JP5069212B2 - Wheel bearing and wheel bearing device provided with the same - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a wheel bearing capable of attaining reduction of weight, size and cost by optimizing wall-thickness of an external member and improving durability of the bearing, and a wheel bearing unit having the wheel bearing. <P>SOLUTION: In the wheel bearing, the external member 7 and an inner ring 8 are formed with plastic working of a pipe material, a circular recessed part 29 is formed on an outer diameter 7b of the external member 7, connecting parts 31 of the circular recessed part 29 to the outer diameter 7b of the external member 7 are formed in an arc shape made of a designated curvature radius R which is approximately concentric with a curvature center of an outside rolling surface 7a, and an inner diameter surface 8d at a large diameter side of the inner ring 8 is formed in an arc shape which is approximately concentric with a curvature center of an inner rolling surface 8a. The external member 7 and the inner ring 8 are set up to be approximately uniform wall-thickness, and when the maximum contact surface pressure received by each rolling surface is 3,000 Mpa or below under conditions of circling acceleration considered at normal running, the wall-thickness Tmo of a groove bottom part and the wall-thickness Tso in a contact angle direction of the external member 7 are set up to be larger than wall-thickness Tmi, Tsi of the inner ring 8 (Tmo&ge;Tmi, Tso&ge;Tsi). <P>COPYRIGHT: (C)2010,JPO&amp;INPIT

Description

  The present invention relates to a wheel bearing for rotatably supporting a wheel of a vehicle such as an automobile, and more particularly, to a wheel bearing for reducing the weight, size and cost, and improving the durability of the bearing. The present invention relates to a wheel bearing device provided.

  2. Description of the Related Art Conventionally, a wheel bearing device for supporting a wheel of an automobile or the like supports a hub wheel for mounting a wheel rotatably via a double row rolling bearing, and includes a drive wheel and a driven wheel. For structural reasons, an inner ring rotation method is generally used for driving wheels, and both an inner ring rotation method and an outer member rotation method are generally used for driven wheels. This wheel bearing device has a structure called a first generation in which a wheel bearing composed of a double-row angular ball bearing or the like is fitted between a knuckle and a hub wheel constituting a suspension device, and is an outer member. 2nd generation structure with body mounting flange or wheel mounting flange formed directly on the outer periphery of the wheel, 3rd generation structure with one inner rolling surface formed directly on the outer periphery of the hub wheel, or constant speed with the hub wheel It is roughly classified into a fourth generation structure in which the inner rolling surface is directly formed on the outer periphery of the outer joint member of the universal joint.

  Conventionally, what is shown in FIG. 6 is known as a wheel bearing composed of a general first generation angular contact ball bearing (see, for example, Patent Document 1). The wheel bearing 50 includes an outer member 51 in which a double-row arc-shaped outer rolling surface 51a is integrally formed on the inner periphery, and an arc-shaped shape facing the double-row outer rolling surfaces 51a and 51a on the outer periphery. A pair of inner rings 52, 52 formed with an inner rolling surface 52 a, and a double row of balls accommodated between the rolling surfaces of the inner ring 52 and the outer member 51 via a retainer 53. 54, 54, and the small-diameter side end faces 52b, 52b of the inner ring 52 abut each other in a butted state to constitute a back-to-back type double row angular ball bearing. Seals 55, 55 are attached to both ends of the outer member 51, and are in sliding contact with the outer diameter of the inner ring 52. Leakage of grease sealed inside the bearing and foreign matter such as rainwater and dust from the outside. It prevents entry into the bearing.

Moreover, the weight reduction wheel bearing shown in FIG. 7 comprised with the angular ball bearing is also known (for example, refer patent document 2). In this wheel bearing 59, the outer member 60 and the inner ring 61 are formed by cold rolling from a pipe material, the outer diameter of the outer member 60 is recessed at the center, and an annular recess 56 is formed. Further, an annular convex portion 57 is formed in a flat shape. The radius of curvature R of the connecting portion between the outer diameter of the outer member 60 and the annular recess 56 is formed in an arc shape in the range of R = 1.5 to 1.8 Rw when the radius of the ball 54 is Rw. This part is set to a substantially uniform thickness. As a result, it is possible to prevent the shoulder 58 from cracking, and to prevent the contact ellipse of the ball 54 from riding on the shoulder 58 when a turning moment is applied, thereby preventing an edge load from being generated. Can be improved. Here, the edge load is an excessive stress concentration generated at a corner or the like, and refers to an event that becomes one of the factors of early peeling.
JP 2007-120771 A JP 2008-256073 A

  When the tire collides with the curb from the side due to slip or the like when the vehicle travels, a shocking moment load is applied to the wheel bearings 50 and 59. In this case, the inner rings 52 and 61 and the outer members 51 and 60 are also loaded. In particular, since the outer members 51 and 60 have a larger dimension from the axial center than the inner rings 52 and 61, this moment is increased. The load increases, and the outer members 51 and 60 are more likely to be damaged than the inner rings 52 and 61.

  However, in the wheel bearing 59, since the outer member 60 and the inner ring 61 are formed to have an equal thickness and the thickness is set to be approximately equal, the risk of the outer member 60 being damaged increases. Here, the outer member 60 and the inner ring 61 may be thickened to increase the strength and rigidity. However, this is not preferable because it goes against weight reduction and the workability decreases, leading to a decrease in accuracy. .

  The present invention has been made in view of such circumstances, and is a wheel that optimizes the thickness of the outer member to reduce the weight, reduce the size, and reduce the cost and improve the durability of the bearing. An object of the present invention is to provide a bearing for a vehicle and a wheel bearing device including the same.

  In order to achieve such an object, the invention according to claim 1 of the present invention includes an outer member in which a double-row arc-shaped outer rolling surface is integrally formed on the inner periphery, and the double-row on the outer periphery. A pair of inner rings formed with an arc-shaped inner rolling surface facing the outer rolling surface, and a plurality of inner rings and a plurality of rolling rings accommodated between the rolling surfaces of the inner member and the outer member via a cage. In a wheel bearing comprising a back-to-back type double row angular contact ball bearing in which the inner diameter of the inner ring abuts in a butted state, and the outer ring and the inner ring are made of plastic material. An annular recess is formed by recessing a central portion of the outer diameter of the outer member, and a connecting portion between the outer diameter and the annular recess is substantially concentric with a center of curvature of the outer rolling surface and has a predetermined curvature. The outer member is formed in a circular arc shape having a radius, and the outer member is set to have a substantially uniform wall thickness. When the maximum contact surface pressure received by each rolling surface is 3000 MPa or less under the condition of turning acceleration considered in traveling, the thickness Tmo of the groove bottom portion of the outer member is the thickness of the groove bottom portion of the inner ring. It is set to be larger than Tmi (Tmo ≧ Tmi).

  In this way, in the wheel bearing constituted by the back-to-back type double row angular contact ball bearings, the outer member and the inner ring are formed by plastic processing from the pipe material, and the central portion of the outer diameter of the outer member is recessed. An annular recess is formed, and the connecting portion between the outer diameter and the annular recess is formed in an arc shape having a predetermined radius of curvature substantially concentric with the center of curvature of the outer rolling surface, and the outer member has a substantially uniform thickness. And the thickness Tmo of the groove bottom portion of the outer member is set to be larger than the thickness Tmi of the groove bottom portion of the inner ring (Tmo ≧ Tmi). In addition, while ensuring a predetermined strength of the inner ring, it is possible to increase the breakage strength of the outer member, improve the durability, and provide a wheel bearing that improves the durability of the bearing. .

  Preferably, as in the invention described in claim 2, the radius of curvature R of the joint portion is set to be in a range of R = 1.5 to 1.8 Rw when the radius of the ball is Rw. In this case, the thickness is not reduced and the rigidity is not lowered, and the thickness is increased and the workability of the plastic working is not lowered.

  Further, as in the invention according to claim 3, the inner diameter surface of the inner ring on the large diameter side is formed in an arc shape substantially concentric with the center of curvature of the inner rolling surface, and the wall thickness of the inner ring is substantially equal. If the thickness Tso in the contact angle direction of the outer member is set to be larger than the thickness Tsi in the contact angle direction of the inner ring (Tso ≧ Tsi), Even if a shocking moment load is applied to the bearing, the damage strength of the outer member can be increased and the durability can be improved.

  Further, as in the invention according to claim 4, if the thickness Tso of the outer member in the contact angle direction is set larger than the thickness Tmo of the groove bottom (Tso> Tmo), this kind In the thin outer member, the strength can be effectively increased.

  Further, as in the invention according to claim 5, if the thickness Tsi of the inner ring in the contact angle direction is set larger than the thickness Tmi of the groove bottom (Tsi> Tmi), this kind of thin wall In the inner ring having a shape, the strength can be effectively increased.

  Further, as in the invention described in claim 6, if the outer member and the inner ring are formed by cold rolling from the pipe material, the thickness can be made substantially uniform, and the shape, The dimensions can be ensured with a predetermined accuracy.

  The invention according to claim 7 of the present invention is a hub wheel having a wheel mounting flange integrally formed at one end and a small-diameter step portion extending in the axial direction from the wheel mounting flange via the shoulder. And a wheel bearing according to any one of claims 1 to 6 which is press-fitted into a small-diameter step portion of the hub wheel through a predetermined squeeze and fitted into a knuckle, and the hub wheel includes a constant velocity universal joint. An outer joint member is fitted through a serration, and the pair of inner rings are sandwiched between a shoulder portion of the hub wheel and a shoulder portion of the outer joint member, and a predetermined bearing preload is applied.

  Thus, in the wheel bearing device of the first generation structure, a hub wheel having a wheel mounting flange integrally formed at one end and a small-diameter step portion extending in the axial direction from the wheel mounting flange via the shoulder is formed. And a bearing for a wheel according to any one of claims 1 to 6 press-fitted into a small-diameter step portion of the hub wheel via a predetermined shishiro, and an outer joint member of a constant velocity universal joint serrated on the hub wheel. And the pair of inner rings are sandwiched between the shoulder part of the hub wheel and the shoulder part of the outer joint member, and a predetermined bearing preload is applied. It becomes a wheel bearing device for a drive wheel with improved rolling fatigue life.

  Further, as in the invention according to claim 8, a space is provided between the outer diameter of the outer member and the knuckle on the line of action in the contact angle direction of the outer member, and / or the inner ring. The inner diameter surface of the large diameter side is formed in an arc shape substantially concentric with the center of curvature of the inner rolling surface, and on the action line in the contact angle direction, the inner diameter surface of the large diameter side and the small diameter step portion of the hub wheel If a space is provided between the two, the weight can be reduced.

  Further, as in the ninth aspect of the invention, the fitting width A between the inner ring and the small-diameter step portion of the hub ring is smaller than the distance B between the intersections of the action line in the contact angle direction and the fitting portion. In addition, if the pitch is set larger than the pitch P between the double rows of balls (P <A <B), a sufficient fitting force to prevent creep between the hub ring and the inner ring while reducing the weight is achieved. Can be secured.

  Further, as in the invention described in claim 10, a wheel mounting flange is integrally formed at one end portion, and a bearing fitting portion and a brake drum portion extending in the axial direction from the inner diameter portion and the outer diameter portion of the wheel mounting flange are provided. A hub drum formed respectively, and a wheel bearing according to any one of claims 1 to 6 press-fitted and fitted into a bearing fitting portion of the hub drum through a predetermined shimoshiro, wherein the bearing for the gravel is a suspension device In the first-generation wheel bearing device, a predetermined bearing preload is applied by fitting the outer ring to the spindle fitting surface, the pair of inner rings being sandwiched between the spindle shoulder and the fixing nut. Thus, the bearing device for a wheel for a driven wheel is obtained in which the bearing rigidity is increased and the rolling fatigue life of the bearing is improved.

  Further, as in the invention described in claim 11, a space is provided between the outer diameter of the outer member and the hub drum on the line of action in the contact angle direction of the outer member, and / or the inner ring. The inner diameter surface of the large diameter side is formed in an arc shape substantially concentric with the center of curvature of the inner rolling surface, and the outer diameter of the fitting surface of the spindle and the inner diameter surface of the large diameter side on the line of action in the contact angle direction If a space is provided between the two, the weight can be reduced.

  The wheel bearing according to the present invention includes an outer member in which a double-row arc-shaped outer rolling surface is integrally formed on the inner periphery, and an arc-shaped inner surface facing the outer-rolling surface of the double-row on the outer periphery. A pair of inner rings on which rolling surfaces are formed, and a double row of balls accommodated between the inner races and the rolling surfaces of the outer member via a cage so as to be freely rollable, and a small diameter of the inner ring In a wheel bearing that forms a back-to-back type double row angular contact ball bearing in which the side end surfaces collide in a butted state, the outer member and the inner ring are formed by plastic processing from a pipe material, and the outer member An annular recess is formed by denting the central portion of the diameter, and the connecting portion of the outer diameter and the annular recess is formed in an arc shape having a predetermined curvature radius substantially concentric with the center of curvature of the outer rolling surface, The outer member is set to a substantially uniform wall thickness, and the condition of turning acceleration considered in normal running When the maximum contact surface pressure received by each rolling surface is 3000 MPa or less, the thickness Tmo of the groove bottom portion of the outer member is larger than the thickness Tmi of the groove bottom portion of the inner ring (Tmo ≧ Tmi). ), So as to achieve light weight, compactness and cost reduction, while ensuring the predetermined strength of the inner ring, it is possible to increase the breaking strength of the outer member and improve the durability, It is possible to provide a wheel bearing in which the durability of the bearing is improved.

  A pair of outer members in which a double-row arc-shaped outer rolling surface is integrally formed on the inner periphery, and an arc-shaped inner rolling surface facing the outer-rolling surface of the double-row is formed on the outer periphery. And an inner ring and a double row of balls accommodated between the inner ring and the rolling surfaces of the outer member via a cage so as to be freely rollable. In the wheel bearing constituting the back-to-back type double row angular contact ball bearing, the outer member and the inner ring are formed by plastic working from a pipe material, and the center part of the outer diameter of the outer member is recessed to form an annular shape. A concave portion is formed, and a connecting portion between the outer diameter and the annular concave portion is formed in an arc shape having a predetermined curvature radius substantially concentric with the center of curvature of the outer rolling surface, and an inner diameter surface on the larger diameter side of the inner ring Is formed in an arc shape substantially concentric with the center of curvature of the inner rolling surface, and the outer member and the inner ring are When the maximum contact surface pressure that each rolling surface receives is 3000 MPa or less under the condition of turning acceleration that is set to an equal thickness and considered in normal traveling, the thickness Tmo of the groove bottom portion of the outer member is The wall thickness Tso in the contact angle direction is set to be larger (Tmo ≧ Tmi, Tso ≧ Tsi) than the wall thickness Tmi of the groove bottom portion of the inner ring and the wall thickness Tsi in the contact angle direction.

Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.
1 is a longitudinal sectional view showing an embodiment of a wheel bearing device according to the present invention, FIG. 2 is an enlarged view showing the wheel bearing of FIG. 1, and FIG. 3 (a) is an outer member of FIG. FIG. 4 is a longitudinal sectional view showing a single inner ring of FIG. 2, FIG. 4 is an explanatory view showing a manufacturing process of an outer member according to the present invention, and FIG. 5 is according to the present invention. It is a longitudinal cross-sectional view which shows other embodiment of the wheel bearing apparatus. In the following description, the side closer to the outer side of the vehicle when assembled to the vehicle is referred to as the outer side (left side in FIG. 1), and the side closer to the center is referred to as the inner side (right side in FIG. 1).

  This wheel bearing device has a first generation structure, and includes a hub wheel 1 and a wheel bearing 2 attached to the hub wheel 1. A constant velocity universal joint 3 is fitted into the hub wheel 1 so as to be able to transmit torque, and the hub wheel 1 and the constant velocity universal joint 3 are detachably integrated via a fixing nut 4.

  The hub wheel 1 has a wheel mounting flange 5 for mounting a wheel (not shown) at one end portion on the outer side, and a cylindrical shape extending from the wheel mounting flange 5 to the outer periphery in the axial direction via a shoulder portion 1a. A small-diameter step portion 1b is formed, and a serration (or spline) 1c for torque transmission is formed on the inner periphery. This hub wheel 1 is made of medium-high carbon steel containing 0.40 to 0.80 wt% of carbon such as S53C, and is not heat-treated after forging, and the structure remains raw. In addition, a method of performing a tempering treatment after forging in order to increase the fatigue strength with respect to the bending strength, or by subjecting the surface hardness to a range of 58 to 64 HRC by induction hardening from the shoulder portion 1a to the small diameter step portion 1b. May be.

  The constant velocity universal joint 3 includes an outer joint member 15, a joint inner ring 16, a cage 17 and a torque transmission ball 18. The outer joint member 15 integrally includes a cup-shaped mouth portion 19, a shoulder portion 20 that is a bottom portion of the mouth portion 19, and a shaft portion 21 that extends from the shoulder portion 20 in the axial direction. A serration 21a that engages with the serration 1c of the hub wheel 1 is formed on the outer periphery of the shaft portion 21, and a male screw 21b is formed at the end of the serration 21a.

  The wheel bearing 2 includes an outer member 7, a pair of inner rings 8, 8, and double-row balls 10, 10 accommodated between the two members, and the outer member 7 forms a knuckle 6 that constitutes a suspension device. While being fitted, the pair of inner rings 8, 8 is press-fitted into the small-diameter step portion 1b of the hub wheel 1 via a predetermined squeeze. The small-diameter side (front side) end faces 8b, 8b of the inner rings 8, 8 are abutted in a butted state to constitute a so-called back-to-back type double row angular ball bearing. Further, the outer joint member 15 is internally fitted to the hub wheel 1 through the serrations 1c and 21a until the shoulder portion 20 of the outer joint member 15 abuts on the large-diameter side (rear) end surface 8c of the inner ring 8. The inner rings 8 and 8 are fixed in a state of being sandwiched between the shoulder portion 1 a of the hub wheel 1 and the shoulder portion 20 of the outer joint member 15. Further, a predetermined bearing preload is applied to the male screw 21b by tightening the fixing nut 4 with a predetermined tightening torque. As a result, the bearing rigidity for the drive wheel is improved and the rolling fatigue life of the bearing is improved.

  As shown in an enlarged view in FIG. 2, the wheel bearing 2 has double rows of arc-shaped outer rolling surfaces 7 a and 7 a formed on the inner periphery of the outer member 7, and the outer sides of these double rows on the outer periphery. Arc-shaped inner rolling surfaces 8a and 8a facing the rolling surfaces 7a and 7a are formed on the pair of inner rings 8 and 8, respectively. A double row of balls 10 and 10 are accommodated between the rolling surfaces via the cages 9 and 9 so as to roll freely, and an annular space formed between the outer member 7 and the inner ring 8 is accommodated. Seals 11 and 12 are attached to the openings to prevent leakage of grease sealed inside the bearing and foreign matters such as rainwater and dust from entering the bearing from the outside.

  The outer-side seal 11 is integrally joined to a cored bar 22 that is press-fitted into a cylindrical fitting part 13 formed at both ends of the outer member 7, and vulcanized and bonded to the cored bar 22. An integral seal composed of a seal member 23 made of an elastomer such as rubber is formed. The metal core 22 has a substantially L-shaped cross section by pressing an austenitic stainless steel plate (JIS standard SUS304, etc.) or a rust-proof cold rolled steel plate (JIS standard SPCC, etc.). Is formed. Further, the seal member 23 includes a pair of radial lips 23a and 23b which are slidably contacted with the shoulder portion 14 of the inner ring 8 via a predetermined shimoshiro.

  The inner-side seal 12 constitutes a so-called pack seal composed of an annular seal plate 24 and a slinger 25 having a substantially L-shaped cross section. The seal plate 24 includes a metal core 26 that is press-fitted into the fitting portion 13 of the outer member 7, and a seal member 27 that is integrally vulcanized and bonded to the metal core 26. The metal core 26 has a substantially L-shaped cross section by pressing an austenitic stainless steel plate (JIS standard SUS304 type or the like) or a rust-proof cold rolled steel plate (JIS standard SPCC type or the like). Is formed. Further, the seal member 27 includes a side lip 27a extending obliquely outward in the radial direction, a grease lip 27b and an intermediate lip 27c formed in a bifurcated shape.

  On the other hand, the slinger 25 is composed of an austenitic stainless steel plate (JIS standard SUS304 type or the like), a ferritic stainless steel plate (JIS standard SUS430 type or the like), or a rust-proof cold rolled steel plate (JIS standard type). A cylindrical portion 25a whose cross section is formed in a substantially L shape by press working, and a vertical plate portion 25b extending radially outward from the cylindrical portion 25a. Consists of. The side lip 27a of the seal member 27 is slidably contacted with the standing plate portion 25b, and the grease lip 27b and the intermediate lip 27c are respectively slidably contacted with the cylindrical portion 25a.

  Here, the outer member 7 and the inner ring 8 are formed by pressing or cold rolling (hereinafter referred to as plastic working) a pipe material made of bearing steel such as SUJ2 or carburized steel such as SCr420 or SCM415. . Specifically, as shown in FIG. 4A, a billet 33 cut to a predetermined size from a steel bar 32 is formed into a pipe material 34 as a material by hot forging and turning, or (b ), The steel pipe 35 is cut into a predetermined dimension and formed into a pipe material 36 as a material. In the case where the pipe members 34 and 36 manufactured in such a process are the outer member 7 as shown in (c), the inner peripheral die 37 and the outer periphery are inserted in the outer peripheral die 37. The pipe members 34 and 36 are formed into a predetermined shape and size by being sandwiched between the molds 38 and being brought close to each other while rotating both molds 37 and 38 in opposite directions. Here, the pipe materials 34 and 36 used as the material are thinned by the two molds 37 and 38, and accordingly, are also rolled in the width direction, but both end surfaces are regulated by the flange portions 38 a of the outer peripheral mold 38. Thus, the outer member 7 with higher accuracy can be manufactured.

  Then, SUJ2 is hardened to a surface hardness of 58 to 64 HRC by submerged or induction hardening, and carburized steel is carburized and quenched. Other examples of the material of the outer member 7 and the inner ring 8 include stainless steel such as SUS440C and carbon steel such as S53C.

  On the other hand, in the case of carbon steel, at least in the outer member 7, the double row outer rolling surfaces 7a, 7a are subjected to a hardening process within a range of 58 to 64 HRC by overall heating by induction hardening, and the inner ring In No. 8, the inner rolling surface 8a is subjected to a hardening process within a range of 58 to 64 HRC by overall heating by induction hardening. And these both rolling surfaces 7a and 8a are formed with a predetermined | prescribed dimension and precision by grinding, and super-finishing is given after that as needed.

Next, the configuration of the outer member 7 and the inner ring 8 will be described in detail with reference to FIG.
As shown in (a), the outer member 7 is formed by forming a circular projection 28 projecting radially inward from the pipe material used as a raw material, and a double row on both sides of the annular projection 28. Arc-shaped outer rolling surfaces 7a, 7a are formed, and fitting portions 13, 13 of the seals 11, 12 are formed at both ends. And the fitting part 13 including the double row outer rolling surfaces 7a and 7a is formed with a predetermined size and accuracy by grinding after the heat treatment after plastic working. Note that both end faces where burrs are generated by plastic working are turned after machining, and further subjected to grinding after heat treatment if necessary. As a result, productivity is improved, yield is improved, cost can be reduced, and accuracy and sealing performance equivalent to those of conventional bearings can be secured.

  Here, in order to appropriately secure the shoulder height of the annular convex portion 28 from the outer rolling surface 7a, the inner diameter of the annular convex portion 28 is formed in a flat shape during plastic processing of the outer member 7, and the outer side The center portion of the member 7 is recessed to form an annular recess 29 so that the shoulder 30 is filled with the material.

  Further, the radius of curvature R of the connecting portion 31 between the outer diameter 7b of the outer member 7 and the annular recess 29 is set within a predetermined range, and the outer member 7 moves outward on the line of action in the contact angle α direction. A space is provided between the outer diameter 7 b of the member 7 and the knuckle 6. Specifically, the connecting portion 31 and the center of curvature of the outer rolling surface 7a are set to be substantially the same position, and when the radius of the ball 10 is Rw, the curvature radius R = 1.5˜ The range is set to 1.8 Rw. As a result, the thickness of this portion can be formed substantially evenly, and the shoulder 30 can be prevented from cracking, and the contact ellipse of the ball 10 can ride on the shoulder 30 when a turning moment is applied, and the edge load is reduced. It is possible to provide the wheel bearing 2 that can prevent the occurrence and improve the durability of the bearing.

  When the radius of curvature R of the connecting portion 31 is smaller than 1.5 times the radius Rw of the ball 10, the thickness is reduced and the rigidity is reduced, so that it cannot withstand the stress during moment loading. If it exceeds 1.8 times of Rw, not only will the wall thickness increase and the workability of plastic working will decrease, but the shape will not greatly differ from conventional forged products, and it will not contribute to light weight and compactness in general. It is. Here, “substantially equal” means that the thickness of the pipe material before molding is uniform, and the thickness of the shape obtained as a result of molding without any plastic flow other than the purpose of forming the arc portion of the connecting portion 31 as well. This means that a state where the thickness of the connecting portion 31 is slightly thin or thick due to the displacement of the material when the arc is formed is included.

  On the other hand, as shown in (b), the inner ring 8 has an arcuate inner rolling surface 8a on the outer periphery and a cylindrical shape extending in the axial direction from the inner rolling surface 8a by plastic processing from a pipe material as a material. A shoulder 14 is formed. Here, the shoulder portion 14 serves as a mating surface for the seal land portion of the outer seal 11 and the inner seal 12 and is ground by a grinding wheel simultaneously with the inner rolling surface 8a after heat treatment after plastic working. , Formed with predetermined dimensions and accuracy. As with the outer member 7, both end faces where burrs are generated by plastic working are turned after machining, and further subjected to grinding after heat treatment as necessary. As a result, productivity is improved, yield is improved, cost can be reduced, and accuracy and sealing performance equivalent to those of conventional bearings can be secured.

  Generally, the inner raceway surface of the inner ring is different from the outer raceway surface of the outer member, and the radius of curvature of the inner raceway surface of the inner ring is set smaller than the radius of curvature of the outer raceway surface of the outer member. However, the contact surface pressure received by each rolling surface during turning of the vehicle is such that the inner rolling surface of the inner ring is in a contact state between the ball and the convex, so that the inner ring is higher than the outer member. Therefore, especially when thin inner rings and outer members are used, the contact surface pressure that each rolling surface receives during turning travels on the action line in the contact angle direction on the outer diameter side of the outer member and the inner diameter side of the inner ring. The stress must be below the critical value for failure. Therefore, the thickness in the contact angle direction is set so that the thickness of the inner ring is equal to the thickness of the outer member, or the inner ring is slightly thicker than the outer member.

  However, under the condition of turning G (acceleration) that can be considered in normal driving, the results of verification by the present applicant show that when the maximum contact surface pressure received by each rolling surface is 3000 MPa or less, the contact angle direction of the inner ring On the inner diameter side on the action line, the stress amplitude is sufficiently small. For example, a bearing steel such as SUS2 has a fatigue limit value of 610 MPa or less without quenching and after grinding. In addition, when a shock moment load is applied to the wheel bearing, the limit value at which the inner ring is not damaged is, for example, a tensile strength after quenching and tempering of 1800 MPa or less for bearing steel such as SUS2. Here, in the present embodiment, with the inner ring 8 having such strength, the thickness Tso of the outer member 7 in the contact angle α direction is thicker than the thickness Tsi of the inner ring 8 in the contact angle α direction. It is set (Tso ≧ Tsi). Thereby, even if an impact moment load is applied to the wheel bearing 2 while ensuring a predetermined strength of the inner ring 8, the breaking strength of the outer member 7 can be increased and the durability can be improved.

  Also, the thickness Tmo and Tmi of the groove bottom portions of the outer member 7 and the inner ring 8 are set so that the thickness Tmo of the groove bottom portion of the outer member 7 is thicker than the thickness Tmi of the groove bottom portion of the inner ring 8. (Tmo ≧ Tmi). Thereby, the breaking strength of the outer member 7 can be increased and the durability can be improved. In the thin outer member 7 and the inner ring 8 of this type, the thicknesses Tso and Tsi in the contact angle direction dominate with respect to the strength rather than the thicknesses Tmo and Tmi at the groove bottoms of the rolling surfaces 7a and 8a. Therefore, the thickness Tso of the outer member 7 in the direction of the contact angle α is set to be larger than the thickness Tmo of the groove bottom (Tso> Tmo). Similarly, the thickness Tsi of the inner ring 8 in the contact angle α direction is set to be larger than the thickness Tmi of the groove bottom (Tsi> Tmi).

  Incidentally, the applicant of the present invention rearranged one of the outer member and the inner ring into a thin shape with respect to the conventional shape product of the wheel bearing, and carried out a comparative test of each rigidity. As a result, the conventional shape shown in FIG. On the other hand, it has been found that the rate of decrease in rigidity is greater when the outer member is made thinner than when the inner ring is made thinner. That is, in reducing the thickness of the outer member, reducing the thickness of the outer member more than the thickness of the inner ring can effectively suppress a decrease in bearing rigidity and improve steering stability. it can. Furthermore, if the inner ring on the rotating side is made thinner than the outer member to reduce the weight, the inertial force due to the rotation will decrease, and the acceleration / deceleration of the wheel rotation will become smoother, improving the steering stability. it can.

  Further, in the present embodiment, the inner diameter surface 8d on the large diameter side of the inner ring 8 is formed in an arc shape substantially concentric with the center of curvature of the inner rolling surface 8a, and the thickness of the inner ring 8 is set to be substantially equal. In addition, a space is provided between the large-diameter inner diameter surface 8d and the small-diameter step portion 1b of the hub wheel 1 on the line of action in the contact angle α direction, and the inner ring 8 is fitted as shown in FIG. The fitting width A with the portion (the small diameter step portion 1b of the hub wheel 1) is smaller than the distance B between the intersections of the action line in the contact angle α direction and the fitting portion, and the double row balls of the wheel bearing 2 It is set to be larger than the pitch P between 10. As a result, it is possible to ensure a sufficient fitting force to prevent creep between the hub wheel 1 and the inner ring 8 while reducing the weight. Here, creep refers to a phenomenon in which the bearing surface slightly moves in the circumferential direction due to a lack of mating squealing or poor mating surface processing accuracy, and the mating surface becomes a mirror surface, and in some cases, seizure or welding occurs with galling. .

  FIG. 5 shows another embodiment of the wheel bearing device according to the present invention. This wheel bearing device also has a first generation structure, and includes a hub drum 39 and a wheel bearing 2 fitted inside the hub drum 39. The wheel bearing 2 is externally fitted to the spindle 40 of the suspension device, and the wheel bearing 2 and the spindle 40 are integrated in a separable manner via the fixing nut 4. In this embodiment, the configuration of the wheel bearing 2 is the same as that described above, and the same components and parts are denoted by the same reference numerals and redundant description is omitted.

  The hub drum 39 has a wheel mounting flange 5 for mounting a wheel (not shown) at one end portion on the outer side, and a cylindrical brake drum portion 39a extending in the axial direction from the outer diameter portion of the hub flange 5 is formed. In addition, a cylindrical bearing fitting portion 39b extending in the axial direction from the inner diameter portion of the hub flange 5 is formed. The hub drum 39 is made of cast iron such as gray cast iron or spheroidal graphite cast iron. A brake shoe (not shown) is pressed against the brake drum portion 39a to generate a braking force. Further, a retaining ring mounting groove 42 is provided on the inner diameter of the inner side of the bearing fitting portion 39b, and a wheel that is press-fitted into the bearing fitting portion 39b via a predetermined shimiro by mounting the retaining ring 41. This prevents the bearing 2 from coming off.

  The spindle 40 has a shoulder portion 43 on the inner side, a shaft portion 44 extending in the axial direction from the shoulder portion 43, and a male screw 21 b formed at an end portion of the shaft portion 44. The spindle 40 is provided as an integral part at the end of the suspension apparatus by screwing or as a separate part from the suspension apparatus or by joining means such as welding.

The wheel bearing 2 press-fitted into the hub drum 39 is moved to the spindle 40 until it abuts against the shoulder 43.
And a pair of inner rings 8, 8 are fixed in a state of being sandwiched between the shoulder 43 of the spindle 40 and the fixing nut 4. Further, a predetermined bearing preload is applied to the male screw 21b by tightening the fixing nut 4 with a predetermined tightening torque. As a result, a bearing device for a wheel for a driven wheel in which the outer member whose bearing rigidity is increased and the outer member whose rolling fatigue life is improved is rotated.

  Here, in this embodiment, as in the above-described embodiment, the thickness Tmo of the groove bottom portion of the outer member 7 and the thickness Tso of the contact angle direction are equal to the thickness Tmi of the groove bottom portion of the inner ring 8 and the contact angle direction. Since each thickness is set to be larger than the wall thickness Tsi (Tmo ≧ Tmi, Tso ≧ Tsi), an impulsive moment load is applied to the wheel bearing 2 while ensuring a predetermined strength of the inner ring 8. Also, the breaking strength of the outer member 7 can be increased and the durability can be improved.

  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.

  A wheel bearing device according to the present invention includes a hub ring integrally having a wheel mounting flange at one end and a pair of inner rings press-fitted into the hub wheel, and a wheel bearing device having a first generation structure and one end. The present invention can be applied to a wheel bearing device of a first generation structure including a hub drum integrally having a wheel mounting flange at a portion and a pair of inner rings press-fitted into the hub drum.

It is a longitudinal section showing one embodiment of a wheel bearing device concerning the present invention. It is an enlarged view which shows the wheel bearing of FIG. (A) is a longitudinal cross-sectional view which shows the outer member ring single-piece | unit of FIG. (B) is the longitudinal cross-sectional view which shows an inner ring single-piece | unit as above. It is explanatory drawing which shows the manufacturing process of the outward member which concerns on this invention. It is a longitudinal cross-sectional view which shows other embodiment of the wheel bearing apparatus which concerns on this invention. It is a longitudinal cross-sectional view which shows the conventional wheel bearing. It is a longitudinal cross-sectional view which shows the other conventional wheel bearing.

Explanation of symbols

1 ····················· Hub wheel 1a, 14, 20, 30, 43 ... shoulder 1b ... Stepped portion 1c, 21a ... Serration 2 ... Wheel bearing 3 ...・ ・ ・ ・ Constant velocity universal joint 4 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Fixing nut 5 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Wheel mounting flange 6 ・ ・.... Knuckle 7 ... Outer member 7a ...・ Outer rolling surface 7b ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Outer diameter 8 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Inner ring 8a ・ ・ ・ ・ ・ ・ ・ ・・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Inner rolling surface 8b ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Small diameter side end surface 8c ・ ・ ・ ・ ・ ・ ・ ・ ・ ・··· Large diameter side end face 8d ····· Large diameter side inner diameter surface 9 ·············· Retainer 10・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Ball 11 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Outer seal 12 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・.... Inner side seal 13 ... Fitting part 15 ... Outer joint member 16 ...・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Fitting inner ring 17 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Cage 18 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Torque transmission ball 19 ・······················· Mouse portion 21, 44 ·············· Shaft portion 21b ·················· Male screw 22 , 26 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Core 23,27 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Sea Members 23a, 23b ... Radial lip 24 ... Seal plate 25 ... Slinger 25a ···························································.・ Side lip 27b ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Grease lip 27c ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Intermediate lip 28 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・... annular protrusion 29 ... annular depression 31 ... connector 32 ... ... steel bar 33 ... billet 34, 36 ... pipe material 35 ...・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Steel pipe 37 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・...... Inner peripheral mold 38 ......... Outer peripheral mold 38a ... ······························································· Brake drum portion 39b・ ・ ・ ・ ・ ・ ・ ・ Spindle 41 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Retaining ring 42 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・Retaining ring mounting groove 50, 59 ... Wheel bearing 51, 60 ... Outer member 51a ...・ ・ ・ ・ ・ Outer rolling surface 52, 61 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Inner ring 52a ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Inner rolling surface 52b ・ ・ ・········ Small diameter side end face 53・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Ball 55 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Seal 56 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Ring recess 57 ... Annular convex part 58 ... Shoulder part A ...・ ・ ・ ・ Fitting width B with the inner ring fitting part ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Intersection distance P between the action line in the contact angle direction and the fitting part・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Double-row pitch R between balls ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Round of curvature Rw ・ ・ ・ ・ ・ ・··· Ball radius Tmi ························ Thickness Tmo of the groove bottom portion of the inner ring Thickness Tsi of the inner ring Tso thickness in the contact angle direction of the inner ring ... Contact angle direction of the thick alpha · · · · · · the contact angle of the outer member

Claims (11)

An outer member in which a double-row arc-shaped outer rolling surface is integrally formed on the inner periphery;
A pair of inner rings each having an arcuate inner rolling surface facing the double row outer rolling surface on the outer periphery;
These inner rings and double rows of balls accommodated between the rolling surfaces of the outer member via a cage to be freely rollable,
In the wheel bearing that the end surface on the small diameter side of the inner ring abuts in a butted state and constitutes a back-to-back type double row angular contact ball bearing,
The outer member and the inner ring are formed by plastic working from a pipe material, a central portion of the outer diameter of the outer member is recessed to form an annular recess, and the joint between the outer diameter and the annular recess is the outer rolling It is formed in an arc shape having a predetermined radius of curvature that is substantially concentric with the center of curvature of the surface, and the outer member is set to a substantially uniform wall thickness, When the maximum contact surface pressure received by the rolling surface is 3000 MPa or less, the thickness Tmo of the groove bottom of the outer member is set to be larger than the thickness Tmi of the groove bottom of the inner ring (Tmo ≧ Tmi). The wheel bearing characterized by being made.   2. The wheel bearing according to claim 1, wherein a radius of curvature R of the joint portion is set to be in a range of R = 1.5 to 1.8 Rw, where Rw is a radius of the ball.   An inner diameter surface on the large diameter side of the inner ring is formed in an arc shape substantially concentric with the center of curvature of the inner rolling surface, and the thickness of the inner ring is set to be substantially equal, and the outer member The wheel bearing according to claim 1 or 2, wherein a wall thickness Tso in the contact angle direction is set to be larger than a wall thickness Tsi in the contact angle direction of the inner ring (Tso ≧ Tsi).   4. The wheel bearing according to claim 1, wherein a wall thickness Tso in a contact angle direction of the outer member is set larger than a wall thickness Tmo of the groove bottom portion (Tso> Tmo).   The wheel bearing according to any one of claims 1 to 4, wherein a wall thickness Tsi in the contact angle direction of the inner ring is set larger than a wall thickness Tmi of the groove bottom portion (Tsi> Tmi).   The wheel bearing according to claim 1, wherein the outer member and the inner ring are formed by cold rolling from a pipe material.   A hub wheel integrally having a wheel mounting flange at one end and having a small-diameter step portion extending in the axial direction from the wheel mounting flange via a shoulder portion, and a predetermined squeeze through a small-diameter step portion of the hub wheel The wheel bearing according to any one of claims 1 to 6 is press-fitted and fitted into a knuckle, and an outer joint member of a constant velocity universal joint is fitted into the hub wheel via a serration. An inner ring is sandwiched between a shoulder portion of the hub wheel and a shoulder portion of the outer joint member, and a predetermined bearing preload is applied to the wheel bearing device.   On the line of action in the contact angle direction of the outer member, a space is provided between the outer diameter of the outer member and the knuckle, and / or the inner diameter surface on the large diameter side of the inner ring is the inner rolling surface. A space is provided between the large-diameter inner diameter surface and the small-diameter step portion of the hub wheel on the line of action in the contact angle direction. The wheel bearing device described.   A fitting width A between the inner ring and the small-diameter step portion of the hub wheel is smaller than a distance B between intersections of the action line in the contact angle direction and the fitting portion, and larger than the pitch P between the balls in the double row. The wheel bearing device according to claim 7 or 8, wherein the wheel bearing device is set (P <A <B).   A hub drum integrally having a wheel mounting flange at one end, and having a bearing fitting portion and a brake drum portion extending in an axial direction from the inner diameter portion and the outer diameter portion of the wheel mounting flange, and the bearing fitting portion of the hub drum And the wheel bearing according to any one of claims 1 to 6, wherein the pair of scintillating bearings are externally fitted to a fitting surface of a spindle of a suspension device, The wheel bearing device is characterized in that the inner ring is sandwiched between the shoulder portion of the spindle and a fixing nut and given a predetermined bearing preload.   On the line of action in the contact angle direction of the outer member, a space is provided between the outer diameter of the outer member and the hub drum, and / or the inner diameter surface on the large diameter side of the inner ring is the inner rolling surface. The space is provided between the inner diameter surface on the large diameter side and the outer diameter of the fitting surface of the spindle on the line of action in the contact angle direction. The wheel bearing apparatus described in 1.

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