WO2010110355A1

WO2010110355A1 - Bearing device for wheel

Info

Publication number: WO2010110355A1
Application number: PCT/JP2010/055186
Authority: WO
Inventors: 平井功
Original assignee: Ntn株式会社
Priority date: 2009-03-27
Filing date: 2010-03-25
Publication date: 2010-09-30

Abstract

A bearing device for a wheel, wherein the wall thickness of the inner ring is optimized to reduce the weight of the device and to make the device compact and wherein the device is low cost achieved by reducing the storage space in the manufacturing process and by making the manufacturing process more efficient. The connection section (31) between an annular recess (29) and each outer-diameter surface (7b) of an outer member (7) is formed in a circular arc shape substantially concentric with the curvature center of each outer rolling surface (7a) to make the wall thickness of the outer member (7) substantially uniform, and the inner-diameter surface (8d) of an inner ring (8) on the large-diameter side thereof is formed in a circular arc shape substantially concentric with the curvature center of an inner rolling surface (8a) to make the wall thickness of the inner ring (8) substantially uniform. The wall thickness (Tmi) of the bottom groove section of the inner rolling surface (8a) is set to be greater than the wall thickness (Tmo) of the bottom groove section of the outer rolling surface (7a) (Tmi ≥ Tmo), the wall thickness (Ti) of the inner ring (8) in the direction of contact angle is set to be greater than the wall thickness (To) of the outer member (7) in the direction of contact angle (Ti ≥ To), and the inner diameter (d1) of a shoulder section (13) is set to be greater than the outer diameter (d2) of the end section (14) on the small-diameter side (φd1 > φd2).

Description

Wheel bearing device

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a wheel bearing device that rotatably supports a wheel of a vehicle such as an automobile, and more particularly, to a wheel bearing device that achieves weight reduction, compactness, and cost reduction and also improves bearing durability. Is.

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. 7 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 and 56 are attached to the opening of the annular space formed between the outer member 51 and 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.

JP 2007-120771 A

This type of wheel bearing is required to reduce the manufacturing cost as well as to make the bearing lighter and more compact. Here, downsizing of the processing equipment and space saving and efficiency improvement of the storage space in the manufacturing process greatly affect the manufacturing cost. Usually, in the manufacturing process, for example, as shown in FIG. 8, the inner ring 52 of the wheel bearing 50 may be aligned in the same direction in the axial direction and stacked and stored in a plurality of stages, or may be put on standby. In this case, in the conventional inner ring 52, the height H0 of the laminated inner rings 52 is increased, and the position of the inner ring 52 is not stable depending on the shape and dimensions of the chamfered portion 57. For example, a support 58 is installed on the inner diameter side. Even if the fall is prevented, the inner ring 52 is tilted and it is difficult to orderly stack in the same direction. This not only makes it difficult to save the storage space, but also hinders workability and increases manufacturing costs.

The present invention has been made in view of such circumstances, and is designed to reduce the weight and size of the inner ring by optimizing the thickness of the inner ring, and to save space and increase the efficiency of the storage space in the manufacturing process. It aims at providing the bearing device for wheels which achieved cost reduction.

In order to achieve such an object, the present invention provides an outer member in which a double-row arc-shaped outer rolling surface is integrally formed on the inner periphery, and a double-row facing the outer rolling surface of the double-row on the outer periphery. An inner member formed of at least one inner ring formed with an arc-shaped inner rolling surface, and is accommodated between the inner member and the outer member via a cage between the rolling surfaces of the inner member and the outer member. In the wheel bearing device comprising a plurality of rows of balls and a seal attached to an opening of an annular space formed between the outer member and the inner member, the inner raceway on the inner ring A cylindrical shoulder extending in the axial direction from the large-diameter side of the inner ring, and a cylindrical small-diameter side end extending in the axial direction from the small-diameter side of the inner rolling surface are formed. 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 set substantially equal, The inner diameter of the section is set larger than the outside diameter of the end portion of the small diameter side (claim 1).

Thus, a cylindrical shoulder extending in the axial direction from the large diameter side of the inner rolling surface and an end portion on the cylindrical small diameter side extending in the axial direction from the small diameter side of the inner rolling surface are formed on the inner ring, The inner ring surface on the large diameter side of the inner ring is formed in an arc shape that is substantially concentric with the center of curvature of the inner rolling surface, and the wall thickness of the inner ring is set to be substantially uniform, and the inner diameter of the shoulder portion is the end on the small diameter side The outer diameter of the inner ring is set to be larger than the outer diameter of the inner ring, so that the inner ring thickness is optimized to reduce weight and size, and the inner ring is aligned in the same direction in the manufacturing process and stacked in multiple stages. In this case, the end on the small diameter side is housed in the inner diameter part of the shoulder, the position of the inner ring is stabilized without increasing the height of the stacked inner rings, and the stacking can be done in the same direction, saving space. Thus, it is possible to provide a wheel bearing device that achieves cost reduction by improving efficiency.

Preferably, as in the present invention, when the inner ring is formed from a pipe material by plastic working and the radius of curvature Ri of the inner diameter surface on the large diameter side of the inner ring is Rw, the radius of the ball is Ri = 1. If it is set to be in the range of 5 to 1.8 Rw, the wall thickness will not increase and the workability of plastic working will not be reduced, the generated stress will be below the fatigue limit, and the fatigue strength will be secured. Bearing rigidity can be obtained, and the breaking strength can be increased. Further, it is possible to prevent the shoulder from cracking, and to prevent the contact ellipse of the ball from riding on the shoulder when the turning moment is applied and the edge load from being generated (claim 2).

Further, as in the present invention, when the outer member is formed from a pipe material by plastic working, and the curvature radius Ro of the joint portion of the outer member is Rw, the radius of the ball is Ro = 1.5. If it is set to be in the range of ~ 1.8 Rw, the thickness is reduced and the rigidity is not lowered, and the thickness is increased and the workability of the plastic working is not lowered. 3).

Further, as in the present invention, the outer member is formed from a pipe material by plastic working, and an annular convex portion projecting radially inward between the outer rolling surfaces of the inner circumferential double row, and the outer circumferential center An annular recess is formed in the portion, and the outer diameter surface of the outer member and the connecting portion of the annular recess are formed in an arc shape substantially concentric with the center of curvature of the outer rolling surface, and the outer member is substantially If the thickness Tmi of the groove bottom portion of the inner rolling surface is set to be equal to the thickness Tmo larger than the thickness Tmo of the groove bottom portion of the outer rolling surface (Tmi ≧ Tmo), It is possible to reduce the weight and size of the inner ring and to optimize the wall thickness of the inner ring to ensure a predetermined strength, while increasing the breaking strength of the outer member and improving the durability of the bearing. ).

Further, as in the present invention, if the thickness Ti in the contact angle direction of the inner ring is set to be thicker than the thickness To in the contact angle direction of the outer member (Ti ≧ To), the outer ring The strength and durability of the inner ring having a higher surface pressure than the member can be improved, and the durability of the bearing can be improved.

Further, as in the present invention, the thickness To in the contact angle direction of the outer member is set to be larger than the thickness Tmo of the groove bottom portion of the outer rolling surface (To ≧ Tmo), and the inner ring If the thickness Ti in the contact angle direction is set larger than the thickness Tmi of the groove bottom portion of the inner rolling surface (Ti ≧ Tmi), the strength and rigidity can be improved while achieving weight reduction. (Claim 6).

Further, as in the present invention, the inner member is composed of a pair of inner rings, and the fitting width A between the inner diameter surface of these inner rings and the mating member into which the inner ring is press-fitted is in contact with the extension of the inner diameter surface. If the distance between the intersection points B with the angular action line is set to be larger than the pitch P of the double row balls (P <A <B), the hub ring and the inner ring are reduced in weight. It is possible to ensure a sufficient fitting force to prevent creep between the two (claim 7).

Further, as in the present invention, the inner member integrally has a wheel mounting flange for mounting a wheel at one end, and a cylindrical small-diameter step portion extending in the axial direction from the wheel mounting flange is formed. The small-diameter step portion in a state of being in close contact with the inner-diameter surface of the large-diameter side of the inner ring, and comprising a hub wheel and the inner ring press-fitted into the small-diameter step portion of the hub ring through a predetermined shimiro If the inner ring is fixed in the axial direction with respect to the hub ring with a predetermined bearing preload applied by plastic deformation of the end of While being able to achieve compactness, it is possible to secure a desired axial force by pressing the inner diameter surface of the inner ring on the large diameter side with the crimping portion.

Further, as in the present invention, the outer member is fitted into the knuckle, and a space is provided between the outer member and the knuckle on the line of action in the contact angle direction, and / or the inner ring If a space is provided between the inner ring and the small-diameter step portion of the hub wheel on the line of action in the contact angle direction, the weight can be reduced (Claim 9).

Further, as in the present invention, if the outer member and the inner ring are formed by cold rolling, the thickness can be made substantially uniform, and the shape and dimensions can be ensured with a predetermined accuracy. (Claim 10).

A wheel bearing device according to the present invention includes an outer member in which a double-row arc-shaped outer rolling surface is integrally formed on an inner periphery, and a double-row facing the outer rolling surface of the double-row on an outer periphery. An inner member composed of at least one inner ring formed with an arc-shaped inner rolling surface, and the inner member and the outer member are accommodated between the rolling surfaces of the inner member and the outer member via a cage. In a wheel bearing device comprising a double row of balls and a seal attached to an opening of an annular space formed between the outer member and the inner member, the inner ring is provided with the inner rolling surface. A cylindrical shoulder extending in the axial direction from the large diameter side and a cylindrical small diameter side end extending in the axial direction from the small diameter side of the inner rolling surface are formed, and an inner diameter surface on the large diameter side of the inner ring is formed. The inner race is formed in a circular arc shape that is substantially concentric with the center of curvature of the rolling surface, and the thickness of the inner ring is set substantially equal, and the shoulder The inner diameter of the inner ring is set to be larger than the outer diameter of the end portion on the small diameter side, so that the inner ring is optimized in the thickness and reduced in weight and size, and the inner ring is made the same in the axial direction in the manufacturing process. When aligned in the direction and stacked in multiple stages, the end on the small diameter side is accommodated in the inner diameter part of the shoulder, the inner ring position is stabilized without increasing the height of the stacked inner rings, and stacked in the same direction Thus, it is possible to provide a wheel bearing device that achieves low cost by saving space and increasing the efficiency of the storage space.

It is a longitudinal section showing a 1st embodiment of a bearing device for wheels 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 single-piece | unit of FIG. 2, (b) is a longitudinal cross-sectional view which shows the inner ring single-piece | unit of FIG. It is explanatory drawing which shows the state which laminated | stacked the inner ring | wheel concerning this invention. 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 2nd 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 explanatory drawing which shows the state which laminated | stacked the inner ring | wheel of the conventional wheel bearing.

An annular projection protruding radially inward on the inner circumference, a double-row arc-shaped outer rolling surface on both sides of the annular projection, and an annular depression in the center of the outer circumference are cold rolled from the pipe material An outer member formed by: an arcuate inner rolling surface facing the outer rolling surface of the double row on the outer periphery, and a cylindrical shoulder extending in the axial direction from the large diameter side of the inner rolling surface And a pair of inner rings formed by cold rolling from a pipe material with cylindrical end portions extending in the axial direction from the smaller diameter side of the inner rolling surface, and both the inner ring and the outer member. A double row of balls accommodated between the rolling surfaces via a cage, and a seal attached to an opening of an annular space formed between the outer member and the inner ring, The inner ring's small diameter side end face collides in a butted state to form a back-to-back type double row angular contact ball bearing. In the wheel bearing device, a connecting portion between the outer diameter surface of the outer member and the annular recess is formed in an arc shape substantially concentric with the center of curvature of the outer rolling surface, and the outer member has a substantially uniform thickness. The inner ring has an inner diameter surface on the large diameter side formed in an arc shape substantially concentric with the center of curvature of the inner rolling surface, and the inner ring has a substantially uniform thickness, and the inner rolling The thickness Tmi of the groove bottom portion of the surface is larger than the thickness Tmo of the groove bottom portion of the outer rolling surface (Tmi ≧ Tmo), and the thickness Ti in the contact angle direction of the inner ring is in the contact angle direction of the outer member. It is set to be thicker than the wall thickness To (Ti ≧ To), and the inner diameter of the shoulder portion is set to be larger than the outer diameter of the end portion on the small diameter side.

Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.
1 is a longitudinal sectional view showing a first 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 outside view of FIG. 2 is a longitudinal sectional view showing a single inner member of FIG. 2, FIG. 4 is an explanatory view showing a state in which inner rings according to the present invention are laminated, and FIG. It is explanatory drawing which shows the manufacturing process of the outer member which concerns. In the following description, the side closer to the outside of the vehicle in the state assembled to the vehicle is referred to as an outer side (left side in FIG. 1), and the side closer to the center is referred to as an inner side (right side in FIG.

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 attachment flange 5 for attaching a wheel (not shown) to an end portion on the outer side, and a cylindrical shape extending from the wheel attachment 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 and 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 intact. 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 performing a hardening treatment in a range of 50 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 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 rows of these double rows. Arc-shaped inner rolling surfaces 8a and 8a facing the

surfaces

7a and 7a are formed on the outer circumferences of 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 seal 11 on the outer side is integrally joined to a cored bar 22 that is press-fitted into a cylindrical fitting part 7c formed at both ends of the outer member 7, and is joined to the cored bar 22 by vulcanization bonding or the like. The seal member 23 made of an elastic member such as rubber constitutes an integral seal. 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 that are slidably contacted with the shoulder portion 13 of the inner ring 8 via a predetermined shimiro.

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 7 c 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. . Preferably, in the cold rolling process, the thickness can be made substantially uniform, and the shape and dimensions can be ensured with a predetermined accuracy. 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 especially for the inner diameter surface 8d other than the purpose of forming an arc. This means that a state where the material is slightly thinned or thickened due to the displacement of the material when the arc is formed is included.

Specifically, as shown in FIG. 5A, a billet 40 cut to a predetermined size from a steel bar 39 is formed into a pipe material 41 as a material by hot forging and turning, or (b ), The steel pipe 42 is cut into a predetermined size and formed into a pipe material 43 as a material. In the case where the

pipe members

41 and 43 manufactured in such a process are the outer members 7 as shown in FIG. 5C, the inner peripheral mold 44 and the outer periphery are inserted in the outer peripheral mold 44. The

pipe members

41 and 43 are formed into a predetermined shape and size by being sandwiched between the molds 45 and being brought close to each other while rotating both

molds

44 and 45 in opposite directions. Here, the

pipe materials

41 and 43 that are the raw materials are thinned by the two dies 44 and 45 and are rolled in the width direction accordingly, but both end surfaces are regulated by the flange portions 45a of the outer peripheral die 45. Thus, the outer member 7 with higher accuracy can be manufactured.

In the case of SUJ2, the surface hardness is hardened to a range of 58 to 64 HRC by submerged quenching, induction quenching, and carburized steel by carburizing and quenching. In addition to this, 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. 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 in a range of 58 to 64 HRC by overall heating by induction hardening. Further, in the inner ring 8, the inner raceway surface 8a is subjected to a hardening process in 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 to the inner circumference, and double rows on both sides of the annular projection 28. Arc-shaped

outer rolling surfaces

7a, 7a are formed, and

fitting portions

7c, 7c of the

seals

11, 12 are formed at both ends. The double row outer rolling surfaces 7a and 7a and the fitting portion 7c are formed with predetermined dimensions 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 as necessary. As a result, the productivity is improved, the yield is good, the cost can be reduced, and the same accuracy and sealing performance as those of the conventional bearing can be secured.

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

Further, the radius of curvature Ro 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 7b of the member 7 and the knuckle 6. The connecting portion 31 and the center of curvature of the outer rolling surface 7a are set at substantially the same position, and the radius of the ball 10 is set to Rw. In this case, the radius of curvature Ro is set in the range of 1.5 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 can be prevented from occurring.

If the radius of curvature Ro 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. 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 rides 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. 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.

On the other hand, as shown in (b), the inner ring 8 is formed by plastic processing from a pipe material as a raw material, and an arcuate inner rolling surface 8a on the outer periphery, and from the large diameter side of the inner rolling surface 8a in the axial direction. An extending cylindrical shoulder 13 is formed. Preferably, in the cold rolling process, the thickness can be made substantially uniform, and the shape and dimensions can be ensured with a predetermined accuracy. Here, the shoulder portion 13 becomes a fitting surface of the seal land portion of the outer seal 11 and the inner seal 12 and is ground by a general grinding wheel simultaneously with the inner rolling surface 8a after heat treatment after plastic working. It is 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.

Here, in this embodiment, the thickness Ti of the inner ring 8 in the contact angle α direction is set to be thicker than the thickness To of the outer member 7 in the contact angle α direction (Ti ≧ To). This makes it possible to improve the strength and durability of the inner ring 8 that has a higher surface pressure than the outer member 7, and to reduce the weight, reduce the cost, and improve the durability of the bearing. A bearing 2 can be provided.

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 Tmi of the groove bottom portion of the inner ring 8 is thicker than the thickness Tmo of the groove bottom portion of the outer member 7. (Tmi ≧ Tmo). Thereby, the breaking strength of the inner ring 8 can be increased and the durability can be improved. In this type of thin outer member 7 and inner ring 8, the thicknesses To and Ti in the contact angle direction are more dominant in terms of strength than the thicknesses Tmo and Tmi at the groove bottoms of the rolling

surfaces

7a and 8a. Therefore, the thickness To of the outer member 7 in the contact angle α direction is set to be larger than the thickness Tmo of the groove bottom (To ≧ Tmo). Similarly, the thickness Ti of the inner ring 8 in the contact angle α direction is set to be larger than the thickness Tmi of the groove bottom (Ti ≧ Tmi). Thereby, strength and rigidity can be improved while achieving weight reduction.

Further, 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 wall thickness of the inner ring 8 is set to be substantially uniform, and the contact angle On the line of action in the α direction, a space is provided between the inner diameter surface 8d on the large diameter side and the small diameter step portion 1b of the hub wheel 1, and as shown in FIG. The fitting width A with the small-diameter step portion 1b) is smaller than the distance B between the intersections of the action line in the contact angle α direction and the fitting portion, and from the pitch P between the double row balls 10 of the wheel bearing 2. Is also set large (P <A <B). 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. .

Further, the radius of curvature Ri of the inner diameter surface 8d on the large diameter side of the inner ring 8 is set to be in the range of Ri = 1.5 to 1.8Rw. As a result, in the durability test conducted by the present applicant, it has been found that the generated stress is below the fatigue limit, the fatigue strength can be ensured, sufficient bearing rigidity can be obtained, and the fracture strength can be increased. Further, it is possible to prevent the shoulder portion 13 from cracking and to prevent the contact ellipse of the ball 10 from riding on the shoulder portion 13 when the turning moment is loaded and the occurrence of edge load.

When the radius of curvature Ri of the inner diameter surface 8d 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 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.

Furthermore, in this embodiment, the inner diameter d1 of the shoulder portion 13 of the inner ring 8 is set to be larger than the outer diameter φd2 of the end portion 14 on the small diameter side (φd1> φd2). As a result, as shown in FIG. 4, when the inner ring 8 is aligned in the same direction in the axial direction and stacked in a plurality of stages in the manufacturing process, the end portion 14 on the small diameter side is accommodated and stacked on the inner diameter portion of the shoulder portion 13. In addition, the inner ring 8 can be stacked in the same direction without increasing the height H1 of the inner ring 8, and the storage space can be saved, and the workability is improved and the cost is reduced. Can be achieved.

FIG. 6 is a longitudinal sectional view showing a second embodiment of the wheel bearing device according to the present invention. In addition, the same code | symbol is attached | subjected to the component and site | part which has the same component same part as embodiment mentioned above, or the same function, and detailed description is abbreviate | omitted.

This wheel bearing device is referred to as a third generation for driven wheels, and is a double

row rolling element

10, 10 accommodated in an freely movable manner between the inner member 32, the outer member 33, and both

members

32, 33. And. The inner member 32 includes a hub ring 34 and an inner ring 8 press-fitted into the hub ring 34.

The hub wheel 34 integrally has a wheel mounting flange 35 for mounting a wheel (not shown) at an end portion on the outer side, and a hub bolt for fixing the wheel at a circumferentially equidistant position of the wheel mounting flange 35. 35a is planted. On the outer periphery of the hub wheel 34, one (outer side) inner rolling surface 34a and a shaft-shaped small-diameter step portion 34b extending in the axial direction from the inner rolling surface 34a via the shoulder portion 34c are formed. 8 is press-fitted into the small-diameter step portion 34b through a predetermined scissors.

In the state where the small-diameter side end face 8b of the inner ring 8 is abutted against the shoulder portion 34c of the hub ring 34, the end portion of the small-diameter step portion 34b is plastically deformed radially outward to form a crimped portion 36. That is, the inner ring 8 is sandwiched between the caulking portion 36 and the shoulder 34c of the hub ring 34, and the inner ring 8 is fixed in the axial direction with respect to the hub ring 34 in a state where a predetermined bearing preload is applied. The caulking portion 36 is formed by plastic deformation in close contact with the surface of the inner diameter surface 8d on the large diameter side of the inner ring 8, and presses the inner diameter surface 8d on the large diameter side to secure a desired axial force. Can do.

The outer member 33 integrally has a vehicle body mounting flange 33b for mounting to a vehicle body (not shown) on the outer periphery, and double row outer rolling surfaces 33a and 33a are integrally formed on the inner periphery. The double-

row rolling elements

10 and 10 are accommodated between the rolling

surfaces

33a and 34a and 33a and 8a, and the double-

row rolling elements

10 and 10 are held by the

cages

9 and 9 so as to freely roll. ing.

Seals

37 and 38 are attached to the opening of the annular space formed between the outer member 33 and the inner member 32, and leakage of lubricating grease sealed inside the bearing and rainwater and dust from the outside. Etc. are prevented from entering the inside of the bearing.

Here, the wheel bearing device for a driven wheel called the third generation in which the inner raceway surface 34a is directly formed on the outer periphery of the hub wheel 34 is illustrated, but the wheel bearing device according to the present invention is described below. For example, a second generation structure for a driven wheel or a drive wheel in which a pair of inner rings are press-fitted into a small-diameter step portion of the hub wheel may be used.

The hub wheel 34 is formed of medium and high carbon steel containing 0.40 to 0.80 wt% of carbon such as S53C, and the inner base portion of the wheel mounting flange 35 slidably in contact with the inner rolling surface 34 a and the outer seal 37. The surface hardness is set to a range of 58 to 64 HRC by induction hardening from 35b to the small diameter step 34b. The caulking portion 36 is an unquenched portion having a surface hardness after forging in the range of 13 to 30 HRC, ensuring workability of caulking, which is cold plastic working, Prevents cracks in the fastening part.

The outer member 33 is formed of medium and high carbon steel containing 0.40 to 0.80 wt% of carbon such as S53C, similar to the hub wheel 34, and at least the double row outer rolling surfaces 33a and 33a are surfaced by induction hardening. Hardness is set in the range of 58 to 64 HRC.

Here, in this 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, as in the above-described embodiment, and the large diameter side of the inner ring 8 is formed. The radius of curvature Ri of the inner diameter surface 8d of the inner ring 8 is set to be in the range of Ri = 1.5 to 1.8Rw, and the inner diameter d1 of the shoulder portion 13 of the inner ring 8 is the outer diameter of the end portion 14 on the small diameter side. The diameter is set to be larger than φd2 (φd1> φd2). As a result, strength and rigidity can be improved while achieving weight reduction and compactness, and the inner ring 8 can be stacked in the same direction in the manufacturing process, and the space for storage can be saved. As a result, workability can be improved and cost reduction can be achieved.

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 first generation to a third generation structure including an inner ring formed by plastic working from a pipe material as a material.

1, 34 Hub wheel 1a, 13, 20, 30, 34c Shoulder 1b, 34b Small diameter step 1c, 21a Serration 2 Wheel bearing 3 Constant velocity universal joint 4 Fixed nut 5, 35 Wheel mounting flange 6 Knuckle 7, 33 Outside Side members 7a, 33a Outer rolling surface 7b Outer diameter 7c Fitting portion 8 Inner ring 8a, 34a Inner rolling surface 8b Small diameter side end surface 8c Large diameter side end surface 8d Large diameter side inner diameter surface 9 Cage 10 Balls 11, 37 Outer Side seals 12, 38 Inner side seal 14 Inner ring small-diameter end 15 Outer joint member 16 Joint inner ring 17 Cage 18 Torque transmission ball 19 Mouse part 21 Shaft part 21 Male thread 22, 26 Core metal 23, 27 Seal member 23a 23b Radial lip 24 Seal plate 25 Slinger 25a Cylindrical portion 25b Standing plate portion 27a Side lip 27b Grease lip 27c Intermediate screw 28 Annular convex part 29 Annular concave part 31 Connecting part 32 Inner member 33b Car body mounting flange 35a Hub bolt 35b Base part 36 Clamping part 39 Steel bar 40 Billet 41, 43 Pipe material 42 Steel pipe 44 Inner peripheral mold 45 Outer peripheral mold 45a Fence 50 Wheel bearing 51 Outer member 51a Outer rolling surface 52 Inner ring 52a Inner rolling surface 52b Small diameter side end surface 53 Cage 54 Ball 55, 56 Seal 57 Chamfered portion 58 Strut A Fitting with inner ring fitting portion Width B Distance between intersections of contact line in line of contact angle and fitting part d1 Inner ring shoulder inner diameter d2 Inner ring outer diameter H0, H1 Stacked inner ring height P Double row ball Inter-pitch Ri The radius of curvature Ro of the inner diameter portion of the inner ring on the inner diameter portion Ro The radius of curvature of the connecting portion of the outer member Rw The radius of the ball Ti The thickness of the inner ring in the contact angle direction To The thickness Tmi of the outer member in the contact angle direction Thickness α contact angle of the groove bottom wall thickness Tmo outer member of the groove bottom of the

Claims

An outer member in which a double-row arc-shaped outer rolling surface is integrally formed on the inner periphery;
An inner member composed of at least one inner ring having a double-row arcuate inner raceway formed on the outer periphery and facing the double-row outer raceway;
A double row of balls accommodated between the rolling surfaces of the inner member and the outer member via a cage so as to roll freely,
In a wheel bearing device comprising a seal mounted in an opening of an annular space formed between the outer member and the inner member,
The inner ring is formed with a cylindrical shoulder extending in the axial direction from the large diameter side of the inner rolling surface and a cylindrical small diameter side end extending in the axial direction from the small diameter side of the inner rolling surface, An inner diameter surface of the inner ring on the large diameter side is formed in an arc shape that is substantially concentric with the center of curvature of the inner rolling surface, and the inner ring has a substantially uniform wall thickness, and the inner diameter of the shoulder portion is on the small diameter side The wheel bearing device is characterized in that it is set to have a larger diameter than the outer diameter of the end portion of the wheel.
The inner ring is formed from a pipe material by plastic working, and the radius of curvature Ri of the inner diameter surface of the inner ring on the large diameter side is in the range of Ri = 1.5 to 1.8 Rw, where Rw is the radius of the ball. The wheel bearing device according to claim 1 set up as follows.
The outer member is formed from a pipe material by plastic working, and the curvature radius Ro of the joint portion of the outer member is in the range of Ro = 1.5 to 1.8 Rw, where Rw is the radius of the ball. The wheel bearing device according to claim 1 set up as follows.
The outer member is formed from a pipe material by plastic working, and an annular convex portion projecting radially inward is formed between the outer rolling surfaces of the double row on the inner circumference, and an annular concave portion is formed in the central portion of the outer circumference. A connecting portion between the outer diameter surface of the outer member and the annular recess is formed in an arc shape substantially concentric with the center of curvature of the outer rolling surface, and the outer member is set to have a substantially uniform thickness. The thickness Tmi of the groove bottom portion of the inner rolling surface is set to be larger than the thickness Tmo of the groove bottom portion of the outer rolling surface (Tmi ≧ Tmo). Wheel bearing device.
The wheel bearing device according to claim 4, wherein a wall thickness Ti in the contact angle direction of the inner ring is set to be larger than a wall thickness To in the contact angle direction of the outer member (Ti ≧ To).
A thickness To in the contact angle direction of the outer member is set to be greater than a thickness Tmo of the groove bottom portion of the outer rolling surface (To ≧ Tmo), and a thickness Ti in the contact angle direction of the inner ring is set to The wheel bearing device according to claim 4, wherein the wheel bearing device is set to be larger than a wall thickness Tmi of the groove bottom portion of the inner rolling surface (Ti ≧ Tmi).
The inner member is composed of a pair of inner rings, and the fitting width A between the inner diameter surfaces of these inner rings and the mating member into which the inner ring is press-fitted is the intersection of the extension of the inner diameter surface and the line of action in the contact angle direction. The wheel bearing device according to claim 1, wherein the wheel bearing device is set to be smaller than the distance B and larger than the pitch P of the double row balls (P <A <B).
The inner member integrally has a wheel mounting flange for mounting a wheel at one end, and a hub wheel formed with a cylindrical small-diameter step portion extending in the axial direction from the wheel mounting flange, and the hub wheel The inner ring is press-fitted into the small-diameter step portion through a predetermined scissors, and the end portion of the small-diameter step portion is radially outwardly in close contact with the surface of the inner diameter surface on the large-diameter side of the inner ring. 8. The wheel according to claim 1, wherein a caulking portion is formed by plastic deformation of the inner ring and the inner ring is axially fixed to the hub ring in a state where a predetermined bearing preload is applied. Bearing device.
The outer member is fitted into the knuckle, and on the line of action in the contact angle direction, a space is provided between the outer member and the knuckle, or / and on the line of action in the contact angle direction of the inner ring, The wheel bearing device according to claim 8, wherein a space is provided between the inner ring and the small-diameter step portion of the hub ring.
The wheel bearing device according to any one of claims 1 to 4, wherein the outer member and the inner ring are formed by cold rolling.