WO2008050488A1

WO2008050488A1 - Bearing device for wheel

Info

Publication number: WO2008050488A1
Application number: PCT/JP2007/001177
Authority: WO
Inventors: Takayuki Norimatsu; Kazuhisa Shigeoka; Akira Fujimura
Original assignee: Ntn Corporation
Priority date: 2006-10-26
Filing date: 2007-10-26
Publication date: 2008-05-02

Abstract

[PROBLEMS] A bearing device for a wheel, in which contradictory problems of reduction in weight and size and increase in rigidity are solved at the same time and which has increased strength and durability. [MEANS FOR SOLVING PROBLEMS] The bearing device for a wheel has double-row (9, 10) tapered rollers, and in the bearing device, an inner ring (6) is fixed by subjecting an end of a small-diameter step section (13b) of a hub ring (13) to rocking die swaging. The pitch circle diameter PCDi of the tapered-roller row (10) on the inner side is set greater than the pitch circle diameter PCDo of the tapered-roller row (9) on the outer side. Further, the number of the tapered rollers in the double rows is set to be the same, the diameter di of the tapered rollers (10) on the inner side is set greater than the diameter do of the tapered rollers (9) on the outer side, and the length Lo of the tapered rollers (9) on the outer side is set more than the length Li of the tapered rollers (10) on the inner side. The construction increases the rigidity and life of the bearing and enables effective use of a bearing space to make the bearing device light-weight and compact.

Description

Specification

Wheel bearing device

Technical field

TECHNICAL FIELD [0001] The present invention relates to a wheel bearing device that rotatably supports a wheel of an automobile or the like, and more particularly to a wheel bearing device that is reduced in weight and increased in rigidity.

Background art

[0002] Conventionally, wheel bearing devices for supporting wheels of automobiles and the like support a hub wheel for mounting a wheel rotatably via a rolling bearing, and there are a drive wheel and a driven wheel. For structural reasons, the inner ring rotation method is generally used for driving wheels, and both the inner ring rotation method and outer ring rotation method are used for driven wheels. In this wheel bearing device, a double-row angular contact ball bearing that has a desired bearing rigidity, exhibits durability against misalignment, and has a low rotational torque from the viewpoint of improving fuel efficiency is often used. . On the other hand, double row tapered roller bearings are used in vehicles with heavy vehicle body weight such as off-road force and trucks.

[0003] In addition, the wheel bearing device has a structure called a first generation in which a wheel bearing composed of a double-row anguilla ball bearing or the like is fitted between a knuckle and a hub wheel constituting a suspension device. Second generation structure with body mounting flange or wheel mounting flange formed directly on the outer periphery of the outer member, or third generation structure with one inner raceway formed directly on the outer periphery of the hub wheel, or hub It is roughly divided into the 4th generation structure in which the inner rolling surface is directly formed on the outer circumference of the outer joint member of the wheel and constant velocity universal joint.

[0004] The wheel bearing device shown in Fig. 3 2 is a lightweight, compact, 4th generation structure with a hub wheel 1 0 0 and double row rolling bearing 1 0 1 and constant velocity universal joint 1 0 2 and are united. The double row rolling bearing 100 includes an outer member 10 3, an inner member 10 4, and a plurality of poles 10 5 and tapered rollers 10 6 accommodated between the two members. In the following description, the side closer to the outer side of the vehicle in the assembled state is the outer side (left side of the drawing), and the side closer to the center is It is called the inner side (right side of the drawing).

[0005] The outer member 10 3 integrally has a vehicle body mounting flange 10 3 c attached to a knuckle constituting a suspension device (not shown) on the outer periphery, and a double row outer rolling surface 10 on the inner periphery. 3 a and 1 0 3 b are formed. Here, the diameter of the outer rolling surface 10 3 a on the outer side is set to be smaller than the diameter of the outer rolling surface 10 3 b on the inner side. On the other hand, the inner member 10 04 is press-fitted into the hub wheel 100, an outer joint member 10 8, which will be described later, integrally formed with the hub wheel 100, and the outer joint member 10 8. And a separate inner ring 1 0 7.

[0006] The hub wheel 1 0 0 has a wheel mounting flange 1 OO b for mounting a wheel (not shown) at one end, and a double row outer rolling surface 1 0 3 a, 1 on the outer periphery. 0 3 b Outer rolling surface on one side of outer side 1 0 3 a Inner rolling surface facing 1 0 3 a is directly formed, and the outer ring of inner ring 1 0 7 has double row outer rolling surface An inner rolling surface 1 0 7 a facing the outer rolling surface 1 0 3 b on the inner side of 1 0 3 a and 1 0 3 b is formed.

[0007] The constant velocity universal joint 1 0 2 has an outer joint member 1 0 8 composed of a cup-shaped mouth portion 1 0 9 and a shoulder portion 1 1 0 which forms the bottom of the mouth portion 1 0 9, A curved track groove 10 8 a is formed on the inner periphery of the outer joint member 10 8. The inner ring 10 07 is press-fitted into the outer diameter of the mouse portion 10 9 and is fixed in the axial direction by a retaining ring 1 1 1.

[0008] A rolling surface on the outer side of the outer member 1 0 3 and the inner member 1 0 4 on the outer side 1 0 3 a, a plurality of poles 1 0 5 between the 1 0 0 a and rolling on the inner side A plurality of tapered rollers 1 0 6 are rotatably accommodated between the faces 1 0 3 b and 1 0 7 a, respectively, and the pole 1 on the outer side of the rows 1 0 5 and 1 0 6 The pitch circle diameter of the fifth row is set smaller than the pitch circle diameter of the inner row of tapered rollers. As a result, the basic rated load of the inner-side bearing row portion to which a larger load is applied than the outer-side bearing row portion is made larger than the basic rated load of the outer-side bearing row portion, and both of these bearing rows are The life of the parts can be made almost the same, and a design without waste can be made possible (for example, patent literature) See 1. )

However, in such a wheel bearing device, since the inner ring 1 0 7 is fixed to the mouse portion 1 0 9 of the outer joint member 1 0 8, it is certainly compact in the axial direction. However, not only does the outer diameter of the outer member 10 3 itself increase, which not only obstructs weight reduction but also changes in the design of peripheral parts such as knuckles. As a solution to these problems, a wheel bearing device as shown in Fig. 33 is known.

[0010] This wheel bearing device has a vehicle body mounting flange 1 1 2 c integrally attached to a knuckle (not shown) on the outer periphery, and a double row outer rolling surface 1 1 2 on the inner periphery. a, 1 1 2 b formed outer member 1 1 2 and wheel mounting flange 1 1 3 for mounting a wheel (not shown) at one end, and double row outside on the outer circumference Rolling surface 1 1 2 a, 1 1 2 b Outer rolling surface 1 1 2 b Inner rolling surface facing 1 1 2 a 1 1 4 a and axial direction from this inner rolling surface 1 1 4 a The hub wheel 1 1 4 formed with a small-diameter step 1 1 4 b extending to the outer ring 1 and the small-diameter step 1 1 4 b of this hub wheel 1 1 4 a, 1 1 2 b Outer rolling surface on one side of inner side 1 1 2 b Inner rolling surface facing 1 1 2 b 1 1 5 Inner member 1 1 6 formed of inner ring 1 1 5 A double row of poles 1 1 7 and 1 1 8 accommodated between these rolling surfaces, These double-row poles 1 1 7 and 1 1 8 are constituted by double-row anguillar ball bearings equipped with cages 1 1 9 and 1 2 0 which hold the rolls freely.

[001 1] The inner ring 1 1 5 is fixed in the axial direction by a caulking portion 1 1 4 c formed by plastically deforming the small diameter step portion 1 1 4 b of the hub wheel 1 1 4 radially outward. . The seal 1 2 1 and 1 2 2 are installed in the opening of the annular space formed between the outer member 1 1 2 and the inner member 1 1 6, and the lubricating grease sealed inside the bearing And prevents rainwater and dust from entering the bearings from the outside.

[0012] Here, the pitch circle diameter D1 of the pole 1 17 row on the one side of the counter is set larger than the pitch circle diameter D2 of the pole 1 1 8 row on the inner side. Along with this, the inner raceway 1 1 4 a of the hub wheel 1 1 4 is the inner raceway 1 1 5 of the inner race 1 1 5 The outer side rolling surface 1 1 2 a on the outer side of the outer member 1 1 2 has a larger diameter than the outer rolling surface 1 1 2 b on the inner side. And more poles 1 1 7 on the outer side are accommodated than poles 1 1 8 on the inner side. In this way, by setting each pitch circle diameter D1, D2 to D1> D2, the rigidity is improved not only when the vehicle is stationary but also when turning, and the service life of the wheel bearing device is extended. (For example, see Patent Document 2). Patent Document 1: Japanese Patent Laid-Open No. 1-9-9 30 8

Patent Document 2: Japanese Patent Laid-Open No. 2 0 0 4 _ 1 0 8 4 4 9

Disclosure of the invention

Problems to be solved by the invention

In such a conventional wheel bearing device, the pitch circle diameter D 1 of the outer pole 1 117 row is set larger than the pitch circle diameter D 2 of the inner pole 1 1 8 row. Accordingly, the inner raceway surface 1 1 4 a of the hub wheel 1 1 4 has a larger diameter than the inner raceway surface 1 1 5 a of the inner race 1 1 5. As a result, the rigidity of the outer bearing row can be improved while avoiding an increase in the size of the device, and the service life of the wheel bearing device can be extended. However, the loads applied to the inner and outer bearing rows are different from each other, and the load applied to the inner bearing row is generally larger than the load applied to the outer bearing row. In such a case, in this conventional wheel bearing device, the basic load rating of the inner side bearing row is smaller than the basic load rating of the outer side bearing row, resulting in a shorter life.

[0014] The present invention has been made in view of such circumstances, and simultaneously solves the conflicting problems of light weight and compactness and high rigidity of the device, and at the same time, has improved strength and durability. An object of the present invention is to provide a bearing device for a vehicle.

Means for solving the problem

[0015] In order to achieve the object, the present invention includes an outer member integrally having a vehicle body mounting flange to be attached to a knuckle on the outer periphery, and a double row outer rolling surface formed on the inner periphery. A hub wheel having a wheel mounting flange for mounting a wheel on one end and a small diameter step portion formed on the outer periphery, and press fitting into the small diameter step portion of this hub ring An inner member comprising at least one inner ring formed on the outer periphery with an inner rolling surface facing the double row outer rolling surface, and both rolling surfaces of the inner member and the outer member. A wheel bearing device having a double row tapered roller row accommodated in a freely rolling manner between the pitch roller diameters of the inner side conical roller row of the double row conical roller row and having a conical shape on the outer side. The roller diameter is set to be larger than the pitch circle diameter of the roller row, and further, the roller diameter of the inner side tapered roller row is set to be larger than the roller diameter of the outer side tapered roller row, The roller length of the outer side tapered roller row is set to be longer than the roller length of the inner side tapered roller row. ■ ■ ■ Claim 1

[001 6] As described above, in the second or third generation wheel bearing device having double row tapered roller rows, the pitch circle of the tapered roller row on the inner side of the double row tapered roller row is provided. The diameter is set larger than the pitch circle diameter of the tapered roller row on the outer side, and the roller diameter of the tapered roller row on the inner side is set larger than the roller diameter of the tapered roller row on the outer side. In addition, the roller length of the outer tapered roller train is set to be longer than the roller length of the inner tapered roller train, so that the rigidity and life of the bearing can be improved, and the bearing The space can be used effectively to make it lighter and more compact. Therefore, it is possible to provide a wheel bearing device that can simultaneously solve the conflicting problems of light weight and compactness and high rigidity of the device, and that has improved strength and durability.

[001 7] The present invention also includes an outer member integrally having a vehicle body mounting flange to be attached to a knuckle on the outer periphery, and a double-row outer rolling surface formed on the inner periphery; A hub wheel that has a wheel mounting flange for mounting the wheel and has a small-diameter step formed on the outer periphery, and is press-fitted into the small-diameter step portion of the hub wheel, and faces the outer surface of the double row on the outer periphery. An inner member formed of at least one inner ring formed with an inner raceway, and a double row conical roller row accommodated between the inner member and the outer member so as to roll freely. The pitch circle diameter of the inner side tapered roller row of the double row tapered roller rows is set larger than the pitch circle diameter of the outer side tapered roller row, The inner The roller diameter of the tapered roller row on the side is set to a large diameter as well. ■ ■ ■ Claim 2

[0018] Thus, in the wheel bearing device of the second or third generation structure provided with the double row tapered roller row, the pitch circle diameter of the tapered roller row on the inner side of the double row tapered roller row is provided. Is set to be larger than the pitch circle diameter of the outer tapered roller train, and the roller diameter of the inner tapered roller train is set to be larger than the roller diameter of the outer tapered roller train. As a result, the rigidity and life of the bearing can be improved, and the bearing space can be effectively utilized to achieve light weight and compactness. Therefore, it is possible to provide a wheel bearing device that can simultaneously solve the conflicting problems of light weight and compactness and high rigidity of the device, and that has improved strength and durability.

[001 9] Further, as in the invention, if the roller length of the inner side tapered roller train is set longer than the roller length of the outer side tapered roller train, The basic dynamic load rating of the bearing row can be increased, further improving the rigidity and life of the bearing. ■ ■ ■ Claim 3

[0020] Further, as in the present invention, the number of rollers of the double row tapered roller row may be set to be the same. ■ ■ ■ Claim 4

[0021] The present invention also includes an outer member integrally including a vehicle body mounting flange to be attached to the knuckle on the outer periphery, a double row outer rolling surface formed on the inner periphery, and a wheel on one end. A hub wheel having a wheel mounting flange for mounting the outer ring, and a small-diameter step portion formed on the outer periphery, and a small-diameter step portion of the hub wheel, and press-fitted into the outer periphery of the double row on the outer periphery. An inner member composed of at least one inner ring formed with an inner rolling surface, and a double row tapered roller row accommodated so as to roll between the inner member and both rolling surfaces of the outer member. In the wheel bearing device provided, the pitch circle diameter of the inner side tapered roller row of the double row tapered roller rows is set larger than the pitch circle diameter of the outer side tapered roller row, and The roller length of the inner side tapered roller row is the outer It is set to be longer than the roller length of the tapered roller rows of the force, one, number rollers of the tapered roller rows of the inner one side the Auta -More than the number of rollers in the tapered roller row on the side. ■ ■ ■ Claim 5 [0022] Thus, in the second or third generation wheel bearing device having double row tapered roller rows, the inner side tapered roller of the double row tapered roller rows. The pitch circle diameter of the row is set to be larger than the pitch circle diameter of the outer side tapered roller row, and the roller length of the inner side tapered roller row is larger than the length of the outer side tapered roller row. The number of rollers in the tapered roller train on the inner side is set to be larger than the number of rollers in the tapered roller row on the outer side, so the weight of the device is compact and the rigidity is increased. Thus, it is possible to provide a wheel bearing device in which the basic rated load of the bearing row on the inner side is increased and the rigidity and life of the bearing are improved.

[0023] The present invention also includes an outer member integrally having a vehicle body mounting flange to be attached to the knuckle on the outer periphery, a double row outer rolling surface formed on the inner periphery, and a wheel on one end. A hub wheel having a wheel mounting flange for mounting the outer ring, and a small-diameter step portion formed on the outer periphery, and a small-diameter step portion of the hub wheel, and press-fitted into the outer periphery of the double row on the outer periphery. An inner member composed of at least one inner ring formed with an inner rolling surface, and a double row tapered roller row accommodated so as to roll between the inner member and both rolling surfaces of the outer member. In the wheel bearing device provided, a pitch circle diameter of an outer side tapered roller row of the double row tapered roller rows is set larger than a pitch circle diameter of an inner side tapered roller row, and The roller length of the inner side tapered roller row is the outer Is set to be longer than the roller length of the tapered roller rows of the force, one, number rollers of the tapered roller rows of the outer side the inner - is set larger than the number roller on the side of the tapered roller rows. ■ ■ ■ Claim 6 [0024] In this way, in the second or third generation wheel bearing device having double-row tapered roller rows, the outer-side tapered roller row of the double-row tapered roller rows. The pitch circle diameter of the inner roller is set to be larger than the pitch circle diameter of the inner side tapered roller train, and the roller length of the inner side tapered roller train is larger than the length of the outer tapered roller train. Is set longer and the number of rollers in the outer tapered roller row is set to be larger than the number of rollers in the inner tapered roller row. It is possible to provide a wheel bearing device that improves the rigidity and life of the bearing without increasing the outer diameter of the outer member, and the basic rated load of the bearing row on the inner side is increased. it can.

[0025] Further, as in the present invention, a roller diameter of the inner side tapered roller train and a roller diameter of the outer tapered roller train may be set to be the same. ■ ■ ■ Claims

[0026] Further, according to the present invention, an outer member having a vehicle body mounting flange to be attached to the knuckle on the outer periphery, a double row outer rolling surface formed on the inner periphery, and a wheel on one end A hub wheel having a wheel mounting flange for mounting the outer ring, and a small-diameter step portion formed on the outer periphery, and a small-diameter step portion of the hub wheel, and press-fitted into the outer periphery of the double row on the outer periphery. An inner member composed of at least one inner ring formed with an inner rolling surface, and a double row tapered roller row accommodated so as to roll between the inner member and both rolling surfaces of the outer member. In the wheel bearing device provided, the pitch circle diameter of the inner side tapered roller row of the double row tapered roller rows is set larger than the pitch circle diameter of the outer side tapered roller row, and The roller length of the inner side tapered roller row is the outer It is set to be longer than the roller length of the tapered roller row of and the number roller diameter Oyobi rollers of these tapered rollers is set to the same. ■ ■ ■ Claim 8

[0027] Thus, in the wheel bearing device of the second or third generation structure provided with the double row tapered roller row, the pitch circle diameter of the tapered roller row on the inner side of the double row tapered roller row is provided. Is set to be larger than the pitch circle diameter of the outer side tapered roller row, the roller length of the inner side tapered roller row is set to be longer than the outer length of the tapered roller row of the outer side, and Since these tapered rollers have the same roller diameter and the same number of rollers, they can be made lighter and more compact, and the inner diameter can be reduced while preventing the cage strength from being reduced by increasing the roller diameter and number of rollers. It is possible to provide a wheel bearing device in which the basic load rating of the side bearing row is increased and the rigidity and life of the bearing are improved.

[0028] Further, the present invention provides a vehicle body mounting flange for mounting to a knuckle on the outer periphery. The outer member with a double row outer raceway formed on the inner periphery and the wheel mounting flange for mounting the wheel on one end are integrated, and the small diameter step is formed on the outer periphery. And an inner member comprising at least one inner ring that is press-fitted into a small-diameter step portion of the hub ring and has an inner rolling surface facing the outer rolling surface of the double row on the outer periphery. In a wheel bearing device including an inner member and a double-row tapered roller row rotatably accommodated between both rolling surfaces of the outer member, a pitch circle diameter of the double-row tapered roller row is The roller diameter of the inner side tapered roller row of the double row tapered roller rows is set to be larger than the roller diameter of the outer side tapered roller row, and these tapered rollers The number of rollers in the row is set to be the same. ■ ■ ■ Claim 9

[0029] Thus, in the second or third generation wheel bearing device having double row tapered roller rows, the pitch circle diameters of the double row tapered roller rows are set to be the same, and The roller diameter of the tapered roller row on the inner side of the row of tapered roller rows is set larger than the roller diameter of the tapered roller row on the outer side, and the number of rollers in these tapered roller rows is set to be the same. Therefore, it is possible to increase the basic rated load of the inner side bearing row without increasing the pitch circle diameter of the inner one side, and to prevent the outer member from increasing its outer diameter. Thus, it is possible to provide a wheel bearing device in which the rigidity and life of the bearing are improved.

[0030] Preferably, as in the invention, if the roller length of the inner side tapered roller row is set to be longer than the roller length of the outer side tapered roller row, the inner one side tapered roller It is possible to further increase the basic load rating of the inner side bearing row without increasing the pitch circle diameter of the row, to suppress the outer diameter of the outer member, and to reduce the outer diameter of the outer member, while reducing the weight and reducing the rigidity of the bearing. The service life can be improved. ■ ■ ■ Claim 1 0

[0031] Further, as in the present invention, if the roller length of the outer tapered roller train is set longer than the roller length of the inner tapered roller train, The basic load rating of double row bearing rows can be increased without increasing the diameter of the pitch circle, and the outer diameter of the outer member can be prevented from increasing, making it light and compact. Thus, the rigidity and life of the bearing can be improved. ■ ■ ■ Claim 1 1 [0032] Further, the present invention has a vehicle body mounting flange integrally attached to a knuckle on the outer periphery, and an outer side in which a double row outer rolling surface is formed on the inner periphery. And a hub wheel having a wheel mounting flange for mounting a wheel at one end, a small-diameter step portion formed on the outer periphery, and press-fitted into the small-diameter step portion of the hub wheel. An inner member composed of at least one inner ring formed with an inner rolling surface opposite to the outer rolling surface, and a composite member housed in a freely rolling manner between the inner and the outer member. In the wheel bearing device provided with a row of tapered roller rows, the pitch circle diameter of the double row tapered roller rows is set to be the same, and the outer side tapered roller row of the double row tapered roller rows is arranged. Set the roller length longer than the roller length of the tapered roller row on the inner side. It is, and the number rollers of these tapered rollers column same - is set to. ■ ■ ■ Claim 1 2

[0033] Thus, in the second or third generation wheel bearing device having a double row tapered roller row, the pitch circle diameter of the double row tapered roller row is set to be the same, and The roller length of the outer tapered roller row in the row is set to be longer than the roller length of the inner tapered roller row, and the number of rollers in these tapered roller rows is set to be the same. Therefore, the basic load rating of the outer side bearing row can be increased without increasing the pitch circle diameter of the outer side tapered roller row and without increasing the number of rollers of the tapered roller. -It is possible to provide a wheel bearing device in which the rigidity and life of the bearing are improved while achieving compactness.

[0034] Further, as in the present invention, if the roller diameter of the outer tapered roller row and the roller diameter of the inner tapered roller row are set to be the same, the outer side of the outer member An increase in the outer diameter can be suppressed. ■ ■ ■ Claim 1 3

[0035] The present invention also includes an outer member integrally having a vehicle body mounting flange to be attached to the knuckle on the outer periphery, a double row outer rolling surface formed on the inner periphery, and a wheel on one end. A hub wheel integrally having a wheel mounting flange for mounting, and having a small-diameter step portion extending in the axial direction from the wheel mounting flange on the outer periphery, and An inner member composed of at least one inner ring press-fitted into the small-diameter step portion of the ring and formed with an inner rolling surface facing the outer rolling surface of the double row on the outer circumference, and the inner member In the wheel bearing device comprising a double row tapered roller row that is rotatably accommodated between both rolling surfaces of the outer member, the pitch circle diameter of the double row tapered roller row is set to be the same. The diameter of the outer tapered roller row of the double row tapered roller rows is set to be smaller than the roller diameter of the inner side tapered roller row, and the outer roller side tapered roller row The number of rollers is set to be greater than the number of rollers in the inner side tapered roller row, and the roller length of the inner side tapered roller row is set to be longer than the roller length of the outer side tapered roller row. Yes. ■ ■ ■ ■ Claim 1 4

[0036] In this way, in the second or third generation wheel bearing device having double-row tapered roller rows, the pitch circle diameters of the double-row tapered roller rows are set to be the same, and the double-row cone rollers The roller diameter of the outer tapered roller train is set to be smaller than the roller diameter of the inner one, and the number of rollers in the outer tapered roller train is the inner one. Since the roller length of the inner tapered roller row is set to be longer than the roller length of the outer tapered roller row, the pitch of the outer tapered roller row is set. It is possible to increase the basic load rating of both bearing rows without increasing the diameter of the circle, and to provide a wheel bearing device that is lightweight and compact, while improving the rigidity and life of the bearing. .

[0037] Further, as in the present invention, if the inner ring is fixed in the axial direction by a caulking portion formed by plastically deforming the end portion of the small diameter step portion radially outward, Can be achieved. ■ ■ ■ Claim 1 5

[0038] Further, as in the present invention, an outer-side inner rolling surface is directly formed on the outer periphery of the hub wheel, and the small-diameter step portion extending in the axial direction from the inner-rolling surface is formed. If the inner ring on the inner side is press-fitted into the small diameter step portion through a predetermined opening, the device can be made lighter and more compact, and the pitch circle diameter in the tapered roller array on the inner side can be reduced. The inner ring on the inner side corresponding to the amount of diameter expansion The hoop stress generated on the inner raceway surface and the outer diameter of the inner ring due to plastic deformation of the caulking part can be suppressed to improve the strength of the hub ring and inner ring. Can do. ■ ■ ■ Claim 1 6

[0039] Further, as in the present invention, if a pair of inner rings are press-fitted into the small-diameter step portion of the hub wheel and the inner diameters of these inner rings are set to be the same, the small-diameter step portion of the hub wheel is It can be formed into any shape, and the workability can be improved, and the inner ring inner wall thickness can be increased corresponding to the amount of pitch circle diameter expansion in the inner roller taper row. It is possible to improve the strength and durability of the inner ring by suppressing the hoop stress generated on the inner raceway surface and outer diameter of the inner ring due to plastic deformation of the caulking portion. ■ ■ ■ Claim 1 7

BEST MODE FOR CARRYING OUT THE INVENTION

[0040] An outer member integrally having a vehicle body mounting flange to be attached to the knuckle on the outer periphery, a double row outer rolling surface formed on the inner periphery, and a wheel attachment for attaching the wheel to one end A hub wheel having a flange integrally formed and formed on the outer periphery thereof with an inner rolling surface facing one of the outer rolling surfaces of the double row, and a small-diameter step portion extending in an axial direction from the inner rolling surface; and An inner member comprising an inner ring that is press-fitted into a small-diameter step portion of the hub wheel and has an inner rolling surface facing the other of the outer rolling surfaces of the double row on the outer periphery; and the inner member and the outer A double row tapered roller row that is rotatably accommodated between both rolling surfaces of the member, and is formed by a caulking portion that is formed by plastically deforming an end portion of the small diameter step portion radially outward. In a bearing device for a wheel in which an inner ring is fixed in an axial direction with respect to a hub wheel, the double-row tapered roller The pitch circle diameter of the inner side tapered roller train is set to be larger than the pitch circle diameter of the outer tapered roller train, and the number of rollers of the double row tapered roller train is set to be the same. The roller diameter of the inner tapered roller train is set to be larger than the roller diameter of the outer tapered roller train, and the roller length of the outer tapered roller train is It is set longer than the roller length of the tapered roller row on the side.

Example 1

Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. FIG. 1 is a longitudinal sectional view showing a first embodiment of a wheel bearing device according to the present invention. This wheel bearing device is for a driven wheel called a second generation, and includes a hub wheel 1, A wheel bearing 2 fixed to the hub wheel 1 is provided. The hub wheel 1 integrally has a wheel mounting flange 3 for mounting a wheel (not shown) at one end portion on the outer side, and has a small diameter extending in an axial direction from the wheel mounting flange 3 through a shoulder portion 1a. A step 1b is formed. Hub ports 3 a are planted on the wheel mounting flange 3 at equal intervals in the circumferential direction.

[0042] The wheel bearing 2 is press-fitted into the small-diameter step portion 1b through a predetermined shimiro while being in contact with the shoulder portion 1a of the hub wheel 1, and the end portion of the small-diameter step portion 1b is It is fixed in the axial direction by a caulking portion 1 c formed by plastic deformation. The hub ring 1 is formed of medium and high carbon steel containing carbon 0.40 to 0.8 O wt% such as S 53 C, and is hardened by induction hardening from the shoulder 1a to the small diameter step 1b. Has been cured to a range of 5 8 to 6 4 HRC. Note that the caulking portion 1c remains the surface hardness after forging. This has sufficient mechanical strength against the rotational bending load applied to the wheel mounting flange 3, and improves the fretting resistance of the small-diameter stepped portion 1b that becomes the fitting portion of the wheel bearing 2. At the same time, the plastic application of the crimped portion 1c can be smoothly performed while preventing the occurrence of minute cracks and the like.

[0043] The wheel bearing 2 is integrally provided with a vehicle body mounting flange 4c to be attached to a knuckle (not shown) constituting a suspension device on the outer periphery, and a double row outer rolling surface 4 on the inner periphery. Two outer rings with outer members 4 with a and 4 b and inner rolling surfaces 5 a and 6 a facing the outer circumferential surfaces 4 a and 4 b of the double row on the outer circumference. 5, 6 and double rolling tapered rollers 9, 10 which are accommodated in a rolling manner via cages 7, 8 between both rolling surfaces 4a, 5a and 4b, 6a. Yes. Seals 1 1 and 1 2 are attached to the opening of the annular space formed between the outer member 4 and the two inner rings 5 and 6, and leakage of grease sealed inside the bearing Prevents rainwater and dust from entering the bearing.

[0044] Inner raceway surfaces 5a and 6a of inner rings 5 and 6 are line contoured to tapered rollers 9 and 10 This is a so-called back-to-back type double-row tapered roller bearing that is formed in a tapered shape with a small diameter side (front) end face 5d and 6d abutting in a butted state. Then, the large rollers 5 b and 6 b for guiding the tapered rollers 9 and 10 to the large diameter side of the inner rolling surfaces 5 a and 6 a and the tapered rollers 9 and 10 to drop off on the small diameter side are provided. Gavels 5 c and 6 c are formed for prevention.

[0045] The outer member 4 is formed of medium and high carbon steel containing 0.40 to 0.80 wt% of carbon such as S 53 C, and the double row outer rolling surfaces 4 a and 4 b are hardened by induction hardening. Hardened to a range of 58-64 H RC. The inner rings 5 and 6 and the tapered rollers 9 and 10 are made of high carbon chrome steel such as SU 2 and hardened in the range of 58 to 64 H RC to the core part by quenching.

Here, in the present embodiment, the pitch circle diameter P CD i of the inner row of tapered rollers 10 on the inner side is larger than the pitch circle diameter PCD o of the row of 9 tapered rollers on the outer side (P CD i> PCDo). In addition, the roller diameter di of the 10-row tapered roller on the inner side is set to a larger diameter (di> do) than the roller diameter do of the 9-side tapered roller on the outer side, and the roller length is The roller length L o of the 9-row tapered roller is set to be longer than the roller length L i of the 10-side tapered roller 10 (L o> L i). Note that the number of rollers in the tapered rollers 9 and 10 row is set to be the same. As a result, it is possible to improve the rigidity and life of the bearing, and to provide a wheel bearing device that is lightweight and compact by effectively utilizing the bearing space.

[0047] Further, since the degree of freedom in design increases, even if there is a difference in pitch circle diameters PCDo and PCD i, the inner diameters of the inner rings 5 and 6 are made the same so that the inner diameters 5 and 6 are fitted to each other. The part 1 b can be formed into a straight shaft shape with the shaft diameter d 1, which can improve the workability of the hub wheel 1, and the pitch circle diameter PC D i in the row of tapered rollers 10 on the inner side The wall thickness t of the inner ring 6 on the inner side can be increased corresponding to the amount of diameter expansion, and the inner raceway surface 6a and the outer diameter 6e of the inner ring 6 can be increased with plastic deformation of the caulking portion 1c. The hoop stress generated can be suppressed and the strength and durability of the inner ring 6 can be improved. Example 1

FIG. 2 is a longitudinal sectional view showing a second embodiment of the wheel bearing device according to the present invention. Note that this embodiment is basically different from the above-described embodiment only in the configuration of the hub wheel, and other parts and parts having the same parts or the same functions are denoted by the same reference numerals for detailed description. Omitted.

[0049] This wheel bearing device is for a driven wheel called the third generation, and is press-fitted into the outer member 4, the hub wheel 1 3 and the small diameter step portion 1 3 b of the hub wheel 13. And an inner member 14 composed of an inner ring 6. The hub wheel 1 3 has an outer outer rolling surface 4 a that faces the outer outer rolling surface 4 a on the outer periphery, and a small-diameter step portion 1 3 that extends in the axial direction from the inner rolling surface 1 3 a. b is formed. The inner ring 6 is abutted against the shoulder 1 3 c of the hub ring 1 3 in abutting condition, is press-fitted into the small-diameter stepped portion 1 3 b through a predetermined shimiro, and is fixed in the axial direction by the crimping portion 1 c. .

[0050] Seals 15 and 1 2 are attached to the openings of the annular space formed between the outer member 4 and the hub ring 13 and the inner ring 6, and the grease sealed inside the bearing is exposed to the outside. It prevents leakage and rainwater and dust from entering the bearing. The hub wheel 13 is made of medium and high carbon steel containing carbon 0.40 to 0.80 wt% such as S 53 C, and the inner rolling surface from the seal land portion 3 b in which the seal 15 is in sliding contact. The surface hardness is hardened to a range of 58 to 64 HRC by induction hardening over 1 3 a and small diameter step 1 3 b.

[0051] Here, in the present embodiment, the tapered roller on the inner side is similar to the above-described embodiment.

10 pitch circle diameter PCD i is set larger than pitch circle diameter PCD o of 9 rows of pitch rollers (PCD i> PCD o), and inner side of tapered rollers 10 rows The roller diameter di is set to a larger diameter (di> do) than the roller diameter do of the outer side tapered roller 9 rows, and the roller length L o of the outer side tapered roller 9 rows is the inner side cone. The roller length is set to be longer than the roller length L i of row 10 (L o> L i). This makes it possible to improve the rigidity and life of the bearing while achieving light weight and compactness, and also to increase the pitch circle diameter PCD i in the inner row of tapered rollers 10 on the inner side. Inner ring The hub ring 1 3 can be made thicker, and the hoop stress generated on the inner raceway surface 6a and outer diameter 6e of the inner ring 6 due to plastic deformation of the caulking portion 1c can be suppressed. And Strength of inner ring 6 ■ Durability can be improved.

Example 3

FIG. 3 is a longitudinal sectional view showing a third embodiment of the wheel bearing device according to the present invention. This embodiment is basically the same as the first embodiment (FIG. 1) described above except that the configuration of the wheel bearing is different, and other parts and parts having the same parts or functions having the same parts have the same reference numerals. The detailed description is omitted.

This wheel bearing device is for a driven wheel called the second generation, and includes a hub wheel 1 ′ and a wheel bearing 16 fixed to the hub wheel 1 ′. The wheel bearing 16 is press-fitted into the small-diameter step portion 1 b ′ through a predetermined squeeze opening in contact with the shoulder portion 1 a of the hub wheel 1 ′, and the end portion of the small-diameter step portion 1 b ′. It is fixed in the axial direction by a caulking portion 1 c formed by plastic deformation.

[0054] The wheel bearing 16 has an outer member 4 integrally formed with a vehicle body mounting flange 4c on the outer periphery and formed with a plurality of outer rolling surfaces 4a and 4b on the inner periphery, and on the outer periphery. Two inner rings 5 ′, 6 ′ formed with inner rolling surfaces 5 a, 6 a facing the outer rolling surfaces 4 a, 4 b of the double row, and both rolling surfaces 4 a, 5 a and A plurality of tapered rollers 9 and 10 are provided between 4 b and 6 a so as to roll freely through cages 7 and 8.

[0055] Here, in the present embodiment, the tapered roller on the inner side is similar to the above-described embodiment.

10 pitch circle diameter PCD i is set larger than pitch circle diameter PCD o of 9 rows of pitch rollers (PCD i> PCD o), and inner side of tapered rollers 10 rows The roller diameter di is set to a larger diameter (di> do) than the roller diameter do of the outer side tapered roller 9 rows, and the roller length L o of the outer side tapered roller 9 rows is the inner side cone. The roller length is set to be longer than the roller length L i of row 10 (L o> L i). This makes it possible to improve the rigidity and life of the bearing while achieving light weight and compactness, and also to increase the pitch circle diameter PCD i in the inner row of tapered rollers 10 on the inner side. Hub of The shaft diameter d2 of the small-diameter step 1b 'in the wheel 1' can be formed as a large diameter (d2> d1 (Fig. 1)), and the strength of the hub wheel 1 'can be improved. Yes Example 4

FIG. 4 is a longitudinal sectional view showing a fourth embodiment of the wheel bearing device according to the present invention. This embodiment is basically the same as the third embodiment described above (Fig. 3) except that the structure of the wheel is different, and that the same parts and parts having the same function or the same function are the same. Reference numerals are assigned and detailed description is omitted.

[0057] This wheel bearing device is for a driven wheel referred to as a third generation, and includes an outer member 4, a hub wheel 1 3 ', and a small-diameter step portion 1 3 b' of the hub wheel 1 3 '. And an inner member 17 made of an inner ring 6 'press-fitted into the inner ring.

[0058] Hub wheel 1 3 'is formed of medium and high carbon steel containing 0.40 to 0.80 wt% of carbon such as S 53 C, and the inner rolling surface from seal land portion 3 b in which seal 15 is in sliding contact. The surface hardness is hardened to a range of 58 to 64 H RC by induction hardening over 1 3 a and the small diameter step portion 1 3 b ′.

[0059] Here, in the present embodiment, as in the third embodiment described above, the pitch circle diameter of the inner one side tapered roller 10 row 10 PCi is the pitch circle diameter of the outer row tapered roller 9 row. Larger than PCDo (PCD i> PCDo), and inner roller tapered roller diameter 10 is larger than roller diameter di of outer side tapered roller 9 rows. (Di> do) and the roller length L o of the outer side conical roller 9 row is set to be longer than the roller length L i of the inner one side tapered roller 10 row (L o> L i). As a result, the rigidity and life of the bearing can be improved while achieving light weight and compactness, and the expansion diameter of the pitch circle diameter P CD i in the tapered row on the inner side 10 can be accommodated. The shaft diameter d2 of the small diameter step 1 3 b 'in the hub ring 1 3' on the inner side can be made larger (d 2> d 1 (Fig. 2)), and the strength of the hub ring 1 3 ' ■ Durability can be improved.

Example 5 FIG. 5 is a longitudinal sectional view showing a fifth embodiment of the wheel bearing device according to the present invention. This embodiment is basically the same as the first embodiment (FIG. 1) described above except that the configuration of the tapered roller on the outer side is different, and other parts and parts having the same parts or the same functions. The same reference numerals are given to the same parts and detailed explanations are omitted.

This wheel bearing device is for a driven wheel called the second generation, and includes a hub wheel 1 and a wheel bearing 18 fixed to the hub wheel 1. The wheel bearing 18 is press-fitted into the small-diameter step 1 b through a predetermined squeeze opening while being abutted against the shoulder 1 a of the hub wheel 1 and the end of the small-diameter step 1 b is plastically deformed. It is fixed in the axial direction by a caulking portion 1 c formed in this manner.

[0062] The wheel bearing 18 has an outer member 4 integrally formed with a vehicle body mounting flange 4c on the outer periphery and a plurality of outer rolling surfaces 4a and 4b formed on the inner periphery, and on the outer periphery. Two inner races 1 9 and 6 formed with inner rolling surfaces 1 9 a and 6 a opposite to these double-row outer rolling surfaces 4 a and 4 b, and both rolling surfaces 4 a and 19 Double row tapered rollers 21 and 10 rows are provided between a and 4 b and 6 a so as to be freely rollable via cages 20 and 8.

[0063] Inner raceway surfaces 19a and 6a of inner rings 19 and 6 are formed in a taper shape in line contact with tapered rollers 21 and 10 and have a small diameter (front) side end surface 5d, 6d constitutes a back-to-back type double row tapered roller bearing where they are abutted in abutting condition. And the large roller 5 b, 6 b to guide the tapered rollers 2 1, 10 on the large diameter side of the inner rolling surfaces 1 9 a, 6 a, and the tapered rollers 2 1, 1 on the small diameter side Gavels 5c and 6c are formed to prevent 0 from falling off.

[0064] Here, in this embodiment, the pitch circle diameter P CD i of the inner one side tapered roller 10 row is larger than the pitch circle diameter P CD o of the outer side tapered roller 21 row (P CD i> P CD o) and the roller diameter di of the inner one side 10 row is set larger than the roller diameter do of the outer row 2 roller row do (di> do) ing. Also, the outer side tapered roller 2 1 row roller length L o and the inner 1 side tapered roller length 10 row roller length L i are the same (L o = L i). In addition, the number of rollers in the 2 1 and 1 0 rows is set to be the same. As a result, it is possible to improve the rigidity and life of the bearing, and to provide a wheel bearing device that is lightweight and compact by effectively utilizing the bearing space.

[0065] Further, since the degree of freedom in design increases, even if there is a difference in pitch circle diameters P C D o and P C D i, the inner diameters of the inner rings 19 and 6 are made the same, so that the inner rings 19

, 6 can be formed into a straight shaft shape with the shaft diameter d 1 and the small diameter stepped portion 1 b can improve the workability of the hub wheel 1 and the tapered roller on the inner side 1 0 The inner diameter of inner ring 6 on the inner side can be increased corresponding to the amount of expansion of pitch circle diameter PCD i in the row, and the inner raceway surface 6 of inner ring 6 can be increased along with plastic deformation of caulking portion 1c. Strength of inner ring 6 by suppressing hoop stress generated at a and outer diameter 6 e

■ Durability can be improved.

Example 6

FIG. 6 is a longitudinal sectional view showing a sixth embodiment of the wheel bearing device according to the invention. This embodiment is basically the same as the second embodiment (FIG. 2) described above except that the configuration of the tapered roller on the outer side is different, and other parts and parts having the same parts or the same functions. The same reference numerals are given to the same parts and detailed explanations are omitted.

This wheel bearing device is for a driven wheel called the third generation, and is press-fitted into the outer member 4, the hub wheel 2 2, and the small-diameter step portion 1 3 b of the hub wheel 2 2. And an inner member 23 made of an inner ring 6. The hub wheel 2 2 has an outer rolling surface 4 a on the outer side facing the outer rolling surface 4 a on the outer side and a small diameter step portion 1 extending in the axial direction from the inner rolling surface 2 2 a. 3 b is formed. The hub wheel 2 2 is formed of medium and high carbon steel containing carbon 0.40 to 0.80 wt% such as S 53 C, and the inner surface of the rolling contact 2 2 from the seal land 3 b in which the seal 15 is in sliding contact. The surface hardness is hardened to a range of 58 to 64 HRC by induction hardening over a and the small diameter step 1 3 b.

[0068] Here, in the present embodiment, the tapered roller on the inner side is the same as the above-described embodiment. 1 0 row pitch circle diameter PCD i is outer tapered roller 2 1 row pitch circle diameter PCD o is larger than PCD o (PCD i> PCD o) and inner one tapered roller The roller diameter di of the 10th row is set to a larger diameter (di> do) than the tapered diameter do of the 2nd row. The outer side tapered roller 21 is set to the same length (L o = L i) as the roller length L o of the first row and the roller length L i of the inner row 10 are set to the same. The number of rollers in the 2 1 and 1 0 rows is set to be the same. This makes it possible to improve the rigidity and life of the bearing while achieving a lighter weight and compactness. In addition, the inner wall 6 on the inner side 6 can be increased in thickness t in accordance with the amount of expansion of the pitch circle diameter PCD i in the row of tapered rollers 10 on the inner side, and the plasticity of the caulking portion 1 c can be increased. The hoop stress generated on the inner raceway surface 6a and outer diameter 6e of the inner ring 6 due to deformation can be suppressed to improve the strength and durability of the hub wheel 22 and inner ring 6 Example 7

FIG. 7 is a longitudinal sectional view showing a seventh embodiment of the wheel bearing device according to the invention. This embodiment is basically the same as the above-described fifth embodiment (FIG. 5) except that the structure of the wheel and the wheel bearing is partially different, and has the same parts and the same functions. Parts and parts are denoted by the same reference numerals, and detailed description is omitted.

[0070] This wheel bearing device is for a driven wheel called the second generation, and includes a hub wheel 1 'and a wheel bearing 24 fixed to the hub wheel 1'. The wheel bearing 2 4 is press-fitted into the small-diameter step portion 1 b ′ through a predetermined squeeze opening while being in contact with the shoulder portion 1 a of the hub wheel 1 ′, and the end portion of the small-diameter step portion 1 b ′. It is fixed in the axial direction by a caulking portion 1 c formed by plastic deformation.

[0071] The wheel bearing 24 has an outer member 4 integrally formed with a vehicle body mounting flange 4c on the outer periphery and formed with a plurality of outer rolling surfaces 4a, 4b on the inner periphery, and on the outer periphery. Two inner races 1 9 ′, 6 ′ formed with inner rolling surfaces 19 a, 6 a facing the outer rolling surfaces 4 a, 4 b of these double rows, and both rolling surfaces 4 a, Between 1 9 a and 4 b, 6 a Are provided with a plurality of tapered rollers 2 1, 1 0, which are rotatably accommodated via cages 20, 8.

[0072] Here, in the present embodiment, the tapered roller on the inner side is similar to the above-described embodiment.

1 0 row pitch circle diameter PCD i is the outer tapered roller 2 1 row pitch diameter P CD o is larger than P CD o (P CD i> P CD o) and the inner cone The roller diameter di of the roller 10 row is set to be larger than the roller diameter do of the outer side roller 2 (di> do). And the outer side tapered roller 2 1 row roller length L o and inner one side tapered roller length L i are set to be the same (L o = L i) The number of rollers in the tapered roller 2 1 and 1 0 rows is set to be the same. As a result, the rigidity and life of the bearing can be improved while achieving light weight and compactness, and the inner diameter of the tapered roller 10 row on the inner side corresponds to the amount of expansion of the pitch circle diameter PCD i. The shaft diameter d2 of the small-diameter stepped portion 1b 'in the hub ring 1' on one side can be made larger (d2> d1 (Fig. 1)), and the strength and durability of the hub ring 1 ' Can be improved.

Example 8

FIG. 8 is a longitudinal sectional view showing an eighth embodiment of the wheel bearing device according to the invention. Note that this embodiment is basically the same as the above-described sixth embodiment (FIG. 6) except that the configuration of the wheel is different, and that the same parts and parts having the same function or the same function are the same. Reference numerals are assigned and detailed description is omitted.

[0074] This wheel bearing device is for a driven wheel called the third generation, and is press-fitted into the outer member 4, the hub wheel 22 ', and the small-diameter step portion 13b' of the hub wheel 22 '. And an inner member 25 made of an inner ring 6 '. The hub wheel 22 'is formed of medium and high carbon steel containing carbon 0.440 to 0.8 ow t%, such as S 53 C, and the inner rolling surface 22a and the small diameter from the seal land 3b where the seal 15 is in sliding contact. The surface hardness of the stepped part 1 3 b 'is in the range of 58 to 64 H RC by induction hardening.

[0075] Here, this embodiment is similar to the above-described sixth embodiment. Tapered roller 1 Pitch circle diameter of row 0 PCD i is set to a larger diameter (PCD i> PCDo) than the pitch circle diameter P CD o of 21 rows of outer side tapered roller on inner side 1 The 0-row roller diameter di is set to a larger diameter (di> do) than the 21-row roller diameter do. In addition, the roller length L o of the outer row of tapered rollers 21 and the roller length L i of the inner row of 10 are set to be the same (L o = L i). , 1 0 The number of rollers in the row is set to be the same. As a result, it is possible to improve the rigidity and life of the bearing while achieving light weight and compactness, and to cope with the expansion amount of the pitch circle diameter PC D i in the 10-row tapered roller on the inner side. The shaft diameter d2 of the small diameter step 1 3 b 'in the hub ring 22' on the inner side can be made larger (d2> d1), and the strength of the hub ring 22 'is improved. Can be made.

Example 9

FIG. 9 is a longitudinal sectional view showing a ninth embodiment of the wheel bearing device according to the invention. This embodiment is basically different from the above-described fifth embodiment (FIG. 5) only in the configuration of the tapered roller on one inner side, and other parts having the same parts, the same parts, or the same functions. The parts are denoted by the same reference numerals, and detailed description is omitted.

This wheel bearing device is for a driven wheel referred to as a second generation, and includes a hub wheel 1 and a wheel bearing 26 fixed to the hub wheel 1. The wheel bearing 26 is press-fitted into the small-diameter step portion 1b through a predetermined squeezing opening while being abutted against the shoulder portion 1a of the hub wheel 1, and the end portion of the small-diameter step portion 1b is plastically deformed. It is fixed in the axial direction by a caulking portion 1 c formed in this way.

[0078] The wheel bearing 26 has an outer member 4 integrally formed with a vehicle body mounting flange 4c on the outer periphery and a plurality of outer rolling surfaces 4a and 4b formed on the inner periphery, and these on the outer periphery. Two inner races 1 9 and 27 formed with inner rolling surfaces 1 9 a and 27 a opposite to the double row outer rolling surfaces 4 a and 4 b, and both rolling surfaces 4 a, 19 a and 4 b, 27 a Double row tapered rollers 21, which are rotatably accommodated between cages 20, 28, It has 29 columns.

[0079] The inner rolling surface 27a of the inner ring 27 is formed in a taper shape that makes line contact with the tapered roller 29, and the rear surface where the small-diameter (front) side end surfaces 5d and 6d are abutted in a butted state A double-row tapered roller bearing of the matching type is constructed. The inner ring 27 and the tapered roller 29 are made of high carbon chrome steel such as SJ2 and hardened in the range of 58 to 64 H RC to the core part by quenching.

[0080] Here, in this embodiment, the pitch circle diameter P CD i of 29 inner tapered rollers 29 rows is larger than the pitch circle diameter PCD o of 21 outer tapered rollers 21 rows (PCD i> PCDo) The roller diameter di of 29 rows of tapered rollers on the inner side is set to a larger diameter (di> do) than the roller diameter do of 21 rows of tapered rollers on the outer side. The roller length L i of the inner side tapered roller 29 row is set to be longer than the roller length L o of the outer side tapered roller 21 row (L i> L o). The number of rollers in the 29th row is set to be the same. As a result, the basic dynamic load rating of the inner bearing row can be increased to improve the bearing rigidity and life, and the bearings for wheels can be made lightweight by making effective use of the bearing space. A device can be provided.

[0081] In addition, since the degree of freedom in design increases, even if there is a difference in pitch circle diameters PCDo and PCD i, the inner rings 19 and 27 are fitted together by making the inner rings 19 and 27 have the same inner diameter. Small diameter step 1 b can be formed into a straight shaft consisting of shaft diameter d 1, improving workability of hub wheel 1 and pitch circle diameter in 29 rows of tapered rollers on the inner side PC D i The inner wall 27 on the inner side 27 can be made thicker in accordance with the amount of expansion of the inner ring 27, and the inner ring 27 inner rolling surface 27a and outer diameter 6e By suppressing the generated hoop stress, the strength and durability of the inner ring 27 can be improved.

Example 10

FIG. 10 is a longitudinal sectional view showing a tenth embodiment of the wheel bearing device according to the present invention. This embodiment is the same as the ninth embodiment (FIG. 9) described above. Specifically, only the configuration of the hub wheel is different, and other parts and parts having the same parts or functions having the same functions are denoted by the same reference numerals and detailed description thereof is omitted.

This wheel bearing device is for a driven wheel called the third generation, and is press-fitted into the outer member 4, the hub wheel 2 2, and the small-diameter step portion 1 3 b of the hub wheel 2 2. And an inner member 30 composed of an inner ring 27. The inner ring 27 has its small-diameter end face 6d abutted against the shoulder 1 3c of the hub ring 2 2 in abutting condition and is press-fitted into the small-diameter step 1 3b via a predetermined shimoshiro. 1 It is fixed in the axial direction by c.

[0084] Here, in the present embodiment, as in the above-described embodiment, the pitch circle diameter PCD i of the inner side tapered roller 29 row is more than the pitch circle diameter PCD o of the outer side tapered roller 21 row. Is also set to a large diameter (PCD i> PCD o), and the roller diameter di of the inner side of the roller 29 is larger than the roller diameter di of the outer side of the tapered roller 21 of the outer side 21 ( di> do). Also, the inner side tapered roller 2 9 row roller length L i is set to be longer than the outer side tapered roller length 2 row roller length L o (L i> L o). Rollers 2 1 and 2 9 The number of rollers is set to be the same. As a result, the basic dynamic load rating of the inner bearing row can be increased and the rigidity and life of the bearing can be improved while further reducing weight and compactness. Also, the inner ring 27 on the inner side 27 can be increased in thickness t corresponding to the amount of expansion of the pitch circle diameter PCD i in the 29-row tapered roller on the inner side, and the plasticity of the caulking portion 1 c can be increased. It is possible to improve the strength and durability of the hub wheel 2 2 and the inner ring 2 7 by suppressing the hoop stress generated on the inner raceway surface 2 7 a and the outer diameter 6 e of the inner ring 2 7 due to the deformation.

Example 11

FIG. 11 is a longitudinal sectional view showing a first embodiment of a wheel bearing device according to the present invention. This embodiment is basically different from the ninth embodiment (FIG. 9) described above except that the configuration of the hub wheel and the wheel bearing is partially different. Parts are denoted by the same reference numerals and detailed description thereof is omitted. This wheel bearing device is for a driven wheel called a second generation, and includes a hub wheel 1 ′ and a wheel bearing 31 fixed to the hub wheel 1 ′. The wheel bearing 31 is press-fitted into the small-diameter step portion 1 b ′ through a predetermined squeeze opening while being abutted against the shoulder portion 1 a of the hub wheel 1 ′, and the end portion of the small-diameter step portion 1 b ′ is It is fixed in the axial direction by a caulking portion 1 c formed by plastic deformation.

[0087] The wheel bearing 31 has a vehicle body mounting flange 4c integrally formed on the outer periphery, an outer member 4 having a plurality of outer rolling surfaces 4a and 4b formed on the inner periphery, and these on the outer periphery. Two inner races 1 9 'and 27' formed with inner rolling surfaces 1 9a and 27a opposite to the double row outer rolling surfaces 4a and 4b, and both rolling surfaces 4a and 19 A plurality of tapered rollers 2 1 and 29 are provided between a and 4 b and 2 7 a so as to be freely rollable via cages 20 and 28.

[0088] Here, in the present embodiment, as in the above-described embodiment, the pitch circle diameter PCD i of 29 rows of tapered rollers on the inner side is larger than the pitch circle diameter PCDo of 21 rows of tapered rollers on the outer side. (PCD i> PCDo) and the roller diameter di of the inner side tapered roller 29 row is set to a larger diameter (di> do) than the roller diameter do of the outer side tapered roller 21 row . The roller length L i of the inner side tapered roller 29 row is set to be longer than the roller length L o of the outer side tapered roller 21 row (L i> L o), and those tapered rollers The number of rollers in the 21st and 29th rows is set to be the same. As a result, the rigidity and life of the bearing can be improved while achieving light weight and compactness, and the inner diameter can be increased in accordance with the amount of expansion of the pitch circle diameter PCD i in the 29 rows of tapered rollers on the inner side. The shaft diameter d2 of the small diameter step 1b 'on the side hub wheel 1' can be made larger (d 2> d 1), and the strength of the hub wheel 1 'can be improved. it can.

Example 12

FIG. 12 is a longitudinal sectional view showing a first embodiment of a wheel bearing device according to the present invention. This embodiment is basically the same as the first embodiment (FIG. 11) described above except that the configuration of the hub wheel is different. Parts and parts having the same function are denoted by the same reference numerals, and detailed description thereof is omitted.

[0090] This wheel bearing device is for a driven wheel referred to as a third generation, and is press-fitted into the outer member 4, the hub wheel 22 ', and the small-diameter step portion 13b' of the hub wheel 22 '. And an inner member 32 comprising an inner ring 27 ′.

[0091] Here, in the present embodiment, like the seventh embodiment described above, the pitch circle diameter of 29 rows of tapered rollers on the inner side PCD i is the pitch circle diameter P of 21 rows of tapered rollers on the outer side. The diameter is set larger than CD o (PCD i> PCDo), and the roller diameter di of the inner side tapered roller 29 row is larger than the roller diameter do of the outer side tapered roller 21 row (di> do ) Is set. Also, the roller length L i of the inner side tapered roller 29 row is set to be longer than the roller length L o of the outer side tapered roller 21 row (L i> L o). , 29 rows are set to have the same number of rollers. This makes it possible to increase the basic dynamic load rating of the inner bearing row while improving weight and compactness, thereby improving the rigidity and life of the bearing, and reducing the inner diameter of the hub ring 22 'on the inner side. The shaft diameter d2 of the stepped portion 13b 'can be formed to have a large diameter (d2> d1), and the strength and durability of the hub wheel 22' can be improved. Example 13

FIG. 13 is a longitudinal sectional view showing a first embodiment of a wheel bearing device according to the present invention. Note that this embodiment is basically different from the ninth embodiment (FIG. 9) described above, except that the configuration of the tapered roller on one side is basically the same. Are denoted by the same reference numerals, and detailed description thereof is omitted.

This wheel bearing device is for a driven wheel called the second generation, and includes a hub wheel 1 and a wheel bearing 33 fixed to the hub wheel 1. The wheel bearing 33 is press-fitted into the small-diameter step portion 1b through a predetermined squeeze opening while being abutted against the shoulder portion 1a of the hub wheel 1, and the end portion of the small-diameter step portion 1b is plastically deformed. It is fixed in the axial direction by a caulking portion 1 c formed in this way.

[0094] The wheel bearing 33 has a vehicle body mounting flange 4c integrally on the outer periphery and a plurality of inner periphery flanges. An outer member 4 in which outer rolling surfaces 4 a and 4 b of the row are formed, and inner rolling surfaces 1 9 a and 34 a facing the outer rolling surfaces 4 a and 4 b of these double rows on the outer periphery are provided. Double-row cones accommodated in a freely rolling manner via cages 20 and 35 between two inner rings 1 9 and 34 formed respectively, and both rolling surfaces 4 a and 19 a and 4 b and 34 a It has 21 and 36 rollers. The inner ring 34 and the tapered roller 36 are made of high carbon chrome steel such as SUJ 2 and hardened in the range of 58 to 64 H RC to the core part by quenching.

[0095] Here, in this embodiment, the pitch circle diameter P CD i of 36 rows of tapered rollers on the inner side is larger than the pitch circle diameter PCD o of 21 rows of tapered rollers on the outer side (PCD i> PCDo) The roller length L i of 36 rows of tapered rollers on the inner side is set to be longer than the roller length L o of 21 rows of tapered rollers on the outer side (L i> L o). Also, the roller diameter di of 36 rows of inner side tapered rollers and the roller diameter do of 21 rows of outer side tapered rollers are set to be the same (di = do), and the number of rollers of 36 rows of inner side tapered rollers is set. Z i is set to be larger than the number of rollers Z o on the outer side tapered roller 21 row (Z i> Z o). As a result, it is possible to provide a wheel bearing device that is lighter and more compact and has a higher basic rated load on the inner bearing row and improved rigidity and life of the bearing.

[0096] Further, since the degree of freedom in design increases, even if there is a difference in pitch circle diameters PCDo and PCD i, the inner rings 19 and 34 are fitted together by making the inner diameters of the inner rings 19 and 34 the same. Small diameter step 1 b can be formed into a straight shaft consisting of shaft diameter d 1, improving workability of hub wheel 1 and pitch circle diameter in 36 rows of tapered rollers on one inner side PC D i The inner wall 34 on the inner side 34 can be increased in thickness t corresponding to the amount of expansion of the inner ring 34, and the inner ring 34 inner rolling surface 34a and outer diameter 6e By suppressing the generated hoop stress, the strength and durability of the inner ring 34 can be improved.

Example 14

FIG. 14 is a longitudinal sectional view showing a 14th embodiment of a wheel bearing device according to the present invention. FIG. Note that this embodiment is basically the same as the above-described first and third embodiments (Fig. 13) except that the configuration of the hub wheel is different, and the same parts and parts having the same function or the same function. Reference numerals are assigned and detailed description is omitted.

[0098] This wheel bearing device is for a driven wheel called the third generation, and the inner member is press-fitted into the outer member 4, the hub wheel 22, and the small-diameter step portion 13b of the hub wheel 22. And an inner member 37 composed of a ring 34.

[0099] Here, in the present embodiment, similar to the above-described embodiment, the pitch circle diameter PCD i of the inner side tapered roller 36 row is derived from the pitch circle diameter P CDo of the outer side tapered roller 21 row. Is also set to a large diameter (P CD i> P CD o), and the inner side tapered roller roller 36 row length L i is longer than the outer side tapered roller 2 single row roller length L o. It is set (L i> Lo). Also, the roller diameter di of 36 rows of tapered rollers on the inner side and the roller diameter do of the outer rows of 2 tapered rollers 21 are set to the same-(di = do), and with the difference in pitch circle diameter, Inner side tapered roller 36 rows of rollers Z i is set larger than roller side tapered roller count Z o (Z i> Z o). This makes it possible to improve the rigidity and life of the bearing while achieving further light weight and compactness, as well as corresponding to the increased diameter of the pitch circle diameter P CDi in the 36-row tapered roller on the inner side. The wall thickness t of the inner ring 34 on the inner side can be increased. Therefore, the hoop stress generated on the inner raceway 34a and outer diameter 6e of the inner ring 34 due to plastic deformation of the caulking portion 1c is suppressed, and the strength and durability of the hub ring 22 and inner ring 34 are improved. Can be made.

Example 15

FIG. 15 is a longitudinal sectional view showing a fifteenth embodiment of the wheel bearing device according to the present invention. Note that this embodiment is basically the same as the above-mentioned first to third embodiments (Fig. 13) except that the configuration of the hub wheel and the wheel bearing is partially different, and has the same parts, the same parts, and the same functions. Parts and parts are denoted by the same reference numerals, and detailed description is omitted.

[0101] This wheel bearing device is for a driven wheel called the second generation. 'And a wheel bearing 38 fixed to the hub wheel 1'. The wheel bearing 38 is press-fitted into the small-diameter step portion 1 b ′ through a predetermined shim opening while abutting against the shoulder portion 1 a of the hub wheel 1 ′, and the end portion of the small-diameter step portion 1 b ′ is It is fixed in the axial direction by a caulking portion 1 c formed by plastic deformation.

[0102] The wheel bearing 38 has an outer member 4 having a body mounting flange 4c integrally formed on the outer periphery and a plurality of outer rolling surfaces 4a, 4b formed on the inner periphery, and these on the outer periphery. Inner rolling surfaces 19a and 34a facing the double-row outer rolling surfaces 4a and 4b were formed, respectively, and were set thinner than the inner rings 19 and 34 of the first to third embodiments described above. Two inner rings 1 9 'and 34' and a plurality of tapered rollers 2 1 accommodated in a rolling manner via cages 20 and 35 between both rolling surfaces 4a, 19a and 4b and 34a 2 1 36.

[0103] Here, in the present embodiment, as with the above-described embodiment, the pitch circle diameter PCD i of the inner side tapered roller 36 row is equal to the pitch circle diameter P CD o of the outer side tapered roller 21 row. Is also set to a large diameter (P CD i> P CD o), and the inner side tapered roller roller 36 row length L i is longer than the outer side tapered roller 2 single row roller length L o. It is set (L i> Lo). Also, the roller diameter di of 36 rows of tapered rollers on the inner side and the roller diameter do of the outer rows of 2 tapered rollers 21 are set to the same-(di = do), and with the difference in pitch circle diameter, Inner side tapered roller 36 rows of rollers Z i is set larger than roller side tapered roller count Z o (Z i> Z o). As a result, the rigidity and life of the bearing can be improved while achieving light weight and compactness, and the hub wheel 1 is compatible with the amount of expansion of the pitch circle diameter PCD i in the 36 rows of tapered rollers on the inner side. The shaft diameter d2 of the small diameter step 1b 'at' can be made large (d 2> d 1 (Fig. 1 3)), and the strength of the hub wheel 1 'can be improved. it can.

Example 16

FIG. 16 is a longitudinal sectional view showing a sixteenth embodiment of the wheel bearing device according to the present invention. This embodiment is the same as the above-described 15th embodiment (FIG. 15). Basically, only the configuration of the hub wheel is different, and other parts and parts having the same parts or functions having the same functions are denoted by the same reference numerals and detailed description thereof is omitted.

[0105] This wheel bearing device is for a driven wheel called the third generation, and is press-fitted into the outer member 4, the hub wheel 22 ', and the small-diameter step portion 1 3 b' of the hub wheel 22 '. And an inner member 39 made of an inner ring 34 '.

Here, in this embodiment, the pitch circle diameter PC D i of 36 rows of tapered rollers on the inner side is larger than the pitch circle diameter PCD o of 21 rows of tapered rollers on the outer side (P CD i> PCDo ) And the length L i of the 36-side tapered roller on the inner side is set longer than the roller length L o of the 21-side tapered roller on the outer side (L i> L o ) In addition, the roller diameter di of 36 rows of tapered rollers on the inner side and the roller diameter do of the 21 rows of tapered rollers on the outer side are set to be the same (di = do). The number of rollers in 36 rows of tapered rollers Z i is set to be greater than the number of rollers Z in outer rows of tapered rollers 21 (Z i> Z o). As a result, the weight and weight of the bearing can be further improved, and the rigidity and life of the bearing can be improved. In addition, it corresponds to the expansion diameter of the pitch circle diameter PC D i in the 36 rows of inner cone cones. The shaft diameter d2 of the small-diameter stepped portion 13b 'in the hub wheel 22' can be formed large, and the strength and durability of the hub wheel 22 'can be improved.

Example 17

FIG. 17 is a longitudinal sectional view showing a seventeenth embodiment of the wheel bearing device according to the present invention. Note that this embodiment is basically different from the above-described first to third embodiments (Fig. 13) except that the configuration of the wheel bearing is basically the same, and other parts and parts having the same parts or the same functions. The same reference numerals are assigned to and detailed descriptions thereof are omitted.

This wheel bearing device is for a driven wheel called the second generation, and includes a hub wheel 1 and a wheel bearing 40 fixed to the hub wheel 1. The wheel bearing 40 is press-fitted into the small-diameter step portion 1b through a predetermined squeeze opening while being abutted against the shoulder portion 1a of the hub wheel 1, and the end portion of the small-diameter step portion 1b is plastically deformed. Formed It is fixed in the axial direction by the caulking portion 1c.

[0109] The wheel bearing 40 has a vehicle body mounting flange 4c integrally formed on the outer periphery, an outer member 41 having a plurality of outer rolling surfaces 4a, 41a formed on the inner periphery, and these on the outer periphery. Two inner races 1 9 and 42 formed with inner rolling surfaces 1 9 a and 42 a opposite to the outer rolling surfaces 4 a and 41 a in double rows, and both rolling surfaces 4 a and 19 A double row of conical rollers 21, 36 are accommodated between a and 41a, 42a via rolling cages 20, 43, respectively. The inner ring 42 is made of high carbon chrome steel such as S U J 2 and hardened in the range of 58 to 64 H RC up to the core part by quenching.

[0110] Here, in this embodiment, the pitch circle diameter P CDo of 21 rows of outer side tapered rollers is larger than the pitch circle diameter PCD i of 36 rows of tapered rollers on the inner side (PCDo> PCD i) The roller length L i of 36 rows of tapered rollers on the inner side is set to be longer than the roller length L o of 21 rows of tapered rollers on the outer side (L i> L o). Also, the roller diameter di of 36 rows of tapered rollers on the inner side and the roller diameter do of 21 rows of outer tapered rollers are set to be the same (di = do), and the number of rollers Z of the outer side tapered rollers 21 row is set to Z. o is set to be larger than the number of rollers Z i in the 36-row tapered roller on the inner side (Z o> Z i). This makes the wheel bearings lighter and more compact, increases the basic load rating of the inner bearing row, and increases the rigidity and life of the bearing without increasing the outer diameter of the outer member 41. An apparatus can be provided.

Example 18

[0111] FIG. 18 is a longitudinal sectional view showing a eighteenth embodiment of the wheel bearing device according to the present invention. This embodiment is basically different from the 17th embodiment described above (Fig. 17) except that the configuration of the hub wheel is different, and other parts and parts having the same function or the same function are not used. The same reference numerals are assigned and detailed description is omitted.

[0112] This wheel bearing device is for a driven wheel called the third generation, and includes an outer member 41, a hub wheel 22, and an inner ring press-fitted into the small-diameter step portion 13b of the hub wheel 22. And an inner member 44 made of 42. [0113] Here, in the present embodiment, the pitch circle diameter PCDo of the outer side tapered roller 21 row is larger than the pitch circle diameter PCDi of the inner side tapered roller roller 36 row, similarly to the embodiment described above. The diameter (PCDo> PCD i) is set, and the roller length L i of the inner side tapered roller row 36 is set to be longer than the roller length L o of the outer side tapered roller row 21 (L i> L o). Also, the roller diameter di of 36 rows of tapered rollers on the inner side and the roller diameter do of 21 rows of tapered rollers on the outer side are set to be the same-(di = do). The roller number Z o in the 21-side tapered roller is set to be larger than the roller number Z i in the 36-side tapered roller 36 on the inner side (Z o> Z i). This makes it possible to improve the rigidity and life of the bearing while reducing the weight and making it more compact, as well as increase the basic load rating of the inner bearing row and increase the outer diameter of the outer member 41. The rigidity and life of the bearing can be improved without doing so.

Example 19

FIG. 19 is a longitudinal sectional view showing a nineteenth embodiment of the wheel bearing device according to the present invention. Note that this embodiment is basically different from the above-described first to third embodiments (Fig. 13) except that the configuration of the hub wheel is different, and other parts or parts having the same function or the same function are used. The same reference numerals are assigned and detailed description is omitted.

This wheel bearing device is for a drive wheel called the second generation, and includes a hub wheel 45 and a wheel bearing 33 ′ fixed to the hub wheel 45. The hub wheel 45 integrally has a wheel mounting flange 3 at one end portion on the outer side, and a cylindrical small-diameter stepped portion 1 b extending in the axial direction from the wheel mounting flange 3 via a shoulder portion 1 a is formed on the outer periphery. In addition, a torque transmission selection (or spline) 45 a is formed on the inner periphery.

[0116] The wheel bearing 33 'is press-fitted into the small-diameter stepped portion 1b through a predetermined squeeze opening in a state where it abuts against the shoulder portion 1a of the hub wheel 45. The hub wheel 45 is made of medium and high carbon steel containing 0.44 to 0.8 Ow t% of carbon such as S 53 C, and is hardened by induction hardening from the shoulder 1a to the small diameter step 1b. Hardened to a range of 58-64 H RC. [0117] The wheel bearing 33 'has an outer member 4 integrally formed with a vehicle body mounting flange 4c on the outer periphery and formed with double-row outer rolling surfaces 4a, 4b on the inner periphery, and on the outer periphery. Two inner rings 1 9 and 34 formed with inner rolling surfaces 1 9 a and 34 a opposite to these double-row outer rolling surfaces 4 a and 4 b, and both rolling surfaces 4 a and 19 Double row tapered rollers 2 1 and 36 rows are provided between a and 4 b and 34 a so as to be freely rollable via cages 20 and 35 ′.

[0118] Here, in this embodiment, the pitch circle diameter P CD i of the inner side tapered roller 36 row is larger than the pitch circle diameter PCD o of the outer side tapered roller 21 row (PCD i> PCDo). The roller length L i of 36 rows of tapered rollers on the inner side is set to be longer than the roller length L o of 21 rows of tapered rollers on the outer side (L i> L o). In addition, the roller diameter di of 36 rows of tapered rollers on the inner side and the roller diameter do of 21 rows of tapered rollers on the outer side are set to be the same (di = do), and the number of rollers Z of these tapered rollers 21, 36 is Z. i and Zo are set to the same value (Zi = Zo). As a result, the basic load rating of the inner side bearing row is increased while reducing the strength of the cage 35 'due to the increase in the roller diameter di and the number of rollers Z i, while reducing the weight and making it compact. It is possible to provide a wheel bearing device in which the rigidity and life of the bearing are improved.

Example 20

FIG. 20 is a longitudinal sectional view showing a twentieth embodiment of the wheel bearing device according to the invention. This embodiment is different from the above-mentioned 15th embodiment (Fig. 15) except that the number of tapered rollers on the inner side is different, and other parts or parts having the same function or function are the same. The same reference numerals are assigned and detailed description is omitted.

[0120] This wheel bearing device is for a driven wheel called a second generation, and includes a hub wheel 1 'and a wheel bearing 38' fixed to the hub wheel 1 '.

[0121] Here, in this embodiment, the pitch circle diameter PC D i of the inner side tapered roller 36 row is larger than the pitch circle diameter PCD o of the outer side tapered roller 21 row (P CD i> PCDo ) And a 36-row saw roller on the inner side. The filter length L i is set to be longer than the roller length L o of one row of outer tapered rollers 2 (L i> L o). Further, the roller diameter di of the inner side tapered roller 36 row and the outer side tapered roller roller 21 are set to be the same (di = do), and the inner side tapered roller 36 row roller is set. The number Z i and the tapered roller 2 on the outer side 2 The number of rollers Z o in one row is set to be the same (Z i = Z o). As a result, it is possible to reduce the size and weight, and increase the basic load rating of the inner side bearing row to improve the rigidity and life of the bearing. Further, the inner side inner ring 34 'can be increased in thickness corresponding to the diameter expansion amount of the pitch circle diameter PCD i in the 36 rows of tapered rollers on the inner side.

Example 21

FIG. 21 is a longitudinal sectional view showing a second embodiment of the wheel bearing device according to the present invention. This embodiment is different from the above-mentioned 16th embodiment (Fig. 16) except that the number of tapered rollers on the inner side is different, and other parts or parts having the same function or function are the same. The same reference numerals are assigned and detailed description is omitted.

[0123] This wheel bearing device is for a driven wheel called the third generation, and is press-fitted into the outer member 4, the hub wheel 22 ', and the small-diameter step portion 13b' of the hub wheel 22 '. And an inner member 39 ′ composed of an inner ring 34 ′.

[0124] Here, in this embodiment, the pitch circle diameter PCD i of the inner side tapered roller 36 row is larger than the pitch circle diameter P CD o of the outer side tapered roller 2 row (P CD i> P CD o), and the length L i of the inner side tapered roller 36 row is set to be longer than the length L o of the outer side tapered roller 21 row (L i> Lo). Further, the roller diameter di of the inner side tapered roller 36 row and the outer side tapered roller roller 21 are set to be the same (di = do), and the inner side tapered roller 36 row roller is set. The number Z i and the tapered roller 2 on the outer side 2 The number of rollers Z o in one row is set to be the same (Z i = Z o). As a result, a lighter and more compact body can be achieved, and the strength of the cage 35 'can be prevented from being lowered. Example 11

FIG. 22 is a longitudinal sectional view showing a twenty-second embodiment of the wheel bearing device according to the present invention. Note that this embodiment is basically different from the above-described fifth embodiment (Fig. 5) only in the configuration of the hub wheel and the wheel bearing, except that the same parts are the same or have the same functions. Are denoted by the same reference numerals, and detailed description is omitted.

This wheel bearing device is for a drive wheel called the second generation, and includes a hub wheel 45 and a wheel bearing 46 fixed to the hub wheel 45. The wheel bearing 46 is integrally formed with an outer member 47 having a body mounting flange 4 c on the outer periphery and a plurality of outer rolling surfaces 4 a and 47 a on the inner periphery, and these double rows on the outer periphery. Outer rolling surfaces 4 a, 47 a Inside inner rolling surfaces 1 9 a, 48 a facing each other Two inner rings 1 9, 48, and both rolling surfaces 4 a, 19 a and 4 b , 48 a are provided with double row tapered rollers 21, 10 rows accommodated so as to roll freely through cages 20, 49.

[0127] The outer member 47 is formed of medium and high carbon steel containing 0.40 to 0.80 wt% of carbon such as S 53 C, and the double-row outer rolling surfaces 4 a and 47 a are represented by induction hardening. Hardened to a surface hardness of 58 to 64 H RC. The inner ring 48 is made of high carbon chrome steel such as SU J 2 and is hardened in the range of 58 to 64 H RC up to the core part by quenching.

Here, in this embodiment, the pitch circle diameter P CDo of the outer side tapered roller 21 row and the pitch circle diameter PC D i of the inner row of tapered roller 10 row are the same (PC Do = PCD i ) And the roller diameter di of the inner one side tapered roller 10 is set to be larger than the roller diameter do of the outer side tapered roller 21 row (di> do). In addition, the roller length L i of the inner row of tapered rollers 10 and the roller length L o of the outer row of tapered rollers 21 are set to be the same (L i = L o). The number of rollers Zo, Zi in the rollers 21, 10 row is set to be the same (Zo = Zi). As a result, the basic rated load of the inner-side bearing row can be increased without increasing the pitch circle diameter PCD i of the inner row-side tapered roller 10 row. It is possible to provide a wheel bearing device that can increase the weight, suppress the outer diameter increase of the outer member 47, reduce the weight, and improve the rigidity and life of the bearing while achieving compactness. .

Example 23

FIG. 23 is a longitudinal sectional view showing a second embodiment of the wheel bearing device according to the present invention. This embodiment is basically the same as the above-described second embodiment (FIG. 2 2) except that the configuration of the wheel bearing is partially different, and other parts having the same parts or the same functions. The same reference numerals are assigned to and detailed descriptions thereof are omitted.

[0130] This wheel bearing device is for a drive wheel called the second generation, and includes a hub wheel 45 and a wheel bearing 50 fixed to the hub wheel 45. The wheel bearing 50 includes an outer member 4 7 having a body mounting flange 4 c integrally formed on the outer periphery and double row outer rolling surfaces 4 a and 4 7 a formed on the inner periphery, and these on the outer periphery. Two inner rings 1 9 and 5 1 formed with inner rolling surfaces 1 9 a and 5 1 a opposite to the outer rolling surfaces 4 a and 4 7 a of the double row, and both rolling surfaces 4 a and 1 9 a and 4 7 a, 5 1 a are provided with double-row tapered rollers 2 1, 2 9 rows that are rotatably accommodated via cages 20, 5 2.

[0131] The inner rolling surface 5 1 a of the inner ring 5 1 is formed in a taper shape that makes line contact with the tapered roller 2 9, and the small diameter side (front) end face 5 d of the two inner rings 1 9, 5 1 6 d is a back-to-back type double row tapered roller bearing that is abutted in a butted state. Further, the inner ring 51 is made of high carbon chrome steel such as SU J 2 and is hardened in the range of 58 to 64 HRC up to the core part by quenching.

[0132] Here, in this embodiment, the outer side tapered roller 21 has one row of pitch circle diameters PCD o and the inner one side tapered roller 29 has the same pitch circle diameter PCD i (PCD o = PCD i). The roller diameter di of the inner side tapered roller 29 is set larger than the roller diameter do of the outer side roller 21 (di> do). Also, the roller length L i in the inner row of the inner row 29 is set longer than the roller length L o in the row of the tapered roller 21 in the outer row (L i> L o). At the same time, the number of rollers ₀ , 2; in these tapered rollers 21, 29 is set to the same _ (o = Z i). As in the above-described embodiment, this makes it possible to further increase the basic load rating of the inner bearing row without increasing the pitch circle diameter PCD i of 29 inner tapered rollers. It is possible to improve the rigidity and life of the bearing while suppressing the increase in the outer diameter of the side member 47 and making it lighter and more compact.

Example 24

FIG. 24 is a longitudinal sectional view showing a twenty-fourth embodiment of the wheel bearing device according to the present invention. Note that this embodiment is basically different from the 22nd embodiment described above (Fig. 22) except that the configuration of the wheel bearing is partially different, and other parts and parts having the same parts or the same functions. Are denoted by the same reference numerals, and detailed description thereof is omitted.

This wheel bearing device is for a drive wheel called the second generation, and includes a hub wheel 45 and a wheel bearing 53 fixed to the hub wheel 45. The wheel bearing 53 includes an outer member 47 having a body mounting flange 4c integrally formed on the outer periphery, and formed with double-row outer rolling surfaces 4a and 47a on the inner periphery, and these double-rows on the outer periphery. Outer raceway surfaces 4 a, 47 a Inner raceway surfaces 5 a, 48 a facing each other 5 a, 48 a formed between the two inner races 5, 48, and both raceways 4 a, 5 a and 47 a, 48 a Are equipped with double-row tapered rollers 9, 10 which are rotatably accommodated through cages 7, 49.

[0135] Here, in this embodiment, the pitch circle diameter P C D o of the nine rows of the outer side tapered rollers is the same as the pitch circle diameter P C D i of the ten rows of the inner side tapered rollers (P CD

0 = P CD i) and the inner roller roller diameter di is set larger than the roller diameter do of the outer roller roller 9 row (di> do) Yes. Also, the roller length L o of the outer side tapered roller 9 row is set to be longer than the roller length L i of the inner row 10 row (L o> L i). 9, the number of rollers in row ₀ , 2; is the same _ ( ₀ = 2

1) is set. As a result, as in the embodiment described above, the inner side And the tapered roller diameters on the outer and outer rows 10 and 9 can increase the basic load rating of the double row bearing row without increasing the PCD i and PCDo, and prevent the outer member 47 from increasing in outer diameter. And light weight ■ The rigidity and life of the bearing can be improved while achieving compactness.

Example 25

FIG. 25 is a longitudinal sectional view showing a 25th embodiment of the wheel bearing device according to the present invention. This embodiment basically differs from the above-described twenty-second embodiment (Fig. 22) only in the configuration of the hub wheel, and the same reference numerals are given to other parts and parts having the same parts or the same functions. Detailed description will be omitted.

[0137] This wheel bearing device is for a drive wheel referred to as the third generation, and includes an outer member 47, a hub wheel 54, and an inner ring press-fitted into the small-diameter step portion 1 3 b of the hub wheel 54. An inner member 55 consisting of 48 is provided. The hub wheel 54 has a wheel mounting flange 3 integrally at the outer end of the outer ring, and has an outer side inner rolling surface 22 a on the outer periphery and a cylindrical shape extending in the axial direction from the inner rolling surface 22 a. A small diameter step portion 1 3 b is formed. The inner ring 48 has a small-diameter end face 6d abutting against the shoulder part 13c of the hub wheel 54 in abutting condition, and is press-fitted into the small-diameter step part 13b through a predetermined shim. It is fixed in the axial direction by c.

[0138] The hub wheel 54 is made of medium and high carbon steel containing 0.40 to 0.80 wt% of carbon such as S 53 C, and the inner surface of the rolling ring 2 2 a from the seal land 3 b in which the seal 15 is in sliding contact. In addition, the surface hardness of the small diameter step portion 1 3 b is hardened by induction hardening to a range of 58 to 64 H RC.

[0139] Here, in the present embodiment, like the first embodiment described above, the inner one side tapered roller 10 row pitch circle diameter PC D i and the outer side tapered roller 21 row pitch circle. The diameter PCDo is set to be the same (PCD i = PCDo) and the roller length L i of the inner row of the tapered roller 10 is the same as the roller length Lo of the row of the tapered rollers 21 of the outer side ( L i = L o). In addition, the tapered diameter of the inner one 10 is set to be larger than the roller diameter do of the outer tapered roller 21 (di> do), and the inner tapered roller 1 0 columns Number of rollers Z i and tapered roller on the outer side 2 Same number of rollers Z o in one row (Z i =

Z o).

[0140] This increases the strength of the hub wheel 54 and increases the basic load rating of the inner bearing row without increasing the pitch circle diameter PCD i of the inner cone cone 10 row. In addition, the outer diameter up of the outer member 47 can be suppressed, and the rigidity and life of the bearing can be improved while further reducing the size and weight.

Example 26

[0141] FIG. 26 is a longitudinal sectional view showing a 26th embodiment of the wheel bearing device according to the present invention. Note that this embodiment is basically different from the above-described 24th embodiment (Fig. 24) except that the configuration of the hub wheel and the bearing for the wheel is different. Parts are denoted by the same reference numerals and detailed description thereof is omitted.

[0142] This wheel bearing device is for a drive wheel called second generation, and includes a hub wheel 56 and a wheel bearing 57 fixed to the hub wheel 56. The hub wheel 56 has a wheel mounting flange 3 integrally at one end on the outer side, and a cylindrical small diameter step 1 b extending in the axial direction from the wheel mounting flange 3 to the outer periphery via a shoulder 1 a. And a torque transmission selection (or spline) 45 a is formed on the inner periphery. The hub ring 56 is formed of medium and high carbon steel containing carbon 0.40 to 0.8 O wt%, such as S53C, and is surfaced by induction hardening from the shoulder 1a to the small diameter step 1b. Hardness is hardened in the range of 58-64 HRC.

[0143] The wheel bearing 5 7 is press-fitted into the small-diameter step portion 1b through a predetermined squeeze opening while being in contact with the shoulder portion 1a of the hub wheel 56, and the end of the small-diameter step portion 1b. It is fixed in the axial direction by a caulking part 1 c formed by plastic deformation of the part. This wheel bearing 5 7 has an outer member 4 7 integrally formed with a vehicle body mounting flange 4 c on the outer periphery and formed with double-row outer rolling surfaces 4 a and 4 7 a on the inner periphery, and on the outer periphery. Inner rolling surfaces 5 8 a and 4 8 a facing the outer rolling surfaces 4 a and 4 7 a of these double rows are formed, respectively. Two inner rings 58 and 48, and double-row tapered rollers 60 and 1 accommodated between the rolling surfaces 4 a, 58 a and 47 a and 48 a via cages 59 and 49, respectively. It has 0 columns. The inner ring 58 and the tapered roller 60 are made of high carbon chrome steel such as SUJ 2 and hardened in the range of 58 to 64 H RC up to the core part by quenching.

Here, in this embodiment, the pitch circle diameter P CD o of the outer side tapered roller 60 rows and the pitch circle diameter PC D i of the inner row of tapered rollers PC D i are the same (PC Do = PCD i ) And the roller length L o of the outer side tapered roller 60 row is set to be longer than the roller length L i of the inner side tapered roller 10 row (L o> L i). . In addition, the roller diameter do of the outer side tapered roller 60 row and the roller diameter di of the inner row 10 tapered roller 10 are set to be the same (do = di), and the tapered roller 60, 10 row roller The numbers Z o and Z i are set to be the same (Z o = Z i). This increases the basic load rating of the outer bearing row without increasing the pitch circle diameter PCDo of the outer side tapered roller 60 row and without increasing the number of rollers Zo of the tapered roller 60 row. Therefore, it is possible to provide a wheel bearing device that suppresses an increase in the outer diameter of the outer member 47 and is light and compact while improving the rigidity and life of the bearing.

Example 27

FIG. 27 is a longitudinal sectional view showing a twenty-seventh embodiment of the wheel bearing device according to the invention. Note that this embodiment is basically different from the above-described 26th embodiment (Fig. 26) only in the configuration of the hub wheel, and other parts and parts having the same parts or parts having the same functions are designated by the same reference numerals. The detailed description is omitted.

[0146] This wheel bearing device is for a driven wheel referred to as a second generation, and includes a hub wheel 1 'and a wheel bearing 57 fixed to the hub wheel 1'. The wheel bearing 57 is press-fitted into the small-diameter step portion 1 b ′ through a predetermined squeeze opening in contact with the shoulder portion 1 a of the hub wheel 1 ′, and the end portion of the small-diameter step portion 1 b ′ is Plastic deformation It is fixed in the axial direction by a caulking portion 1 c formed by the above.

Here, in this embodiment, the pitch circle diameter P CDo of the outer side tapered roller 60 rows and the pitch circle diameter PC D i of the inner row of tapered rollers PC D i are the same (PC Do = PCD i ) And the roller length L o of the outer side tapered roller 60 row is set to be longer than the roller length L i of the inner side tapered roller 10 row (L o> L i). . In addition, the roller diameter do of the outer side tapered roller 60 row and the roller diameter di of the inner row 10 tapered roller 10 are set to be the same (do = di), and the tapered roller 60, 10 row roller The numbers Z o and Z i are set to be the same (Z o = Z i). This increases the basic load rating of the outer bearing row without increasing the pitch circle diameter PCDo of the outer side tapered roller 60 row and without increasing the number of rollers Zo of the tapered roller 60 row. Therefore, the outer diameter of the outer member 47 can be suppressed and the rigidity and life of the bearing can be improved while reducing the weight and size.

Example 28

FIG. 28 is a longitudinal sectional view showing a twenty-eighth embodiment of the wheel bearing device according to the invention. Note that this embodiment is basically different from the above-described twenty-sixth embodiment (Fig. 26) except that the configuration of the hub wheel is basically the same, and other parts and parts having the same parts or the same functions are denoted by the same reference numerals. Detailed description will be omitted.

[0149] This wheel bearing device is for a drive wheel referred to as the third generation, and includes an outer member 47, a hub wheel 61, and an inner ring press-fitted into the small-diameter step portion 1 3 b of the hub wheel 61. An inner member 62 consisting of 48 is provided. The hub wheel 61 integrally has a wheel mounting flange 3 at the outer end thereof, and has an outer inner rolling surface 61 a on the outer periphery and a cylindrical shape extending in the axial direction from the inner rolling surface 61 a. A small diameter step portion 1 3 b is formed.

[0150] The hub wheel 61 is made of medium and high carbon steel containing 0.44 to 0.80 wt% of carbon such as S 53 C, and the seal land portion 3 b in sliding contact with the seal 1 5 to the inner rolling surface 6 1 a In addition, the surface hardness of the small diameter step portion 1 3 b is hardened by induction hardening to a range of 58 to 64 H RC. [0151] Here, in the present embodiment, as in the above-described embodiment, the pitch circle diameter P CDo of the outer side tapered roller 60 rows and the pitch circle diameter P CD i of the 10 inner row tapered rollers P CD i Are set to the same (P CD o = P CD i), and the roller length L o of the outer side tapered roller 60 row is set longer than the roller length L i of the inner side tapered roller 100 row. (L o> L i). Further, the roller diameter do of the outer side conical roller 60 rows and the roller diameter di of the inner row 10 tapered rollers 10 are set to be the same (do = di), and the tapered rollers 60, 10 rows The number of rollers Zo and Zi are set to be the same (Zo = Zi). This increases the strength and rigidity of the hub wheel 61, and also increases the number of rollers Z o of the tapered roller 60 without increasing the pitch diameter P CD o of the outer tapered roller 60 row. As a result, the basic load rating of the bearing row on the one side of the counter can be increased, and the outer diameter of the outer member 47 can be suppressed to increase the weight and the rigidity and life of the bearing can be improved while achieving compactness.

Example 29

[0152] Fig. 29 is a longitudinal sectional view showing a twenty-ninth embodiment of the wheel bearing device according to the present invention. This embodiment is basically different from the 28th embodiment (FIG. 28) described above except that the configuration of the hub wheel is different, and other parts having the same parts or the same functions are denoted by the same reference numerals. Detailed description is omitted.

[0153] This wheel bearing device is for a driven wheel referred to as a third generation, and includes an outer member 47, a hub wheel 63, and an inner ring press-fitted into the small-diameter step portion 1 3 b of the hub wheel 63. An inner member 64 consisting of 48 is provided. The hub wheel 63 integrally has a wheel mounting flange 3 at the outer end portion, and has an outer inner rolling surface 61a on the outer periphery and a small diameter extending in the axial direction from the inner rolling surface 61a. A stepped portion 1 3 b is formed. This hub ring 63 is formed of medium and high carbon steel containing carbon 0.40 to 0.80 wt% such as S 53 C, and from the seal land portion 3 b in which the seal 15 is in sliding contact to the inner rolling surface 6 1 a and The surface hardness is hardened to 58 to 64 H RC by induction hardening over the small diameter step 1 3 b.

[0154] Here, the present embodiment is similar to the above-described embodiment, in that the outer side tapered roller 60-row pitch circle diameter PCD o and inner one-side tapered roller 10 0-row pitch circle diameter PCD i is set to the same (PCDo = PCD i) and outer-side tapered roller 60-row roller length L o is set to be longer than the roller length L i of the row 10 tapered roller on the inner side (L o> L i). Further, the roller diameter do of the outer side conical roller 60 rows and the roller diameter di of the inner row 10 tapered rollers 10 are set to be the same (do = di), and the tapered rollers 60, 10 rows The number of rollers Zo and Zi are set to be the same (Zo = Zi). As a result, the strength and rigidity of the hub wheel 63 are increased, and the outer diameter of the tapered roller 60 rows of the 60 rows is increased without increasing the pitch diameter PCDo and without increasing the number of rollers Z o of the tapered roller 60. The basic load rating of the bearing row on one side can be increased, and the outer diameter of the outer member 47 can be prevented from increasing and the rigidity and life of the bearing can be improved while achieving light weight and compactness.

Example 30

[0155] Fig. 30 is a longitudinal sectional view showing a thirtieth embodiment of the wheel bearing device according to the present invention. Note that this embodiment is basically different from the 28th embodiment (Fig. 28) described above, except that the structure of the wheel is only partially different, and other parts having the same parts, the same parts, or the same functions. Parts are denoted by the same reference numerals and detailed description is omitted.

[0156] This wheel bearing device is for a drive wheel called a third generation, and includes an inner member 64 comprising a hub wheel 63 and an inner ring 48 press-fitted and fixed to the hub wheel 63. And an outer member 47 inserted on the inner member 64.

[0157] The hub wheel 63 integrally has a wheel mounting flange 3 at one end portion on the outer side, and has a taper-shaped inner rolling surface 63a on the outer side on the outer periphery, and the inner rolling surface 63a. A cylindrical small diameter step portion 13 b extending in the axial direction via the shoulder portion 13 c is formed, and a torque transmission selection (or spline) 45 a is formed on the inner periphery. The hub wheel 63 is made of medium and high carbon steel containing 0.40 to 0.80 wt% of carbon such as S 53 C, and the base 3 b on the inner side of the wheel mounting flange 3 to the inner rolling surface 63 a and the shoulder. Inductive firing over small diameter step 1 3 b through part 1 3 c The surface hardness is set in the range of 58 to 64 H RC by putting.

[0158] The outer member 47 has a vehicle body mounting flange 4c integrally on its outer periphery, and an outer rolling surface 4a on the one side of the hub wheel 63 facing the inner rolling surface 63a of the hub wheel 63 on the inner periphery, An inner side outer raceway surface 47a facing the inner raceway surface 48a of the inner ring 48 is integrally formed. Then, double rows of tapered rollers 66, 10 are accommodated in a freely rolling manner via cages 65, 49 between both rolling surfaces. The tapered roller 66 is made of high carbon chrome steel such as S U J 2 and hardened to the core by a quenching process in the range of 58 to 64 H RC.

[0159] Here, in this embodiment, the pitch circle diameter PCDo of the outer side tapered roller 66 row and the pitch circle diameter PCDi of the inner row of tapered roller 10 row are the same (PC Do = PCD i ) And the outer side tapered roller 66 row roller diameter do is set smaller than the inner roller roller diameter di (do <di), and the inner side tapered roller The roller length L i of the 10th row is set longer than the roller length L o of the outer side tapered roller 66 row (L i> L o). Further, the number of rollers Zo in the outer side tapered roller 66 row is set to be larger than the number of rollers Zi in the inner row of tapered roller 10 row (Zo> Zi). As a result, it is possible to increase the basic load rating of both bearing rows without increasing the pitch circle diameter PCDo of the outer side tapered rollers 66 rows, reducing the outer diameter of the outer member 47 and reducing the weight. ■ It is possible to provide a wheel bearing device that improves the rigidity and life of the bearing while achieving compactness.

Example 31

FIG. 31 is a longitudinal sectional view showing a thirty-first embodiment of the wheel bearing device according to the present invention. This embodiment is for a driven wheel and basically differs from the 30th embodiment (FIG. 30) described above except that the configuration of the hub wheel is different, and other parts and parts having the same parts or the same functions. The same reference numerals are assigned to the same and detailed description thereof is omitted.

[0161] This wheel bearing device is for a driven wheel called the second generation, and includes a hub wheel 1 'and a wheel bearing 67 fixed to the hub wheel 1'. For wheels The bearing 67 is press-fitted into the small-diameter step portion 1 b ′ through a predetermined squeeze opening while being abutted against the shoulder portion 1 a of the hub wheel 1 ′, and the end of the small-diameter step portion 1 b ′ is plastically deformed It is fixed in the axial direction by the caulking portion 1 c formed in advance.

[0162] The wheel bearing 67 is composed of an outer member 47 and two inner rings 6 each formed with an inner rolling surface 68a, 48a opposite to the outer circumferential surface 4a, 47a of the double row on the outer circumference. 8, 48, and double-row tapered rollers 66, 10 which are rotatably accommodated via cages 65, 49 between both rolling surfaces 4a, 68a and 47a, 48a. The

[0163] The inner rolling surface 68a of the inner ring 68 on the outer side is formed in a taper shape that makes a line contact with the tapered roller 66. Then, a back-to-back type double-row tapered roller bearing in which the small-diameter side (front) end faces 5 d and 6 d of the pair of inner rings 68 and 48 are abutted in a butted state is configured. The inner diameter of the inner ring 68 is set to be the same as the inner diameter of the inner ring 48 on the inner side. As a result, the small-diameter stepped portion 1 b ′ can be integrally processed in a uniform shape, and the number of processing steps can be simplified and the cost can be reduced. The inner ring 68 is formed of a high carbon chrome steel such as SU J 2 and is hardened in the range of 58 to 64 HRC to the core portion by quenching, like the inner ring 48 on the inner side.

Here, in the present embodiment, as in the first embodiment described above, the outer side tapered roller 66 rows of pitch circle diameters P CDo and the inner one side tapered rollers 10 rows of pitch circle diameters. PC D i is set to the same value (PCDo = PCD i), and the roller diameter dough of the outer roller row 66 is smaller than the roller diameter di of the 10 row tapered roller di ( do <di), and the roller length L i of the inner one side roller is set to be longer than the roller length L o of the outer side tapered roller row 66 (L i> L o ) Also, due to the difference in diameter between the outer side tapered roller 66 row roller diameter do and the inner side tapered roller roller 10, the outer roller side tapered roller 66 row roller count Z o Tapered roller on the side 10 Rollers in row 0 are accommodated more than Z i (Z o> Z i). This allows both bearings without increasing the pitch circle diameter P CD o of the 66 rows of tapered rollers on the outer side. The basic load rating of the row can be increased, the outer diameter of the outer member 47 can be suppressed, and the rigidity and life of the bearing can be improved while achieving light weight and compactness.

Although the embodiments of the present invention have been described above, the present invention is not limited to these embodiments and is merely an example and does not depart from the gist of the present invention. In addition, it is needless to say that the present invention can be carried out in various forms, and the scope of the present invention is indicated by the description of the scope of claims, and further, the equivalent meaning and scope of the scope of the claims Includes all changes.

Industrial applicability

The wheel bearing device according to the present invention can be applied to a wheel bearing device of a second or third generation structure regardless of whether it is for a driving wheel or a driven wheel.

Brief Description of Drawings

FIG. 1 is a longitudinal sectional view showing a first embodiment of a wheel bearing device according to the present invention.

FIG. 2 is a longitudinal sectional view showing a second embodiment of the wheel bearing device according to the present invention.

FIG. 3 is a longitudinal sectional view showing a third embodiment of a wheel bearing device according to the present invention.

FIG. 4 is a longitudinal sectional view showing a fourth embodiment of a wheel bearing device according to the present invention.

FIG. 5 is a longitudinal sectional view showing a fifth embodiment of the wheel bearing device according to the invention.

FIG. 6 is a longitudinal sectional view showing a sixth embodiment of the wheel bearing device according to the invention.

FIG. 7 is a longitudinal sectional view showing a seventh embodiment of the wheel bearing device according to the invention.

FIG. 8 is a longitudinal sectional view showing an eighth embodiment of the wheel bearing device according to the invention.

FIG. 9 is a longitudinal sectional view showing a ninth embodiment of the wheel bearing device according to the invention.

FIG. 10 is a longitudinal sectional view showing a tenth embodiment of the wheel bearing device according to the present invention.

FIG. 11 is a longitudinal sectional view showing a first embodiment of a wheel bearing device according to the present invention.

FIG. 12 is a longitudinal sectional view showing a first embodiment of a wheel bearing device according to the present invention. FIG. 13 is a longitudinal sectional view showing a third embodiment of the wheel bearing device according to the present invention ί ::.

FIG. 14 is a longitudinal sectional view showing a fourteenth embodiment of the wheel bearing device according to the present invention ί ::.

FIG. 15 is a longitudinal sectional view showing the fifteenth embodiment of the wheel bearing device according to the present invention I :.

FIG. 16 is a longitudinal sectional view showing the sixteenth embodiment of the wheel bearing device according to the present invention I :.

FIG. 17 is a longitudinal sectional view showing the seventeenth embodiment of the present invention I :: wheel bearing device according to the present invention.

FIG. 18 is a longitudinal sectional view showing the eighteenth embodiment of the wheel bearing device according to the present invention I :.

FIG. 19 is a longitudinal sectional view showing the nineteenth embodiment of the wheel bearing device according to the present invention I :.

FIG. 20 is a longitudinal sectional view showing the 20th embodiment of the wheel bearing device according to the present invention I :.

FIG. 21 is a longitudinal sectional view showing a second embodiment of the wheel bearing device according to the present invention I :.

FIG. 22 is a longitudinal sectional view showing a second embodiment of the wheel bearing device according to the present invention I :.

FIG. 23 is a longitudinal sectional view showing a second embodiment of the wheel bearing device according to the present invention I :.

FIG. 24 is a longitudinal sectional view showing a 24th embodiment of the wheel bearing device according to the present invention I :.

FIG. 25 is a longitudinal sectional view showing a 25th embodiment of the wheel bearing device according to the present invention I :.

FIG. 26 is a longitudinal sectional view showing a 26th embodiment of the wheel bearing device according to the present invention I :. FIG. 27 is a longitudinal sectional view showing a twenty-seventh embodiment of a wheel bearing device according to the invention.

FIG. 28 is a longitudinal sectional view showing a twenty-eighth embodiment of the wheel bearing device according to the invention.

FIG. 29 is a longitudinal sectional view showing a twenty-ninth embodiment of the wheel bearing device according to the present invention.

FIG. 30 is a longitudinal sectional view showing a thirtieth embodiment of the wheel bearing device according to the invention.

FIG. 31 is a longitudinal sectional view showing a 31st embodiment of a wheel bearing device according to the present invention.

FIG. 32 is a longitudinal sectional view showing a conventional wheel bearing device.

FIG. 33 is a longitudinal sectional view showing another conventional wheel bearing device.

Explanation of symbols

1, 1 ', 1 3, 1 3', 22, 22 ', 45, 54, 56, 6 1, 63-

1 a, 1 3 c

Shoulder

1 b, 1 b ', 1 3 b, 1 3 b'

• Small diameter step

1 c

Caulking section

2, 1 6, 1 8, 24 26, 3 1, 33, 33 38, 38 ', 40, 46, 50, 53, 5, 67

3 Single wheel Mounting flange Leland

4, 4 1, 47 Outer member

4 a, 4 b, 4 1 a, 47 a Outer rolling surface

4 c Body mounting flange

5, 6, 5 ', 6', 1 9, 19 ', 27, 27', 34, 34 ', 42, 48, 51, 58, 68-

5 a, 6 a, 1 3 a, 1 9 a, 22 a, 27 a, 34 a, 42 a, 48 a, 5 1 a, 58 a, 6 1 a, 63 a, 68 a- Running surface

5 b, 6 b

5 c, 6 c small! ¾

5d, 6d small diameter side u meta

6 e Outer diameter of inner ring on inner side

7, 8, 20, 28, 35, 35 ', 43, 49, 52, 59, 65-' Retainer

9, 2 1, 66 One side of tapered roller

1 0, 29, 36, 60 One side tapered roller

1 1, 1 2, 1 5 series

1 4, 1 7, 23, 25, 30, 32, 37, 39, 39 ', 44, 55,

62, 64 Inner member

45 a celebrity —Chillon

1 00, 1 1 4 Hub car m

1 00 a, 1 07 a, 1 1 4 a, 1 1 5 a Inside Rolling surface

1 00 b, 1 1 3 Wheel mounting flange

1 0 1 Double row rolling bearing

1 02 Constant velocity universal joint

1 03, 1 1 2 Outer part

1 03 a, 1 03 b, 1 1 2 a, 1 1 2 b Outer rolling surface

1 03 c, 1 1 2 c Body mounting flange

1 04, 1 1 6 Inner part

1 05, 1 1 7, 1 1 8 Poles

1 06 Conical roller

1 07, 1 1 5 Inner ring

1 08 Outer joint member

1 08 a Track groove 1 09 Mouse part

1 1 0 shoulder

1 1 1 stop car ffl

1 1 4 b Small diameter Step

1 1 4 c Clamping section

1 1 9, 1 20 hold

1 21, 1 22 series

d 1, d 2 Small diameter Step diameter

d i Roller diameter of tapered roller on inner side

d o Outer side tapered roller diameter

D 1 Pitch circle diameter of outer pole

D 2 Inner side pole pitch circle diameter

L i Roller length of tapered roller on one side

L o Roller length of outer side tapered roller

PCD i inner tapered roller Pitch circle diameter

PCDo Pitch circle diameter of outer side tapered roller

t Inner ring of inner roller

Z i Tapered roller on one inner side

Z o Outer side tapered roller

Claims

The scope of the claims

[1] An outer member integrally having a vehicle body mounting flange to be attached to the knuckle on the outer periphery, and having a double row outer rolling surface formed on the inner periphery;

-Hub wheel with a wheel mounting flange for mounting the wheel at the end, with a small diameter step formed on the outer periphery, and press-fitted into the small diameter step of this hub wheel, and the outer periphery of the double row on the outer periphery An inner member composed of at least one inner ring formed with an inner rolling surface facing the rolling surface;

In the wheel bearing device comprising the inner member and a double row tapered roller row accommodated so as to roll between both rolling surfaces of the outer member,

The pitch circle diameter of the inner side tapered roller row of the double row tapered roller row is set larger than the pitch circle diameter of the outer side tapered roller row, and further, the inner side tapered roller row. The roller diameter of the tapered roller row on the one side of the outer side is set to be larger than the roller diameter of the tapered roller row on the one side, and the roller length of the tapered roller row on the outer side is set to the roller length of the tapered roller row on the one side. The wheel bearing device is characterized in that it is set longer than the above.

[2] An outer member integrally having a vehicle body mounting flange to be attached to the knuckle on the outer periphery, and having a double row outer rolling surface formed on the inner periphery;

The pitch circle diameter of the inner side tapered roller row of the double row tapered roller rows is set larger than the pitch circle diameter of the outer side tapered roller row, and the inner side tapered roller row The roller bearing is characterized in that the roller diameter of the tapered roller row on one side of the outer is set to be larger.

[3] The roller length of the inner side tapered roller row is equal to that of the outer side tapered roller row. 3. The wheel bearing device according to claim 1, wherein the wheel bearing device is set longer than the roller length.

[4] The wheel bearing device according to any one of claims 1 to 3, wherein the number of rollers of the double row tapered roller row is set to be the same.

[5] An outer member integrally having a vehicle body mounting flange to be attached to the knuckle on the outer periphery, and having a double row outer rolling surface formed on the inner periphery;

The pitch circle diameter of the inner side tapered roller row of the double row tapered roller rows is set larger than the pitch circle diameter of the outer side tapered roller row, and the inner side tapered roller row The roller length is set to be longer than the roller length of the outer side tapered roller row, and the number of rollers in the inner side tapered roller row is larger than the number of rollers in the outer side tapered roller row. A wheel bearing device characterized by a large number of settings.

[6] An outer member integrally having a vehicle body mounting flange to be attached to the knuckle on the outer periphery, and having a double row outer rolling surface formed on the inner periphery;

The pitch circle diameter of the outer side tapered roller row of the double row tapered roller row is set larger than the pitch circle diameter of the inner side tapered roller row, and The roller length of the inner side tapered roller row is set to be longer than the roller length of the outer side tapered roller row, and the number of rollers in the outer side tapered roller row is equal to the inner side cone. A bearing device for a wheel, characterized in that the number of rollers is set to be greater than the number of rollers in a roller train.

7. The wheel bearing device according to claim 5, wherein a roller diameter of the inner side tapered roller array and a roller diameter of the outer side tapered roller array are set to be the same.

[8] An outer member integrally having a vehicle body mounting flange to be attached to the knuckle on the outer periphery, and having a double row outer rolling surface formed on the inner periphery,

The pitch circle diameter of the inner side tapered roller row of the double row tapered roller row is set larger than the pitch circle diameter of the outer side tapered roller row, and the inner side tapered roller A roller bearing in which the roller length of the row is set longer than the roller length of the tapered roller row on the outer side, and the diameter of the roller and the number of rollers of these tapered rollers are set to be the same. apparatus.

[9] An outer member integrally having a vehicle body mounting flange to be attached to the knuckle on the outer periphery, and having a double-row outer rolling surface formed on the inner periphery,

The pitch circle diameters of the double row tapered roller rows are set to be the same, and the double row The roller diameter of the tapered roller row on the inner side of the row is set to be larger than the roller diameter of the outer tapered roller row, and the number of rollers in these tapered roller rows is set to be the same. A bearing device for a wheel, characterized in that

10. The wheel bearing device according to claim 9, wherein a roller length of the inner one side tapered roller row is set to be longer than a roller length of the outer side tapered roller row.

[11] The wheel bearing device according to claim 9, wherein a roller length of the outer side tapered roller row is set to be longer than a roller length of the inner one side tapered roller row.

[12] An outer member integrally having a vehicle body mounting flange to be attached to the knuckle on the outer periphery, and having a double row outer rolling surface formed on the inner periphery;

The double-row tapered roller rows have the same pitch circle diameter, and the outer-side tapered roller row of the double-row tapered roller rows has a roller length of the inner one-side tapered roller row. The wheel bearing device is characterized in that the number of rollers of the tapered roller rows is set to be the same, and the number of rollers of these tapered roller rows is set to be the same.

13. The wheel bearing device according to claim 12, wherein a roller diameter of the outer tapered roller array and a diameter of the inner tapered roller array are set to be the same.

[14] An outer member integrally having a vehicle body mounting flange to be attached to the knuckle on the outer periphery, and having a double row outer rolling surface formed on the inner periphery;

—Hub wheel that has a wheel mounting flange for mounting the wheel at the end and has a small diameter step formed on the outer periphery extending in the axial direction from this wheel mounting flange, and press fit into the small diameter step of this hub ring An inner member formed of at least one inner ring having an inner race surface facing the outer race surface of the double row on the outer periphery, and between the inner race member and the outer member. Double row of rolls In a wheel bearing device having a tapered roller array,

The pitch circle diameter of the double row tapered roller row is set to be the same, and the roller diameter of the outer side tapered roller row in the double row tapered roller row is set smaller than the roller diameter of the inner side tapered roller row. And the number of rollers in the outer side tapered roller train is set to be greater than the number of rollers in the inner side tapered roller train, and the force of the roller length of the inner side tapered roller train is A wheel bearing device characterized in that it is set longer than the length of the outer tapered roller row.

15. The wheel bearing according to any one of claims 1 to 14, wherein the inner ring is fixed in an axial direction by a crimping portion formed by plastically deforming an end portion of the small diameter step portion radially outward. apparatus.

[16] An outer side inner rolling surface is directly formed on the outer periphery of the hub wheel, and the small-diameter step portion extending in the axial direction from the inner rolling surface is formed. The wheel bearing device according to any one of claims 1 to 15, wherein an inner ring on the inner side is press-fitted through a mouth.

17. The wheel bearing device according to any one of claims 1 to 16, wherein a pair of inner rings are press-fitted into the small-diameter step portion of the hub ring, and the inner diameters of these inner rings are set to be the same.