JP2011007272A - Wheel bearing device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a wheel bearing device which improves seal performance and attains low cost by enabling common use of a seal.SOLUTION: A bearing seal 8 includes a metal core 12 which is internally suitable for the inner circumference of the end of an outer member 5, and a seal member 13 which turns around the fitting part of the metal core 12 and is integrally bonded by vulcanization. The seal member 13 includes side lips 13a, 13b which extend slantingly in the radial direction and contact the base part 6b of a wheel mounting flange 6 slidably via an interference in the axial direction. A weir member 31 is provided that includes a cylindrical part 20a which is suitable for the inner circumference of the end of the outer member 5, a vertical plate part 31a which extends outside in the radial direction from the cylindrical part, and an elastic member 31b which is jointed to the vertical plate part and protrudes outside in the radial direction farther from the outer circumference of the end of the outer member 5. The elastic member 31b is made to face a side surface 6c of the wheel attaching flange 6 via a slight gap in the axial direction and is sealed by the side surface 6c, the end surface of the outer member 5, and the bearing seal 8.

Description

  The present invention relates to a wheel bearing device that is intended to improve sealing performance and to reduce the cost by using a seal.

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

  Since these wheel bearing devices are disposed at sites where muddy water or the like is easily applied, a sealing device is attached so as to seal between the outer member and the inner member. Here, when the bearing damage situation of the market-recovered product is verified, the damage due to the malfunction of the sealing device occupies more than the original bearing life resulting from peeling or the like. Therefore, it is possible to reliably improve the bearing life by increasing the sealing performance and durability of the sealing device. Generally, in a sealing device, a seal member having a seal lip is attached to an outer member serving as a stationary member, and the seal lip is slidably contacted with an outer peripheral surface of the inner member.

  Conventionally, various 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 100 that is non-rotatably attached to the vehicle body side via a knuckle and has outer rows 100a and 100a formed in double rows on the inner periphery. A hub wheel 103 and an outer joint member of a constant velocity universal joint (not shown) which are integrally attached to the hub wheel 103 through double rows of balls 102 and 102 held at circumferentially equidistant positions on the cage 101. It is supported so as to be rotatable around its axis.

  An inner rolling surface 103a opposite to the double row outer rolling surfaces 100a, 100a of the outer member 100 is formed on the outer periphery of the hub wheel 103, and a wheel mounting flange for mounting a brake disk and a wheel (not shown) at one end. 104 protrudes radially outward.

  The seal structure 105 includes a side surface 104 a on the outer member 100 side of the wheel mounting flange 104, a core metal 106 fitted to the inner peripheral surface of the outer member 100, and an elastic seal body 107 fixed to the core metal 106. It consists of and. The elastic seal body 107 has two axial lip portions 108 that contact the side surface 104a of the wheel mounting flange 104 in the axial direction, and a radial lip portion 109 that contacts the outer peripheral surface of the hub wheel 103 in the radial direction. ing.

  Further, the cored bar 106 has a circular arc shape (a crescent shape) that is partially extended along the side surface 104 a of the wheel mounting flange 104 so as to protrude radially outward from the outer peripheral surface 100 b of the outer member 100. A dam member 106 a is formed, and the dam member 106 a is in close contact with the end surface of the outer member 100 on the side surface 104 a side. Further, the weir member 106a is formed only above the axis.

  For example, when muddy water is applied to the outer member 100 during traveling of the vehicle, such a seal structure 105 is formed so that a part of the cored bar 106 has a radially outward direction upward from the outer peripheral surface 100b of the outer member 100. Since the dam member 106a extended so as to protrude is formed, the muddy water is prevented from flowing to the outer member 100 and the side surface 104a of the wheel mounting flange 104 by the dam member 106a. Therefore, the muddy water of the outer member 100 does not flow and collect in the axial lip portion 108, and the sealing performance can be maintained (see, for example, Patent Document 1).

JP 2003-49852 A

  However, in such a conventional seal structure 105, it is necessary to prepare products having different shapes and dimensions for each bearing specification, and there is a problem that the seal parts cannot be used in common. In addition, since the dam member 106a extended so as to protrude outward in the radial direction is formed on a part of the core metal 106, the core metal 106 is fitted to the outer member 100 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.

  The present invention has been made in view of such conventional problems, and an object of the present invention is to provide a wheel bearing device that improves the sealing performance and reduces the cost by using a seal.

  In order to achieve such an object, the invention described in claim 1 of the present invention has a vehicle body mounting flange for being attached to a knuckle on the outer periphery, and a double row outer rolling surface on the inner periphery. A hub wheel integrally formed with a formed outer member and a wheel mounting flange for mounting a wheel at one end, and a small-diameter step portion extending in the axial direction from the wheel mounting flange on the outer periphery, and the hub ring An inner member composed of at least one inner ring that is press-fitted into the small-diameter step portion and formed with an inner rolling surface that faces the outer rolling surface of the double row, and both rolling of the inner member and the outer member. For a wheel including a double row rolling element accommodated between the running surfaces so as to be freely rollable, and a bearing seal attached to an opening of an annular space formed between the outer member and the inner member. In the bearing device, the bearing seal has an inner periphery of an end portion of the outer member. It consists of a core metal that is fitted inside, and a seal member that is vulcanized and bonded integrally around the core metal fitting part, and this seal member is integrated with a side lip and a radial lip that extend in a radial direction. And an annular weir member is provided at the outer end of the outer member, and the weir member is opposed to the inner side surface of the wheel mounting flange via a slight axial clearance, It is sealed by a side surface, an end surface of the outer member, and the bearing seal.

  Thus, in the wheel bearing device including the bearing seal mounted in the opening portion of the annular space formed between the outer member and the inner member, the bearing seal has an inner periphery of the end portion of the outer member. And a side lip and a radial lip extending incline in the radial direction. An annular weir member is provided at the outer end of the outer member, and the weir member is opposed to the inner side surface of the wheel mounting flange via a slight axial clearance. And the outer member end face and the bearing seal, so that it is possible to prevent the bearing seal from being directly covered with muddy water, and even if the outer member is covered with muddy water while the vehicle is running, Wheel mounting hula Can be prevented from flowing between the side surface of di, it can be improved durability and sealing performance of the bearing seal for a long period of time.

  Preferably, as in the invention described in claim 2, the dam member is disposed as a separate member on the radially outer side of the bearing seal, and the dam member is pressed from a steel plate having rust prevention ability. A cylindrical portion that is formed of a member that has been processed or coated with a rust preventive ability after pressing from a steel plate, and that is press-fitted into the end portion of the outer member through a predetermined shimoshiro, and a diameter from the cylindrical portion If the outer member is covered with muddy water while the vehicle is running, the outer member extends outward in the direction and protrudes radially outward from the outer periphery of the end of the outer member. It can be prevented from flowing between the outer peripheral surface of the member and the side surface of the wheel mounting flange, and it is not necessary to prepare bearing seals with different shapes and sizes for each bearing specification, and the cost is reduced by standardizing the seal. Can be achieved.

  Further, as in the invention described in claim 3, the cylindrical portion of the dam member may be press-fitted into the outer periphery of the end portion of the outer member, and as in the invention described in claim 4, The cylindrical portion of the dam member may be press-fitted into the inner periphery of the end portion of the outer member.

  In addition, as in the invention described in claim 5, if the elastic member is joined around the end of the cylindrical portion, the airtightness of the fitting portion between the weir member and the outer member becomes high.

  Further, as in the invention described in claim 6, the outer bearing seals of the bearing seals are arranged to face each other, and are press-fitted to the inner periphery of the outer end portion of the outer member via a predetermined shimoshiro. And a pack seal comprising an annular seal plate having the seal member and a slinger that is press-fitted into the inner member through a predetermined shimiro, and the side lip and radial lip of the seal member are attached to the slinger. The dam member is slidably contacted and integrally has a disk part extending radially inward from the cylindrical part, and the disk part faces the slinger via a slight axial clearance to form a labyrinth. If the seal is configured, it is possible to reliably prevent the muddy water from being directly applied to the bearing seal, and the sealability of the bearing seal can be improved.

  Further, as in the invention according to claim 7, the seal plate is press-fitted into a base portion on the inner side of the wheel mounting flange via a predetermined shimeshiro, and a radial lip of the seal member extends radially outward, The seal member is directly slidably contacted to the inner periphery of the end portion of the outer member via a predetermined radial shimoshiro, and the weir member integrally includes a disk portion extending radially inward from the cylindrical portion, and the seal If the side lip of the member extends obliquely inward in the radial direction and is in sliding contact with the disk portion of the weir member via a predetermined axial squeeze, the number of parts can be reduced and downsizing can be achieved. it can.

  Further, as in the invention according to claim 8, an elastic member is joined to the standing plate portion of the weir member, and this elastic member faces the inner side surface of the wheel mounting flange via a slight axial clearance. If this is done, contact with other parts during assembly and stepping stones etc. will collide when the vehicle is running to prevent the weir member from being plastically deformed. Can be maintained.

  Further, as in the ninth aspect of the invention, an external seal having a side lip integrally disposed on the radially outer side of the bearing seal is disposed as a separate body, and the side lip is provided on the vertical plate portion with a predetermined amount. If it is slidably contacted via the axial shimoshiro, even if muddy water is applied to the outer member during traveling of the vehicle and travels along the outer peripheral surface of the outer member, it flows between the side surfaces of the wheel mounting flanges. It is possible to prevent the muddy water from being directly applied to the bearing seal.

  Further, as in the invention described in claim 10, even if the outer seal has a disk part and the disk part is bonded to the inner side surface of the wheel mounting flange by a hub bolt. good.

  Further, as in the invention of claim 11, the outer side bearing seals of the bearing seals are arranged to face each other, and are press-fitted into the inner periphery of the outer side end portion of the outer member via a predetermined squeeze. And a pack seal comprising an annular seal plate having the seal member and a slinger that is press-fitted into the inner member through a predetermined shimiro, and the side lip and radial lip of the seal member are attached to the slinger. The dam member is integrally formed on the seal member so as to protrude from the end portion of the core bar beyond the end surface of the outer member, and a slight shaft is formed on the inner side surface of the wheel mounting flange. The labyrinth seal is configured to face through a directional clearance, and the labyrinth seal is configured by the dam member and the slinger facing each other through a slight radial clearance. With this configuration, it is possible to prevent the muddy water from being directly applied to the bearing seal with a simple structure, and even if muddy water is applied to the outer member while the vehicle is running, it can flow to the bearing seal along the outer peripheral surface of the outer member. The durability and sealing performance of the bearing seal can be improved over a long period of time.

  Further, as in the invention described in claim 12, of the bearing seals, the inner side bearing seals are arranged to face each other, and are press-fitted into the inner periphery of the inner side end portion of the outer member via a predetermined squeeze. And a pack seal comprising an annular seal plate having the seal member and a slinger that is press-fitted into the outer diameter of the inner ring through a predetermined scissors, and the side lip and radial lip of the seal member are the slinger And the dam member is integrally formed on the seal member from the end of the core bar beyond the end surface of the outer member. The outer joint of the constant velocity universal joint is formed on the inner member. A member is coupled to transmit torque, the weir member is opposed to a shoulder portion of the outer joint member through a slight axial clearance, a labyrinth seal is formed, and the weir member and the slit are formed. Gas are opposed through a slight radial clearance, the labyrinth seal may be configured.

  Further, as in a thirteenth aspect of the present invention, a core metal in which an inner side bearing seal of the bearing seals is press-fitted into a inner periphery of an inner side end portion of the outer member via a predetermined shimoshiro A seal member integrally joined to the metal core by vulcanization adhesion, the seal member extending in a radially outward direction and a pair of side lips extending in a radially inward direction. The seal member is integrally formed, and the weir member is integrally protruded from the fitting portion of the core bar to the seal member so as to protrude from the end surface of the outer member. The outer joint member of the joint is coupled so as to be able to transmit torque, the pair of side lips are slidably in contact with the shoulders of the outer joint member via a predetermined axial nip, and the grease lip has a diameter equal to the outer diameter of the inner ring. Sliding contact through direction It may be.

  Further, as in the invention described in claim 14, if the side lip on the outer diameter side of the pair of side lips is set larger than the side lip on the inner diameter side, the sliding torque of the bearing seal is suppressed. Even if the outer side lip is worn, the desired sealing performance can be maintained.

  Further, as in the invention described in claim 15, a slinger is externally fitted to the shoulder portion of the outer joint member, and the weir member is opposed to the slinger via a slight axial clearance to form a labyrinth seal. As a result, it is possible to prevent the muddy water from being directly applied to the bearing seal, and even if muddy water is applied to the outer member or the outer joint member while the vehicle is running, the bearing seal or the inner member and the outer It is possible to prevent flow to the abutting surface with the joint member, and it is possible to improve the durability and sealing performance of the bearing seal over a long period of time.

  Further, as in the invention described in claim 16, an annular recess is formed in a shoulder portion of the outer joint member, and the weir member is opposed to the annular recess via a slight axial clearance, and a labyrinth seal May be configured.

  According to a seventeenth aspect of the present invention, the dam member includes a base portion that extends radially outward in close contact with the end surface of the outer member, and an inner side from the base portion toward the radially outer side. If it has the lip part which inclines and extends, the airtightness between the bearing seal and the outer member is improved.

  The wheel bearing device according to the present invention has an outer member integrally formed with a vehicle body mounting flange to be attached to a knuckle on the outer periphery, and an outer member in which a double row outer rolling surface is integrally formed on the inner periphery, and one end portion A hub wheel having a wheel mounting flange for mounting a wheel integrally on the outer periphery, and a small diameter step portion extending in the axial direction from the wheel mounting flange on the outer periphery, and the small diameter step portion of the hub wheel are press-fitted into the hub wheel. An inner member composed of at least one inner ring formed with an inner rolling surface facing the outer rolling surface of the row, and is accommodated in a freely rollable manner between both rolling surfaces of the inner member and the outer member. In a wheel bearing device comprising: a double row rolling element; and a bearing seal mounted in an opening of an annular space formed between the outer member and the inner member, the bearing seal includes the A cored bar fitted into the inner periphery of the end of the outer member, and this The seal member is formed of a seal member that wraps around a gold fitting portion and is integrally vulcanized and bonded. The seal member integrally includes a side lip and a radial lip extending in a radial direction, and an outer member of the outer member. An annular weir member is provided at the end on the side, and this weir member is opposed to the inner side surface of the wheel mounting flange via a slight axial clearance, and the side surface and the end surface of the outer member and the Since it is sealed by the bearing seal, it is possible to prevent the muddy water from being directly applied to the bearing seal, and even if muddy water is applied to the outer member while the vehicle is running, the side surface of the wheel mounting flange is transmitted along the outer peripheral surface of the outer member. It is possible to prevent the fluid from flowing between the two, and the durability and sealing performance of the bearing seal can be improved over a long period of time.

It is a longitudinal section showing a 1st embodiment of a bearing device for wheels concerning the present invention. (A) is a principal part enlarged view which shows the seal part of FIG. 1, (b) is a principal part enlarged view which shows the modification of (a). (A) is a principal part enlarged view which shows the modification of Fig.2 (a). (A) is a principal part enlarged view which shows the modification of Fig.2 (a), (b) is a principal part enlarged view which shows the other modification of (a). (A)-(c) is a principal part enlarged view which shows the other modification of FIG.2 (b). (A), (b) is a principal part enlarged view which shows the other modification of Fig.2 (a). (A) is a principal part enlarged view which shows the modification of Fig.3 (a), (b) is a principal part enlarged view which shows the modification of (a). It is a longitudinal cross-sectional view which shows 2nd Embodiment of the wheel bearing apparatus which concerns on this invention. It is a principal part enlarged view which shows the seal | sticker part of the outer side of FIG. It is a longitudinal cross-sectional view which shows 3rd Embodiment of the wheel bearing apparatus which concerns on this invention. (A) is a principal part enlarged view which shows the seal part of the outer side of FIG. 10, (b) is a principal part enlarged view which shows the seal part of the inner side of FIG. It is a longitudinal cross-sectional view which shows 4th Embodiment of the wheel bearing apparatus which concerns on this invention. It is a principal part enlarged view which shows the seal part of the inner side of FIG. It is a longitudinal cross-sectional view which shows 5th Embodiment of the wheel bearing apparatus which concerns on this invention. It is a principal part enlarged view which shows the seal part of the inner side of FIG. It is a longitudinal cross-sectional view which shows 6th Embodiment of the wheel bearing apparatus which concerns on this invention. It is a principal part enlarged view which shows the seal part of the inner side of FIG. It is a longitudinal cross-sectional view which shows 7th Embodiment of the wheel bearing apparatus which concerns on this invention. It is a principal part enlarged view which shows the seal part of the inner side of FIG. It is a principal part enlarged view which shows the conventional seal structure.

  A vehicle body mounting flange to be attached to the knuckle on the outer periphery, an outer member in which a double row outer rolling surface is integrally formed on the inner periphery, and a wheel mounting flange to mount a wheel on one end A hub wheel integrally formed and having an inner rolling surface facing one of the outer rolling surfaces of the double row on the outer periphery, and a small-diameter step portion extending in the axial direction from the inner rolling surface, and the hub wheel An inner member made of an inner ring that is press-fitted into a small-diameter step portion of the inner diameter through a predetermined squeeze and has an inner rolling surface that faces the other of the outer rolling surfaces of the double row on the outer periphery, and the inner member A double row rolling element housed between the rolling surfaces of the outer member so as to roll freely, and a bearing mounted in an opening of an annular space formed between the outer member and the inner member. A wheel bearing device comprising a seal, wherein the bearing seal is an end portion of the outer member. A core member fitted in the periphery, and a seal member which is vulcanized and bonded to the fitting portion of the core metal, the seal member extending in a radial direction, and the wheel mounting flange The base portion has a side lip that is slidably contacted via a predetermined axial shimoshiro, and a cylindrical portion that is fitted to the inner periphery of the outer side end of the outer member, and extends radially outward from the cylindrical portion. A weir member having a substantially L-shaped cross section, which is formed of an upright plate portion and an elastic member that is joined to the upright plate portion and protrudes radially outward from the outer periphery of the end portion of the outer member, The wheel mounting flange is opposed to the inner side surface of the wheel mounting flange via a slight axial clearance, and is sealed by the side surface, the end surface of the outer member, and the bearing seal.

Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.
FIG. 1 is a longitudinal sectional view showing a first embodiment of a wheel bearing device according to the present invention, FIG. 2A is an enlarged view of a main part showing a seal portion of FIG. 1, and FIG. ) Is a principal part enlarged view showing a modification example of FIG. 2A, FIG. 3A is a principal part enlarged view showing a modification example of FIG. 2A, and FIG. 3B is a principal part showing a modification example of FIG. 4 (a) is an enlarged view of a main part showing a modification of FIG. 2 (a), FIG. 4 (b) is an enlarged view of a main part showing another modification of (a), and FIG. 5 (a). FIG. 6C is an enlarged view of a main part showing another modification of FIG. 2B, FIG. 6A is an enlarged view of a main part showing another modification of FIG. 2A, and FIG. FIG. 7A is a main part enlarged view showing another modification of FIG. 3A, FIG. 7A is a main part enlarged view showing another modification of FIG. 3A, and FIG. It is a principal part enlarged view which shows the modification of (). In the following description, the side closer to the outer side of the vehicle when assembled to the vehicle is referred to as the outer side (left side in FIG. 1), and the side closer to the center is referred to as the inner side (right side in FIG. 1).

  This wheel bearing device is referred to as a third generation for a driven wheel, and includes an inner member 3 including a hub wheel 1 and an inner ring 2 press-fitted into the hub wheel 1, and a double row of the inner member 3. And an outer member 5 inserted through rolling elements (balls) 4 and 4.

  The hub wheel 1 integrally has a wheel mounting flange 6 for attaching a wheel (not shown) to an end portion on the outer side, one (outer side) inner rolling surface 1a on the outer periphery, and this inner rolling. A small-diameter step portion 1b extending in the axial direction from the surface 1a is formed. Further, hub bolts 6 a are implanted at circumferentially equidistant positions of the wheel mounting flange 6.

  The inner ring 2 is formed with the other (inner side) inner rolling surface 2a on the outer periphery, and is press-fitted into the small-diameter step portion 1b of the hub wheel 1 through a predetermined shimiro, and the end portion of the small-diameter step portion 1b is radially inserted. It is fixed in the axial direction in a state where a predetermined bearing preload is applied by a caulking portion 1c formed by plastic deformation outward.

  The hub wheel 1 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 1a and an inner side of a wheel mounting flange 6 that becomes a seal land portion of a seal 8 to be described later. The surface is hardened in the range of 58 to 64 HRC by induction hardening from the base 6b to the small diameter step 1b. The caulking portion 1c is an unquenched portion with the surface hardness after forging. On the other hand, the inner ring 2 and the rolling element 4 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 5 integrally has a vehicle body mounting flange 5b to be attached to a knuckle (not shown) constituting a suspension device on the outer periphery, and the inner rolling surfaces 1a and 2a of the inner member 3 on the inner periphery. Opposing double-row outer rolling surfaces 5a and 5a are integrally formed. Between these rolling surfaces 5a, 1a and 5a, 2a, double-row rolling elements 4, 4 are accommodated via a cage 7 so as to roll freely.

  The outer member 5 is made 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 5a and 5a are hardened in the range of 58 to 64 HRC by induction hardening. Has been processed. Further, seals 8 and 9 are attached to the opening of the annular space formed between the outer member 5 and the inner member 3, leakage of the lubricating grease enclosed inside the bearing to the outside, and rainwater from the outside And dust are prevented from entering the bearing.

  Of the seals 8 and 9, the inner seal 9 is disposed opposite to each other, and is annularly inserted into the inner periphery of the inner side end portion of the outer member 5 serving as a fixed member via a predetermined scissors. And a so-called pack seal comprising a slinger 11 press-fitted into the outer diameter of the inner ring 2 serving as a rotation-side member via a predetermined scissors. The outer-side seal 8 includes a cored bar 12 press-fitted into the inner periphery of the outer-side end portion of the outer member 5 through a predetermined shimiro, and a seal member 13 joined to the cored bar 12. It is composed of an integral seal.

  The metal core 12 of the seal 8 is formed by pressing a cross section of an austenitic stainless steel plate (JIS standard SUS304 type) or cold rolled steel plate (JIS standard SPCC type) by press working. It is formed in a letter shape, and is formed in an annular shape as a whole. If the core metal 12 is formed by pressing from a steel plate having this type of rust prevention ability, rusting of the core metal 12 can be suppressed over a long period of time, and durability and sealing performance can be improved. .

  On the other hand, the seal member 13 is made of synthetic rubber such as NBR (acrylonitrile-butadiene rubber) and is integrally joined to the core metal 12 by vulcanization adhesion. As shown in an enlarged view in FIG. 2 (a), the seal member 13 has a side lip 13a extending inclined in the radially outward direction, and also inclined radially outward on the inner diameter side of the side lip 13a. The dust strip 13b that extends and the grease lip 13c that extends while inclining toward the inner side of the bearing are integrally provided.

  The base 6b on the inner side of the wheel mounting flange 6 is formed in a curved surface having an arc-shaped cross section. The side lip 13a and the dust lip 13b are slidably contacted with the base 6b with a predetermined axial squeeze, and the grease lip 13c is predetermined. Are arranged opposite to each other through a radial clearance. In addition to NBR, the material of the seal member 13 is excellent in heat resistance and chemical resistance, such as HNBR (hydrogenated acrylonitrile butadiene rubber), EPDM (ethylene propylene rubber), etc., which have excellent heat resistance. Examples thereof include ACM (polyacrylic rubber), FKM (fluororubber), and silicon rubber.

  Further, in this embodiment, a dam member 14 is disposed on the radially outer side of the seal 8. This dam member 14 is made of an austenitic stainless steel plate (JIS standard SUS304 type) or cold rolled steel plate (JIS standard SPCC type), such as a steel plate having rust prevention ability, and is substantially L-shaped in cross section by press working. A cylindrical portion 14a that is press-fitted to the outer peripheral surface of the end portion of the outer member 5 via a predetermined shimiro, and a standing plate portion 14b that extends radially outward from the cylindrical portion 14a. A labyrinth seal is formed by facing the inner side surface 6c of the wheel mounting flange 6 through a slight axial clearance. As a result, it is possible to prevent the muddy water from being directly applied to the side lip 13a of the seal 8, and even if muddy water is applied to the outer member 5 during traveling of the vehicle, it is transmitted along the outer peripheral surface of the outer member 5 to the wheel mounting flange 6. It is possible to prevent the fluid from flowing between the side surface 6c and to improve the durability and sealing performance of the seal 8 over a long period of time. In addition, it is possible to provide a wheel bearing device that can be used at least as the seal 8 and can be reduced in cost.

  (B) is a modification of (a). In this embodiment, only the seal configuration 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.

  The seal 15 shown in (b) is disposed opposite to each other, and an annular seal plate 16 that is press-fitted to the inner periphery of the outer side end portion of the outer member 5 via a predetermined shimoshiro, and the inner side of the wheel mounting flange 6 It is comprised by the pack seal | sticker which consists of the slinger 17 press-fitted in the base part 6b through predetermined | prescribed shimeshiro.

  The seal plate 16 includes a metal core 18 that is press-fitted into the outer member 5 and a seal member 19 that is bonded to the metal core 18 by vulcanization adhesion. The metal core 18 is formed into a substantially L-shaped cross section by pressing from a steel plate having rust prevention ability, such as an austenitic stainless steel plate (JIS standard SUS304 type) or a cold rolled steel plate (JIS standard SPCC type). Is formed. On the other hand, the seal member 19 is made of synthetic rubber such as NBR, and includes a side lip 19a, a dust lip 19b, and a grease lip 19c.

  The slinger 17 is formed into a substantially L-shaped cross section by press working from a steel plate having rust prevention ability, such as an austenitic stainless steel plate (JIS standard SUS304 type) or a cold rolled steel plate (JIS standard SPCC type). The side lip 19a is slidably contacted with the upright plate portion 17b via a predetermined axial direction sushi, and the dust lip 19b and the grease lip 19c are slidably contacted with the cylindrical portion 17a via a predetermined radial direction shimeros.

  Further, as in the above-described embodiment, a dam member 14 is disposed on the radially outer side of the seal 15, and faces the inner side surface 6 c of the wheel mounting flange 6 through a slight axial clearance to form a labyrinth seal. Is configured. Accordingly, it is possible to prevent the muddy water from being directly applied to the seal 15, and even if muddy water is applied to the outer member 5 and travels along the outer peripheral surface of the outer member 5 while the vehicle is running, the side surface 6 c of the wheel mounting flange 6 It is possible to prevent the fluid from flowing in between, and the durability and sealing performance of the seal 15 can be improved over a long period of time. Further, at least the seal 15 can be used at the same time, and the cost can be reduced by standardizing the seal.

  Fig.3 (a) is a modification of Fig.2 (a). A seal 8 is fitted to the inner periphery of the outer side end portion of the outer member 5, and a dam member 20 is disposed on the radially outer side of the seal 8. This weir member 20 has a substantially L-shaped cross section by press working from a steel plate having rust-preventing ability, such as an austenitic stainless steel plate (JIS standard SUS304 type) or a cold rolled steel plate (JIS standard SPCC type). And a cylindrical portion 20a that is press-fitted to the inner peripheral surface of the end portion of the outer member 5 via a predetermined shimiro and a standing plate portion 20b that extends radially outward from the cylindrical portion 20a. The upright plate portion 20b faces the inner side surface 6c of the wheel mounting flange 6 through a slight axial clearance to constitute a labyrinth seal. As a result, it is possible to prevent the muddy water from being directly applied to the side lip 13a of the seal 8, and even if muddy water is applied to the outer member 5 during traveling of the vehicle, it is transmitted along the outer peripheral surface of the outer member 5 to the wheel mounting flange 6. It is possible to prevent the fluid from flowing between the side surface 6c and to improve the durability and sealing performance of the seal 8 over a long period of time. 2B is a modification of FIG. 2B, the dam member 20 described above may be fitted to the end of the outer member 5 instead of the dam member 14.

  FIG. 4A is a modification of FIG. This dam member 21 is formed into a substantially L-shaped cross section by pressing from a steel plate having rust prevention capability, and a cylindrical portion 21a that is press-fitted into the outer peripheral surface of the end portion of the outer member 5 via a predetermined shimiro, There is a standing plate portion 14b extending radially outward from the cylindrical portion 21a. An L-shaped labyrinth clearance is formed between the inner side surface 6c and the base portion 6b of the wheel mounting flange 6, thereby forming a strong labyrinth seal. Here, the elastic member 22 made of synthetic rubber such as NBR is joined to the end of the cylindrical portion 21a so as to go around. Thereby, the airtightness of the fitting portion between the weir member 21 and the outer member 5 is increased, and muddy water or the like flows between the outer surface of the outer member 5 and the side surface 6c of the wheel mounting flange 6. Can be reliably prevented.

  (B) is a modification of FIG. This dam member 23 is formed into a substantially L-shaped cross section by pressing from a steel plate having rust prevention ability, and a cylindrical portion 23a that is press-fitted into the inner peripheral surface of the end portion of the outer member 5 via a predetermined shimiro, There is a standing plate portion 20b extending radially outward from the cylindrical portion 23a. An L-shaped labyrinth clearance is formed between the inner side surface 6c and the base portion 6b of the wheel mounting flange 6, thereby forming a strong labyrinth seal. Here, the elastic member 22 is joined to the end of the cylindrical portion 23a so as to improve the airtightness of the fitting portion between the weir member 23 and the outer member 5.

  FIG. 5A is another modification of FIG. The dam member 24 is formed by pressing from a steel plate having rust prevention ability, and is pressed into the outer peripheral surface of the end portion of the outer member 5 via a predetermined shimiro, and the diameter from the cylindrical portion 24a. It has a standing plate portion 24b extending outward in the direction and a disc portion 24c extending inward in the radial direction in close contact with the end surface of the outer member 5 from the cylindrical portion 24a. A labyrinth seal is formed by facing the inner side surface 6c of the wheel mounting flange 6, the base portion 6b, and the slinger 17 of the seal 15 through a slight axial clearance. Accordingly, it is possible to prevent the muddy water from being directly applied to the seal 15, and even if muddy water is applied to the outer member 5 and travels along the outer peripheral surface of the outer member 5 while the vehicle is running, the side surface 6c of the wheel mounting flange 6 It is possible to prevent the fluid from flowing in between, and the durability and sealing performance of the seal 15 can be improved over a long period of time. Further, at least the seal 15 can be used at the same time, and the cost can be reduced by standardizing the seal.

  (B) is a modification of (a). The dam member 25 is formed by pressing from a steel plate having a rust-preventing ability, and is pressed into the inner peripheral surface of the end portion of the outer member 5 via a predetermined shimiro, and the dam member 25 is external to the cylindrical portion 25a. It has the standing board part 25b extended in radial direction outward in the state closely_contact | adhered to the end surface of the direction member 5, and the disc part 25c extended in radial direction from the cylindrical part 25a. A labyrinth seal is formed by facing the inner side surface 6c of the wheel mounting flange 6, the base portion 6b, and the slinger 17 of the seal 15 through a slight axial clearance. Accordingly, it is possible to prevent the muddy water from being directly applied to the seal 15, and even if muddy water is applied to the outer member 5 and travels along the outer peripheral surface of the outer member 5 while the vehicle is running, the side surface 6c of the wheel mounting flange 6 It is possible to prevent the fluid from flowing between.

  (C) is a modification of (b), and the configuration of the seal is different. The seals 26 are arranged so as to face each other, and are fitted to an annular seal plate 27 that is press-fitted into a base portion 6 b on the inner side of the wheel mounting flange 6 via a predetermined shimiro, and an inner peripheral surface of an end portion of the outer member 5. The dam member 25 is composed of a pack seal.

  The seal plate 27 includes a core metal 28 press-fitted into the base 6b, and a seal member 29 joined to the core metal 28 by vulcanization adhesion. The core metal 28 is formed into a substantially L-shaped cross section by pressing from a steel plate having rust prevention ability such as an austenitic stainless steel plate (JIS standard SUS304 type) or a cold rolled steel plate (JIS standard SPCC type). Is formed. On the other hand, the seal member 29 is made of synthetic rubber such as NBR, and has a side wipe 29a, a dust lip 29b, and a grease lip 29c. The side lip 29a is in sliding contact with the disk portion 25c of the weir member 25 via a predetermined axial squeeze, and the dust lip 29b and the grease lip 29c are directly connected to the inner peripheral surface of the outer member 5 in the predetermined radial direction. It is in sliding contact with a shime-shiro.

  Here, the dam member 25 constitutes a labyrinth seal by facing the inner side surface 6c of the wheel mounting flange 6 through a slight axial clearance, as in the above-described embodiment, and the role of the slinger of the seal 26 I am doing. Accordingly, it is possible to prevent the muddy water from being directly applied to the seal 26, and even if muddy water is applied to the outer member 5 and travels along the outer peripheral surface of the outer member 5 while the vehicle is running, the side surface 6 c of the wheel mounting flange 6 It is possible to prevent the fluid from flowing in between, and the durability and sealing performance of the seal 26 can be improved over a long period of time. Furthermore, the number of parts can be reduced, and the size can be reduced.

  FIG. 6A is another modification of FIG. This dam member 30 is formed into a substantially L-shaped cross section by pressing from a steel plate having rust prevention ability, and a cylindrical portion 14a that is press-fitted into the outer peripheral surface of the end portion of the outer member 5 via a predetermined shimiro, The cylindrical portion 14a is integrally joined by vulcanization and extends radially outward, and has a standing plate portion 30a made of synthetic rubber such as NBR. The upright plate portion 30a faces the inner side surface 6c of the wheel mounting flange 6 via an axial clearance to form a labyrinth seal. This prevents the weir member 30 from plastically deforming due to contact with other parts during assembly or when the vehicle travels, and the desired labyrinth seal is formed over a long period of time to improve the sealing performance. Can be maintained.

  (B) is another modification of FIG. 3 (a). This dam member 31 is formed into a substantially L-shaped cross section by pressing from a steel plate having rust prevention ability, and a cylindrical portion 20a that is press-fitted to the inner peripheral surface of the end portion of the outer member 5 via a predetermined shimiro, A bent portion 31a extending radially outward from the cylindrical portion 20a, and a standing plate portion 31b made of synthetic rubber such as NBR that is integrally joined to the bent portion 31a by vulcanization and extends radially outward. have. An L-shaped labyrinth clearance is formed between the inner side surface 6c and the base portion 6b of the wheel mounting flange 6, thereby forming a strong labyrinth seal. As in the above-described embodiment, this prevents the weir member 30 from being plastically deformed by contact with other components during assembly or collision of flying stones when the vehicle is running, and a desired labyrinth seal over a long period of time. The sealing property can be maintained.

  FIG. 7A shows another modification of FIG. This dam member 32 is formed into a substantially L-shaped cross section by pressing from a steel plate having rust prevention ability, and is a cylindrical portion 20a that is press-fitted into the inner peripheral surface of the end portion of the outer member 5 via a predetermined shimiro, A bent portion 32a extending from the cylindrical portion 20a to the end surface of the outer member 5 and extending radially outward; and a standing plate portion 32c extending radially outward from the bent portion 32a via an inclined portion 32b. have.

  Further, an external seal 33 is fixed to the wheel mounting flange 6 by a hub bolt 6a. The outer seal 33 is formed by press working from a steel plate having rust prevention ability, and is fitted to the outer diameter of the wheel mounting flange 6 and extends radially inward from the cylindrical portion 33a. A disc portion 33b joined in close contact with the inner side surface 6c of the mounting flange 6, an inner diameter portion 33c bent from the disc portion 33b to the inner side, and vulcanization adhesion to the inner diameter portion 33c. A side lip 33d made of synthetic rubber such as NBR is integrally bonded. The side lip 33d is in sliding contact with the upright plate portion 32c of the weir member 32 via a predetermined axial squeeze. Accordingly, it is possible to reliably prevent the muddy water from being directly applied to the seal 8, and even if the muddy water is applied to the outer member 5 and travels along the outer peripheral surface of the outer member 5 while the vehicle is traveling, the side surface of the wheel mounting flange 6. It is possible to prevent the fluid from flowing between 6c.

  (B) is a modification of (a), and an external seal 34 is fitted to the base 6 c on the inner side of the wheel mounting flange 6. This external seal 34 is formed from a steel plate having a rust-proofing ability in a substantially L-shaped section by press working, and a cylindrical portion 34a fitted to a step portion 35 formed on the base portion 6c of the wheel mounting flange 6, A bent portion 34b extending radially outward from the cylindrical portion 34a and a side lip 33d made of synthetic rubber such as NBR are integrally joined to the bent portion 34b by vulcanization adhesion. The side lip 33d is in sliding contact with the upright plate portion 20b of the weir member 20 via a predetermined axial squeeze. Accordingly, it is possible to prevent the muddy water from being directly applied to the seal 8, and even if muddy water is applied to the outer member 5 and travels along the outer peripheral surface of the outer member 5 while the vehicle is running, It is possible to prevent the fluid from flowing between.

  FIG. 8 is a longitudinal sectional view showing a second embodiment of the wheel bearing device according to the present invention, and FIG. 9 is an enlarged view of a main part showing a seal part on the outer side of FIG. This embodiment basically differs from the first embodiment described above (FIG. 1) only in the seal structure, and other parts and parts having the same function or the same function as those of the above-described embodiment are used. The same reference numerals are assigned and detailed description is omitted.

  This wheel bearing device is referred to as a third generation for a driven wheel, and includes an inner member 3 including a hub wheel 1 and an inner ring 2 press-fitted into the hub wheel 1, and a double row of the inner member 3. And an outer member 5 inserted through rolling elements 4 and 4. Seals 36 and 9 are attached to the opening of the annular space formed between the outer member 5 and the inner member 3, leakage of the lubricating grease enclosed in the bearing inside, and rainwater and dust from the outside. Etc. are prevented from entering the inside of the bearing.

  As shown in an enlarged view in FIG. 9, the outer side seal 36 is disposed opposite to each other, and an annular seal plate 37 press-fitted into the inner periphery of the outer side end portion of the outer member 5 via a predetermined shimiro. The pack seal is composed of a slinger 17 that is press-fitted into the outer diameter of the base portion 6b of the hub wheel 1 through a predetermined scissors.

  The seal plate 37 includes a metal core 18 that is press-fitted into the outer member 5, and a seal member 38 that is bonded to the metal core 18 by vulcanization adhesion. The seal member 38 is made of synthetic rubber such as NBR, and has a side lip 19a, a dust lip 19b, and a grease lip 19c. The side lip 19a is in sliding contact with the upright plate portion 17b of the slinger 17 via a predetermined axial shimiro, and the dust lip 19b and the grease lip 19c are in sliding contact with the cylindrical portion 17a via a predetermined radial shimillo. .

  Here, the seal member 38 is formed with a weir 39 that protrudes from the end of the core 18 beyond the end surface of the outer member 5, and a slight axial clearance is provided on the inner side surface 6 c of the wheel mounting flange 6. The labyrinth seal is constructed, and the dam portion 39 and the standing plate portion 17b of the slinger 17 are opposed to each other through a slight radial clearance to constitute the labyrinth seal. Accordingly, it is possible to prevent the muddy water from being directly applied to the seal 36 and to prevent the muddy water from flowing to the seal 36 along the outer peripheral surface of the outer member 5 even when muddy water is applied to the outer member 5 while the vehicle is running. The durability and sealing performance of the seal 36 can be improved over a long period of time.

  FIG. 10 is a longitudinal sectional view showing a third embodiment of the wheel bearing device according to the present invention, FIG. 11A is an enlarged view of the main part showing the outer seal portion of FIG. 10, and FIG. FIG. 11 is an enlarged view of a main part showing a seal part on the inner side of FIG. 10. The same parts and parts as those of the second embodiment (FIG. 8) described above or parts and parts having the same functions are denoted by the same reference numerals and detailed description thereof is omitted.

  This wheel bearing device is referred to as a third generation for driving wheels, and includes an inner member 41 including a hub wheel 40 and an inner ring 2 press-fitted into the hub wheel 40, and a double row of the inner member 41. And an outer member 5 inserted through rolling elements 4 and 4. Seals 42 and 36 are attached to the opening of the annular space formed between the outer member 5 and the inner member 41, leakage of the lubricating grease enclosed in the bearing inside, and rainwater and dust from the outside. Etc. are prevented from entering the inside of the bearing.

  As shown in an enlarged view in FIG. 11A, the outer-side seal 42 includes a core metal 12 press-fitted through a predetermined shimiro to the inner periphery of the outer-side end portion of the outer member 5, and the core metal. 12 and a seal member 43 joined to the integrated seal 12.

  The seal member 43 is made of synthetic rubber such as NBR and is integrally joined to the cored bar 12 by vulcanization adhesion. The seal member 43 is inclined to the radially inwardly extending side lip 13a, to the inner diameter side of the side lip 13a, the dust lip 13b extending to be radially outwardly inclined, and the inward bearing side. It has a grease lip 13c extending in an integral manner.

  Here, the seal member 43 is wrapped around and joined to the fitting portion of the core metal 12, and the weir portion 44 that protrudes beyond the end surface of the outer member 5 is formed. The labyrinth seal is configured to face the inner side surface 6c of the wheel mounting flange 6 via a slight axial clearance. Accordingly, it is possible to prevent the muddy water from being directly applied to the side lip 13a of the seal 42, and even if muddy water is applied to the outer member 5 during traveling of the vehicle, the muddy water flows along the outer peripheral surface of the outer member 5 to the seal 42. In addition, the airtightness of the fitting portion between the seal 42 and the outer member 5 can be improved, and the durability and sealing performance of the seal 42 can be improved over a long period of time.

  On the other hand, the inner seal 36 is disposed opposite to the outer joint member 46 of the constant velocity universal joint 45. Then, as shown in an enlarged view in (b), the protruding dam portion 39 faces the shoulder portion 47 of the outer joint member 46 through a slight axial clearance, thereby forming a labyrinth seal. Accordingly, it is possible to prevent the muddy water from being directly applied to the seal 36, and even if muddy water is applied to the outer member 5 during traveling of the vehicle, the muddy water flows along the outer peripheral surface of the outer member 5 and flows to the seal 36 and the caulking portion 1c. In addition to improving the durability and sealing performance of the seal 36 over a long period of time, it is possible to prevent rusting of the crimped portion 1c.

  FIG. 12 is a longitudinal sectional view showing a fourth embodiment of the wheel bearing device according to the present invention, and FIG. 13 is an enlarged view of a main part showing a seal part on the inner side of FIG. Note 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.

  This wheel bearing device is referred to as the 2.5th generation for driving wheels, and includes a hub wheel 48 and a wheel bearing 49 that is externally fixed to the hub wheel 48. The hub wheel 48 integrally has a wheel mounting flange 6 at an end portion on the outer side, and a cylindrical small-diameter step portion 48b extending in the axial direction from the wheel mounting flange 6 via a shoulder portion 48a is formed. The hub ring 48 is formed of medium and high carbon steel containing 0.40 to 0.80 wt% of carbon such as S53C, and the surface is hardened in the range of 50 to 64 HRC by induction hardening from the shoulder portion 48a to the small diameter step portion 48b. Has been processed.

  The wheel bearing 49 has a vehicle body mounting flange 5b integrally formed on the outer periphery, and an outer member 50 formed with tapered double-row outer rolling surfaces 50a and 50a that are opened outward on the inner periphery, A tapered inner rolling surface 52a that is inserted into the outer member 50 via double row rolling elements (cone rollers) 51, 51 and faces the double row outer rolling surfaces 50a, 50a is formed on the outer periphery. A pair of inner rings 52, 52 are provided. The double-row rolling elements 51, 51 are held by the cages 53, 53 so as to be freely rotatable in the circumferential direction, and by a large collar 52b formed on the large diameter side of the inner rolling surface 52a of the inner ring 52. Guided.

  The outer member 50 is made 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 50a and 50a are hardened in the range of 58 to 64HRC by induction hardening. Has been processed. On the other hand, the inner ring 52 and the rolling element 51 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.

  Seals 9 and 36 are attached to the openings of the annular space formed between the outer member 50 and the pair of inner rings 52 and 52. Leakage of the lubricating grease sealed inside the bearing and rainwater from the outside And dust are prevented from entering the bearing.

  A pulsar ring 54 for detecting the rotational speed of the wheel is fitted to the outer diameter of the shoulder 47 of the outer joint member 46. The pulsar ring 54 is made of a sintered alloy, and uneven portions 54a are formed on the outer periphery at equal intervals in the circumferential direction. As shown in an enlarged view in FIG. 13, the weir 39 of the inner side seal 36 faces the pulsar ring 54 through a slight axial clearance to form a labyrinth seal. Accordingly, it is possible to prevent the muddy water from being directly applied to the seal 36, and even if muddy water is applied to the outer member 5 and the outer joint member 46 while the vehicle is running, the seal 36 and the caulking portion 1c are transmitted along the outer peripheral surface thereof. In addition to improving the durability and sealing performance of the seal 36 over a long period of time, it is possible to prevent rusting of the crimped portion 1c.

  FIG. 14 is a longitudinal sectional view showing a fifth embodiment of the wheel bearing device according to the present invention, and FIG. 15 is an enlarged view of a main part showing a seal part on the inner side of FIG. This embodiment basically differs from the above-described fourth embodiment (FIG. 12) only in the configuration of the pulsar ring, and is the same as the above-described embodiment in the same parts or parts having the same functions. Are denoted by the same reference numerals, and detailed description thereof is omitted.

  In the present embodiment, the slinger 55 is fitted to the outer diameter of the shoulder 47 of the outer joint member 46. This weir member 55 is formed into a substantially L-shaped cross section by pressing from a stainless steel plate such as an austenitic stainless steel plate (JIS standard SUS304 series) or a ferritic stainless steel plate (JIS standard SUS430 series), As shown in FIG. 15 in an enlarged manner, it has a cylindrical fitting portion 55a that is press-fitted into the outer diameter of the shoulder portion 47, and a standing plate portion 55b that extends radially outward from the fitting portion 55a. Yes. The weir portion 39 of the inner seal 36 faces the upright plate portion 55b of the slinger 55 through a slight axial clearance to form a labyrinth seal. Accordingly, it is possible to prevent the muddy water from being directly applied to the seal 36, and even if muddy water is applied to the outer member 5 and the outer joint member 46 while the vehicle is running, the seal 36 and the caulking portion 1c are transmitted along the outer peripheral surface thereof. In addition to improving the durability and sealing performance of the seal 36 over a long period of time, it is possible to prevent rusting of the crimped portion 1c.

  FIG. 16 is a longitudinal sectional view showing a sixth embodiment of the wheel bearing device according to the present invention, and FIG. 17 is an enlarged view of a main part showing a seal part on the inner side of FIG. This embodiment basically differs from the above-described fourth embodiment (FIG. 12) only in the configuration of the pulsar ring, and is the same as the above-described embodiment in the same parts or parts having the same functions. Are denoted by the same reference numerals, and detailed description thereof is omitted.

  This wheel bearing device is referred to as the 2.5th generation for driving wheels, and includes a hub wheel 56 and a wheel bearing 57 that is fitted and fixed to the hub wheel 56. The hub wheel 56 integrally has a wheel mounting flange 6 at an end on the outer side, and a cylindrical small-diameter stepped portion 48b extending in the axial direction from the wheel mounting flange 6 via a shoulder portion 48a is formed. The hub wheel 56 is formed of medium and high carbon steel containing 0.40 to 0.80 wt% of carbon such as S53C, and the surface is hardened in the range of 50 to 64 HRC by induction hardening from the shoulder portion 48a to the small diameter step portion 48b. Has been processed.

  The wheel bearing 57 has an outer member 50 integrally formed with a vehicle body mounting flange 5b on the outer periphery and formed with tapered double-row outer rolling surfaces 50a, 50a opened outward on the inner periphery. A tapered inner rolling surface 52a that is inserted into the outer member 50 via double row rolling elements (cone rollers) 51, 51 and faces the double row outer rolling surfaces 50a, 50a is formed on the outer periphery. A pair of inner rings 52, 52 are provided. Further, seals 9 and 58 are attached to the opening of the annular space formed between the outer member 50 and the pair of inner rings 52 and 52, and leakage of the lubricating grease sealed inside the bearing to the outside This prevents rainwater and dust from entering the bearing.

  In the present embodiment, the sensor rotor 59 is fitted in contact with the caulking portion 1 c of the hub wheel 56. The sensor rotor 59 is formed of a sintered alloy so as to have a substantially L-shaped cross section, a cylindrical fitting portion 59a that is press-fitted into the inner periphery of the hub wheel 56, and a disk that extends radially outward from the fitting portion 59a. And an uneven portion 54a is formed on the outer periphery of the disc portion 59 at equal intervals in the circumferential direction.

  As shown in an enlarged view in FIG. 17, the inner-side seal 58 includes an annular seal plate 60 that is disposed to face each other and is press-fitted to the inner periphery of the outer-side end portion of the outer member 5 via a predetermined shimoshiro. The pack ring is composed of a slinger 17 that is press-fitted into the outer diameter of the inner ring 52 via a predetermined scissors.

  The seal plate 60 includes a metal core 18 that is press-fitted into the outer member 5, and a seal member 61 that is bonded to the metal core 18 by vulcanization adhesion. The seal member 61 is made of synthetic rubber such as NBR, and includes a side lip 19a, a dust lip 19b, and a grease lip 19c. The side lip 19a is in sliding contact with the standing plate portion 17b of the slinger 17 via a predetermined axial shimiro, and the dust lip 19b and the grease lip 19c are in sliding contact with the cylindrical portion 17a via a predetermined radial shimillo. .

  Here, the sealing member 61 wraps around and is joined to the fitting portion of the cored bar 18, and the weir portion 62 that protrudes beyond the end surface on the inner side of the outer member 5 is formed. The weir portion 62 includes a base portion 62a extending radially outward in close contact with the end surface of the outer member 5, and a lip portion 62b extending inclined from the base portion 62a toward the inner side toward the radially outer side. Have. The lip portion 62b faces the disc portion 59b of the sensor rotor 59 via a slight axial clearance, thereby forming a labyrinth seal. As a result, it is possible to prevent the muddy water from being directly applied to the seal 58 and the caulking portion 1c, and even if muddy water is applied to the outer member 5 while the vehicle is running, the seal 58 and the additional pressure are transmitted along the outer peripheral surface of the outer member 5. It is possible to prevent flow to the tightening portion 1c, to improve the durability and sealing performance of the seal 58 over a long period of time, and to prevent rusting of the crimping portion 1c.

  FIG. 18 is a longitudinal sectional view showing a seventh embodiment of the wheel bearing device according to the present invention, and FIG. 19 is an enlarged view of a main part showing a seal part on the inner side of FIG. Note 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.

  This wheel bearing device is referred to as the 2.5th generation for driving wheels, and includes a hub wheel 63 and a wheel bearing 64 that is externally fixed to the hub wheel 63. The hub wheel 63 integrally has a wheel mounting flange 6 at an end portion on the outer side, and a cylindrical small-diameter stepped portion 48b extending in the axial direction from the wheel mounting flange 6 via a shoulder portion 48a is formed. The hub wheel 63 is made of medium and high carbon steel containing 0.40 to 0.80 wt% of carbon such as S53C, and the surface is hardened in the range of 50 to 64 HRC by induction hardening from the shoulder portion 48a to the small diameter step portion 48b. Has been processed.

  The wheel bearing 64 has an outer member 50 integrally formed with a vehicle body mounting flange 5b on the outer periphery and formed with tapered double-row outer rolling surfaces 50a, 50a opened outward on the inner periphery. A pair of inner rolling surfaces 52a, which are inserted into the outer member 50 via double row rolling elements 51, 51, and have outer circumferential surfaces 50a, 50a facing the double rows on the outer periphery. Inner rings 52 and 52 are provided. Seals 9 and 65 are attached to the openings of the annular space formed between the outer member 50 and the pair of inner rings 52 and 52, and leakage of the lubricating grease sealed inside the bearing to the outside This prevents rainwater and dust from entering the bearing.

  In the present embodiment, the outer joint member 66 is coupled to the hub wheel 63 so that torque can be transmitted with the shoulder 67 of the outer joint member 66 abutting against the large end surface of the inner ring 52 on the inner side. An annular recess 68 is formed at the outer diameter corner of the shoulder 67, and a weir 62 of a seal 65 described later is engaged with the annular recess 68.

  As shown in an enlarged view in FIG. 19, the inner-side seal 65 is joined to a cored bar 69 that is press-fitted into the inner periphery of the inner-side end portion of the outer member 5 via a predetermined shimiro, and to the cored bar 69. It is comprised by the integral type seal | sticker which consists of the sealed member 70 made.

  The metal core 69 of the seal 65 has an approximately L cross-section by pressing from a steel plate having rust prevention ability such as an austenitic stainless steel plate (JIS standard SUS304 type) or a cold rolled steel plate (JIS standard SPCC type). It is formed in a letter shape and is formed in an annular shape as a whole. On the other hand, the seal member 70 is made of synthetic rubber such as NBR, and is integrally joined to the cored bar 69 by vulcanization adhesion. The seal member 70 integrally includes a pair of side lips 70a and 70b extending obliquely outward in the radial direction and a grease lip 70c extending obliquely toward the bearing inward side.

  Here, the pair of side lips 70a and 70b are slidably contacted with the shoulder portion 67 of the outer joint member 66 with a predetermined axial squeezing force, and the grease lip 70c is adjusted to the outer diameter of the inner ring 52 via the predetermined radial squeezing force. It is in sliding contact. Note that the pair of side lips 70a and 70b is set differently. That is, the side lip 70a on the outer diameter side is set larger than the side lip 70b on the inner diameter side. As a result, the sliding torque of the seal 65 can be suppressed, and the desired sealing performance can be maintained even if the outer side lip 70a is worn.

  Further, the seal member 70 wraps around and is joined to the fitting portion of the cored bar 18, and a dam portion 62 that protrudes beyond the end surface on the inner side of the outer member 5 is formed. The weir portion 62 includes a base portion 62a extending radially outward in close contact with the end face of the outer member 5, and a lip portion 62b extending inclined from the base portion 62a toward the inner side in the radial direction. Have. The lip portion 62b faces the disc portion 59b of the sensor rotor 59 via a slight axial clearance, thereby forming a labyrinth seal. Accordingly, it is possible to prevent the muddy water from being directly applied to the seal 65 and to prevent the muddy water from being applied to the outer member 5 during traveling of the vehicle and flowing to the seal 65 along the outer peripheral surface of the outer member 5. The durability and sealing performance of the seal 65 can be improved over a long period of time.

  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 according to the present invention is a first generation in which a seal is attached to an opening of an annular space formed between an inner member serving as a rotation-side member and an outer member serving as a fixed-side member. It can be applied to wheel bearing devices of second generation, third generation, or fourth generation structure.

1, 40, 48, 56, 63 Hub wheel 1a, 2a, 52a Inner rolling surface 1b, 48b Small diameter step portion 1c Clamping portion 2, 52 Inner ring 3, 41 Inner member 4, 51 Rolling element 5, 50 Outer Members 5a, 50a Outer rolling surface 5b Car body mounting flange 6 Wheel mounting flange 6a Hub bolt 6b Base side 6c on the inner side of the wheel mounting flange Side surface 7, 53 on the inner side of the wheel mounting flange Cage 8, 9, 15, 26, 36 , 42, 58, 65 Seal 10, 16, 27, 37, 60 Seal plate 11, 17, 55 Slinger 12, 18, 28, 69 Core 13, 13, 29, 38, 43, 61, 70 Seal member 13a, 19b, 29a, 33d, 70a, 70b Side lip 13b, 19b, 29b Dustrip 13c, 19c, 29c, 70c Grease lip 14, 20, 21, 3, 24, 25, 30, 31, 32 Weir members 14a, 17a, 20a, 21a, 23a, 24a, 25a, 33a, 34a Cylindrical portions 14b, 17b, 20b, 24b, 25b, 30a, 31b, 32c, 55b Plate portion 22 Elastic members 31a, 32a, 34a Bent portions 24c, 25c, 33b, 59b Disc portion 32b Inclined portion 33 External seal 33c Inner diameter portion 35 Step portions 39, 44, 62 Weir portion 45 Constant velocity universal joints 46, 66 Outer joint member 47, 58a, 67 Shoulder portion 49, 57, 64 Wheel bearing 52b Large flange 54 Pulsar ring 54a Uneven portion 59 Sensor rotor 55a, 59a Fitting portion 62a Base portion 62b Lip portion 68 Annular recess 100 Outer member 100a Outside Rolling surface 100b Outer peripheral surface 101 Cage 102 Ball 103 Hub wheel 103a Inner rolling surface 104 Wheel mounting Side surface 105 sealing structure Nji 104a wheel mounting flange 106 core metal 106a dam member 107 elastic sealing member 108 axial lip portion 109 radial lip portion

Claims (17)

An outer member integrally having a vehicle body mounting flange for being attached to the knuckle on the outer periphery, and an outer rolling surface of a double row integrally formed on the inner periphery;
A hub wheel having a wheel mounting flange for mounting a wheel at one end thereof, and a hub wheel having a small diameter step portion extending in the axial direction from the wheel mounting flange on the outer periphery, and a small diameter step portion of the hub wheel are press-fitted, An inner member composed of at least one inner ring formed with an inner rolling surface opposite to the double row outer rolling surface;
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 device comprising a bearing seal mounted in an opening of an annular space formed between the outer member and the inner member,
The bearing seal is composed of a core metal fitted in the inner periphery of the end portion of the outer member, and a seal member that wraps around the fitting part of the core metal and is integrally vulcanized and bonded. The side lip and the radial lip extending in an inclined direction are integrally provided, and an annular dam member is provided at the outer side end of the outer member, and the dam member is provided on the inner side of the wheel mounting flange. A wheel bearing device, wherein the wheel bearing device is opposed to a side surface through a slight axial clearance and is sealed by the side surface, an end surface of the outer member, and the bearing seal.   The dam member is disposed as a separate body on the radially outer side of the bearing seal, and the dam member has a rust prevention ability after pressing from a steel plate having a rust prevention ability or after pressing from a steel plate. A cylindrical portion that is formed of a painted member and is press-fitted into the end portion of the outer member via a predetermined squeeze, and extends radially outward from the cylindrical portion, and the outer periphery of the end portion of the outer member The wheel bearing device according to claim 1, further comprising a standing plate portion that protrudes radially outward.   The wheel bearing device according to claim 2, wherein the cylindrical portion of the dam member is press-fitted into the outer periphery of the end portion of the outer member.   The wheel bearing device according to claim 2, wherein the cylindrical portion of the dam member is press-fitted into the inner periphery of the end portion of the outer member.   The wheel bearing device according to claim 2, wherein an elastic member is joined to an end portion of the cylindrical portion so as to go around.   Outer side bearing seals of the bearing seals are arranged to face each other, and are press-fitted into the inner periphery of the outer side end of the outer member via a predetermined shimiro, and have an annular seal plate having the seal member; It is composed of a pack seal composed of a slinger that is press-fitted into the inward member through a predetermined scissors, and a side lip and a radial lip of the seal member are in sliding contact with the slinger, and the weir member is the cylinder 5. A disc portion extending inward in the radial direction from the portion is integrally formed, and the disc portion is opposed to the slinger via a slight axial clearance to form a labyrinth seal. The wheel bearing apparatus described in 1.   The seal plate is press-fitted into a base portion on the inner side of the wheel mounting flange via a predetermined squeeze, a radial lip of the seal member extends radially outward, and a predetermined radial direction is formed on the inner periphery of the end of the outer member. The dam member is integrally slidably contacted through a shimoshiro, and the weir member integrally has a disk portion extending radially inward from the cylindrical portion, and the side lip of the seal member is inclined radially inward. 5. The wheel bearing device according to claim 2, wherein the wheel bearing device extends and is slidably contacted with a disk portion of the dam member via a predetermined axial shimiro.   The elastic member is joined to the standing plate portion of the dam member, and the elastic member is opposed to the inner side surface of the wheel mounting flange via a slight axial clearance. Wheel bearing device.   An external seal having a side lip integrally disposed on a radially outer side of the bearing seal is disposed as a separate body, and the side lip is slidably contacted with the upright plate portion via a predetermined axial nip. Bearing device for 2 to 7 wheels.   The wheel bearing device according to claim 9, wherein the outer seal has a disk part, and the disk part is joined to the inner side surface of the wheel mounting flange by a hub bolt.   Outer side bearing seals of the bearing seals are arranged to face each other, and are press-fitted into the inner periphery of the outer side end of the outer member via a predetermined shimiro, and have an annular seal plate having the seal member; The seal member is composed of a pack seal made of a slinger that is press-fitted into the inner member through a predetermined scissors, and a side lip and a radial lip of the seal member are in sliding contact with the slinger, and the core metal The dam member is formed so as to protrude integrally from the end of the outer member beyond the end surface of the outer member, and is opposed to the inner side surface of the wheel mounting flange via a slight axial clearance to form a labyrinth seal. 2. The wheel bearing device according to claim 1, wherein the weir member and the slinger face each other with a slight radial clearance to form a labyrinth seal. .   Of the bearing seals, bearing seals on the inner side are arranged to face each other, and are press-fitted into the inner periphery of the inner side end portion of the outer member via a predetermined shimiro, and have an annular seal plate having the seal member; A pack seal is formed of a slinger that is press-fitted into the outer diameter of the inner ring through a predetermined scissors, and a side lip and a radial lip of the seal member are in sliding contact with the slinger, and the core is in contact with the seal member. The weir member is integrally formed so as to protrude from the end portion of the gold beyond the end surface of the outer member, and an outer joint member of a constant velocity universal joint is coupled to the inner member so as to transmit torque, and the outer joint member The weir member is opposed to the shoulder portion through a slight axial clearance to form a labyrinth seal, and the weir member and the slinger are opposed to each other through a slight radial clearance. Labyrinth seals are the wheel bearing apparatus according to any one of claims 1 to 11 is constructed.   Of the bearing seals, an inner side bearing seal is integrally joined to the inner periphery of the inner side end portion of the outer member via a predetermined shimoshiro, and the cored bar is integrally joined by vulcanization adhesion. The seal member integrally includes a pair of side lips extending obliquely outward in the radial direction and a grease lip extending inclined toward the inner side of the bearing. The dam member is integrally formed so as to protrude from the fitting portion of the core bar beyond the end surface of the outer member, and the outer joint member of the constant velocity universal joint is coupled to the inner member so as to transmit torque. The pair of side lips are slidably contacted with a shoulder portion of the outer joint member via a predetermined axial nip, the grease lip is slidably contacted with an outer diameter of the inner ring via a radial nip, and the seal The metal core in the member The dam member is formed so as to protrude integrally from the fitting portion beyond the end surface of the outer member, and an outer joint member of a constant velocity universal joint is coupled to the inner member so as to be able to transmit torque. The wheel bearing device according to any one of claims 1 to 11, wherein a labyrinth seal is configured by the weir member facing a shoulder portion via a slight axial clearance.   The wheel bearing device according to claim 13, wherein a side lip on the outer diameter side of the pair of side lips is set to be larger than a side lip on the inner diameter side.   The slinger is externally fitted to the shoulder portion of the outer joint member, and the labyrinth seal is configured by the dam member facing the slinger via a slight axial clearance. Wheel bearing device.   An annular recess is formed in a shoulder portion of the outer joint member, and the labyrinth seal is configured by the dam member facing the annular recess through a slight axial clearance. The wheel bearing device described.   The weir member has a base portion extending radially outward in close contact with the end face of the outer member, and a lip portion extending inclined from the base portion toward the radially outer side toward the inner side. The wheel bearing device according to any one of claims 12 to 16.

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