JP2011117529A - Wheel bearing, and in-wheel type motor integrated wheel bearing device including the same - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a wheel bearing, and an in-wheel type motor integrated wheel bearing device in an electric vehicle improving sealing performance and durability. <P>SOLUTION: A seal 34 is composed as an integral type constituted of a core metal 36 pressed into an end inner periphery of an outer member 27, and a seal member 37 joined to the core metal 36 by vulcanized adhesion. The seal member 37 has a side lip 37a and a dust lip 37b inclined and extended radially outward and slidably contacting a base 28b of a wheel mounting flange 28 via an axial margin, and a grease lip 37c inclined and extended to a bearing inward side. The base 28b is formed in a cross-sectionally arced curved surface, and the side lip 37a and the dust lip 37b are slidably contacted to the base 28b via the axial margin. A cover 37d of the seal member 37 integrally molded so as to cover a weir part 36c of the core metal 36 is formed so as to project radially outward than an outer diameter of an end of the outer member 27. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a wheel bearing device for rotatably supporting a wheel, and more particularly to a wheel bearing with improved sealing performance and improved durability, and an electric motor combining the wheel bearing, a speed reducer, and a motor. The present invention relates to a wheel bearing device for an in-wheel motor built-in motor vehicle.

  In recent years, as a countermeasure for reducing the environmental load of automobiles, a shift from a conventional driving type using an engine to a driving type using a motor has been studied. Under such circumstances, as a wheel bearing device for an electric vehicle, an in-wheel motor built-in wheel bearing device in which a wheel bearing, a speed reducer, and a motor are combined is attracting attention. When the in-wheel type motor-equipped wheel bearing device is used as a driving wheel of an electric vehicle, each wheel can be individually driven to rotate, so that a large-scale power transmission mechanism such as a conventional propeller shaft or a differential is not required. Can be made lighter and more compact.

  As an example of this in-wheel type motor-equipped wheel bearing device, one shown in FIG. 13 is known. The in-wheel motor-equipped wheel bearing device includes a wheel bearing A that rotatably supports the hub of the drive wheel 100, a motor B as a rotational drive source, and the rotation of the motor B that is decelerated and transmitted to the hub. A reduction gear C that performs braking and a brake D that applies braking force to the hub are arranged on the central axis O of the drive wheel 100. Here, the side closer to the outer side of the vehicle when assembled to the vehicle is referred to as an outer side (left side in FIG. 13), and the side closer to the center is referred to as an inner side (right side in FIG. 13).

  The wheel bearing A includes an outer member 101 having a double row outer raceway surface 101a formed on the inner periphery, and a double row inner raceway surfaces 103a and 104a facing the double row outer raceway surface 101a. The inner member 102 is formed, and a double row of balls 105 accommodated between the rolling surfaces of the inner member 102 and the outer member 101 so as to roll freely. A seal 106 is attached and sealed in an opening on the outer side of the annular space formed between the outer member 101 and the inner member 102.

  The outer member 101 serving as a stationary side race ring integrally has a vehicle body attachment flange 101b attached to the outer casing 107 of the reduction gear C on the outer periphery, and is fixed via an attachment bolt (not shown). .

  The inward member 102 serving as the rotation-side raceway includes a hub wheel 103 and an inner ring member 104 fitted to the hub wheel 103. The hub wheel 103 integrally has a wheel mounting flange 108 for mounting the drive wheel 100 on the outer side end portion, and an outer side inner rolling surface 103a is formed on the outer periphery. A hub bolt 108a for mounting the wheel mounting flange 108 driving wheel 100 is implanted. On the other hand, the inner ring member 104 has an inner-side inner rolling surface 104a formed on the outer periphery, and is fixed integrally with the hub ring 103 by plastic coupling such as enlarged diameter caulking.

  The motor B is an axial gap type in which an axial gap is provided between a stator 110 fixed to a cylindrical casing 109 and a rotor 112 attached to an output shaft 111. The output shaft 111 is cantilevered by a pair of bearings 114 on the inner casing 113 of the reduction gear C. The inner side end of the clearance between the output shaft 111 and the casing 113 is sealed with a seal 115, and the opening on the inner side of the bottom 116 of the casing 109 is closed with a cap 117.

  The reducer C is a cycloid reducer, and includes an input shaft 119 having an eccentric shaft 118, an outer pin 120 passed between the casings 107 and 113, an inner pin 121 attached to the inner ring member 104, and each pin. And two curved plates 124 and 125 which are rotatably supported via bearings 122 and 123 and have a undulating trochoidal curve. The input shaft 119 is spline-coupled with the output shaft 111 of the motor B and is integrally rotated. When the output shaft 111 of the motor B rotates, the curved plates 124 and 125 attached to the input shaft 119 that rotates integrally with the motor B perform an eccentric motion, and are transmitted as a rotational motion of the inner member 102 (for example, Patent Documents). 1).

  In such a conventional in-wheel type motor-equipped wheel bearing device, the outer diameter of the wheel bearing A is smaller than the outer diameter of the casing 107 of the reduction gear C and the casing 109 of the motor B. When entering a water pool, rainwater and muddy water are more likely to collect at the outer diameter portion of the outer member 101 than in a conventional wheel bearing. Although the wheel bearing A is sealed by a seal 106 mounted on the outer side, when foreign matter such as rainwater enters the inside through the seal 106, the wheel bearing A is directly connected to the speed reducer C or the motor B. Therefore, not only the bearing portion but also the speed reducer C and the motor B may be damaged.

  Conventionally, various types of seal structures with improved sealing performance have been proposed. A typical example of a wheel bearing device having such a seal structure is shown in FIG. This wheel bearing device has an outer member 150 that is non-rotatably attached to the vehicle body side via a knuckle and has outer rows 150a and 150a of double rows formed on the inner periphery. A hub wheel 153 and an outer joint member of a constant velocity universal joint (not shown) attached integrally to the hub wheel 153 via double rows of balls 152, 152 held at circumferentially equidistant positions on the cage 151. It is supported so as to be rotatable around its axis.

  Inner rolling surfaces 153a facing the outer rolling surfaces 150a and 150a of the double row of the outer member 150 are formed on the outer periphery of the hub wheel 153, and a wheel mounting flange for mounting a brake disk and a wheel (not shown) at one end. 154 protrudes radially outward.

  The seal structure 155 includes a side surface 154 a on the outer member 150 side of the wheel mounting flange 154, a core metal 156 fitted to the inner peripheral surface of the outer member 150, and an elastic seal body 157 fixed to the core metal 156. It consists of and. The elastic seal body 157 includes two axial lip portions 158 that contact the side surface 154a of the wheel mounting flange 154 in the axial direction, and a radial lip portion 159 that contacts the outer peripheral surface of the hub wheel 153 in the radial direction. Yes.

  Further, the cored bar 156 has a circular arc shape (a crescent shape) that is partially extended along the side surface 154 a of the wheel mounting flange 154 so as to protrude radially outward from the outer peripheral surface 150 b of the outer member 150. A dam member 156a is formed, and the dam member 156a is in close contact with the end surface of the outer member 150 on the side surface 154a side. Further, the dam member 156a is formed only above the axis.

  Such a seal structure 155 is, for example, when the muddy water is applied to the outer member 150 during traveling of the vehicle, a part of the cored bar 156 has a radially outwardly upward direction from the outer peripheral surface 150b of the outer member 150. Since the dam member 156a extended so as to protrude is formed, the muddy water is prevented from flowing to the outer member 150 and the side surface 154a of the wheel mounting flange 154 by the dam member 156a. Therefore, the muddy water of the outer member 150 does not flow and collect in the axial lip portion 158, and the sealing performance can be maintained (see, for example, Patent Document 2).

JP 2008-74135 A JP 2003-49852 A

  However, in such a conventional seal structure 155, in order to maintain a desired contact surface pressure of the axial lip portion 158, it is necessary to narrow a gap between the cored bar 156 and the side surface 154a of the wheel mounting flange 154. was there. In addition, since a dam member 156a extended so as to protrude radially outward is formed on a part of the core metal 156, the core metal 156 is fitted to the outer member 150 in a state in which the phases are matched at the time of assembly. As a result, the number of assembling steps is increased and the cost reduction is hindered. Furthermore, there is a possibility that the dam member 156a may interfere with other parts at the time of assembling, or a stepping stone or the like may collide and plastically deform during traveling.

  The present invention has been made in view of such conventional problems, and provides a wheel bearing with improved sealing performance and improved durability, and a wheel bearing device with an in-wheel motor built-in motor in an electric vehicle. With the goal.

  In order to achieve such an object, the invention according to claim 1 of the present invention is an outer member having a vehicle body mounting flange integrally on the outer periphery and a double row outer rolling surface formed integrally on the inner periphery. And a hub wheel integrally having a wheel mounting flange for mounting the wheel at one end thereof, and having a small diameter step portion extending in the axial direction on the outer periphery, and at least one press-fitted into the small diameter step portion of the hub wheel An inner member formed of two inner rings and having an outer periphery formed with a double-row inner rolling surface opposite to the double-row outer rolling surface, and between both rolling surfaces of the inner member and the outer member. In a wheel bearing comprising: a double row of rolling elements housed so as to be freely rollable; and seals attached to both end openings of an annular space formed between the outer member and the inner member; The seal on the outer side of the seal is press-fitted into the inner periphery of the end on the outer side of the outer member. A core portion having a cylindrical portion, an inner diameter portion that is bent and extends radially inward from the cylindrical portion, and a disk-shaped weir portion that extends radially outward from the cylindrical portion, and an inner diameter portion of the core portion And a seal member integrally vulcanized and bonded, and the seal member extends obliquely outward in the radial direction, and an axial shimeshiro is provided at the base on the inner side of the wheel mounting flange. The side lip that is slidably contacted is integrally formed, and the dam portion of the core metal or the cover portion of the seal member that is integrally molded so as to cover the dam portion is larger than the outer diameter of the end portion of the outer member. Is also formed to project outward in the radial direction.

  Thus, in the wheel bearing provided with the seals mounted on the opening portions at both ends of the annular space formed between the outer member and the inner member, the outer seal of the seals is the outer member. A cored bar having a cylindrical portion press-fitted into the inner periphery of the outer end, an inner diameter portion that extends by bending inward in the radial direction from the cylindrical portion, and a disk-shaped weir portion that extends radially outward from the cylindrical portion And a seal member integrally vulcanized and bonded to the inner diameter portion of the core metal, and the seal member extends obliquely outward in the radial direction, and the base portion on the inner side of the wheel mounting flange The side lip that is slidably contacted through the axial shimiro is integrally formed, and the dam portion of the core metal or the cover portion of the seal member that is integrally molded so as to cover the dam portion is provided at the end portion of the outer member. It is formed to project radially outward from the outer diameter Therefore, even if rain water or muddy water is applied to the outer member during traveling of the vehicle, it can be prevented from flowing between the outer peripheral surface of the outer member and the wheel mounting flange, for a long period of time. It is possible to provide a wheel bearing with improved durability by improving the sealing performance of the seal.

  Preferably, as in the invention described in claim 2, if the weir portion of the core metal is formed thicker than other portions, the strength and rigidity of the core metal is increased. Even if the weir part interferes with other parts or a stepping stone collides during traveling, it can be reliably prevented from plastic deformation.

  Moreover, if the covering portion of the sealing member is joined so as to cover the exposed surface of the core metal as in the invention described in claim 3, rusting of the core metal is suppressed, and the core metal is expensive. Even if a stainless steel plate is not used, for example, a cold rolled steel plate that is inexpensive and has good workability can be used, and the cost can be reduced.

  Further, as in the invention described in claim 4, if the dam portion of the core metal is formed so as to be in close contact with the outer end surface of the outer member, the seal can be positioned with high accuracy. At the same time, the airtightness between the seal and the outer member can be improved.

  Further, as in the invention according to claim 5, if the seal member has a covering portion joined from the inner diameter portion of the cored bar to the surface of the dam portion, the seal and the outer member It is possible to prevent muddy water or the like from entering from a contact portion with the end face of the shaft, thereby improving airtightness and preventing leakage of grease sealed inside the bearing to the outside.

  Further, as in the invention described in claim 6, if the covering portion of the seal member is elastically contacted with the outer periphery of the outer side end portion of the outer member, the airtightness between the seal and the outer member is further increased. Can be improved.

  Moreover, if the cylindrical collar part extended in the inner side from the dam part of the said metal core is formed like invention of Claim 7, the intensity | strength and rigidity of a metal core will become high, and other time will be sufficient at the time of an assembly. It can be prevented from being damaged even if it interferes with parts or a stepping stone collides during traveling.

  Further, as in the invention described in claim 8, if the covering portion of the seal member is opposed to the inner side surface of the wheel mounting flange via a slight axial clearance, and a labyrinth seal is configured, It is possible to prevent rainwater, muddy water, etc. from entering the lip portion and improve the sealing performance.

  According to a ninth aspect of the present invention, the seal member is integrally formed with a dust lip extending obliquely outward in the radial direction on the inner diameter side of the side lip and a grease lip extending inclined toward the inner side of the bearing. And the base portion on the inner side of the wheel mounting flange is formed in a curved surface having an arcuate cross section, and the side lip and the dust lip are slidably contacted to the base portion via a predetermined axial direction shimoshiro. Sealing performance can be improved.

  Further, as in the invention described in claim 10, the base portion on the inner side of the wheel mounting flange is formed in an arc surface having a predetermined radius of curvature, and a metal ring is fitted to the base portion. Is a curved portion formed in an arc shape corresponding to the shape of the base portion, a disc portion extending radially outward from the curved portion and being in close contact with the side surface of the base portion, and an outer diameter of the disc portion And an umbrella portion that is axially spaced from the wheel mounting flange and extends in a radially outwardly inclined manner, and the side lip and the dust lip are slidably contacted via a predetermined axial shimiro If the grease lip is slidably contacted via a predetermined radial shimiro, rusting of the lip slidable contact portion can be suppressed and desired sealing performance can be ensured over a long period of time.

  Further, as in the invention described in claim 11, if the curved portion of the metal ring is set to have a larger radius of curvature than the radius of curvature of the base portion, the arc surface of the base portion when the metal ring is fitted to the base portion The curved part of the metal ring can be prevented from interfering with the metal ring, and the gap between the side surface of the base part and the disk part of the metal ring can be prevented and the two can be in close contact with each other. Stable sealability can be ensured by suppressing variations in the strip and grease lip.

  In addition, as in the invention described in claim 12, the metal ring is formed by press working from a steel plate having corrosion resistance, and the surface roughness of the steel plate as a material is set in a range of Ra 0.2 to 0.6. If it is made, a favorable seal sliding contact surface can be obtained, lip wear can be suppressed, and the sealing performance of the seal can be maintained even when used in a poor environment.

  Further, as in the invention described in claim 13, if an annular concave groove is formed on the outer periphery of the outer end of the outer member, rain water or muddy water is applied to the outer member while the vehicle is running. However, it can prevent flowing between the outer peripheral surface of the outer member and the wheel mounting flange.

  The invention according to claim 14 of the present invention is the in-wheel type motor-integrated wheel bearing device in which a reduction gear and a motor are arranged coaxially with respect to the wheel bearing and the central axis of the wheel. The vehicle body mounting flange is attached to a casing of the speed reducer, and a drive shaft constituting the speed reducer is connected to the hub wheel so as to be able to transmit torque, and the speed reducer comprises a cycloid speed reducer and includes an eccentric shaft. The input shaft, a plurality of outer pins passed between the speed reducer casing and the motor casing, a plurality of inner pins attached to the drive shaft, and each pin is rotatable via a rolling bearing. Two curved plates supported on the outer surface, and these curved plates are formed in a wavy trochoid curve with a gentle outer shape and mounted on the eccentric shaft, and the outer pin is rotated. Since the eccentric movement of the curved plate is guided on the outer peripheral side by this outer pin, which is supported rotatably by the bearing, the sealing performance of the seal in the electric vehicle is improved, the durability is increased, and the motor is rotated. However, it is possible to provide an in-wheel motor-equipped wheel bearing device that can transmit smoothly and efficiently with a large reduction ratio as the rotational movement of the drive shaft.

  In addition, as in the invention described in claim 15, if a groove is formed at least in the 180 ° range on the opposite road surface side of the outer periphery of the casing of the speed reducer, rainwater, muddy water, etc. Accordingly, it is possible to prevent the fluid from flowing to the outer member and to improve the sealing performance.

  Further, as in the invention described in claim 16, rainwater, muddy water, etc. travel along the outer peripheral surface of the casing as long as a concave groove is formed in a range of 180 ° on at least the opposite road surface side of the outer periphery of the casing of the motor. Thus, the flow to the outer member can be prevented, and the sealing performance can be improved.

  A wheel bearing according to the present invention has a vehicle body mounting flange integrally formed on an outer periphery, an outer member integrally formed with a double row outer rolling surface on an inner periphery, and a wheel for mounting the wheel on one end. A hub wheel integrally including a wheel mounting flange and having a small-diameter step portion extending in the axial direction on the outer periphery, and at least one inner ring press-fitted into the small-diameter step portion of the hub wheel. An inner member in which a double row of inner rolling surfaces facing the outer rolling surface is formed, and a double row of rolling members housed between the inner member and the outer member so as to roll freely. A wheel bearing comprising: a moving body; and seals mounted at both end openings of an annular space formed between the outer member and the inner member. A cylindrical portion that is press-fitted into the inner circumference of the outer end of the side member, and a radial direction from the cylindrical portion A cored bar having an inner diameter bent and extending inward, and a disk-like weir extending radially outward from the cylindrical part, and a sealing member integrally vulcanized and bonded to the inner diameter of the core; The seal member extends obliquely outward in the radial direction, and integrally has a side lip that is slidably contacted with the base portion on the inner side of the wheel mounting flange via an axial shimiro. And a covering portion of the sealing member integrally molded so as to cover the dam portion of the metal core or the dam portion is formed so as to protrude radially outward from the outer diameter of the end portion of the outer member. Therefore, even if rain water or muddy water is applied to the outer member during traveling of the vehicle, it can be prevented from flowing between the outer peripheral surface of the outer member and the wheel mounting flange. Improved sealing performance and improved durability It is possible to provide a wheel bearing.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a longitudinal sectional view showing an embodiment of an in-wheel motor-equipped wheel bearing device according to the present invention. It is a principal part enlarged view which shows the wheel bearing apparatus of FIG. (A) is an enlarged view of the main part showing the outer seal part of FIG. 2, (b) is an enlarged view of the main part showing the casing part of the reducer of FIG. 1, and (c) is the motor of FIG. It is a principal part enlarged view which shows a casing part. It is a principal part enlarged view which shows the modification of the seal | sticker of Fig.3 (a). It is a principal part enlarged view which shows the modification of the seal | sticker of FIG. It is a principal part enlarged view which shows the other modification of the seal | sticker of Fig.3 (a). (A)-(e) is a principal part enlarged view which shows the other modification of the seal | sticker of Fig.3 (a). (A)-(d) is a principal part enlarged view which shows the modification of the seal | sticker of FIG. (A), (b) is a principal part enlarged view which shows the modification of the seal | sticker of FIG. (A), (b) is a principal part enlarged view which shows the other modification of the seal | sticker of FIG. It is a principal part enlarged view which shows the modification of the seal | sticker of FIG.8 (b). (A)-(e) is a principal part enlarged view which shows the other modification of the seal | sticker of FIG. It is a longitudinal cross-sectional view which shows the conventional bearing apparatus for in-wheel type motor built-in wheels. It is a principal part enlarged view which shows the conventional seal structure.

  An in-wheel type motor-equipped wheel bearing device in which a wheel bearing, a reducer, and a motor are arranged coaxially with respect to a central axis of the wheel, wherein the wheel bearing is attached to a casing of the reducer on an outer periphery. A vehicle body mounting flange integrally formed, an outer member in which a double row outer rolling surface is integrally formed on the inner periphery, and a wheel mounting flange for mounting the wheel on one end portion. A hub wheel having an inner rolling surface facing one of the outer rolling surfaces of the double row on the outer periphery, a small-diameter step portion extending in the axial direction from the inner rolling surface, and a small-diameter step portion of the hub ring An inner member formed of an inner ring that is press-fitted into the inner ring and has an inner rolling surface facing the other of the outer rolling surfaces of the double row on the outer periphery, and between the rolling surfaces of the inner member and the outer member. Double row rolling elements housed in a freely rollable manner, the outer member and the inner part An in-wheel type motor-integrated wheel bearing device provided with a seal attached to an opening on the outer side of an annular space formed between the outer periphery of the outer member and the inner periphery of the outer member. A metal core having a cylindrical portion that is press-fitted into the cylindrical portion, an inner diameter portion that is bent and extends radially inward from the cylindrical portion, and a disk-shaped weir portion that extends radially outward from the cylindrical portion; The seal member is composed of a seal member integrally vulcanized and bonded to the inner diameter portion of the wheel, and the seal member extends obliquely outward in the radial direction and axially extends to the base portion on the inner side of the wheel mounting flange. It integrally has a side lip that is slidably contacted via a shimeshiro, a dust lip that extends radially outward on the inner diameter side of the side lip, and a grease lip that extends inclined toward the bearing inward side, Wheel mounting A base portion on the inner side of the lunge is formed into a curved surface having an arcuate cross section, and the side lip and dust lip are slidably contacted with each other via a predetermined axial shimiro to integrally cover the dam portion of the cored bar. The molded covering portion of the sealing member is formed so as to protrude outward in the radial direction from the outer diameter of the end portion of the outer member.

Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.
FIG. 1 is a longitudinal sectional view showing an embodiment of an in-wheel motor-equipped wheel bearing device according to the present invention, FIG. 2 is an enlarged view of a main part showing the wheel bearing device of FIG. 1, and FIG. FIG. 2 is an enlarged view of the main part showing the outer seal part of FIG. 2, (b) is an enlarged view of the main part showing the casing part of the reduction gear of FIG. 1, and (c) is the casing part of the motor of FIG. FIG. 4 is an enlarged view of a main part showing a modification of the seal shown in FIG. 3A, FIG. 5 is an enlarged view of a main part showing a modified example of the seal shown in FIG. 4, and FIG. 3 (a) is an enlarged view of a main part showing another modification of the seal, and FIGS. 7 (a) to 7 (e) are enlarged views of a main part showing another modification of the seal of FIG. 3 (a), FIG. (A)-(d) is the principal part enlarged view which shows the modification of the seal | sticker of FIG. 7, FIG. 9 (a), (b) is the principal part enlarged view which shows the modification of the seal | sticker of FIG. (A), (b) FIG. 11 is an enlarged view of a main part showing another modification of the seal of FIG. 8B, and FIGS. 12A to 12E are views of FIG. It is a principal part enlarged view which shows the other modification of a seal | sticker. In the following description, the side closer to the outer side of the vehicle when assembled to the vehicle is referred to as the outer side (left side in FIG. 1), and the side closer to the center is referred to as the inner side (right side in FIG. 1).

  The in-wheel motor-equipped wheel bearing device includes a wheel bearing device 1 that rotatably supports a wheel (not shown), a motor 2 as a rotational drive source, and a hub that decelerates the rotation of the motor 2 The speed reducer 3 for transmitting to is disposed on the central axis O of the wheel.

  The motor 2 is configured by a radial gap type motor in which a radial gap is provided between a stator 5 fixed to a cylindrical motor casing 4 and a rotor 7 attached to an output shaft 6. The output shaft 6 is rotatably supported with respect to the motor casing 4 by rolling bearings 8 and 8 including a pair of deep groove ball bearings. The opening on the inner side of the motor casing 4 is closed with a cap 9.

  The speed reducer 3 is a cycloid speed reducer, and is attached to an input shaft 11 having an eccentric shaft 10, a plurality of outer pins 13 passed between the speed reducer casing 12 and the motor casing 4, and a drive shaft 14. A plurality of inner pins 15, and two curved plates 18 and 19 that are rotatably supported by the pins 13 and 15 via rolling bearings 16 and 17 made of cylindrical roller bearings. These curved plates 18 and 19 are formed in a wavy trochoid curve having a gentle outer shape, and are mounted on the eccentric shaft 10. The outer pin 13 is rotatably supported by rolling bearings 20 and 20 including a pair of needle roller bearings, and the eccentric motion of the curved plates 18 and 19 is guided on the outer peripheral side by the outer pin 13.

  The input shaft 11 is coupled to the output shaft 6 of the motor 2 via a spline (or serration) 11a and is rotationally driven integrally. When the output shaft 6 of the motor 2 rotates, the eccentric shaft 10 attached to the input shaft 11 that rotates integrally therewith rotates, and the curved plates 18 and 19 that engage with the eccentric shaft 10 perform eccentric motion. The rotation of the rotor 7 is smoothly and efficiently transmitted as a rotational movement of the drive shaft 14 with a large reduction ratio.

  The two curved plates 18 and 19 are mounted on the eccentric shaft 10 of the input shaft 11 with a phase difference of 180 ° so that the eccentric motion is canceled out. The curved plates 18 and 19 are disposed on both sides of the eccentric shaft 10. Counterweights 21 and 21 that are eccentric in the direction opposite to the eccentric direction of the eccentric shaft 10 are mounted so as to cancel the vibration caused by the eccentric movement of the eccentric shaft 10. The input shaft 11 is rotatably supported by a rolling bearing 22 formed of a deep groove ball bearing with respect to a drive shaft 14 described later.

  The wheel bearing device 1 is called a third generation for driving wheels, and as shown in an enlarged view in FIG. 2, an inner member 25 comprising a hub wheel 23 and an inner ring 24 press-fitted into the hub wheel 23. The inner member 25 is provided with an outer member 27 which is externally inserted via double-row rolling elements (balls) 26, 26.

  The hub wheel 23 integrally has a wheel mounting flange 28 for mounting a wheel (not shown) at an end portion on the outer side, one (outer side) inner rolling surface 23a on the outer periphery, and this inner rolling. A small diameter step portion 23b extending in the axial direction from the surface 23a is formed, and a serration (or spline) 23c for torque transmission is formed on the inner periphery. The inner ring 24 is formed with the other (inner side) inner rolling surface 24a on the outer periphery, and is press-fitted into the small-diameter step portion 23b of the hub ring 23 through a predetermined scissors. Further, hub bolts 28 a are implanted at equidistant positions in the circumferential direction of the wheel mounting flanges 28.

  The hub wheel 23 is made of medium and high carbon steel containing carbon of 0.40 to 0.80 wt% such as S53C, and includes an inner rolling surface 23a and an inner side of a wheel mounting flange 28 serving as a seal land portion of a seal 34 described later. The surface is hardened in the range of 58 to 64 HRC by induction hardening from the base 28b to the small diameter step 23b. On the other hand, the inner ring 24 and the rolling element 26 are made of high carbon chrome steel such as SUJ2, and are hardened in the range of 58 to 64 HRC up to the core part by quenching.

  The outer member 27 integrally has a vehicle body mounting flange 27b attached to the reduction gear casing 12 via a fixing bolt 12a on the outer periphery, and a plurality of outer members 27 facing the inner rolling surfaces 23a, 24a of the inner member 25 on the inner periphery. The outer rolling surfaces 27a, 27a of the rows are integrally formed. Between these rolling surfaces 27a, 23a and 27a, 24a, double row rolling elements 26, 26 are accommodated via a cage 29 so as to be freely rollable.

  The outer member 27 is formed of medium and high carbon steel containing 0.40 to 0.80 wt% of carbon such as S53C, and at least the double row outer rolling surfaces 27a and 27a are hardened in the range of 58 to 64HRC by induction hardening. Has been processed.

  The drive shaft 14 constituting the speed reducer 3 includes a flange portion 30 to which the inner pin 15 is attached, a cylindrical shoulder portion 31 extending in the axial direction from the flange portion 30, and a shaft extending in the axial direction from the shoulder portion 31. The part 32 is integrally formed (see FIG. 1). A serration (or spline) 32a that meshes with the serration 23c of the hub wheel 23 and an external thread 32b are formed at the end of the outer periphery of the shaft portion 32. The drive shaft 14 is fitted into the hub wheel 23 until the shoulder 31 abuts the end surface of the inner ring 24, and is tightened with a predetermined tightening torque by the fixing nut 33 screwed to the male screw 32b. The hub wheel 23 is coupled in the axial direction so that torque can be transmitted.

  In addition, a seal 34 is attached to the opening on the outer side of the annular space formed between the outer member 27 and the inner member 25, and the inner opening is slid on the outer periphery of the drive shaft 14. An oil seal 35 that comes into contact is mounted to prevent leakage of the lubricating grease sealed inside the bearing and prevent the lubricating oil, contamination, and the like from entering the bearing from the reduction gear 3 side.

  As shown in an enlarged view in FIG. 3A, the seal 34 is an integrated seal composed of a core metal 36 fitted in the outer member 27 and a seal member 37 joined to the core metal 36. It is configured. The core metal 36 is formed by press working from a steel plate having rust prevention ability such as an austenitic stainless steel plate (JIS standard SUS304 type) or a rust-proof cold rolled steel plate (JIS standard SPCC type). A cylindrical portion 36a that is press-fitted into the inner periphery of the outer side end portion of the outer member 27 via a predetermined shimiro, an inner diameter portion 36b that is bent and extends radially inward from the cylindrical portion 36a, and a cylindrical portion 36a. A disc-shaped weir portion 36 c that extends radially outward from the outer member 27 and is in close contact with the outer end surface 27 c of the outer member 27 is integrally formed. As described above, the dam portion 36c is brought into close contact with the outer end surface 27c of the outer member 27, so that the seal 34 can be accurately positioned and the airtightness between the seal 34 and the outer member 27 is improved. be able to.

  On the other hand, the seal member 37 is made of synthetic rubber such as NBR (acrylonitrile-butadiene rubber) and is integrally joined to the cored bar 36 by vulcanization adhesion. The seal member 37 includes a side lip 37a extending obliquely outward in the radial direction, a dust lip 37b extending obliquely outward in the radial direction on the inner diameter side of the side lip 37a, and a bearing inner side (inner side). ) And a grease lip 37c extending in an inclined manner and a covering portion 37d that covers the exposed surface of the cored bar 36.

  A base portion 28b on the inner side of the wheel mounting flange 28 is formed in a curved surface having an arc-shaped cross section, and a side lip 37a and a dust lip 37b are slidably contacted with the base portion 28b with a predetermined axial squeeze, and a grease lip 37c is predetermined. Are in sliding contact with each other through a radial shimoshiro. In addition to NBR, the material of the seal member 37 is excellent in heat resistance and chemical resistance, such as HNBR (hydrogenated acrylonitrile butadiene rubber), EPDM (ethylene propylene rubber), etc., which are excellent in heat resistance. Examples thereof include ACM (polyacrylic rubber), FKM (fluororubber), and silicon rubber.

  Here, in the present embodiment, the weir portion 36c of the cored bar 36 is formed so as to protrude outward in the radial direction from the outer diameter of the outer end portion of the outer member 27, and the end portion of the outer member 27 is formed. An annular groove 38 is formed on the outer periphery. Strength and rigidity are increased by the bent cored bar 36 as described above, and the dam part 36c of the cored bar 36 interferes with other parts at the time of assembling, or plastic deformation occurs even if a stepping stone or the like collides during traveling. In addition, the weir portion 36c and the concave groove 38 can prevent the wheel mounting flange 28 and the wheel mounting flange 28 from traveling along the outer peripheral surface of the outer member 27 even when rainwater or muddy water is applied to the outer member 27 during traveling of the vehicle. It is possible to provide a bearing device for a wheel with a built-in in-wheel type motor that can prevent the fluid from flowing between the two, improve the sealing performance of the seal 34 in the electric vehicle over a long period of time, and improve the durability. it can. The above-described concave groove 38 may be formed over the entire circumference. However, if it is formed at least in the range of 180 ° on the side opposite to the road surface, rainwater and muddy water that has traveled on the outer circumferential surface of the outer member 27 are formed. It accumulates in this concave groove 38 and is discharged downward.

  In addition, although the 3rd generation structure was illustrated as the wheel bearing apparatus 1 here, not only this but the 1st generation structure with which the bearing which consists of a double row angular ball bearing etc. is fitted to the hub ring | wheel, It may be a second generation structure having a pair of inner rings whose members are externally fitted to the hub ring. In addition, although the wheel bearing device constituted by a double row angular contact ball bearing using balls as the rolling elements 26 has been illustrated, the present invention is not limited to this, and it is constituted by a double row tapered roller bearing using tapered rollers. May be.

  FIG.3 (b) is a principal part enlarged view which shows the reduction gear casing 12 of the reduction gear 3 of FIG. The speed reducer casing 12 is in contact with the inner side surface of the vehicle body mounting flange 27b of the outer member 27 via an elastic member 39 such as an O-ring, and an annular concave groove 40 is formed on the outer periphery. By this concave groove 40, it is possible to prevent the outer casing 27 from flowing along the outer peripheral surface of the speed reducer casing 12, and the sealing performance can be further improved. In addition, although the ditch | groove 40 may be formed over a perimeter, if it is formed in the range of 180 degrees at least on the anti-road surface side, the rainwater and muddy water which were transmitted along the outer peripheral surface of the reduction gear casing 12 will be sufficient as it. It accumulates in the concave groove 40 and is discharged downward.

  FIG.3 (c) is a principal part enlarged view which shows the motor casing 4 of the motor 2 of FIG. A cylindrical cover 41 is attached via an elastic member 42 such as an O-ring so as to cover the outer periphery of the motor casing 4, and an annular concave groove 43 is formed on the outer periphery. The concave grooves 43 can prevent the cover 41 from flowing to the speed reducer casing 12 and the outer member 27 along the outer peripheral surface, thereby further improving the sealing performance. The concave groove 43 may be formed over the entire circumference, but if it is formed at least in the range of 180 ° on the side opposite to the road surface, rainwater and muddy water that has traveled along the outer peripheral surface of the cover 41 are formed in the concave groove 43. It accumulates in the groove 43 and is discharged downward.

  FIG. 4 is a modification of the seal 34 in FIG. In this embodiment, only a part of the configuration of the cored bar 36 is basically different, and other parts and parts having the same parts or parts having the same functions are denoted by the same reference numerals and detailed description thereof is omitted. To do.

  The seal 44 is constituted by an integral seal including a cored bar 45 fitted in the outer member 27 and a seal member 37 joined to the cored bar 45. The metal core 45 is formed by press working from a steel plate having rust prevention ability, such as an austenitic stainless steel plate or a cold-rolled steel plate treated with rust, and is formed on the inner periphery of the outer side end of the outer member 27. A cylindrical portion 36a that is press-fitted through a predetermined scissors, an inner diameter portion 36b that bends and extends radially inward from the cylindrical portion 36a, and extends radially outward from the cylindrical portion 36a. A disc-shaped weir portion 45a that is in close contact with the side end surface 27c is integrally formed.

  In this embodiment, the weir part 45a of the cored bar 45 is formed thicker than the other parts. As a result, the strength and rigidity are increased, and it is possible to further prevent the weir portion 45a of the cored bar 45 from interfering with other parts during assembly or even plastic deformation even when a stepping stone or the like collides during traveling.

  FIG. 5 is a modification of the seal 44 of FIG. In this embodiment, basically, only a part of the configuration of the seal member 37 is different, and the same parts and parts having the same functions or the same functions as those of the other embodiments are denoted by the same reference numerals and detailed. Description is omitted. The seal 46 is constituted by an integral seal composed of a cored bar 45 ′ press-fitted into the outer periphery of the outer side end of the outer member 27 and a seal member 47 joined to the cored bar 45 ′. .

  The weir portion 45b of the cored bar 45 'is formed to be thicker than the other portions, and is further extended outward in the radial direction. On the other hand, the seal member 46 is made of synthetic rubber such as NBR and is integrally joined to the cored bar 45 'by vulcanization adhesion. The seal member 47 includes a side lip 37a extending obliquely outward in the radial direction, a dust lip 37b extending obliquely outward in the radial direction on the inner diameter side of the side lip 37a, and a bearing inner side (inner side). ) And a grease lip 37c extending in an inclined manner, and the weir portion 45b of the cored bar 45 'is exposed. As a result, the strength and rigidity are increased, and it is possible to further prevent the weir portion 45b of the cored bar 45 'from interfering with other parts at the time of assembling or plastic deformation even if a stepping stone or the like collides during traveling. At the same time, even when rain or muddy water is applied to the outer member 27 during traveling of the vehicle, it can be further prevented from flowing between the outer peripheral surface of the outer member 27 and the wheel mounting flange 28.

  FIG. 6 shows another modification of the seal 34 shown in FIG. In this embodiment, basically only the structure of the seal member of the seal 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.

  The seal 48 is constituted by an integral seal composed of a core metal 36 press-fitted into the outer periphery of the outer end of the outer member 27 and a seal member 49 joined to the core metal 36. The seal member 49 is made of a synthetic rubber such as NBR, and is integrally joined to the cored bar 36 by vulcanization bonding. The side lip 37a extends obliquely outward in the radial direction, and the radial direction on the inner diameter side of the side lip 37a is the same. A dust lip 37b extending obliquely outward, a grease lip 37c extending obliquely toward the bearing inward side (inner side), and a covering portion 49a joined so as to cover the weir portion 36c are integrally provided. .

  In the present embodiment, since the covering portion 49a of the seal member 48 completely covers the exposed portion of the dam portion 36c of the core metal 36, the contact between the dam portion 36c of the core metal 36 and the end surface 27c of the outer member 27. It is possible to prevent intrusion of muddy water or the like from the portion to improve airtightness, and to prevent the grease enclosed in the bearing from leaking to the outside. Further, even if an expensive stainless steel plate or a rust-proof steel plate is not used as the material of the core metal 36, there is a risk of rusting even if a cold rolled steel plate having a low price and good formability is used. Therefore, the cost can be reduced.

  FIG. 7 shows another modification of the seal 34 shown in FIG. It should be noted that the same parts and parts as those in the above-described embodiment or parts and parts having the same functions are denoted by the same reference numerals and detailed description thereof is omitted.

  The seal 50 shown in (a) is formed by an integral seal composed of a core metal 36 press-fitted into the outer periphery of the outer end of the outer member 27 and a seal member 51 joined to the core metal 36. ing.

  The seal member 51 is made of a synthetic rubber such as NBR, and is integrally joined to the cored bar 36 by vulcanization adhesion. The side lip 37a extends obliquely outward in the radial direction, and the radial direction on the inner diameter side of the side lip 37a is the same. A dust lip 37b extending inclining outward, a grease lip 37c extending inclining toward the bearing inward side (inner side), and a surface of the weir portion 36c of the cored bar 36 from the base portion of the side lip 37a are covered. The cover 51a is integrally joined. The covering portion 51 a is in elastic contact with the end surface 27 c of the outer member 27. Thereby, the airtightness of the dam part 36c and the outward member 27 improves further.

  The seal 52 shown in (b) is an integrated seal composed of a core metal 36 ′ press-fitted into the inner periphery of the outer side end of the outer member 27 and a seal member 51 joined to the core metal 36 ′. It is configured.

  The seal member 51 is made of a synthetic rubber such as NBR, and is integrally joined to the cored bar 36 'by vulcanization adhesion. The side lip 37a extends obliquely outward in the radial direction, and the same diameter on the inner diameter side of the side lip 37a. Covers the surface of the weir portion 36c of the cored bar 36 'from the root portion of the side lip 37a and the grease lip 37c extending inclined toward the bearing inner side (inner side). Thus, the cover portion 51a is integrally formed.

  The dam portion 36d of the core metal 36 'is formed shorter than the above-described embodiment, and the covering portion 51a of the seal member 51 serves as a dam portion. Thereby, even if the covering part 51a interferes with other parts at the time of assembly, or a stepping stone collides during traveling, it can be easily deformed and restored, and damage to the weir part can be prevented.

  The seal 53 shown in (c) is an integrated seal composed of a core bar 36 ′ press-fitted into the outer periphery of the outer side end of the outer member 27 and a seal member 54 joined to the core bar 36 ′. It is configured.

  The seal member 54 is made of a synthetic rubber such as NBR, and is integrally joined to the core metal 36 'by vulcanization adhesion. The side lip 37a extends obliquely outward in the radial direction, and the same diameter on the inner diameter side of the side lip 37a. Covers the surface of the weir portion 36d of the cored bar 36 'from the root portion of the side lip 37a, the grease lip 37c extending inclined toward the bearing inner side (inner side), and the dust lip 37b extending inclined outward in the direction. Thus, the cover portion 54a is integrally formed.

  In the present embodiment, the covering portion 54a is formed thicker than the covering portion 51a described above. Accordingly, it is possible to prevent the covering portion 54a from interfering with other parts at the time of assembling or elastically deforming and damaging even if a stepping stone or the like collides during traveling.

  The seal 55 shown in (d) is an integral seal composed of a core metal 36 ′ press-fitted into the inner periphery of the outer end of the outer member 27 and a seal member 56 joined to the core metal 36 ′. It is configured.

  The seal member 56 is made of a synthetic rubber such as NBR, and is integrally joined to the core metal 36 'by vulcanization adhesion. The side lip 37a extends obliquely outward in the radial direction, and the same diameter on the inner diameter side of the side lip 37a. A dust lip 37b extending inclined outward in the direction, a grease lip 37c extending inclined toward the inner side (inner side) of the bearing, and a root portion of the side lip 37a from the root portion to the weir portion 36d of the metal core 36 ′. The cover portion 56a is integrally joined.

  In the present embodiment, the covering portion 56 a is formed thicker than the covering portion 51 a described above, and a part thereof is in elastic contact with the outer periphery of the end portion of the outer member 27. Accordingly, it is possible to prevent the covering portion 56a from interfering with other parts at the time of assembly or to be elastically deformed and damaged even if a stepping stone or the like collides during traveling, and the weir portion 36d of the core metal 36 '. The airtightness between the outer member 27 and the outer member 27 can be improved.

  The seal 57 shown in (e) is formed by an integral seal composed of a core metal 36 press-fitted into the inner periphery of the outer end of the outer member 27 and a seal member 58 joined to the core metal 36. ing.

  The seal member 58 is made of a synthetic rubber such as NBR, and is integrally joined to the cored bar 36 by vulcanization adhesion. The side lip 37a extends obliquely outward in the radial direction, and the radial direction on the inner diameter side of the side lip 37a is the same. The dust lip 37b extending obliquely outward, the grease lip 37c extending obliquely inwardly of the bearing (inner side), and the base lip 37a are joined to the weir portion 36c of the metal core 36 from the base portion. The cover portion 58a is integrally provided.

  In the present embodiment, a part of the covering portion 58 a protrudes and elastically contacts the outer periphery of the end portion of the outer member 27. This prevents the covering portion 58a from interfering with other parts during assembly, or can be prevented from elastically deforming and damaging even if a stepping stone or the like collides during traveling. The airtightness with the outer member 27 can be improved.

  FIG. 8 shows a modification of the seal of FIG. Note that this embodiment is basically the same as the above-described embodiment except that the configuration of the cored bar is partially different, and other parts and parts having the same parts or parts having the same functions are denoted by the same reference numerals. Description is omitted.

  The seal 59 shown in (a) is formed by an integral seal composed of a core metal 60 press-fitted into the inner periphery of the outer end of the outer member 27 and a seal member 54 joined to the core metal 60. ing.

  The metal core 60 is formed by press working from a rust-proof cold-rolled steel plate, and a cylindrical portion 36a that is press-fitted into the inner periphery of the outer side end portion of the outer member 27 via a predetermined shimiro, An inner diameter portion 36b that is bent and extended radially inward from the cylindrical portion 36a, a disk-shaped dam portion 36d that extends radially outward from the cylindrical portion 36a, and a cylindrical ridge that extends from the dam portion 36d to the inner side The part 60a is integrally formed.

  In the present embodiment, since the flange portion 60a is formed from the weir portion 36d of the core metal 60, the strength and rigidity are increased, and the covering portion 54a interferes with other parts during assembly, or a stepping stone or the like is generated during traveling. Even if it collides, damage can be prevented.

  The seal 61 shown in (b) is formed by an integral seal composed of a core metal 60 press-fitted into the inner periphery of the outer end of the outer member 27 and a seal member 56 joined to the core metal 60. ing. A part of the covering portion 56 a of the seal member 56 is in elastic contact with the outer periphery of the end portion of the outer member 27. As described above, the strength and rigidity of the covering portion 56a is increased by the dam portion 36d and the flange portion 60a of the integrally molded cored bar 60, and the covering portion 56a interferes with other parts at the time of assembly. Can be prevented from being damaged even if they collide with each other, and the airtightness between the weir portion 36d of the cored bar 60 and the outer member 27 can be improved.

  The seal 62 shown in (c) is constituted by an integral seal composed of a core metal 63 fitted in the outer member 27 and a seal member 54 joined to the core metal 63. The cored bar 63 is formed by press working from a rust-proof cold-rolled steel plate, and a cylindrical part 36a that is press-fitted into the inner periphery of the outer side end of the outer member 27 via a predetermined shimiro, An inner diameter portion 36b that is bent and extended radially inward from the cylindrical portion 36a, a disk-shaped dam portion 63a that extends radially outward from the cylindrical portion 36a, and a cylindrical ridge that extends from the dam portion 63a to the inner side The part 60a is integrally formed. As described above, the strength and rigidity of the covering portion 54a are increased by the dam portion 63a and the flange portion 60a of the integrally molded cored bar 63. The covering portion 54a interferes with other parts during assembly, or a stepping stone or the like is generated during traveling. Can be prevented from being damaged even if they collide.

  The seal 64 shown in (d) is configured as an integral seal composed of a core metal 65 fitted in the outer member 27 and a seal member 56 joined to the core metal 65. The core metal 65 is formed by press working from a rust-proof cold-rolled steel plate, and a cylindrical portion 36a press-fitted into the inner periphery of the outer side end of the outer member 27 via a predetermined shimiro, An inner diameter portion 36b that is bent and extended radially inward from the cylindrical portion 36a, a disk-shaped dam portion 36d that extends radially outward from the cylindrical portion 36a, and a cylindrical ridge that extends from the dam portion 36d to the inner side A tongue piece 65a that protrudes radially outward from the portion 60a and the flange portion 60a is integrally formed. Thus, the structure and the rigidity of the covering portion 56a are increased by the structure of the integrally molded cored bar 63, and the covering portion 56a interferes with other parts at the time of assembly or is damaged even if a stepping stone collides during traveling. It is possible to prevent this, and the airtightness between the seal 64 and the outer member 27 can be improved.

  FIG. 9 shows a modification of the seal of FIG. Note that this embodiment is basically different from the above-described embodiment except that the configuration of the seal member is only partially different, and the same parts and parts having the same functions or the same functions are denoted by the same reference numerals and detailed. Description is omitted.

  The seal 66 shown in (a) is configured by an integral seal including a core metal 60 press-fitted into the inner periphery of the outer end of the outer member 27 and a seal member 67 joined to the core metal 60. ing. The seal member 67 is made of a synthetic rubber such as NBR, and is integrally joined to the cored bar 60 by vulcanization adhesion. The side lip 37a extends obliquely outward in the radial direction, and the radial direction on the inner diameter side of the side lip 37a is the same. Dustrip 37b extending inclining outward, grease lip 37c extending inclining toward the bearing inner side (inner side), and surfaces of weir portion 36d and flange portion 60a of cored bar 60 from the base portion of side lip 37a The cover part 67a joined so that it may cover is integrated.

  In the present embodiment, the covering portion 67a is formed in a thick shape, and is formed in a tapered shape whose outer diameter gradually becomes smaller toward the inner side. As a result, the material of the seal member 67 is reduced and the moldability is improved.

  The seal 68 shown in (b) is configured by an integral seal composed of a core metal 60 press-fitted into the inner periphery of the outer end of the outer member 27 and a seal member 69 joined to the core metal 60. ing. The seal member 69 is made of a synthetic rubber such as NBR, and is integrally joined to the cored bar 60 by vulcanization adhesion. The side lip 37a extends obliquely outward in the radial direction, and the radial direction on the inner diameter side of the side lip 37a is the same. Dustrip 37b extending inclining outward, grease lip 37c extending inclining toward the bearing inner side (inner side), and surfaces of weir portion 36d and flange portion 60a of cored bar 60 from the base portion of side lip 37a The cover part 69a joined so that it may cover is integrated.

  In this embodiment, the coating | coated part 69a is formed in thickness, and is formed in the taper shape from which an outer diameter becomes a small diameter gradually toward an outer side. As a result, the material of the seal member 69 is reduced and the moldability is improved.

  FIG. 10 shows another modification of the seal of FIG. Note that this embodiment basically differs from the above-described embodiment only in a part of the configuration of the lip of the seal member, and other parts or parts having the same function or the same function are denoted by the same reference numerals. Detailed description is omitted.

  A seal 70 shown in FIG. 6A is constituted by an integral seal composed of a core metal 36 press-fitted into the outer circumference of the outer end of the outer member 27 and a seal member 71 joined to the core metal 36. ing. The seal member 71 is made of a synthetic rubber such as NBR, and is integrally joined to the cored bar 36 by vulcanization adhesion. The side lip 37a extends obliquely outward in the radial direction, and the radial direction on the inner diameter side of the side lip 37a is the same. A dust lip 37b extending inclining outward, a grease lip 71a extending inclining toward the bearing inward side (inner side), and a surface of the weir portion 36c of the metal core 36 from the base portion of the side lip 37a are covered. The cover 51a is integrally joined.

  In the present embodiment, the grease lip 71a is opposed to the base portion 28b via a predetermined radial clearance to constitute a labyrinth seal. Thereby, the rotational torque of the seal 70 is reduced.

  The seal 72 shown in (b) is formed of an integral seal composed of a core metal 60 press-fitted into the inner periphery of the outer end of the outer member 27 and a seal member 73 joined to the core metal 60. ing. The seal member 73 is made of a synthetic rubber such as NBR, and is integrally joined to the core metal 60 by vulcanization adhesion. The side lip 37a extends obliquely outward in the radial direction, and the radial direction on the inner diameter side of the side lip 37a. Dustrip 37b extending inclining outward, grease lip 71a extending inclining toward the bearing inward side (inner side), and surfaces of weir portion 36d and flange 60a of cored bar 36 from the base of side lip 37a The cover portion 56a is integrally joined so as to cover the cover.

  In the present embodiment, the grease lip 71a is opposed to the base portion 28b via a predetermined radial clearance to constitute a labyrinth seal. Thereby, the rotational torque of the seal 72 is reduced.

  FIG. 11 shows a modification of the seal 61 in FIG. Note that this embodiment is basically different from the above-described embodiment only in the configuration of the lip sliding contact portion of the seal member, and the same reference numerals are given to the same parts or parts having the same function or the same function. Detailed description is omitted.

  The seal 61 is constituted by an integral seal composed of a core metal 60 press-fitted into the outer periphery of the outer side end of the outer member 27 and a seal member 56 joined to the core metal 60. A part of the covering portion 56 a of the seal member 56 is in elastic contact with the outer periphery of the end portion of the outer member 27.

  In the present embodiment, the side lip 37a, the dust lip 37b, and the grease lip 37c are in sliding contact with a metal ring 74 fitted to the base portion 28b on the inner side of the wheel mounting flange 28. This metal ring 74 is pressed from a corrosion-resistant steel plate, for example, an austenitic stainless steel plate (JIS standard SUS304 type or the like) or a rust-proof cold rolled steel plate (JIS standard SPCC type or the like). A curved portion 74a formed in an arc shape corresponding to the shape of the base portion 28b, and a disk portion 74b extending radially outward from the curved portion 74a and closely contacting the side surface 28c of the base portion 28b. The disc portion 74b is provided with an umbrella portion 74c that is spaced apart from the outer diameter portion of the disc portion 74b in the axial direction with respect to the wheel mounting flange 28 and that extends obliquely outward in the radial direction.

  The metal ring 74 can prevent rusting of the lip sliding surface, and the surface roughness of the steel plate as the material is set in the range of Ra 0.2 to 0.6. A contact surface can be obtained, lip wear can be suppressed, and the sealing performance of the seal 61 can be maintained even when used in a poor environment. Note that Ra is one of JIS roughness shape parameters (JIS B0601: 2001) and is an arithmetic average roughness, which means an average value of absolute value deviations from an average line.

  The base portion 28b is formed in an arc surface having a predetermined radius of curvature r, and the curved portion 74a of the metal ring 74 has a radius of curvature R larger than the radius of curvature r of the base portion 28b corresponding to the arc surface. It is set (R ≧ r). Thereby, when the metal ring 74 is fitted to the base portion 28b, the curved portion 74a of the metal ring 74 can be prevented from interfering with the arc surface of the base portion 28b to be lifted, and the side surface 28c of the base portion 28b and the metal ring 74 can be prevented from floating. It is possible to prevent a gap from being formed between the disk portion 74b and the two portions to be in close contact with each other, thereby suppressing unevenness of the side lip 37a, the dust lip 37b, and the grease lip 37c and ensuring stable sealing performance.

  FIG. 12 shows another modification of the seal of FIG. Note that this embodiment is basically different from the above-described embodiment except that the configuration of the seal member is only partially different, and the same parts and parts having the same functions or the same functions are denoted by the same reference numerals and detailed. Description is omitted.

  The seal 75 shown in (a) is configured by an integral seal including a core bar 36 press-fitted into the outer periphery of the outer side end of the outer member 27 and a seal member 76 joined to the core bar 36. ing. The seal member 76 is made of a synthetic rubber such as NBR, and is integrally bonded to the cored bar 36 by vulcanization adhesion. The side lip 37a extends obliquely outward in the radial direction, and the radial direction on the inner diameter side of the side lip 37a is the same. A dust lip 37b extending inclining outward, a grease lip 37c extending inclining toward the bearing inward side (inner side), and a surface of the weir portion 36c of the cored bar 36 from the base portion of the side lip 37a are covered. The cover portion 76a is integrally joined.

  In the present embodiment, the covering portion 76 a is formed thick and faces the inner side surface 28 d of the wheel mounting flange 28 via a slight axial clearance e to constitute a labyrinth seal 77. Thereby, rain water, muddy water, etc. can prevent entering a lip | rip part, and can improve sealing performance.

  The seal 78 shown in FIG. 5B is formed by an integral seal composed of a core metal 60 press-fitted into the inner periphery of the outer side end of the outer member 27 and a seal member 79 joined to the core metal 60. ing. The seal member 79 is made of a synthetic rubber such as NBR, and is integrally joined to the cored bar 60 by vulcanization adhesion. The side lip 37a extends obliquely outward in the radial direction, and the radial direction on the inner diameter side of the side lip 37a is the same. Dustrip 37b extending inclining outward, grease lip 37c extending inclining toward the bearing inner side (inner side), and surfaces of weir portion 36d and flange portion 60a of cored bar 60 from the base portion of side lip 37a The cover portion 79a is integrally joined so as to cover the cover.

  In the present embodiment, the covering portion 79 a is formed thick and faces the inner side surface 28 d of the wheel mounting flange 28 via a slight axial clearance e to constitute a labyrinth seal 77. Thereby, rain water, muddy water, etc. can prevent entering a lip | rip part, and can improve sealing performance.

  The seal 80 shown in (c) is configured by an integral seal composed of a core metal 60 press-fitted into the inner periphery of the outer end of the outer member 27 and a seal member 81 joined to the core metal 60. ing. The seal member 81 is made of a synthetic rubber such as NBR, and is integrally joined to the cored bar 60 by vulcanization adhesion. The side lip 37a extends obliquely outward in the radial direction, and the radial direction on the inner diameter side of the side lip 37a is the same. Dustrip 37b extending inclining outward, grease lip 37c extending inclining toward the bearing inner side (inner side), and surfaces of weir portion 36d and flange portion 60a of cored bar 60 from the base portion of side lip 37a The cover portion 81a is integrally joined so as to cover the cover.

  In the present embodiment, the covering portion 81a is formed to be thick, and is formed in a tapered shape having an outer diameter that gradually decreases toward the outer side, and is slightly smaller than the side surface 28d on the inner side of the wheel mounting flange 28. The labyrinth seal 77 is configured to face each other through the axial clearance e. Thereby, while the moldability of the sealing member 81 improves, it can prevent that rainwater, muddy water, etc. penetrate | invade into a lip | rip part, and can improve sealing performance.

  The seal 82 shown in (d) is an integral seal composed of a core metal 36 ′ press-fitted into the inner periphery of the outer end of the outer member 27, and a seal member 83 joined to the core metal 36 ′. It is configured. The sealing member 83 is made of a synthetic rubber such as NBR, and is integrally joined to the cored bar 36 'by vulcanization adhesion. The side lip 37a extends obliquely outward in the radial direction, and the same diameter on the inner diameter side of the side lip 37a. Covers the surface of the weir portion 36d of the cored bar 36 'from the root portion of the side lip 37a, the grease lip 37c extending inclined toward the bearing inner side (inner side), and the dust lip 37b extending inclined outward in the direction. Thus, the cover portion 83a is integrally joined.

  In the present embodiment, the covering portion 83 a is formed thick and faces the inner side surface 28 d of the wheel mounting flange 28 via a slight axial clearance e to constitute a labyrinth seal 77. Thereby, rain water, muddy water, etc. can prevent entering a lip | rip part, and can improve sealing performance.

  The seal 78 shown in (e) is formed of an integral seal comprising a metal core 60 press-fitted into the inner periphery of the outer end of the outer member 27 and a seal member 79 joined to the metal core 60. ing. The side lip 37a, the dust lip 37b, and the grease lip 37c are in sliding contact with a metal ring 74 fitted to the base portion 28b on the inner side of the wheel mounting flange 28.

  In the present embodiment, the labyrinth seal 77 prevents rainwater, muddy water, etc. from entering the lip portion and improves the sealing performance, and the metal ring 74 prevents rusting on the lip sliding surface for a long period of time. This can be prevented over a long period of time, and the durability can be improved.

  The embodiment of the present invention has been described above, but the present invention is not limited to such an embodiment, and is merely an example. Of course, the scope of the present invention is indicated by the description of the scope of claims, and further, the equivalent meanings described in the scope of claims and all modifications within the scope of the scope of the present invention are included. Including.

  The wheel bearing device with a built-in in-wheel type motor according to the present invention is a combination of a wheel bearing, a speed reducer, and a motor, and the wheel bearing is an inner member serving as a rotating member and an outer member serving as a stationary member. The present invention can be applied to a first generation to a third generation structure in which a seal is attached to an opening on the outer side of an annular space formed between the members.

DESCRIPTION OF SYMBOLS 1 Wheel bearing apparatus 2 Motor 3 Reduction gear 4 Motor casing 5 Stator 6 Output shaft 7, 8, 16, 17, 20, 21 Rolling bearing 9 Cap 10 Eccentric shaft 11 Input shaft 11a Spline 12 Reduction gear casing 13 Outer pin 14 Drive Shaft 15 Inner pins 18, 19 Curved plate 22 Counterweight 23 Hub wheels 23a, 24a Inner rolling surface 23b Small diameter step 23c, 32a Serration 24 Inner ring 25 Inner member 26 Rolling member 27 Outer member 27a Outer rolling surface 27b Mounting flange 27c Outer member outer side end surface 28 Wheel mounting flange 28a Hub bolt 28b Wheel mounting flange inner side base 28c Base side surface 28d Wheel mounting flange inner side surface 29 Cage 30 Flange portion 31 Shoulder portion 32 Shaft Portion 32b Male Thread 33 Fixing Nuts 34, 44, 4 48, 50, 52, 53, 55, 57, 59, 61, 62, 64, 66, 68, 70, 72, 75, 78, 80, 82 Outer side seal 35 Inner side oil seals 36, 36 ' 45, 45 ′, 60, 63, 65 Core 36a Cylindrical part 36b Inner diameter part 36c, 36d, 45a, 45b, 63a Weir part 37, 47, 47, 51, 54, 56, 58, 67, 69, 71, 73, 76, 79, 81, 83 Seal member 37a Side lip 37b Dustrip 37c, 71a Grease lip 37d, 49a, 51a, 54a, 56a, 58a, 67a, 69a Covering portion 38, 40, 43 Recessed groove 39, 42 Elasticity Member 41 cover 60a collar portion 65a tongue piece 74 metal ring 74a curved portion 74b disc portion 74c umbrella portion 77 labyrinth seal 100 driving wheel 101 outward Material 101a Outer rolling surface 101b Car body mounting flange 102 Inner member 103 Hub wheels 103a, 104a Inner rolling surface 104 Inner ring member 105 Ball 106, 115 Seal 107, 109, 113 Casing 108 Wheel mounting flange 108a Hub bolt 110 Stator 111 Output shaft 112 Rotor 114, 122, 123 Bearing 116 Casing bottom 117 Cap 118 Eccentric shaft 119 Output shaft 120 Outer pin 121 Inner pins 124, 125 Curved plate 150 Outer member 150a Outer rolling surface 150b Outer surface 151 Cage 152 Ball 153 Hub Wheel 153a Inner rolling surface 154 Wheel mounting flange 154a Side surface 155 of wheel mounting flange Seal structure 156 Core metal 156a Weir member 157 Elastic seal body 158 Axial lip portion 159 Radial lip portion Wheel bearing B motor C reducer D brake e axial clearance O curvature radius of the curved portion of the curvature radius R metal ring central axis r base of the drive wheel

Claims (16)

An outer member integrally including a vehicle body mounting flange on the outer periphery, and a double row outer rolling surface formed integrally on the inner periphery;
From a hub wheel integrally having a wheel mounting flange for mounting a wheel at one end and having a small-diameter step portion extending in the axial direction on the outer periphery, and at least one inner ring press-fitted into the small-diameter step portion of the hub ring An inner member in which a double-row inner rolling surface facing the outer rolling surface of the double row is formed on the outer periphery,
A double row rolling element housed in a freely rolling manner between the rolling surfaces of the inner member and the outer member;
In a wheel bearing comprising a seal mounted on both ends of an annular space formed between the outer member and the inner member,
Out of the seals, an outer side seal is a cylindrical portion press-fitted into an inner periphery of an outer side end of the outer member, an inner diameter portion that is bent and extends radially inward from the cylindrical portion, and the cylindrical portion. It is composed of an integral seal composed of a mandrel having a disk-shaped weir extending radially outward and a seal member integrally vulcanized and bonded to the inner diameter of the mandrel,
The seal member extends obliquely outward in the radial direction, and integrally includes a side lip that is slidably contacted with the base portion on the inner side of the wheel mounting flange via an axial shimiro,
The dam portion of the metal core or the cover portion of the seal member that is integrally molded so as to cover the dam portion is formed to protrude outward in the radial direction from the outer diameter of the end portion of the outer member. A wheel bearing characterized by.   The wheel bearing according to claim 1, wherein the dam portion of the metal core is formed thicker than other portions.   The wheel bearing according to claim 1 or 2, wherein the covering portion of the seal member is joined so as to cover the exposed surface of the cored bar.   The wheel bearing according to any one of claims 1 to 3, wherein a dam portion of the metal core is formed so as to be in close contact with an outer end surface of the outer member.   The wheel bearing according to any one of claims 1 to 3, wherein the seal member has a covering portion joined from the inner diameter portion of the core metal to the surface of the dam portion.   The wheel bearing according to any one of claims 1 to 5, wherein the covering portion of the seal member is in elastic contact with the outer periphery of the outer end portion of the outer member.   The wheel bearing according to any one of claims 1 to 6, wherein a cylindrical flange portion is formed extending from the dam portion of the metal core to the inner side.   8. The labyrinth seal is configured by the covering portion of the seal member facing the inner side surface of the wheel mounting flange via a slight axial clearance. Wheel bearings.   The seal member integrally includes a dust lip that extends obliquely outward in the radial direction on the inner diameter side of the side lip and a grease lip that extends inclined to the bearing inward side, and a base portion on the inner side of the wheel mounting flange The wheel bearing according to claim 1, wherein the side lip and the dust lip are slidably contacted to the base portion via a predetermined axial squealing.   The base portion on the inner side of the wheel mounting flange is formed in an arc surface having a predetermined radius of curvature, and a metal ring is fitted to the base portion, and the metal ring is formed in an arc shape corresponding to the shape of the base portion. A curved portion that extends radially outward from the curved portion and is in close contact with the side surface of the base portion, and is axially spaced from the outer diameter portion of the disk portion to the wheel mounting flange. And the side lip and the dust lip are slidably contacted with each other via a predetermined axial nip, and the grease lip is provided with a predetermined radial nip. The wheel bearing according to claim 9, which is in sliding contact.   The wheel bearing according to claim 10, wherein the curved portion of the metal ring is set to have a larger curvature radius than the curvature radius of the base portion.   The wheel according to claim 10 or 11, wherein the metal ring is formed by press working from a steel plate having corrosion resistance, and a surface roughness of the steel plate as a material is set in a range of Ra 0.2 to 0.6. Bearings.   The wheel bearing according to claim 1, wherein an annular groove is formed on the outer periphery of the outer end of the outer member.   In the wheel bearing device with a built-in in-wheel type motor in which a reduction gear and a motor are arranged coaxially with respect to the wheel bearing and the central axis of the wheel, the vehicle body mounting flange is attached to a casing of the reduction gear, A drive shaft constituting the speed reducer is connected to the hub wheel so that torque can be transmitted, and the speed reducer is a cycloid speed reducer, and includes an input shaft having an eccentric shaft, a casing of the speed reducer, and a casing of the motor A plurality of outer pins, a plurality of inner pins attached to the drive shaft, and two curved plates rotatably supported by each pin via a rolling bearing. A plate is formed in a wavy trochoid curve with a gentle outer shape and is mounted on the eccentric shaft, and the outer pin is rotatably supported by a rolling bearing. In the curved plate eccentric motion-wheel type motor built wheel bearing device characterized in that it is guided on the outer peripheral side of the.   The in-wheel type motor built-in wheel bearing device according to claim 14, wherein a concave groove is formed in a range of 180 ° at least on the opposite road surface side of the outer periphery of the casing of the speed reducer.   The in-wheel type motor-integrated wheel bearing device according to claim 14, wherein a concave groove is formed in a range of 180 ° at least on an opposite road surface side of an outer periphery of the casing of the motor.

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