.40 to 0.80 wt% of carbon such as S53C, and the outer periphery thereof has an inner rolling on the outboard side facing the double row outer rolling surfaces 10a and 10a. A running surface 18a and a cylindrical small diameter step portion 18b extending in the axial direction from the inner rolling surface 18a are formed. A hardened layer is formed with a surface hardness in the range of 58 to 64 HRC by induction hardening over the inner rolling surface 18a and the small diameter step portion 18b from the seal land portion in which the seal 8 on the outboard side is in sliding contact.

  The constant velocity universal joint 20 includes an outer joint member 22, a joint inner ring 23, a cage 24, and a torque transmission ball 25. The outer joint member 22 is made of medium carbon steel containing 0.40 to 0.80 wt% of carbon such as S53C, and has a cup-shaped mouth portion 26, a shoulder portion 27 that forms the bottom portion of the mouth portion 26, and the shoulder portion. A cylindrical shaft portion 28 extending in the axial direction from 27 is integrally provided. On the outer periphery of the shoulder portion 27, an inboard-side inner rolling surface 22 a facing the double row outer rolling surfaces 10 a, 10 a of the outer member 10 is formed, and a hub wheel is formed on the shaft portion 28. An in-row portion 28a that is cylindrically fitted to the 18 small-diameter step portions 18b through a predetermined shimiro is formed, and a fitting portion 28b is formed at the end of the in-row portion 28a. And the hardened layer is formed in the range of 58-64 HRC by surface hardening from the shoulder part 27 to the inner side rolling surface 22a and the axial part 28 by induction hardening. The fitting portion 28b of the shaft portion 28 is an unquenched portion having a material surface hardness of 25 HRC or less after forging.

  Here, on the inner periphery of the hub wheel 18, a concavo-convex portion 29 having a surface hardness of 54 to 64 HRC is formed by heat treatment. As the heat treatment, local heating is preferable, and quenching by high-frequency induction heating that can set the hardened layer depth relatively easily is preferable. The concavo-convex portion 29 is formed in the shape of a iris knurl, and a plurality of annular grooves formed independently by turning or the like and a plurality of axial grooves formed by broaching or the like are crossed grooves configured to be substantially orthogonal, Or it consists of the crossing groove | channel comprised by the helical groove | channel inclined mutually. Moreover, in order to ensure good biting property, the tip of the concavo-convex portion 29 is formed in a spire shape such as a triangular shape.

  Then, the end surface of the small-diameter step portion 18b of the hub wheel 18 is abutted with the shoulder portion 27 of the outer joint member 22, and the shaft portion 28 is fitted into the hub wheel 18 until it comes into a butted state. Further, a diameter expanding jig such as a mandrel is pushed into the inner diameter of the fitting portion 28b in the shaft portion 28 to increase the diameter of the fitting portion 28b, and this fitting portion 28b is bitten into the uneven portion 29 of the hub wheel 18. The hub wheel 18 and the outer joint member 22 are integrally plastically bonded (expanded diameter caulking).

  Here, the axial clearance δ1 is measured by the method described above before the outer joint member 22 is diameter-enlarged and crimped to the hub wheel 18. That is, as shown in FIG. 7A, the outer joint member 22 is press-fitted into the small-diameter step portion 18b of the hub wheel 18, and the shoulder portion 27 of the outer joint member 22 contacts the end surface of the small-diameter step portion 18b of the hub wheel 18. Stop before touching. That is, at this time, a predetermined distance S remains between the shoulder portion 27 of the outer joint member 22 and the small diameter step portion 18b of the hub wheel 18, and the axial clearance of the bearing is positive. In this state, the axial dimension T0 from the reference surface 30 (end surface on the inboard side) of the outer joint member 22 to the reference surface 14 (flange side surface) of the hub wheel 18 is measured, and further outward with respect to the inner member 21. The initial axial clearance δ0 of the bearing is measured from the amount of axial movement of the member 10.

  Subsequently, as shown in FIG. 7B, the outer joint member 22 is press-fitted until the shoulder portion 27 of the outer joint member 22 abuts against the end surface of the small-diameter step portion 18 b of the hub wheel 18. An axial dimension T1 from the surface 30 to the reference surface 14 of the hub wheel 18 is measured. Then, the axial clearance δ1 of the bearing after the outer joint member 22 is press-fitted into the hub wheel 18 is obtained from the formula δ1 = δ0− (T0−T1). Here, the reference surface 14 of the hub wheel 18 is not limited to the side surface of the wheel mounting flange 4 but may be the end surface of the hub wheel 18 on the outboard side.

  Here, the axial clearance reduction amount Δδ of the bearing is calculated based on the relational expression between the axial clearance reduction amount Δδ of the bearing due to the diameter-enlarged caulking and the end face movement amount ΔL of the outer member. Further, the axial clearance reduction amount Δδ of the bearing and the axial clearance (negative clearance) δ of the bearing after diameter-enlarged caulking from the axial clearance δ1 of the bearing after the outer joint member 22 is press-fitted, that is, δ = Δ1-Δδ can be obtained. Further, the preload amount of the bearing can be obtained from the axial clearance δ of the bearing.

  Thus, also in this embodiment, the axial clearance δ1 of the bearing after the press fitting of the outer joint member 22 measured and the end face movement amount ΔL of the outer member 10 before and after the diameter expansion caulking are calculated. After the diameter expansion caulking from the axial clearance reduction amount Δδ of the bearing due to the expanded caulking, the axial clearance clearance amount Δδ of the bearing due to the enlarging caulking and the axial clearance δ1 of the bearing after the outer joint member 22 is press-fitted. The axial clearance (negative clearance) δ of the bearing is calculated so that the rotational torque in which the variation factors such as the agitation resistance of the lubricating grease sealed in the bearing and the squeeze of the seal are present is not used as a medium. The bearing clearance can be set accurately and stably based on the value.

  FIG. 9 is a longitudinal sectional view showing a third embodiment of the wheel bearing device according to the present invention. This embodiment is a modification of the above-described second embodiment (FIG. 6), and the same parts, parts, parts having the same functions, and parts as those of the above-described embodiment are denoted by the same reference numerals and overlapped. The description that has been made will be omitted.

  The wheel bearing device includes a hub wheel 31, a double row rolling bearing 32, and a constant velocity universal joint 33 that are unitized. The double row rolling bearing 32 includes an outer member 10, an inner member 34, and double row rolling elements 6 and 6. The inner member 34 includes a hub wheel 31 and an outer joint member 36 (described later) that is externally fitted to the hub wheel 31.

  The hub wheel 31 is made of medium carbon steel containing 0.40 to 0.80 wt% of carbon such as S53C, and the outer periphery of the hub wheel 31 is on the outboard side on the outboard side facing the double row outer rolling surfaces 10a and 10a. A running surface 18a and a cylindrical shaft portion 35 extending in the axial direction from the inner rolling surface 18a are formed. The shaft portion 35 is formed with an in-row portion 35a and a fitting portion 35b at the end of the in-row portion 35a. Then, a hardened layer is formed with a surface hardness in the range of 58 to 64 HRC by induction hardening over the inner rolling surface 18a and the shaft portion 35 from the seal land portion where the seal 8 on the outboard side of the hub wheel 31 is in sliding contact. ing. The fitting portion 35b of the shaft portion 35 is an unquenched portion having a surface hardness of 25HRC or less after forging.

  The constant velocity universal joint 33 includes an outer joint member 36, a joint inner ring 23, a cage 24, and a torque transmission ball 25. The outer joint member 36 is made of medium carbon steel containing 0.40 to 0.80 wt% of carbon such as S53C, and has a cup-shaped mouth portion 26, a shoulder portion 37 that forms the bottom of the mouth portion 26, and the shoulder portion. A small-diameter step portion 37a extending in the axial direction from 37 is integrally provided. On the outer periphery of the shoulder portion 37, an inboard-side inner rolling surface 22 a facing the double row outer rolling surfaces 10 a, 10 a of the outer member 10 is formed. A hardened layer having a surface hardness in the range of 58 to 64 HRC is formed by induction hardening over the small diameter step portion 37a. The small-diameter step portion 37a is cylindrically fitted to the in-row portion 35a of the hub wheel 31 via a predetermined shimiro. Here, an uneven portion 29 cured by heat treatment is formed on the inner periphery of the outer joint member 36.

  Then, the shoulder portion 37 of the outer joint member 36 is abutted against the shoulder portion 12 of the hub wheel 31, and the small-diameter step portion 37 a of the outer joint member 36 is externally fitted to the hub wheel 31 until the butt state is reached. Further, a diameter expansion jig such as a mandrel is pushed into the inner diameter of the fitting portion 35b of the hub wheel 31 to increase the diameter of the fitting portion 35b, and this fitting portion 35b is bitten into the uneven portion 29 of the outer joint member 36. The hub wheel 31 and the outer joint member 36 are integrally plastically coupled.

  Also in the present embodiment, similarly to the above-described embodiment, calculation is made from the measured axial clearance δ1 of the bearing after press-fitting the hub wheel 31 and the measured end face movement amount ΔL of the outer member 10 before and after the enlarged diameter caulking. The axial clearance reduction amount Δδ of the bearing due to the expanded diameter caulking, the axial clearance reduction amount Δδ of the bearing due to the expanded caulking and the axial clearance δ1 of the bearing after press fitting of the outer joint member 36 is increased. Since the axial clearance (negative clearance) δ of the bearing after tightening has been obtained, the rotational torque that contains variation factors such as the agitation resistance of the lubricating grease enclosed in the bearing and the squeeze of the seal is not used as a medium. The bearing clearance can be set accurately and stably based on the measured values.

  FIG. 10 is a longitudinal sectional view showing a fourth embodiment of the wheel bearing device according to the present invention. In addition, in the modified example of the first embodiment (FIG. 1) described above, the same parts, parts, parts having the same functions, and parts as in this embodiment are denoted by the same reference numerals and redundant description is omitted. .

  The wheel bearing device includes an inner member 38, an outer member 10, and double-row rolling elements 6 and 6 accommodated between the members 38 and 10 so as to be freely rollable. The inner member 38 includes a hub ring 39 and a separate inner ring 40 that is externally fitted to the hub ring 39.

  The hub wheel 39 is made of medium carbon steel containing 0.40 to 0.80 wt% of carbon such as S53C, and has an inner rolling surface 2a on the outer periphery and a small cylindrical diameter extending in the axial direction from the inner rolling surface 2a. A step 39a is formed, and a serration (or spline) 2c for torque transmission is formed on the inner periphery. A hardened layer is formed with a surface hardness in the range of 58 to 64 HRC by induction hardening over the inner rolling surface 2a and the shoulder 12 from the seal land portion where the seal 8 on the outboard side is in sliding contact. The small diameter step 39a is an unquenched portion having a surface hardness of 25HRC or less after forging.

  On the other hand, the inner ring 40 has an inner raceway surface 3a on the outer periphery, and an uneven portion 29 having a surface hardness of 54 to 64 HRC by heat treatment is formed on the inner periphery. The inner ring 40 is made of a high carbon chrome bearing steel such as SUJ2, and is hardened in the range of 58 to 64 HRC up to the core portion by quenching. Here, the small end face 11 of the inner ring 40 is abutted against the shoulder 12 of the hub ring 39, and the inner ring 40 is externally fitted to the hub ring 39 until it comes into a butted state. Further, a diameter expanding jig such as a mandrel is pushed into the inner diameter of the small diameter step portion 39a of the hub wheel 39 to increase the diameter of the small diameter step portion 39a, and this small diameter step portion 39a is bitten into the uneven portion 29 of the inner ring 40. 39 and the inner ring 40 are integrally plastically coupled.

  In this embodiment, the outer joint member 42 constituting the constant velocity universal joint 41 is fitted into the inner member 38 so as to be able to transmit torque, and the inner member 38 and the outer joint member 42 are detachable via the circlip 43. Are connected in the axial direction.

  Also in the present embodiment, similarly to the above-described embodiment, calculation is made from the measured axial clearance δ1 of the bearing after the inner ring 40 is fitted and the measured end face movement amount ΔL of the outer member 10 before and after the diameter expansion caulking. The axial clearance reduction amount Δδ of the bearing due to the increased diameter caulking, the axial clearance reduction amount Δδ of the bearing due to the increased diameter caulking, and the axial clearance δ1 of the bearing after the inner ring 40 is externally fitted is expanded caulking. Since the axial clearance (negative clearance) δ of the subsequent bearing is obtained, the rotational torque that causes the dispersion factors such as the stirring resistance of the lubricating grease enclosed in the bearing and the squeeze of the seal is not used as a medium. The bearing clearance can be set accurately and stably based on the measured values.

  The embodiment of the present invention has been described above, but the present invention is not limited to such an embodiment, and is merely an example, and various modifications can be made without departing from the scope of the present invention. Of course, the scope of the present invention is indicated by the description of the scope of claims, and further, the equivalent meanings described in the scope of claims and all modifications within the scope of the scope of the present invention are included. Including.

  The wheel bearing device according to the present invention can be applied to a wheel bearing device having a self-retaining structure in which a hub wheel or an outer joint member of a constant velocity universal joint constituting a bearing portion is plastically deformed to form a unit.

It is a longitudinal section showing a 1st embodiment of a bearing device for wheels concerning the present invention. It is explanatory drawing which shows the clearance measuring method of the bearing of an assembly process, (a) shows the process of press-fitting an inner ring in a hub ring, (b) shows the state which press-fitted the inner ring in the hub ring. It is a longitudinal cross-sectional view which shows the wheel bearing apparatus before the crimping process in embodiment of FIG. It is a graph which shows the relationship between the axial direction clearance reduction amount of a bearing, and the end surface movement amount of an outer member. (A) is explanatory drawing which shows the method of measuring the axial direction dimension from a reference plane to the end surface of an outward member. (B) is explanatory drawing which shows the method of measuring the axial direction dimension from another reference surface to the end surface of an outer member. It is a longitudinal cross-sectional view which shows 2nd Embodiment of the wheel bearing apparatus which concerns on this invention. It is explanatory drawing which shows the clearance measuring method of the bearing of an assembly process, (a) shows the process of press-fitting an outer joint member in a hub ring, (b) shows the state which press-fitted the outer joint member in the hub ring. . It is a longitudinal cross-sectional view which shows the wheel bearing apparatus before the diameter expansion caulking in embodiment of FIG. It is a longitudinal cross-sectional view which shows 3rd Embodiment of the wheel bearing apparatus which concerns on this invention. It is a longitudinal cross-sectional view which shows 4th Embodiment of the wheel bearing apparatus which concerns on this invention. (A) is the schematic for demonstrating the prior art. (B) is a graph which shows the change of the crimping position and rotational torque of a rocking type crimping apparatus with respect to the crimping process time.

Explanation of symbols

1, 2, 34, 38... Inner members 2, 18, 31, 39... Hub wheels 2a, 3a, 18a, 22a .. Inner rolling surfaces 2b, 18b, 37a, 39a. Small diameter step 2c ········· Serration 2d ······················································ 4 ... Wheel mounting flange 5 ... Hub bolt 6 ... Roll Moving body 7 ... Cage 8, 9 ... Seal 10 ... Outside Member 10a ... Outer rolling surface 10b ... Car body mounting flange 11 ... Small end face 12, 27, 37 ... shoulder 13 ...・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Inner ring reference surface 14 ・ ・ ・ ・ ・ ・ ・ ・ Hub wheel reference surface 15 ・ ・ ・ ・ ・ ・ ・ ・ Pilot part 16 ・ ・ ・········ Reference surface 17 of outer member ········································································ 20, 33, 41 ... Constant velocity universal joints 22, 36, 42 ... Outer joint member 23 ... Inner joint ring 24 ... ····················································· Torque transmission balls 28, 35 ... In-row parts 28b and 35b ... Fitting part 29 ... Uneven part 30 ...・ Reference surface 43 of the outer joint member ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・・ Circlip B1, B2 ・ ・ ・ ・ ・ ・ Surface L1, L2 ・ ・ ・ ・ ・ ・ Axial dimension S from the reference surface to the end face of the outer member ········ Tap, T1 between the shoulder portion of the hub wheel and the small end surface of the inner ring or the shoulder portion of the outer joint member ··· An axial dimension ΔL between the reference surfaces・ ・ ・ ・ ・ ・ ・ ・ ・ ・ End face movement of outer member Δδ ・ ・ ・ ・ ・ ・ ・ ・ Axial clearance reduction amount δ0, δ1 ・ ・ ・ ・ ・ ・ ・ ・ ・・ Bearing axial clearance 50 ・ ・ ・ ・ ・ ・ ・ ・ Bearing bearing device 51 ・ ・ ・ ・ ・ ・ ・ ・ Preload monitoring device 52 ・ ・ ・ ・ ・ ・ ・ ・...... Outer member 52a ......... Car body mounting flange 53 ......... Gear 54 ... ... Drive gear 55 ...・ ・ ・ ・ Motor 56 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Torque detector 57 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Determinator 58 ・ ・ ・ ・ ・ ・..Oscillating type caulking device 58a ... caulking die 59, 60 ... seal A ... ... Positioning die position T ... Torque torque t, t0, t1 ... Clamping time Δ ... .... Rotational torque fluctuation range

Claims (3)

An outer member integrally having a vehicle body mounting flange on the outer periphery, and a double row outer rolling surface formed on the inner periphery;
A wheel mounting flange is integrally formed at one end, and an inner rolling surface facing one of the double row outer rolling surfaces and a small-diameter step portion extending in the axial direction from the inner rolling surface are formed on the outer periphery. A hub ring, and an inner member that is an inner ring that is press-fitted into a small-diameter step portion of the hub ring and has an inner rolling surface that is opposed to the other outer rolling surface of the double row on the outer periphery;
A double row rolling element that is rotatably accommodated between the inner member and the outer member, and a crimping portion that is formed by plastically deforming the end portion of the small diameter step portion of the hub wheel in the radial direction. In the bearing clearance measuring method of the wheel bearing device in which the inner ring is fixed in the axial direction ,
When press-fitting the annulus to the wheel hub, it stopped once the press-fit clearance is positive state, the axial dimension T0 the initial axial clearance δ0 between the reference surface of the inner wheel and the hub wheel in this state after the actually measured, is pressed to continue the further press-fitting has been completed, the actually measured axial dimension T1 between the reference surface of the hub wheel and the inner wheel, the axial clearance .delta.1 in this state equation δ1 = δ0- (T0 -T1), the end face movement amount is calculated from the difference in the end face position of the outer member measured before and after the plastic coupling of the inner member, and the end face movement amount of the outer member is calculated in advance. By applying the set relationship between the axial clearance reduction amount of the bearing and the end face movement amount of the outer member, the axial clearance reduction amount Δδ of the bearing due to plastic coupling is obtained, and the axial clearance reduction amount Δδ of this bearing is calculated. Before the inner member is plastically bonded A bearing clearance measuring method for a wheel bearing device, characterized in that an axial clearance δ of a bearing after plastic coupling is obtained by subtracting from the actually measured axial clearance δ1.   2. The wheel use according to claim 1, wherein an end face movement amount of the outer member is a difference in axial dimension from a reference surface of the outer member to a reference surface of the hub wheel before and after plastic coupling of the inner member. Bearing clearance measurement method for bearing devices. The wheel according to claim 1 or 2, wherein the position of the end surface of the outer member is measured by placing the wheel bearing device in a vertical state so that a reference surface of the hub wheel contacts a surface plate. For measuring bearing clearance of bearing equipment.

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