WO2009093535A1

WO2009093535A1 - Rotational speed detecting device and bearing edevice for wheel

Info

Publication number: WO2009093535A1
Application number: PCT/JP2009/050613
Authority: WO
Inventors: Kazunari Yamamoto; Katsumi Furukawa
Original assignee: Ntn Corporation
Priority date: 2008-01-22
Filing date: 2009-01-19
Publication date: 2009-07-30

Abstract

Provided are a rotational speed detecting device capable of accurate speed detection and being produced at reduced cost, and a bearing device for a wheel, provided with the rotational speed detecting device. A rotational speed detecting device has an encoder mounted to the inner member side of a bearing structure section of a bearing device for a wheel, and also has a sensor forming section in which a core is fixed to the outer member side of the bearing structure section. The sensor forming section has the core fitted and fixed to an end of the outer member of the bearing structure section, a resin section attached to the core, and a rotational speed sensor embedded in the resin section and facing the magnetic encoder with an air gap in between. Substantially that entire portion of the core which corresponds to the resin section protrudes from the remaining portion of the core to that side of the outer member which makes pressure contact with the core.

Description

Rotational speed detection device and wheel bearing device

The present invention relates to a rotational speed detection device and a wheel bearing device including the rotational speed detection device.

The wheel bearing device has evolved from a structure in which a double row rolling bearing called a first generation is used alone to a second generation in which a vehicle body mounting flange is integrated with an outer member. The third generation in which the inner raceway is integrally formed on one of the double row rolling bearings on the outer periphery of the hub wheel having an integral, and the constant velocity universal joint is integrated with the hub wheel. A fourth generation type has been developed in which the other inner rolling surface of the double row rolling bearing is integrally formed on the outer periphery of the outer joint member constituting the joint.

As shown in FIG. 15, a wheel bearing device called a third generation (for example, Patent Document 1) includes a hub wheel 102 having a flange 101 extending in the outer diameter direction, and an outer joint member 103 fixed to the hub wheel 102. The constant velocity universal joint 104 and the bearing structure 100 disposed on the outer peripheral side of the hub wheel 102 are provided.

The constant velocity universal joint 104 includes an outer joint member 103, an inner joint member 108 disposed in the bowl-shaped portion 107 of the outer joint member 103, and the inner joint member 108 and the outer joint member 103. A ball 109 is provided, and a holder 110 that holds the ball 109. Further, a spline portion 111 is formed on the inner peripheral surface of the center hole of the inner joint member 108, and an end spline portion of a shaft (not shown) is inserted into the center hole, and the spline portion 111 on the inner joint member 108 side The spline portion on the shaft side is engaged.

The hub wheel 102 has a cylindrical portion 113 and the flange 101, and a short cylindrical shape in which a wheel and a brake rotor (not shown) are mounted on the outer end surface 114 (end surface on the opposite joint side) of the flange 101. A pilot part 115 is provided in a protruding manner. The pilot portion 115 includes a large-diameter first portion 115a and a small-diameter second portion 115b. A brake rotor is externally fitted to the first portion 115a, and a wheel is externally fitted to the second portion 115b. Further, a bolt mounting hole 112 is provided in the flange 101 of the hub wheel 102, and a hub bolt for fixing the wheel and the brake rotor to the flange 101 is mounted in the bolt mounting hole 112.

The bearing structure 100 includes an outer member 105 and an inner ring 117 that is press-fitted into a small-diameter stepped portion 116 provided at the end of the tubular portion 113 on the saddle-shaped portion 107 side. A first inner raceway surface 118 is provided near the flange on the outer peripheral surface of the cylindrical portion 113 of the hub wheel 102, and a second inner raceway surface 119 is provided on the outer peripheral surface of the inner ring 117.

The outer member 105 is provided with two rows of

outer raceway surfaces

120 and 121 on its inner periphery and a flange (vehicle body mounting flange) 132 on its outer periphery. Then, the first outer raceway surface 120 of the outer member 105 and the first inner raceway surface 118 of the hub wheel 102 face each other, and the second outer raceway surface 121 of the outer member 105 and the raceway surface 119 of the inner ring 117 are formed. Opposing and the rolling element 122 is interposed between these.

The shaft portion 123 of the outer joint member 103 is inserted into the tube portion 113 of the hub wheel 102. The shaft portion 123 has a threaded portion 124 formed at the end of the ridged portion, and a spline portion 125 is formed between the threaded portion 124 and the hooked portion 107. Further, a spline portion 126 is formed on the inner peripheral surface (inner diameter surface) of the tube portion 113 of the hub wheel 102, and when the shaft portion 123 is inserted into the tube portion 113 of the hub wheel 102, The spline portion 125 engages with the spline portion 126 on the hub wheel 102 side.

Then, the nut member 127 is screwed to the screw portion 124 of the shaft portion 123 protruding from the tube portion 113, and the hub wheel 102 and the outer joint member 103 are connected. At this time, the inner end surface (back surface) 128 of the nut member 127 and the outer end surface 129 of the cylindrical portion 113 are in contact with each other, and the end surface 130 on the shaft portion side of the hook-shaped portion 107 and the outer end surface 131 of the inner ring 117 are in contact with each other. That is, by tightening the nut member 127, the hub wheel 102 is sandwiched between the nut member 127 and the hook-shaped portion 107 via the inner ring 117.

By the way, while supporting the wheel of a motor vehicle freely with respect to a suspension apparatus, the wheel bearing apparatus provided with the rotational speed detection apparatus which controls an anti-lock brake system (ABS) and detects the rotational speed of a wheel (patent document) 1) is generally known.

As shown in FIG. 16, the rotational speed detection device includes a cored bar 150 attached to the end 105 a on the inboard side of the outer member 105 of the bearing structure 100, and a resin mold 151 attached to the cored bar 150. And a rotational speed sensor 152 embedded in the resin mold 151.

In the rotational speed detection device as shown in FIG. 16, the cored bar 150 has a peripheral wall 156 press-fitted into the outer diameter surface of the end portion 105 a of the outer member 105, and an inner diameter from the end portion on the inboard side of the peripheral wall 156. This is an annular body having an L-shaped cross section composed of a side wall 157 extending in the direction. The resin mold body 151 is attached to a part of the side wall 157.

Also, a magnetic encoder 153 is attached to the seal member S that closes the opening on the inboard side of the bearing structure. That is, the magnetic encoder 153 includes a support ring 154 attached to an end portion on the inboard side of the inner ring 117 and an encoder body 155 attached to the support ring 154. The encoder body 155 is made of a rubber magnet having N and S poles alternately formed in the circumferential direction. Note that the side closer to the outside of the vehicle when assembled to the vehicle is called the outboard side (left side of the drawing), and the side closer to the center is called the inboard side (right side of the drawing).

The rotational speed sensor 152 is an IC that incorporates a magnetic detection element such as a Hall element, a magnetoresistive element (MR element), etc. that changes characteristics according to the flow direction of magnetic flux, and a waveform circuit that adjusts the output waveform of the magnetic detection element. It consists of. The magnetic encoder 153 is opposed through a predetermined air gap.

In the wheel bearing device as in Patent Document 1, when the vehicle repeats turning, the load on the bearing also changes, so that the outer member repeats elliptical deformation as the load changes. As a result, the core metal 150 fitted to the outer diameter of the outer member may come off in the axial direction or may be displaced in the circumferential direction, and ABS and vehicle speed detection may malfunction.

For this reason, a method for preventing malfunction of ABS and vehicle speed detection has been proposed (Patent Document 2). The thing of patent document 2 provides a groove | channel in an outer member, and crimps and fixes a metal core to this groove | channel.

The output of the rotational speed sensor 152 is taken out by the harness 162 and sent to an ABS controller (not shown). For this reason, as shown in FIG. 18, the harness 162 is connected via the take-out port 163 provided in the resin mold body 151, and the take-out port 163 has an inclination angle β of the outer peripheral surface of the outer joint member 103. In some cases, the inclination angle α is set to be large (Patent Document 3).

As a result, it is possible to prevent the harness 162 from hanging down and interfering with the outer joint member 103. Therefore, the clip for stopping the harness 162 from hanging down can be minimized, and the harness 162 itself need not be bent excessively. Therefore, the adverse effect on the internal wiring can be prevented and the reliability can be further improved.

Further, in the one shown in FIG. 18, the cored bar 150 includes a cylindrical fitting portion 150a fitted on the outer member 105, and a flange portion 150b extending radially inward from the fitting portion 150a. The bottom portion 150c extends in the axial direction from the flange portion 150b. Therefore, the inner edge of the inner end of the cored bar 150, that is, the inner end edge 165 of the bottom 150c, faces the outer peripheral surface of the shoulder 166 of the outer joint member 103 through a slight radial clearance to form a labyrinth seal 167. ing. Thereby, it is possible to prevent foreign matter such as magnetic powder from entering between the encoder 153 and the detection unit of the rotation speed sensor 152 even during actual running, which is a severe environment. Therefore, the reliability of the wheel rotation speed detection device can be further improved.
JP 2003-254985 A JP 2006-177897 A JP 2006-145418 A

By the way, if the rotational speed detection device as shown in FIG. 16 is to be mounted on the outer member 105, the peripheral wall 156 of the metal core 150 is press-fitted into the outer diameter surface of the end portion 105 a of the outer member 105, thereby 157 is brought into contact (close contact) with the end surface 158 of the end portion 105a. In this case, the resin mold body 151 is not directly applied with pressure input when press-fitting. This is to prevent the resin mold body 151 from being scratched, cracked, cracked, or the like by directly applying pressure input to the resin mold body 151.

However, unless the pressure input is directly applied to the resin mold 151, the side wall 157 may not be brought into close contact with the end surface 158 of the end portion 105a. That is, the side wall 157 of the cored bar 150 is a flat plate ring body, and a resin mold body 151 is attached to a part of the flat plate ring body in the circumferential direction, and a pressure input is directly applied to the resin mold body 151. Otherwise, even if a portion other than the resin mold body corresponding portion is brought into close contact with the end surface 158 of the end portion 105a, the resin mold body corresponding portion is lifted and a gap 160 is formed between the end surface 158 and the end surface 158 as shown in FIG. May occur.

Thus, when the gap 160 is formed, the side wall 157 cannot be brought into close contact with the end surface 158 of the end portion 105a. If the contact is not made in this way, the air gap formed between the rotational speed sensor 152 embedded in the resin mold 151 and the magnetic encoder 153 is different from the preset gap. That is, the air gap amount is set by determining the distance from the end surface 158 to the rotational speed sensor 152 with reference to the state where the side wall 157 is in contact with the end surface 158 of the end portion 105a of the outer member 105. . For this reason, if the resin mold body corresponding part does not contact the end surface 158, the air gap to be formed does not become the set air gap.

That is, the air gap between the rotational speed sensor 152 and the magnetic encoder 153 becomes larger than the set value, an error occurs in the output characteristics of the rotational speed sensor 152, and the accurate rotational speed cannot be detected.

Further, in the wheel bearing device as in Patent Document 2, the manufacturing process increases due to the groove processing on the outer member, the manufacturing cost of the outer member increases, or the core metal is crimped. There is a problem in that new equipment is required and processing costs increase. Furthermore, the cored bar cylindrical part that is press-fitted to the outer member is usually fitted with the outer member with a tightening allowance, but in the state of the cored bar cylinder, the cored bar tip may open in the outer diameter direction after press-fitting. If opened in the outer diameter direction, the tip of the metal core may interfere with the knuckle inner diameter.

Further, in the wheel bearing device as shown in FIG. 18, since the labyrinth seal 167 is opposed to the outer peripheral surface of the shoulder portion 166 of the outer joint member 103 and the inner edge of the cored bar 150, the confronting range in which the labyrinth effect is exhibited. However, it was difficult to obtain sufficient sealing performance. That is, since the labyrinth seal 167 is configured between the cored bar 150 attached to the outer member 105 and the shoulder 166 of the outer joint member 103, it is difficult to accurately define the radial clearance. There was a limit to obtaining high sealing performance.

SUMMARY OF THE INVENTION A first object of the present invention is to provide a rotational speed detecting device capable of reliably managing an air gap between a magnetic encoder and a rotational speed sensor, and capable of detecting an accurate rotational speed, and the same. Provided is a wheel bearing device provided. The second object is to provide a rotational speed detection device capable of preventing interference between the metal core and the inner diameter of the knuckle, enabling accurate speed detection and reducing the manufacturing cost, and a wheel provided with the same. It is in the provision of the bearing apparatus. The third object is to provide a wheel with a rotational speed detection device that can reduce the weight and size, and can prevent the intrusion of foreign matter directly into the detection unit to improve reliability and detect an accurate rotational speed. It is in providing a bearing device.

The first rotational speed detection device of the present invention includes an encoder mounted on the inner member side of the bearing structure portion of the wheel bearing device, and a sensor configuration portion in which the core metal is fixed on the outer member side of the bearing structure portion. And the sensor component is a core metal that is press-fitted and fixed to the end of the outer member of the bearing structure part, a resin part that is attached to the core metal, and the magnetic encoder that is embedded in the resin part And a rotation speed sensor that faces the air gap, and substantially the entire resin portion corresponding portion of the core metal protrudes to the core metal pressure contact surface side of the outer member from other portions.

According to the first rotational speed detection device of the present invention, when the core metal is press-fitted into the end portion of the outer member, the pressure input is directly applied to the other part of the core metal, The part is brought into close contact with the core metal pressure contact surface of the outer member. At this time, since the entire resin portion corresponding portion of the core metal protrudes toward the core metal pressure contact surface side of the outer member than the other sites, the other part tends to be brought into close contact with the core metal pressure contact surface of the outer member. Thus, without directly applying pressure input to the resin portion, the protruding portion (resin portion corresponding portion) protruding to the core metal pressure contact surface side of the outer member is brought into close contact with the core metal pressure contact surface of the outer member. be able to.

In the second rotational speed detection device of the present invention, the sensor corresponding portion of the resin portion corresponding portion in the core metal protrudes to the core metal pressure contact surface side of the outer member. In this case, the sensor-corresponding part of the resin part corresponding part is not attached to the resin part without applying pressure to the resin part by trying to bring the other part into close contact with the core metal pressure contact surface of the outer member. It can be brought into close contact with the core metal pressure contact surface.

It is preferable that 0 mm <A <0.5 mm, where A is the amount of protrusion of the protruding portion of the outer member toward the core metal pressure contact surface side.

The third rotational speed detection device includes an encoder that is mounted on the inner member side of the bearing structure portion of the wheel bearing device, and a sensor component that has a metal core fixed to the outer member side of the bearing structure portion. The core bar has a cylindrical portion that is press-fitted into the end portion of the outer member, and the cylindrical portion is reduced in diameter from the press-fit end side toward the press-fit start end side.

According to the rotational speed detection device of the present invention, since the diameter of the cylindrical portion of the core metal is reduced from the press-fitting end side toward the press-fitting start end side, the press-fitting start end side has a small diameter, and this press-fitting start end side is the outer diameter of the outer member. It press-contacts so that it may press to an inner diameter side with respect to a surface. For this reason, even if the vehicle repeatedly turns, the load on the bearing changes, and even if the outer member repeats elliptical deformation with this load change, the press-fitting start end side is closer to the outer diameter side than the outer diameter surface of the outer member. It is possible to prevent the cored bar from coming off in the axial direction or from being displaced in the circumferential direction without opening.

At this time, the diameter of the press-fitting start end of the cored bar can be reduced by 0.5 mm at the maximum from the press-fitting end of the cored bar.

Further, in the bearing structure portion of the wheel bearing device, a chamfered portion constituted by a tapered surface and / or a round is formed at the outer diameter end portion of the end portion of the outer member into which the core metal is press-fitted. Is preferred. As a result, when the mandrel is attached, the mandrel can be attached while being guided by the rounded and / or tapered surfaces. The tapered surface is preferably 5 ° to 30 ° with respect to the press-fitting direction.

The wheel bearing device of the present invention includes an outer member having a double row outer rolling surface, an inner member having a double row inner rolling surface facing the outer rolling surface of the outer member, and an outer side. A wheel bearing device including a rolling element that is rotatably accommodated between the outer rolling surface of the member and the rolling surface of the inner member, and includes the above-described rotation speed detection device. is there.

In addition, as a wheel bearing device, the inner member includes a hub ring having a wheel mounting flange on the outboard side, and a pair of inner rings having an inner rolling surface on the outer periphery is made into a hub ring in a state where the abutting surfaces are abutted with each other. There is something attached.

As the wheel bearing device, the inner member includes a hub wheel having an inner rolling surface on the outboard side on the outer diameter surface, and forms a small diameter stepped portion on the inboard side of the outer diameter surface of the hub wheel, Some of these small-diameter stepped portions are fitted with an inner ring on which an inner rolling surface on the inboard side is formed.

As a wheel bearing device, a hub wheel having a wheel mounting flange on the outboard side is provided, and the shaft portion of the outer joint member of the constant velocity universal joint is fitted into the hub wheel, and the outer diameter surface of the hub wheel is An outer rolling surface on the outboard side facing the outer rolling surface on the outboard side of the outer member is formed, and on the outer diameter surface of the outer joint member of the constant velocity universal joint, the inboard side of the outer member There is an inboard-side inner rolling surface that is opposed to the outer rolling surface.

That is, from what uses the double row rolling bearing called the 1st generation independently, what is called the 2nd generation which has a body mounting flange integrally with an outer member, and the hub ring which has a wheel mounting flange integrally. It can be used for what is called the third generation in which the inner rolling surface is integrally formed on one of the double row rolling bearings on the outer periphery, and further on the outer periphery of the outer joint member constituting the constant velocity universal joint. It can be adopted for the fourth generation in which the other inner rolling surface of the rolling bearing is integrally formed, and is excellent in versatility.

In each of the wheel bearing devices, a labyrinth seal disposed on the outer side of the seal member that closes the opening on the inboard side of the bearing structure can be configured by mounting the sensor component.

Another wheel bearing device has an outer member integrally formed with a vehicle body mounting flange to be attached to the 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 a wheel on one end. A hub wheel integrally having a wheel mounting flange for mounting a ring and having a cylindrical small-diameter stepped portion extending in the axial direction on the outer periphery, and at least one inner ring press-fitted into the small-diameter stepped 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, and rolling between both rolling surfaces of the inner member and the outer member. A double row rolling element accommodated freely, and a seal attached to an opening of an annular space formed between the outer member and the inner member, and the hub wheel has a constant velocity universal joint. An outer joint member is fitted inside, and a shoulder portion of the outer joint member abuts on the inner member. In this state, the outer joint member is unitized so that torque can be transmitted to and detached from the hub wheel, and the outer joint member is mounted on the inner side end of the outer member to detect the rotation speed of the wheel. Rotation comprising a sensor component provided with a speed sensor and an encoder provided on the side surface of a slinger that is fitted on the inner ring and constitutes the seal, and is opposed to the rotational speed sensor via an axial clearance. In the wheel bearing device with a built-in speed detection device, the sensor component includes a cylindrical fitting portion that is fitted on the inner end of the outer member, and a radially inner portion from the fitting portion. An annular cored bar comprising a flange part extending inward and in close contact with the end face of the outer member, a bottom part extending further radially inward from the flange part, and a cylindrical part extending axially from the bottom part, The collar part of this metal core And a resin portion embedded integrally with the outer surface of the outer circumferential surface of the cylindrical portion and embedded with the rotational speed sensor, and an inner end of the inner ring is connected to the outer member. The labyrinth seal is formed by projecting from the end surface, and the outer peripheral surface of the end portion and the cylindrical portion of the core metal are opposed to each other through a predetermined radial clearance.

According to the other wheel bearing device of the present invention, the radial clearance can be set with high accuracy and a sufficient sealing effect is exhibited. Therefore, it is possible to provide a wheel bearing device with a rotational speed detection device that prevents foreign matter from directly entering the detection unit from the outside and improves reliability.

The radial clearance of the labyrinth seal is preferably set to 2 mm or less, and the axial length of the labyrinth seal is preferably set to a range of 2 to 10 mm.

The encoder is composed of a magnetic encoder in which magnetic powder is mixed in an elastomer and magnetic poles N and S are alternately magnetized in the circumferential direction, and the core metal is formed of a non-magnetic austenitic stainless steel plate. It is preferable.

The sensor component includes a mandrel that is press-fitted and fixed to the inner side end of the outer member, and a resin part that is attached to the mandrel, and the resin part is a non-magnetic material to which glass fiber is added. The polyphenylene sulfide is preferably used.

Further, it is preferable that the resin portion is arranged in a radial upper portion with respect to the horizontal position of the cored bar, and a harness is connected in a tangential direction of the resin portion.

According to the first and second rotational speed detection devices of the present invention, the protruding portion that protrudes toward the core metal pressure contact surface side is brought into close contact with the core metal pressure contact surface of the outer member without applying pressure input to the resin portion. Can be made. For this reason, the air gap between the rotation speed sensor embedded in the resin portion and the magnetic encoder can be reliably managed, and an accurate rotation speed can be detected. In addition, since no pressure is applied to the resin portion, no external force acts on the resin portion, and it is possible to prevent the resin portion from being scratched, cracked, or cracked.

Further, when the protrusion amount of the protruding portion of the outer member toward the core metal pressure contact surface side is A, if 0 mm <A <0.5 mm, the metal core pressure contact surface of the outer member of the metal core protrusion portion It is possible to improve the closeness. That is, by setting 0 mm <A <0.5 mm, when press-fitting the cored bar into the end of the outer member, if the pressure input is applied to the other part that is not the resin part corresponding part, it protrudes. The resin portion corresponding portion first comes into contact with the core metal pressure contact surface of the outer member, and a predetermined air gap can be secured stably. If A is 0, the projecting portion cannot be secured, and if A exceeds 0.5 mm, the projecting amount of the projecting portion increases, and the core metal can secure the press-fit amount that can obtain a stable press input. Disappear.

In the third rotational speed detection device of the present invention, since the cored bar can be prevented from opening in the outer diameter direction, interference between the cored bar and the knuckle inner diameter can be prevented, and it is firmly fixed to the outer member. be able to. Furthermore, the mandrel can be fixed to the outer member with a simple configuration, and the manufacturing cost can be reduced.

The core metal can be stably fixed to the outer member by making the inner diameter of the press-fitting start end side of the core metal 0.5 mm smaller than the inner diameter of the press-fitting end side of the core metal, Interference between the cored bar and the knuckle inner diameter can be effectively prevented.

Since the cored bar can be prevented from opening in the outer diameter direction, interference between the cored bar and the knuckle inner diameter can be prevented, and it can be firmly fixed to the outer member. Thereby, the function as a wheel bearing apparatus can be stably demonstrated over a long period of time. Furthermore, the mandrel can be fixed to the outer member with a simple configuration, and the manufacturing cost can be reduced.

When the cored bar is mounted, the cored bar can be mounted while being guided by a round or tapered surface, so that the cored bar can be easily mounted on the outer member.

By configuring the labyrinth seal, in addition to the sealing function of the sealing member, the labyrinth seal can exhibit a more accurate sealing function.

In the other wheel bearing device of the present invention, the radial clearance can be set with high accuracy and a sufficient sealing effect is exhibited. Therefore, it is possible to provide a wheel bearing device with a rotational speed detection device that prevents foreign matters from directly entering the detection unit from the outside and improves reliability.

Moreover, if the radial clearance of the labyrinth seal is set to 2 mm or less, the sealing performance can be improved. If the axial length of the labyrinth seal is set in the range of 2 to 10 mm, the sealing performance can be improved more effectively. The encoder is composed of a magnetic encoder in which magnetic powder is mixed in an elastomer, and magnetic poles N and S are alternately magnetized in the circumferential direction, and the core metal is formed from a non-magnetic austenitic stainless steel plate. If so, accurate detection accuracy can be ensured without adversely affecting the sensing performance of the rotational speed sensor. Also, if the resin part is made of non-magnetic polyphenylene sulfide with glass fiber added, it will not adversely affect the sensing performance of the rotational speed sensor, it will also have excellent corrosion resistance, long-term strength and durability Can be improved.

Furthermore, if the resin part is arranged in the radial direction upper than the horizontal position of the cored bar and the harness is connected in the tangential direction of the resin part, the length of the harness itself does not become longer than necessary. The knuckle can be easily taken out to the outer diameter side, and the assembly workability is improved.

It is sectional drawing of the wheel bearing apparatus which shows 1st Embodiment of this invention. It is a side view of the said wheel bearing apparatus. It is a principal part expanded sectional view of the said wheel bearing apparatus. It is a simplification figure of the rotational speed detection apparatus of the said wheel bearing apparatus. The rotation speed detection apparatus of the said wheel bearing apparatus is shown, and it is a simplified diagram of a 1st modification. The rotation speed detection apparatus of the said wheel bearing apparatus is shown, and it is a simplified diagram of the 2nd modification. The rotation speed detection apparatus of the said wheel bearing apparatus is shown, and it is a simplified diagram of the 3rd modification. It is a principal part expanded sectional view of the wheel bearing apparatus which shows 2nd Embodiment of this invention. It is an expanded sectional view of the core metal of the rotational speed detection apparatus used for the wheel bearing apparatus shown in the said FIG. It is a principal part expanded sectional view which shows the modification of the wheel bearing apparatus shown in the said FIG. It is a principal part expanded sectional view which shows the other modification of the wheel bearing apparatus shown in the said FIG. It is a principal part expanded sectional view of the wheel bearing apparatus which shows 3rd Embodiment of this invention. It is a principal part expanded sectional view of the wheel bearing apparatus shown in the said FIG. It is a principal part expanded sectional view of the wheel bearing apparatus which shows 4th Embodiment of this invention. It is a principal part expanded sectional view of the wheel bearing apparatus which shows 5th Embodiment of this invention. It is a principal part expanded sectional view of the wheel bearing apparatus which shows 6th Embodiment of this invention. It is a longitudinal cross-sectional view of the conventional wheel bearing apparatus. It is sectional drawing of the conventional rotational speed detection apparatus. It is a simplified sectional view of a conventional rotational speed detection device. It is sectional drawing of the other conventional rotational speed detection apparatus.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Hub wheel 3 Constant velocity universal joint 21 Wheel mounting flange 23 Small diameter step part 24

Inner ring

24A, 24B Inner ring 24Aa24Ba Abutting surface 25

Outer member

26, 27

Outer rolling surface

28, 29 Inner rolling surface 30 Rolling element 35 Inward Member 60 Rotational speed detection device 61 Magnetic encoder 62 Sensor component 63 Core metal 63a Short cylindrical part 63b Side wall 63c Cylindrical part 64 Resin part 65 Rotational speed sensor 68 Resin part corresponding part 69 Core metal pressure contact surface 70 Chamfered part 71 Core metal protruding part 76 Tapered surface 77 R 80 Labyrinth seal 81 Press-fit start end 82 Press-fit end S Seal member S1 Seal member S2 Seal member

Hereinafter, embodiments of the present invention will be described with reference to FIGS. FIG. 1 shows a wheel bearing device provided with a rotational speed detection device 60 according to the first embodiment. The wheel bearing device includes a hub wheel 1, a double row rolling bearing (bearing structure portion) 2, a constant velocity. The universal joint 3 is integrated.

The constant velocity universal joint 3 includes a plurality of outer rings 5 serving as outer joint members, an inner ring 6 serving as an inner joint member disposed on the inner side of the outer ring 5, and a plurality of torque transmissions interposed between the outer ring 5 and the inner ring 6. The ball 7 and the cage 8 that is interposed between the outer ring 5 and the inner ring 6 and holds the ball 7 are configured as main members. The inner ring 6 is spline-fitted by press-fitting an end of a shaft (not shown) into the shaft hole inner diameter 6a and is coupled to the shaft so that torque can be transmitted.

The outer ring 5 is composed of a mouse part 11 and a stem part (shaft part) 12. The mouse part 11 has a bowl shape opened at one end, and a plurality of track grooves 14 extending in the axial direction are circumferentially formed on the inner spherical surface 13 thereof. It is formed at equal intervals in the direction. The track groove 14 extends to the open end of the mouse portion 11. In the inner ring 6, a plurality of track grooves 16 extending in the axial direction are formed on the outer spherical surface 15 at equal intervals in the circumferential direction.

The track groove 14 of the outer ring 5 and the track groove 16 of the inner ring 6 make a pair, and one ball 7 as a torque transmitting element can roll on each ball track constituted by the pair of

track grooves

14 and 16. It is incorporated. The ball 7 is interposed between the track groove 14 of the outer ring 5 and the track groove 16 of the inner ring 6 to transmit torque. The constant velocity universal joint in this case is a Zepper type, but may be another constant velocity universal joint such as an undercut free type having a straight straight portion at the bottom of each track groove.

The rolling bearing (bearing structure) 2 includes an outer member 25 having double-row outer rolling surfaces 26 and 27, and a double-row inner rolling surface facing the outer rolling surfaces 26 and 27 of the outer member 25. An inner member 35 having 28, 29, and a rolling element 30 that is accommodated between the outer rolling surfaces 26, 27 of the outer member 25 and the rolling surfaces 28, 29 of the inner member 35 so as to roll freely. It has. The outer member 25 is made of medium-high carbon steel containing 0.40 to 0.80 wt% of carbon such as 53C, for example. Further, the outer rolling surfaces 26 and 27 of the outer member 25 are subjected to a hardening process within a range of 58 HRC to 64 HRC by induction hardening or the like.

The inner member 35 in this case includes the hub wheel 1 having the wheel mounting flange 21 on the outboard side, and the inner ring 24 mounted on the small-diameter stepped portion 23 provided on the inboard side of the hub wheel 1. Prepare. The hub wheel 1 includes a cylindrical portion 20 and a flange 21 provided at an end of the cylindrical portion 20 on the side opposite to the joint. A short cylindrical pilot portion 45 to which a wheel and a brake rotor (not shown) are mounted is projected from an end face of the hub wheel 1 on the outboard side. The pilot portion 45 includes a large-diameter first portion 45a and a small-diameter second portion 45b. A brake rotor is externally fitted to the first portion 45a, and a wheel is externally fitted to the second portion 45b. A bolt mounting hole 32 is provided in the flange 21 of the hub wheel 1, and a hub bolt 33 for fixing the wheel and the brake rotor to the flange 21 is mounted in the bolt mounting hole 32. The side closer to the outside of the vehicle in the state assembled to the vehicle is referred to as the outboard side (left side in the drawing), and the side closer to the center is referred to as the inboard side (right side in the drawing).

The shaft portion 12 of the outer ring 5 of the constant velocity universal joint 3 is inserted into the inner peripheral surface (inner diameter surface) of the cylindrical portion 20 of the hub wheel 1. The shaft portion 12 has a screw portion 40 formed at an end portion on the outboard side, and a spline portion 41 formed on the outer periphery of the shaft portion 12. A spline portion 42 is formed on the inner peripheral surface (inner diameter surface) of the cylindrical portion 20 of the hub wheel 1. When the shaft portion 12 is inserted into the cylindrical portion 20 of the hub wheel 1, The spline portion 41 engages with the spline portion 42 on the hub wheel 1 side.

An inner rolling surface 28 corresponding to the outer rolling surface 26 of the outer member 25 is formed on the outer diameter surface of the cylindrical portion 20, and the outer rolling surface 27 of the outer member 25 corresponds to the outer diameter surface of the inner ring 24. An inner rolling surface 29 is formed. And, between the outer side rolling surface 26 of the outer member 25 and the inner side rolling surface 28 of the tubular portion 20, between the outer side rolling surface 27 of the outer member 25 and the inner side rolling surface 29 of the inner ring 24, The rolling element 30 held by the holder 31 is accommodated so as to roll freely.

The hub wheel 1 is made of medium and high carbon steel containing carbon of 0.40 to 0.80 wt%, such as 53C, and includes an inner rolling surface 29 and an inner side of a wheel mounting flange 21 serving as a seal land portion of a seal member S1 described later. From the base portion 91 to the small-diameter stepped portion 23, the surface hardness is set to a range of 58 to 64 HRC by induction hardening. Thereby, not only the wear resistance of the base portion 91 is improved, but also the fretting of the small diameter stepped portion 23 which becomes the fitting surface of the inner ring 24 is suppressed, and the rotational bending load applied to the wheel mounting flange 21 is suppressed. On the other hand, it has sufficient mechanical strength and the durability of the hub wheel 1 is improved. The inner ring 24 and the rolling element 30 are made of a high carbon chrome bearing steel such as SUJ2, and are hardened in the range of 58 to 64 HRC up to the core part by quenching.

A vehicle body mounting flange 50 having a screw hole 50a is provided on the outer diameter surface of the outer member 25, and the outer diameter surface on the inboard side of the vehicle body mounting flange 50 has a predetermined clearance fit to a knuckle (not shown). It becomes the knuckle pilot part 25a combined.

Seal members S1 and S2 made of lip seals are mounted on both openings of the rolling bearing 2. This prevents leakage of the lubricating grease sealed inside the bearing and prevents rainwater and dust from entering the bearing from the outside. The outboard-side seal member S1 includes a reinforcing ring 51 and a lip portion 52 attached to the reinforcing ring 51. The lip portion 52 includes a radial lip 52a and a side lip 52b.

Further, as shown in FIG. 3, the inboard-side seal member S <b> 2 includes L-shaped

cross-section seal plates

53 and 54, and a seal portion 55 attached to one seal plate 53. That is, the seal plate 53 includes a cylindrical portion 53a and a side wall portion 53b extending from the end on the outboard side of the cylindrical portion 53a toward the inner diameter side. The cylindrical portion 53a is on the inboard side of the inner diameter surface of the outer member 25. It is fitted to the end of the. The seal plate (slinger) 54 includes a cylindrical portion 54 a and a side wall portion 54 b extending from the end on the inboard side of the cylindrical portion 54 a to the outer diameter side. The cylindrical portion 54 a is fitted to the outer diameter surface of the inner ring 24. Has been. The seal portion 55 includes a radial lip 55a and a side lip 55b.

The seal plate 53 is formed into a substantially L-shaped cross section by press working from 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). Has been. The seal portion 55 is made of an elastic member such as synthetic rubber. The slinger 54 is pressed from a ferromagnetic steel plate, for example, a ferritic stainless steel plate (JIS standard SUS430 or the like) or a rust-proof cold rolled steel plate (JIS standard SPCC or the like). The cross section is formed in a substantially L shape by processing. The side lip 55b of the seal portion 55 is slidably contacted with the side wall portion 54b, and the radial lip 55a of the seal portion 55 is slidably contacted with the cylindrical portion 54a.

Next, a method for assembling the wheel bearing device will be described. The shaft portion 12 is inserted into the tube portion 20 of the hub wheel 1 to engage the spline portion 41 on the shaft portion 12 side with the spline portion 42 on the hub wheel 1 side. In this state, the nut member 43 is screwed onto the screw portion 40 protruding from the tube portion 20 of the hub wheel 1 to the outboard side.

Thus, the seat 43a of the nut member 43 contacts the end surface of the hub wheel 1 on the outboard side, and the back surface 11a of the mouse unit 11 contacts the end surface 24b of the inner ring 24. For this reason, the end surface 24a of the inner ring 24 abuts on the end surface 23a of the small-diameter stepped portion 23, and preload can be applied to the double row rolling bearing (bearing structure portion) 2.

Incidentally, the rotational speed detection device 60 attached to the wheel bearing device includes a magnetic encoder 61 mounted on the inner ring 24 side of the double row rolling bearing (bearing structure portion) 2 and a double row rolling bearing (bearing structure). Part) 2 on the outer member 25 side.

The magnetic encoder 61 is made of, for example, a rubber magnet made of rubber or other elastomer mixed with magnetic powder such as ferrite, and is attached to the outer surface of the side wall portion 54b of the seal plate 54 of the seal member S2. Yes. That is, the magnetic encoder 61 is integrally joined to the side wall portion 54b of the seal plate 54 by vulcanization adhesion or the like. The magnetic encoder 61 has N and S poles alternately formed in the circumferential direction.

The sensor component 62 includes a cored bar 63 that is press-fitted and fixed to the end of the outer member 25 of the double row rolling bearing (bearing structure) 2, a resin part 64 that is attached to the cored bar 63, and this resin A rotational speed sensor 65 embedded in the portion 64 and facing the magnetic encoder through an air gap.

The metal core 63 includes a short cylindrical portion 63a and a ring-shaped side wall 63b extending in the inner diameter direction from an end portion on the inboard side of the short cylindrical portion 63a. The side wall 63 b has an outer diameter portion 66 and an inner diameter portion 67, and the inner diameter portion 67 is disposed on the inboard side with respect to the outer diameter portion 66. The core metal 63 is formed by pressing a non-magnetic steel plate having corrosion resistance, for example, a stainless steel plate such as an austenitic stainless steel plate (JIS standard SUS304 type or the like). As a result, a wheel bearing device with a rotational speed detection device that does not adversely affect the sensing performance of the rotational speed sensor 65, which will be described later, and suppresses rusting of the core metal 63 and maintains reliability over a long period of time. Can be provided. The core metal 63 may be a cold rolled steel sheet (JIS standard SPCC or the like) that has been rust-proofed in addition to the materials described above.

The resin portion 64 is formed of a block body having a square cross section, and is provided in a part of the side wall 63b in the circumferential direction as shown in FIG. The resin portion 64 is formed by injection molding from a non-magnetic special ether-based synthetic resin material such as polyphenylene sulfide (PPS), and further a reinforcing material such as GF (glass fiber) is added. As a result, the sensing performance of the rotation speed sensor 65 is not adversely affected, the corrosion resistance is excellent, and the strength and durability can be improved over a long period of time. In addition, the resin part 64 can illustrate injection-moldable synthetic resins such as PA (polyamide) 66, PPA (polyphthalamide), and PBT (polybutylene terephthalate) in addition to the materials described above.

The rotation speed sensor 65 is an IC incorporating a magnetic detection element such as a Hall element, a magnetoresistive element (MR element), etc. that changes characteristics according to the flow direction of magnetic flux, and a waveform circuit that adjusts the output waveform of the magnetic detection element. It consists of. Further, a harness 75 for sending a signal from the rotation speed sensor 65 to control means (not shown) is drawn out from the resin portion 64.

In this case, as shown in FIG. 4 (a simplified view of the cored bar 63 and the resin part 64), substantially the entire resin part corresponding part 68 of the cored bar 63 is pressed against the cored bar of the outer member 25 rather than other parts. Projects to the surface side. That is, a part of the cored bar 63 to which the resin part 64 is attached bulges toward the outboard side to form the protruding part 71. In this case, the protrusion 71 can be formed by forming the recess 72 on the end face of the cored bar 63 on the inboard side. When the protrusion amount of the protrusion 71 is A, 0 mm <A <0.5 mm. In this case, the portion where the protruding portion 71 is provided is the outer diameter portion 66 of the side wall 63b.

In the rotational speed detection device 60 configured as described above, when the magnetic encoder 61 rotates together with the inner ring 24 as the wheel (not shown) rotates, the output of the rotational speed sensor 65 changes when facing the magnetic encoder 61. Since the frequency at which the output of the rotational speed sensor 65 changes is proportional to the rotational speed of the wheel, the ABS is controlled by inputting the output signal of the rotational speed sensor 65 to the control means (not shown) via the harness 75. It will be.

Therefore, in order to perform high-precision control, the magnetic encoder 61 and the rotation speed sensor 65 need to face each other through a predetermined air gap. Therefore, when the cored bar 63 is press-fitted into the end part on the inboard side of the outer member 25, the outer diameter part 66 of the cored bar 63 is brought into contact with the cored bar pressure contact surface of the outer member 25 as shown in FIG. 3. The air gap can be defined by abutting against 69.

However, when press-fitting, in order to prevent the resin part 64 from being scratched, cracked, or cracked, it is not possible to apply a pressing force to the resin part 64. For this reason, even if a portion other than the resin portion corresponding portion 68 of the core metal 63 is brought into contact with the core metal pressure contact surface 69 of the outer member 25, the resin portion corresponding portion 68 of the core metal 63 is lifted to the outside. In some cases, the air gap is not brought into contact with the core metal pressure contact surface 69 of the member 25, and the formed air gap may be larger than a preset air gap.

Therefore, in the present invention, substantially the entire resin portion corresponding portion 68 of the core metal 63 protrudes toward the core metal pressure contact surface 69 side of the outer member 25 from other portions. As a result, the resin portion corresponding portion 68 of the core metal 63 is in contact with the core metal pressure contact surface 69 of the outer member 25 without directly applying pressure input to the resin portion 64. The air gap is set to be a predetermined air gap.

The seal member S2 and the sensor component 62 of the rotational speed detection device 60 constitute a labyrinth seal 80 on the inboard side with respect to the seal member S2. That is, the labyrinth seal 79 can be configured by the magnetic encoder 61 and the core metal 63 facing each other with a minute gap. Further, the labyrinth seal 80 can also be configured between the inner diameter portion 67 of the core metal 63 and the mouse portion 11.

In the present invention, the protruding portion 71 protruding toward the core metal pressure contact surface 69 side of the outer member 25 is brought into close contact with the core metal pressure contact surface 69 of the outer member 25 without directly applying pressure input to the resin portion 64. Can be made. For this reason, the air gap between the rotation speed sensor 65 embedded in the resin portion 64 and the magnetic encoder 61 can be reliably managed, and an accurate rotation speed can be detected. In addition, since no pressure input is applied to the resin portion 64, no external force acts on the resin portion 64, and it is possible to prevent the resin portion 64 from being scratched, cracked, or cracked.

Further, assuming that 0 mm <A <0.5 mm when the protruding amount of the protruding portion 71 toward the core metal pressure contact surface 69 side of the outer member 25 is 0 mm <A <0.5 mm, the outer member 25 of the core metal protruding portion 71 The close contact with the core metal pressure contact surface 69 can be improved. In other words, by setting 0 mm <A <0.5 mm, when press-fitting the cored bar into the end of the outer member 25, if pressure is applied to other parts that are not the resin part corresponding part 68, The resin portion corresponding portion 68 protrudes and first comes into contact with the core metal pressure contact surface of the outer member 25, so that a predetermined air gap can be secured stably. If A is 0, the projecting portion cannot be secured, and if A exceeds 0.5 mm, the projecting amount of the projecting portion increases, and the core metal can secure the press-fit amount that can obtain a stable press input. Disappear.

Furthermore, by configuring the labyrinth seals 79 and 80, in addition to the sealing function of the seal member S2, the labyrinth seals 79 and 80 can exhibit a more accurate sealing function.

In FIG. 4, the resin portion 64 is provided with a main body portion 64 a larger than the concave portion 72 of the core metal 63 and a convex portion 64 b that fits into the concave portion 72, but as shown in FIG. 5A. In addition, the resin part 64 may be provided with a main body part 64 a smaller than the recessed part 72 of the cored bar 63 and an outer flange part 64 c that fits into the opening-side inclined part 72 a of the recessed part 72.

Further, as shown in FIG. 5B, the protruding portion 71 provided on the cored bar 63 may be provided only at a portion corresponding to the rotational speed sensor 65. In this case, the protrusion 71 can be formed by forming the small concave recess 73 on the end surface of the cored bar 63 on the inboard side. For this reason, the resin part 64 is provided with the main-body part 64a and the small convex ridge part 64d fitted to the small recessed part 73. FIG.

As shown in FIG. 5C, in addition to the small concave portions 73, other small

concave portions

73 a and 73 b may be provided in other portions of the resin portion corresponding portion 68. As shown in FIGS. 5B and 5C, the portion corresponding to the rotation speed sensor 65 is a portion that coincides with the radial direction when the inner diameter side is viewed from the outer diameter side.

Thus, even if the sensor corresponding portion of the resin portion corresponding portion 68 of the core metal 63 protrudes toward the core metal pressure contact surface 69 side of the outer member 25, the air gap is stably set to the set value. It can be.

As a second embodiment of the rotational speed detection device, as shown in FIG. 7, the cylindrical portion (short cylindrical portion) 63a of the cored bar 63 is reduced in diameter from the press-fit terminal side toward the press-fit start side. In this case, the diameter of the press-fit start end 81 side is reduced by 0.5 mm at the maximum from the press-fit end end 82 side. That is, the start radius is R1, the end radius is R2, and the difference δ between R1 and R2 is 0.5 mm at the maximum.

As shown in FIG. 6, a chamfered portion 70 is provided at an outer diameter end portion of the end portion of the outer member 25, and the chamfered portion 70 is configured by a tapered surface 76 and a round 77. Accordingly, the chamfered portion 70 can guide the core metal 63 when the core metal 63 is attached to the outer member 25. The inclination angle α of the tapered surface 76 is preferably 5 ° to 30 ° with respect to the press-fitting direction. When α is less than 5 °, there is almost no inclination at the boundary between the tapered surface 76 and the outer diameter surface of the outer member 25. In this case, if the taper surface 76 is long, the press-fitting allowance of the cored bar 63 becomes small, the cored bar 63 cannot be firmly fixed to the outer member 25, and if the tapered surface 76 is short, the chamfered portion 70 is almost eliminated. The function of guiding the cored bar 63 cannot be exhibited. When the angle exceeds 30 °, the inclination of the boundary between the tapered surface 76 and the outer diameter surface of the outer member 25 increases, and when the core metal 63 is press-fitted, the leading edge of the core metal 63 (the press-fitting start end 81 side). ) Abuts against the tapered surface 76, and the core metal 63 cannot be easily press-fitted.

When the difference δ between R1 and R2 exceeds 0.5 mm, the difference between the press-fit start end 81 side and the press-fit end end 82 side becomes large, and the press-fit start end 81 side becomes too small in diameter so that the core metal 63 can be guided by the chamfer 70. As a result, the press-fit property of the core metal 63 is deteriorated. The phantom line in FIG. 7 shows the cored bar 63 in which the short cylindrical portion 63a is not reduced in diameter, and the diameter of the inner diameter surface on the press-fitting start end 81 side is substantially the same as the diameter of the inner diameter surface on the press-fit end point 82 side. belongs to.

In the present invention, since the diameter of the short cylindrical portion 63a of the core metal 63 is reduced from the press-fit end 82 side toward the press-fit start end 81 side, the press-fit start end 81 side has a small diameter, and the press-fit start end 81 side is outside the outer member 25. It press-contacts so that it may press to an internal diameter side with respect to a radial surface. For this reason, even if the vehicle repeatedly turns and the load on the bearing changes, and the outer member 25 repeats elliptical deformation along with this load change, the press-fitting start end 81 side is outside the outer diameter surface of the outer member 25. It is possible to prevent the cored bar 63 from slipping off in the axial direction or shifting in the circumferential direction without opening to the radial side. Thereby, interference with the metal core 63 and the knuckle inner diameter can be prevented, and the outer member 25 can be firmly fixed. Thereby, the function as a wheel bearing apparatus can be stably demonstrated over a long period of time. Furthermore, the core metal 63 can be fixed to the outer member 25 with a simple configuration, and the manufacturing cost can be reduced.

The cored bar 63 is stably fixed to the outer member 25 by making the inner diameter of the cored bar 63 on the press-fitting start end 81 side smaller than the inner diameter of the cored bar on the press-fit terminal end 82 side by a maximum of 0.5 mm. In addition, interference between the cored bar 63 and the knuckle inner diameter can be effectively prevented.

A chamfered portion 70 is provided at the outer diameter end portion of the end portion of the outer member 25, and the chamfered portion 70 is constituted by a tapered surface 76 and a round 77, and the tapered surface 76 is 5 ° to 30 ° with respect to the press-fitting direction. Therefore, when the cored bar is mounted, the cored bar 63 can be mounted while being guided by the round 77 or the tapered surface 76, so that the cored bar can be easily mounted on the outer member 25.

In the above-described embodiment, the chamfered portion 70 of the outer member 25 is configured by the tapered surface 76 and the radius 77, but the chamfered portion 70 can be configured by only the radius 77 as shown in FIG. Further, as shown in FIG. 9, the chamfered portion 70 can be configured by only the tapered surface 76.

Next, in the wheel bearing device shown in FIGS. 10 and 11, the axial length of the labyrinth seal 80 is increased. That is, the end portion 36 on the inboard side of the inner ring 24 is formed so as to protrude from the end surface 37 of the outer member 25. Further, the cored bar 63 is formed with a cylindrical part 63c extending in the axial direction at the inner diameter end of the inner diameter part 67 of the side wall 63b. The cored bar 63 in this case includes a cylindrical fitting part (short cylindrical part) 63a that is fitted on the inner side end of the outer member 25, and a side wall that extends radially inward from the fitting part 63a. 63b and a cylindrical portion 63c extending in the axial direction from the inner diameter end on the side wall 63b. The side wall 63 b has a flange portion (outer diameter portion) 66 that is in close contact with the end surface 37 of the outer member 25, and a bottom portion (inner diameter portion) 67 that extends further radially inward from the flange portion 66. For this reason, the outer diameter surface 85 of the end portion 36 on the inboard side of the inner ring 24 and the inner diameter surface 86 of the cylindrical portion 63c of the cored bar 63 are opposed to each other through a predetermined radial clearance, thereby forming the labyrinth seal 80. ing.

Thereby, the labyrinth effect can be exhibited and the sealing performance can be improved. The radial clearance between the cored bar 63 and the end portion 36 of the inner ring 24 is set to 2.0 mm or less, preferably 0.5 to 1.5 mm. The axial length of the labyrinth seal 80 is set in the range of 2 to 10 mm. As described above, in the present embodiment, the labyrinth seal 80 having a desired axial length is configured between the core metal 63 press-fitted into the outer member 25 and the inner ring 24. Therefore, the radial clearance is accurately provided. Can be set, and a sufficient sealing effect is exhibited. Therefore, it is possible to provide a wheel bearing device with a rotational speed detection device that prevents foreign matters from directly entering the detection unit from the outside and improves reliability.

10 and 11 are the same as those of the wheel bearing device shown in FIG. 1, and the same members are denoted by the same reference numerals and the description thereof is omitted. In addition, the cross-sectional shape of the resin part 64 is provided with a protruding part 64e corresponding to the cylindrical part 63c of the cored bar 63.

Next, the wheel bearing device shown in FIG. 12 is a hub wheel in a state where a predetermined bearing preload is applied by a caulking portion 90 formed by plastically deforming an end portion of the small diameter stepped portion 23 radially outward. 1, the inner ring 24 is fixed in the axial direction. The hub wheel 1 is made of medium and high carbon steel containing 0.40 to 0.80 wt% of carbon such as S53C, and includes the inner rolling surface 28 and the base 91 on the inboard side of the wheel mounting flange 21 to the small diameter stepped portion 23. In other words, the surface is hardened in a range of 58 to 64 HRC by induction hardening. The caulking portion 90 is kept at the surface hardness after forging.

Here, in this embodiment, the end surface 90a of the crimping portion 90 is formed as a flat surface, and the end surface 90a of the crimping portion 90 and the back surface 11a of the outer ring 5 of the constant velocity universal joint 3 are in surface contact. . As a result, the surface pressure applied to the caulking portion 90 based on the tightening force of the nut member 43 can be reduced, the plastic deformation of the caulking portion 90 and the loosening of the nut member 43 are prevented, and a large moment load is applied. Even when loaded, sufficient rigidity can be exhibited.

Further, in the wheel bearing device shown in FIG. 12, the protruding end surface 83 of the resin portion 64 and the end surface 90a of the crimping portion 90 are formed substantially flush with each other. Thereby, in an assembly process, an apparatus can be mounted vertically and assembly workability | operativity can be improved.

By the way, as a wheel bearing device, an inner rolling surface 28 is formed on the outer diameter surface of the hub wheel 1 so that the outer rolling surface 26 of the outer member 25 faces the inboard surface. A small-diameter stepped portion 23 is formed on the side, and this small-diameter stepped portion 23 is fitted with an inner ring 24 formed with an inner rolling surface 29 opposed to the outer rolling surface 27 on the outer periphery. However, other generation wheel bearing devices may be used.

That is, as shown in FIG. 13, a so-called first-generation or second-generation wheel bearing device in which a pair of

inner rings

24A, 24B are mounted in a state where the abutting surfaces 24Aa, 24Ba are abutted may be used. In this case, the

inner rings

24A and 24B are fitted to the cylindrical portion 20 of the hub wheel 1, and the shaft portion 12 of the outer ring 5 of the constant velocity universal joint 3 is fitted to the cylindrical portion 20 of the hub wheel 1. A nut member 43 is screwed onto the threaded portion 40 of the screw. As a result, the inner rings 24 </ b> A and 24 </ b> B are sandwiched between the notch end surface 92 of the hub wheel 1 and the back surface 11 a of the outer ring 5 of the constant velocity universal joint 3. For this reason, a preload can be applied to the double row rolling bearing (bearing structure portion) 2. In this case, the inner member 35 of the bearing structure 2 is constituted by a pair of

inner rings

24A and 24B.

Further, as shown in FIG. 14, an outer rolling surface 28 on the outboard side facing the outer rolling surface 26 on the outboard side of the outer member 25 is formed on the outer diameter surface of the hub wheel 1, A so-called fourth generation wheel in which an inboard-side inner rolling surface 29 is formed on the outer diameter surface of the outer ring 5 of the constant velocity universal joint 3, and the inboard-side outer rolling surface 27 of the outer member 25 is opposed to the outer-ring 25. It may be a bearing device. In the fourth generation, a part of the outer diameter surface of the outer ring 5 that forms the rolling surface 29 on the inboard side becomes a part of the inner member.

In the wheel bearing device shown in FIG. 14, the outer ring 5 includes a cup-shaped mouth portion 11, a shoulder portion 95 that forms the bottom of the mouth portion 11, and a hollow shaft that extends in the axial direction from the shoulder portion 95. It has the part 12 integrally. On the outer periphery of the shaft portion 12, an in-row portion 12a that is fitted in the small-diameter step portion 96 of the hub wheel 1 and a fitting portion 12b that further extends in the axial direction from the in-row portion 12a are formed. Then, a diameter expanding jig such as a mandrel is pushed into the inner diameter of the shaft portion 12 to expand the fitting portion 12b, and the fitting portion 12b is bitten into the concavo-convex portion 97 of the hub wheel 1 and caulked. The outer ring 5 is integrally plastically coupled. As a result, it is possible to provide a wheel bearing device that is lighter and more compact, and that prevents loosening of the coupling portion over a long period of time even when a large moment load is applied, and has improved durability.

As described above, the embodiment of the present invention has been described. However, the present invention is not limited to the above embodiment, and various modifications are possible. For example, in the wheel bearing device shown in FIG. The rolling element as the torque transmission means of the bearing 2 is constituted by the ball 30, but a tapered roller may be used. As the sensor of the rotational speed detection device, a so-called active sensor is used in the above-described embodiment. However, a so-called passive sensor in which an encoder is formed of a magnetic ring having an uneven shape may be used.

When the protruding amount of the protruding portion 71 toward the core metal pressure contact surface 69 side of the outer member 25 is A, when 0 mm <A <0.5 mm is set, when the core metal 63 is press-fitted into the outer member 25 In addition, as long as the protruding portion 71 comes into contact with the core metal pressure contact surface 69, the other portion may or may not be in contact.

The first generation of a structure that uses a double row rolling bearing alone, the second generation that has a body mounting flange integrally with the outer member, and one of the double row rolling bearings on the outer periphery of a hub wheel that integrally has a wheel mounting flange. The constant velocity universal joint is integrated with the third generation in which the inner raceway surface is integrally formed with the hub wheel, and the inner side of the other side of the double row rolling bearing is formed on the outer periphery of the outer joint member constituting the constant velocity universal joint. The present invention can be applied to a fourth-generation wheel bearing device in which raceway surfaces are integrally formed.

Claims

An encoder mounted on the inner member side of the bearing structure portion of the wheel bearing device, and a sensor component portion having a mandrel fixed to the outer member side of the bearing structure portion. A metal core that is press-fitted and fixed to the end of the outer member of the unit, a resin part that is attached to the metal core, and a rotational speed sensor that is embedded in the resin part and faces the magnetic encoder via an air gap And a rotation speed detecting device characterized in that substantially the entire resin portion corresponding portion of the core metal protrudes toward the core metal pressure contact surface side of the outer member from other portions.
Equipped with an encoder mounted on the inner member side of the bearing structure part of the wheel bearing device, and a sensor component having a metal core fixed to the outer member side of the bearing structure part, and mounted on the inner ring side of the bearing structure part A magnetic encoder and a sensor component mounted on the outer member side of the bearing structure, and the sensor component is press-fitted and fixed to the end of the outer member of the bearing structure, The resin portion attached to the metal core, and a rotation speed sensor embedded in the resin portion and facing the magnetic encoder via an air gap, and the sensor corresponding portion of the resin portion corresponding portion in the metal core are A rotational speed detecting device, characterized in that the outer member protrudes toward the core metal pressure contact surface side.
The rotational speed detection according to claim 1 or 2, wherein 0 mm <A <0.5 mm, where A is the amount of protrusion of the protruding portion of the outer member toward the core metal pressure contact surface side. apparatus.
An encoder mounted on the inner member side of the bearing structure portion of the wheel bearing device, and a sensor component having a core metal fixed to the outer member side of the bearing structure portion, the core metal of the outer member A rotational speed detecting device comprising a cylindrical portion press-fitted into an end portion, and the cylindrical portion having a diameter reduced from a press-fitting end side toward a press-fitting start end side.
The rotational speed detection device according to claim 4, wherein the press-fitting start end of the metal core is reduced in diameter by 0.5 mm at the maximum from the press-fitting end of the metal core.
In the bearing structure portion of the wheel bearing device, a chamfered portion formed by a tapered surface and / or a round shape is formed at the outer diameter end portion of the end portion of the outer member into which the core metal is press-fitted. The rotation speed detection device according to claim 4 or 5.
The rotational speed detection device according to claim 6, wherein the tapered surface is set to 5 ° to 30 ° with respect to the press-fitting direction.
An outer member having a double row outer rolling surface, an inner member having a double row inner rolling surface facing the outer rolling surface of the outer member, and an outer rolling surface and inward of the outer member 8. A wheel speed bearing device comprising a rolling element that is rotatably accommodated between a rolling surface of a member, and the rotational speed detecting device according to claim 1. A wheel bearing device comprising:
The inner member is provided with a hub ring having a wheel mounting flange on the outboard side, and a pair of inner rings having inner rolling surfaces on the outer periphery are mounted on the hub ring in a state where the abutting surfaces are abutted with each other. Item 9. A wheel bearing device according to Item 8.
The inner member includes a hub ring having an outer rolling surface on the outer side on the outer diameter surface, and a small diameter stepped portion is formed on the inboard side of the outer diameter surface of the hub wheel. 9. The wheel bearing device according to claim 8, wherein an inner ring on which an inner rolling surface on the inboard side is formed is fitted.
A hub ring having a wheel mounting flange is provided on the outboard side, the shaft portion of the outer joint member of the constant velocity universal joint is fitted into the hub ring, and the outer board of the outer member is provided on the outer diameter surface of the hub ring. The outer rolling surface on the outboard side facing the outer rolling surface on the side is formed, and the outer rolling surface on the inboard side of the outer member is formed on the outer diameter surface of the outer joint member of the constant velocity universal joint. 9. The wheel bearing device according to claim 8, wherein inner rolling surfaces on the opposite inboard side are formed.
12. The labyrinth seal disposed on the outer side of the seal member that closes the opening on the inboard side of the bearing structure portion by mounting the sensor component portion. The wheel bearing apparatus of any one of Claims.
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 integrally having a wheel mounting flange for mounting a wheel at one end and having a cylindrical small-diameter stepped portion extending in the axial direction on the outer periphery, and press-fitted into the small-diameter stepped portion of the hub wheel An inner member formed of at least one inner ring, and formed with a double-row inner rolling surface opposed to the double-row outer rolling surface on the outer periphery;
A double row rolling element accommodated in a freely rolling manner between both rolling surfaces of the inner member and the outer member;
A seal attached to an opening of an annular space formed between the outer member and the inner member;
An outer joint member of a constant velocity universal joint is fitted into the hub wheel, and the outer joint member can transmit torque to the hub wheel in a state where a shoulder portion of the outer joint member abuts on the inner member. And it is unitized so that it can be attached and detached,
A sensor component mounted on an inner side end of the outer member and provided with a rotation speed sensor for detecting the rotation speed of the wheel, and a side surface of a slinger that is fitted on the inner ring and forms the seal. In a wheel bearing device in which a rotational speed detection device comprising an encoder opposed to the rotational speed sensor via an axial clearance is incorporated,
The sensor component includes a cylindrical fitting portion that is fitted on the inner end of the outer member, and extends radially inward from the fitting portion, and is in close contact with the end surface of the outer member. An annular cored bar comprising a flange part, a bottom part extending further radially inward from the collar part, and a cylindrical part extending axially from the bottom part, and an outer part extending from the collar part to the cylindrical part of the core metal A resin portion integrally joined to a surface radially outwardly and having the rotational speed sensor embedded therein, and an inner side end portion of the inner ring protruding from an end surface of the outer member. A labyrinth seal is constituted by the outer peripheral surface of the end portion and the cylindrical portion of the core metal facing each other through a predetermined radial clearance.
The wheel bearing device according to claim 13, wherein an outer diameter of an end portion of the inner ring of the inner member is smaller than an outer diameter into which the slinger is press-fitted.
The wheel bearing device according to claim 13 or 14, wherein a radial clearance of the labyrinth seal is set to 2 mm or less.
The wheel bearing device according to any one of claims 113 to 15, wherein an axial length of the labyrinth seal is set in a range of 2 to 10 mm.
The encoder is composed of a magnetic encoder in which magnetic powder is mixed in an elastomer and magnetic poles N and S are alternately magnetized in the circumferential direction, and the core metal is formed of a non-magnetic austenitic stainless steel plate. The wheel bearing device according to any one of claims 8 to 16, wherein the wheel bearing device is provided.
The sensor component includes a mandrel that is press-fitted and fixed to the inner side end of the outer member, and a resin part that is attached to the mandrel, and the resin part is a non-magnetic material to which glass fiber is added. The wheel bearing device according to any one of claims 8 to 17, wherein the wheel bearing device is formed of polyphenylene sulfide.
The wheel for a vehicle according to any one of claims 8 to 17, wherein the resin portion is disposed radially above the horizontal position of the metal core, and a harness is connected in a tangential direction of the resin portion. Bearing device.