JP2010188895A - Rolling bearing unit for supporting wheel - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a structure securing sufficient durability, even if a reinforcing member 4A is thinned, by reducing amplitude of stress applied to the reinforcing member 4a, and easily reducing weight of an outer ring member 2A including the reinforcing member 4A. <P>SOLUTION: A small diameter side end edge part of the reinforcing member 4A is locked in a locking groove 11 formed in a portion closer to an axially inward of an outer peripheral surface of the outer ring member 2A. Even if a rotating side flange 7A has a tendency to be inclined by moment applied during turning traveling, force is only applied in a compressing direction in the reinforcing member 4A, and force is not applied in a pulling direction. The amplitude of the stress therefore can be reduced. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to an improvement of a rolling bearing unit for supporting a wheel for rotatably supporting a wheel with respect to a suspension system of an automobile. Specifically, of the so-called outer ring rotating type in which the outer ring member rotates without rotating the inner ring member, the structure intended to reduce the weight of the outer ring member has been improved, and sufficient durability even under severe use conditions. A structure that can be secured is realized.

  The outer ring rotating type wheel bearing unit for supporting the wheel can make the structure of the mounting part to the suspension device easier than the inner ring rotating type, so that some motor vehicles have driven wheels (rear wheels of FF vehicles, FR vehicles). And the front wheel of an MR vehicle) is used as a rolling bearing unit for support. However, because the outer ring member whose diameter is larger than that of the inner ring member is rotated, the moment of inertia is increased, and the inner ring rotation type rolling bearing unit for wheel support is provided from the viewpoint of ensuring the driving performance and fuel efficiency performance centering on the acceleration performance. It is disadvantageous compared to. In order to reduce or eliminate such disadvantages, it is effective to reduce the weight of the outer ring member. Conventionally, structures described in Patent Documents 1 to 3 are known as rolling bearing units for wheel support of an outer ring rotation type that have been considered in view of such circumstances.

  10 to 13 show three examples of conventional structures described in Patent Documents 1 to 3. FIG. Each of these conventional structures includes inner ring members 1a, 1b, 1c, outer ring members 2a, 2b, 2c, a plurality of rolling elements 3, 3, and reinforcing members 4a, 4b, 4c. Of these, the inner ring members 1a, 1b, and 1c have double-row inner ring raceways 5A and 5B on the outer peripheral surface, and are supported and fixed to the suspension device in use so that they do not rotate. The outer ring members 2a, 2b, and 2c have outer ring raceways 6A and 6B in double rows on the inner peripheral surface, and axially outer portions of the outer peripheral surface (the outside in the axial direction is the outside in the width direction of the vehicle body in the assembled state). The same is applied throughout the present specification and claims), and each has a rotation side flange 7a, 7b, 7c. And it rotates with the wheel couple | bonded and fixed to this rotation side flange 7a, 7b, 7c in use condition. A plurality of rolling elements 3, 3 are provided for each row between the inner ring raceways 5A, 5B and the outer ring raceways 6A, 6B.

  The reinforcing members 4a, 4b, and 4c have a partially conical cylindrical shape as a whole. The large diameter side ends of the reinforcing members 4a, 4b, and 4c are the outer peripheral edge portions of the rotation side flanges 7a, 7b, and 7c, and the small diameter side ends are the outer peripheral surfaces of the outer ring members 2a, 2b, and 2c. The rotary side flanges 7a, 7b, 7c are joined and fixed by welding to the inner portions in the axial direction. Furthermore, in order to fix the inner ring members 1a, 1b and 1c to the suspension device, stationary flanges 8a, 8b and 8c are provided on the peripheral surfaces of the inner ring members 1a, 1b and 1c. Of the three examples of the conventional structure described above, in the case of the two examples shown in FIGS. 10 and 13, the inner ends of the outer peripheral surfaces of the inner ring members 1a and 1c (the inner side in the axial direction refers to the vehicle body in the assembled state. The stationary side flanges 8a and 8c in the form of outward flanges are provided in the same direction throughout the present specification and claims. On the other hand, in the case of the structure shown in FIGS. 11 to 12, by projecting a plurality of circumferentially equidistant portions in the axially inward portion of the inner peripheral surface of the inner ring member 1b inward in the radial direction. The stationary flange 8b having an inward flange shape is provided.

  When the wheel-supporting rolling bearing units 9a, 9b, and 9c each having the above-described configuration are used, the stationary ring flanges 8a, 8b, and 8c allow the inner ring members 1a, 1b, and 1c to be components of the suspension device. (For example, knuckle). Further, a braking rotator such as a disc rotor and a drum and wheels are supported and fixed to the outer ring members 2a, 2b and 2c by the rotation side flanges 7a, 7b and 7c. In this state, the braking rotator and the wheel are rotatably supported with respect to the suspension device. When turning, for example, an input from a contact portion (grounding surface) between the wheel and the road surface is applied to the rotation side flanges 7a, 7b, 7c, and the rotation side flanges 7a, 7b, 7c are connected to the outer ring member 2a, 2b and 2c are applied as moments in the bending direction. In all three examples of the conventional structure, the reinforcing members 4a, 4b, and 4c are provided between the rotation-side flanges 7a, 7b, and 7c and the main body portions of the outer ring members 2a, 2b, and 2c. Regardless of the moment, the rotation-side flanges 7a, 7b, 7c can be prevented from bending with respect to the main body portions of the outer ring members 2a, 2b, 2c. For this reason, even if the outer ring members 2a, 2b, and 2c are thinned, it is possible to ensure the supporting rigidity of the wheels and to ensure the required performance such as running stability.

  In this way, the rotation side flanges 7a, 7b, 7c are suppressed by the reinforcing members 4a, 4b, 4c from bending the rotation side flanges 7a, 7b, 7c with respect to the main body portions of the outer ring members 2a, 2b, 2c. 7c and the body portion can be made thinner. In the case of the three examples of the conventional structure, as shown in FIGS. 10, 11 and 13, the outer ring members 2a, 2b and 2c are provided with meat stealing portions 10a, 10b and 10c, respectively. 2b and 2c are sufficiently thinned. By reducing the thickness in this way, the moment of inertia of the outer ring members 2a, 2b and 2c can be reduced, and the running performance and fuel efficiency performance centering on the acceleration performance can be improved.

  In order to further improve the advantages of the conventional structure as described above, the reinforcing members 4a, 4b, and 4c are thinned, and the outer ring members 2a, 2b, and 2c including the reinforcing members 4a, 4b, and 4c are formed as a whole. It may be possible to further reduce the weight. However, as in the three examples of the conventional structure, both ends of the reinforcing members 4a, 4b, and 4c are connected to the outer peripheral edges of the rotation side flanges 7a, 7b, and 7c and the outer peripheral surfaces of the outer ring members 2a, 2b, and 2c. In the case of a structure that is welded and fixed, it is difficult to sufficiently reduce the thickness of the reinforcing members 4a, 4b, and 4c. The reason for this will be described by adding (A) to (C) of FIG. 3 to FIGS.

  When an automobile incorporating rolling bearing units 9a, 9b, and 9c for supporting the outer ring rotating is turning, the outer ring members 2a, 2b, and 2c have a moment in the turning direction with the ground contact surface as an input point. Join in the appropriate direction. Due to this moment, the outer ring members 2a, 2b, 2c tend to displace in the torsional direction around the horizontal axis in the front-rear direction, and the both outer rings provided on the inner peripheral surfaces of the outer ring members 2a, 2b, 2c. Reaction forces from the rolling elements 3 and 3 are applied to the tracks 6A and 6B. For example, when a clockwise moment about the horizontal axis O is applied to the outer ring member 2A as indicated by a solid line arrow A in FIG. The reaction force is applied to the upper part of the outer ring raceway 6B and the lower part of the outer ring raceway 6A on the outer side in the axial direction. On the other hand, when a counterclockwise moment is applied as shown by the broken arrow c in FIG. 3A, the lower portion of the outer ring raceway 6B on the inner side in the axial direction and the shaft as shown by the broken arrows d The reaction force is applied to the upper portion of the outer ring raceway 6A on the outer side in the direction.

  When viewed at a specific position of the outer ring member 2A, such a reaction force is alternately applied as the outer ring member 2A rotates, and the outer ring member 2A is elastically deformed accordingly. And the space | interval of the outer peripheral edge part of the rotation side flange 7A which welded and fixed the both ends of the said reinforcement member 4a, 4b, 4c, and the axially inward part of the outer peripheral surface of the said outer ring member 2A changes. Specifically, at the moment when the reaction force indicated by the solid arrows B and B is applied, this interval tends to be narrower in the upper part of FIG. 3A, and the reaction force indicated by the broken arrows D and D above. At the moment when is added, this interval tends to increase. As a result, stresses in different directions are repeatedly generated in the reinforcing member 4A in which both end portions are welded and fixed to the outer peripheral edge portion and the axially inward portion.

  That is, with respect to the upper portion of FIG. 3A, the solid line arrow is formed on the portion of the reinforcing member 4A welded to the outer ring member 2A as shown in FIG. 3B. At the moment when the reaction force is applied in the direction indicated by B and B and the interval is narrowed, stress in the compression shear direction is generated in the reinforcing member 4A. On the other hand, at the moment when the reaction force is applied in the direction indicated by the broken arrows D and D and the interval is widened, stress in the tensile shear direction is generated at the same portion. As a result, as shown in FIG. 3C, stress in the compressive shear direction and stress in the tensile shear direction are alternately generated in each part of the reinforcing member 4A. As a result, the amplitude W of the stress generated in the reinforcing member 4A is increased, and when the reinforcing member 4A is thinned, the reinforcing member 4A is likely to be damaged such as a crack. For this reason, in the conventional structures described in Patent Documents 1 to 3, it is difficult to reduce the thickness of the reinforcing members 4a, 4b, and 4c, and the outer ring members 2a, 2b, and 2c including the reinforcing members 4a, 4b, and 4c are difficult to achieve. It is difficult to reduce weight.

German Patent Application Publication No. 10 2007 023 661 German Patent Application Publication No. 10 2007 060 627 German Patent Application Publication No. 10 2008 023 588

  In view of the circumstances as described above, the present invention can reduce the amplitude of stress applied to the reinforcing member and ensure sufficient durability even if the reinforcing member is thinned. The weight of the outer ring member including the reinforcing member It was invented to realize a structure that can be easily reduced.

The wheel support rolling bearing unit of the present invention includes an inner ring member, an outer ring member, a plurality of rolling elements, a reinforcement member, and the wheel support rolling bearing unit described in Patent Documents 1 to 3 described above. Is provided.
Of these, the inner ring member has a double-row inner ring raceway on the outer peripheral surface, and is supported and fixed to the suspension device in a used state so as not to rotate.
The outer ring member has a double-row outer ring raceway on the inner peripheral surface and a rotating flange on the outer peripheral surface in the axial direction. The outer ring member rotates together with the wheel fixedly connected to the rotating flange in use. To do.
A plurality of rolling elements are provided for each row between the inner ring raceways and the outer ring raceways.
Further, the reinforcing member has a partially conical cylindrical shape, with the large-diameter end on the radially outer side of the rotating flange and the small-diameter end on the outer peripheral surface of the outer ring member from the rotating flange. Are also locked to the axially inward portions and stretched between the two portions.

In particular, in the rolling bearing unit for supporting a wheel according to the present invention, the small-diameter side end edge portion of the reinforcing member is formed on the outer peripheral surface of the outer ring member at a portion closer to the inner side in the axial direction than the rotation-side flange. It is locked in a state of abutting against the locking groove or the locking protrusion.
When implementing such a wheel-supporting rolling bearing unit of the present invention, for example, as in the invention described in claim 2, a locking step is provided on the axially inner side surface of the rotating side flange, and the reinforcing member is provided. The large-diameter-side end portion is locked to the locking step portion.
Alternatively, as in the invention described in claim 3, a locking bent portion bent radially inward is provided on the large diameter side end portion of the reinforcing member, and the outer diameter side of the axially outer side surface of the rotation side flange. A recess is provided at each end. And this latching bending part is clamped between this recessed part and the axial direction inner side surface of the member couple | bonded and fixed to the axial direction outer side surface of the said rotation side flange.
Further, as in the invention described in claim 4, the honeycomb member in which the reinforcing member is partitioned by a plurality of partition walls between the inner peripheral surface of the outer cylinder and the outer peripheral surface of the inner cylinder, each of which is a partial conical cylinder shape. It can also be a structure.

  According to the rolling bearing unit for supporting a wheel of the present invention configured as described above, the amplitude of stress applied to the reinforcing member can be reduced. That is, it is possible to transmit only the force in the compression direction to at least the engaging portion between the small-diameter side end edge portion of the reinforcing member and the outer peripheral surface of the outer ring member and the axially inward portion end portion of the rotating side flange. In other words, it is possible to prevent the force in the pulling direction from being transmitted by this locking portion. For this reason, the distance between the radially outward portion of the rotating flange and the outer peripheral surface of the outer ring member that engages both ends of the reinforcing member and the axially inward portion of the outer ring member is expanded or reduced. Even in such a tendency, stress in the pulling direction is not generated in the reinforcing member. Since only the stress in the compression direction is generated in the reinforcing member, the amplitude of the stress can be reduced to easily ensure the durability of the reinforcing member. For this reason, even if the reinforcing member is thinned, sufficient durability can be secured, and the weight of the outer ring member including the reinforcing member can be reduced. The reinforcing member does not prevent the distance between the radially outer portion of the rotation side flange and the outer peripheral surface of the outer ring member from extending in the direction in which the distance between the rotation side flange and the axially inward portion increases. In terms of securing the bending rigidity of the rotation side flange, it is somewhat disadvantageous compared to the conventional structure described above. However, since the reinforcing member prevents displacement in the direction in which the distance is reduced, the rigidity in the circumferential direction of the rotating flange can be ensured in a state where the braking rotor and the wheel are coupled and fixed to the rotating flange. If so, the above-mentioned bending rigidity can be secured to a practically sufficient level.

FIG. 3 is a cross-sectional view of a main part showing a first example of an embodiment of the present invention. The principal part sectional drawing which shows the process of assembling a reinforcement member in order. It is a figure for demonstrating the state which stress generate | occur | produces in a reinforcement member at the time of turning, (A) is sectional drawing of the outer ring member provided with the reinforcement member, (B) is a small diameter side edge part of the reinforcement member in a conventional structure (C) is a diagram showing a state in which the stress generated in the reinforcing member in this conventional structure changes as the outer ring member rotates, and (D) shows the structure of the present invention. Sectional drawing which shows the coupling | bond part of the small diameter side edge part and outer ring member of a reinforcement member in this, (E) is a radial direction outer side part of the rotation side flange, and the outer peripheral surface of the said outer ring member, and it is axial direction rather than this rotation side flange Sectional drawing which shows the state of the said coupling | bond part in the state displaced to the direction where the distance with an inward part spreads, (F) is a stress which generate | occur | produces in a reinforcement member with the structure of this invention changes with rotation of an outer ring member. The diagram which shows a state. The principal part sectional drawing which shows the 2nd example of embodiment of this invention. The principal part sectional view showing the 3rd example. The end elevations which show two examples of another structure of a reinforcement member. The fragmentary perspective view which shows another example of a reinforcement member. Similarly a partial end view. The principal part sectional drawing which shows another example of the use condition of this reinforcement member. Sectional drawing which shows the 1st example of a conventional structure. Sectional drawing which shows the 2nd example. The perspective view seen from the right side of FIG. The cutting perspective view which shows the 3rd example of a conventional structure.

[First example of embodiment]
A first example of an embodiment of the present invention corresponding to claims 1 and 2 will be described with reference to FIGS. The feature of the present invention including this example is that the structure of the assembly portion of the reinforcing member 4A with respect to the outer ring member 2A is devised to add to the reinforcing member 4A as the outer ring member 2A rotates during turning. Even if the amplitude of the stress is reduced and the thickness of the reinforcing member 4A is kept small, the durability of the reinforcing member 4A can be sufficiently ensured. Since the configuration and operation of other parts are the same as those of the first to third examples of the conventional structure shown in FIGS. The explanation will focus on the part.

  In order to lock the small-diameter side edge of the reinforcing member 4A, a locking groove 11 having a substantially V-shaped cross section is formed on the outer peripheral surface of the outer ring member 2A in the axially inward portion of the rotation side flange 7A. It is formed over the entire circumference. Further, a locking step portion 12 is provided at the outer diameter side end portion of the inner side surface in the axial direction of the rotation side flange 7A. Regarding the cross-sectional shape in a virtual plane including the central axis of the outer ring member 2A, the inner diameter side bottom surface 13 of the locking step portion 12 and the outer side bottom surface 14 of the locking groove 11 exist on the same straight line. Further, regarding the cross-sectional shape in the same virtual plane, the rear end surface 15 of the locking step portion 12 is orthogonal to the inner diameter side bottom surface 13, and the inner side bottom surface 16 of the locking groove 11 is orthogonal to the outer side bottom surface 14. . Therefore, the inner side bottom surface 16 and the back end surface 15 are parallel to each other. Further, the distance between the inner side bottom surface 16 and the back end surface 15 is matched with the distance between the small diameter side end surface 17 and the large diameter side end surface 18 of the reinforcing member 4A. In addition, these both end surfaces 17 and 18 are also mutually parallel. Further, the inner diameters of both ends of the reinforcing member 4A in the free state coincide with the diameters of the inner diameter side bottom face 13 and the outer side bottom face 14, respectively. Therefore, the inner diameter in the free state of the small-diameter side end of the reinforcing member 4A is smaller than the outer diameter of the inner end of the outer ring member 2A in the axial direction. .

  The reinforcing member 4A as described above is attached to the outer ring member 2A as shown in FIG. That is, as shown in FIG. 2A, the reinforcing member 4A is disposed on the axially inner side of the outer ring member 2A in a state where the large-diameter side end of the reinforcing member 4A is positioned on the axially outer side. To do. From this state, the inner end portion in the axial direction of the outer ring member 2A is pushed into the inner diameter side of the reinforcing member 4A (or the reinforcing member 4A is strongly fitted on the inner end portion in the axial direction of the outer ring member 2A. ). Then, as shown in FIG. 2B, the small diameter side end of the reinforcing member 4A is elastically deformed radially outward and gets over the axial inner end of the outer ring member 2A. Then, the reinforcing member 4A and the outer ring are engaged until the large-diameter side end of the reinforcing member 4A is fitted onto the locking step portion 12 and the large-diameter side end surface 18 of the reinforcing member 4A hits the back end surface 15. When the member 2A is relatively displaced in the axial direction, the small diameter side end of the reinforcing member 4A engages with the locking groove 11 as shown in FIG. At the same time, the small diameter side end surface 17 of the reinforcing member 4A and the inner side bottom surface 16 of the locking groove 11 abut against each other.

  In a state where the reinforcing member 4A is assembled to the outer ring member 2A in this way, the reinforcing member 4A is between the outer diameter side end portion of the rotation side flange 7A and the axially inner end portion of the outer ring member 2A. Stretch with. Therefore, regardless of the moment applied to the rotation side flange 7A during turning, the rotation side flange 7A is not elastically deformed in the direction of falling inward in the axial direction. The reinforcing member 4A cannot prevent the rotation-side flange 7A from elastically deforming in a direction in which the rotation-side flange 7A tilts outward in the axial direction. However, when a certain part of the rotation side flange 7A tends to be displaced in any direction with respect to the axial direction, the radially opposite part tends to be displaced in the other direction with respect to the axial direction. In particular, when the rotating flange 7A reinforced by the braking rotator and the wheels is considered to be a highly rigid disc-shaped member as the braking rotator and the wheels are coupled and fixed, the above tendency is observed. Becomes remarkable. Therefore, if the reinforcing member 4A prevents the rotation side flange 7A from elastically deforming in the direction in which the rotation side flange 7A falls inward in the axial direction, the rotation side flange 7A also prevents elastic deformation in the direction in which the rotation side flange 7A falls down in the axial direction. .

  According to the rolling bearing unit for supporting a wheel of this example configured as described above, the amplitude of stress applied to the reinforcing member 4A can be reduced. That is, the small-diameter side and large-diameter side end faces 17 and 18 of the reinforcing member 4A are merely abutted against the back end face 15 and the inner side bottom face 16 and are not fixed by welding or adhesion. Therefore, the reinforcing member 4A and the outer ring member 2A are engaged so as to be able to transmit only the force in the compression direction, and the force in the pulling direction is transmitted between the reinforcing member 4A and the outer ring member 2A. Absent. For this reason, even if the distance between the back end surface 15 and the inner side bottom surface 16 that engages both ends of the reinforcing member 4A tends to be expanded or contracted, stress in the tensile shear direction is generated on the reinforcing member 4A. There is nothing to do. When the distance tends to increase, as shown exaggeratedly in FIG. 3E, the end face (for example, the small diameter side end face 17) of the reinforcing member 4A and the mating face (for example, the inner side bottom face 16) are separated from each other. Therefore, no stress is generated in the reinforcing member 4A in the pulling direction. The stress generated in the reinforcing member 4A tends to reduce the distance, and as shown in FIG. 3D, the end surface (for example, the small diameter side end surface 17) of the reinforcing member 4A and the mating surface (for example, the inner surface). Only when the side bottom surface 16) is pressed against each other, the generated stress is only compressive stress.

  As described above, since the stress generated in the case of the structure of the present invention is only the compressive stress, the amplitude w of the stress is reduced as compared with the case where the shear stress and the compressive stress are generated as in the conventional structure described above. (W> w> W / 2). In addition, since the stress generation direction is constant and only the stress in the compression direction is unlikely to cause damage such as cracks, it is easy to ensure the durability of the reinforcing member 4A. For this reason, even if the reinforcing member 4A is thinned, sufficient durability can be secured, and the weight of the entire outer ring member 2A including the reinforcing member 4A can be reduced.

  The small diameter side and large diameter side end faces 17 and 18 of the reinforcing member 4A, the back end face 15 and the inner side bottom face 16 are preferably brought into contact with each other over the entire radial width of both end faces 17 and 18. . For example, as shown in FIG. 3D, when only the inner diameter side portion of the small diameter side end surface 17 abuts against the inner side bottom surface 16, damage to the small diameter side end portion of the reinforcing member 4A is prevented. A stress in the shear direction is generated which is harmful from the surface. If the surfaces 17, 16 (18, 15) that engage with each other are brought into contact with each other over the entire width of the end surfaces 17, 18, the stress in the shearing direction is not generated. With respect to the back end face 15, processing for abutting the entire width of the large-diameter side end face 18 is easy. On the other hand, if the locking groove 11 is deepened to secure the width dimension of the inner side bottom surface 16, the thickness of the outer ring member 2A is likely to be insufficient at the locking groove 11 portion. . Therefore, in such a case, a locking protrusion is formed over the entire circumference at a portion adjacent to the inner side in the axial direction of the locking groove 11 at the axially inner end portion of the outer peripheral surface of the outer ring member 2A. To do. And the axial direction outer side surface of this latching protrusion is made to function as the said inner side bottom face. If comprised in this way, the thickness dimension of the said outer ring member 2A will be ensured, and the said small diameter side end surface 17 will be covered over the full width, and it will be abutted by the said inner side bottom face. The locking groove can be omitted only by the locking protrusion.

[Second Example of Embodiment]
FIG. 4 also shows a second example of an embodiment of the present invention corresponding to claims 1 and 2. In the case of this example, both the small-diameter side and large-diameter-side folded portions 19, 20 each having a convex curved surface on the inner diameter side are formed by bending both ends of the reinforcing member 4B made of a metal plate and having a partially conical cylindrical shape. Is forming. Of these, the small-diameter folded portion 19 is engaged with a locking groove 11a formed near the inner end of the outer ring member 2A in the axial direction of the outer ring surface, and the large-diameter folded portion 20 is connected to the rotation-side flange 7A. Is engaged with an outer diameter side locking groove 21 formed in a portion closer to the outer diameter on the inner side surface in the axial direction. In the case of the structure of this example as well, as in the case of the first example of the above-described embodiment, the amplitude of the stress applied to the reinforcing member 4B is reduced to reduce the thickness of the reinforcing member 4B. The weight of the outer ring member 2A including the reinforcing member 4B can be reduced.

[Third example of embodiment]
FIG. 5 shows a third example of an embodiment of the present invention corresponding to claims 1 and 3. In the case of this example, a locking bent portion 22 bent radially inward is formed at the large diameter side end of the reinforcing member 4C, and a concave portion 23 is formed at the outer diameter side end of the axially outer side surface of the rotation side flange 7A. Are provided over the entire circumference. And the said latching bending part 22 is clamped between this recessed part 23 and the axial direction inner side surface of the disk rotor 24 couple | bonded and fixed to the axial direction outer side surface of the said rotation side flange 7A. With this configuration, the large-diameter side end of the reinforcing member 4C is coupled and fixed to the outer peripheral edge of the rotation-side flange 4C. Other configurations and operations are the same as in the case of the first example of the above-described embodiment, and thus redundant description is omitted.

  When carrying out the present invention, it is necessary to engage the small diameter side end portion of the partially conical cylindrical reinforcing member with the engaging groove provided at the inner end portion in the axial direction of the outer peripheral surface of the outer ring member. In order to perform this locking operation by elastic deformation of the reinforcing member 4A as shown in FIG. 2, a considerably large force is required. Therefore, as shown in FIG. 6A, if a reinforcing member 4D having a cut 25 in one circumferential direction is used, the locking operation can be easily performed. The cut 25 is welded after the locking operation is completed so that the diameter of the reinforcing member 4D does not expand unintentionally. Alternatively, as shown in FIG. 6B, a reinforcing member 4E divided into two in the circumferential direction is used, and while the reinforcing member 4E is assembled, the small-diameter side end thereof is positioned in the outer peripheral surface axial direction of the outer ring member. After engaging the locking groove provided at the end, the butted portion can be welded.

  In addition, in order to reduce the weight of the reinforcing member while ensuring the strength and rigidity of the reinforcing member, a reinforcing member 4F having a honeycomb structure as shown in FIGS. 7 to 8 can be used. The reinforcing member 4F is formed by dividing the inner peripheral surface of the outer tube 26 and the outer peripheral surface of the inner tube 27, each of which is a partial conical cylinder shape, by a number of partition walls 28, 28, or an aluminum alloy. A cylindrical member made of aramid fibers or the like is arranged without gaps. If the reinforcing member 4F having such a honeycomb structure is spanned between the locking groove 11 and the locking step portion 12 provided in the outer ring member 2A, for example, as in the case of the first example of the above-described embodiment. The weight of the outer ring member 2A including the reinforcing member 4F can be further reduced while securing the moment rigidity of the rotation side flange 7A provided on the outer peripheral surface of the outer ring member 2A. The sectional shape of the partition walls 28, 28 is most preferably a hexagon, but it can also be a triangle or a quadrangle.

  Further, the reinforcing member 4F having the honeycomb structure as described above is applied to the structure of the present invention, and as shown in FIG. 9, simply between the rotation side flange 7A of the outer ring member 2A and the portion near the inner end in the axial direction. Can be handed over. In this case, the two positions separated in the axial direction of the inner peripheral surface of the reinforcing member 4F and the two positions separated in the axial direction of the outer peripheral surface of the outer ring member 2A are joined and fixed by adhesion or the like. Even in such a structure, the effect of reducing the weight of the reinforcing member 4F can be obtained to some extent.

1a, 1b, 1c Inner ring member 2a, 2b, 2c, 2A Outer ring member 3 Rolling element 4a, 4b, 4c, 4A, 4B, 4C, 4D, 4E, 4F Reinforcing member 5A, 5B Inner ring raceway 6A, 6B Outer ring raceway 7a, 7b, 7c, 7A Rotating side flanges 8a, 8b, 8c Stationary side flanges 9a, 9b, 9c Rolling bearing units for wheel support 10a, 10b, 10c Meat stealing part 11, 11a Locking groove 12 Locking step part 13 Inner diameter side bottom face 14 Outer side bottom surface 15 Back end surface 16 Inner side bottom surface 17 Small diameter side end surface 18 Large diameter side end surface 19 Small diameter side folded portion 20 Large diameter side folded portion 21 Outer diameter side locking groove 22 Locked bent portion 23 Recessed portion 24 Disc rotor 25 Cut 26 Outer cylinder 27 Inner cylinder 28 Partition wall

Claims (4)

  Inner ring member with double row inner ring raceway on the outer peripheral surface, which is supported and fixed to the suspension device in use and does not rotate, double row outer ring raceway on the inner peripheral surface, and rotation side on the outer side in the axial direction of the outer peripheral surface A plurality of flanges are provided for each row between the outer ring member that rotates with a wheel that is coupled and fixed to the rotation side flange in use, and both the inner ring raceway and the both outer ring raceways. A rolling element and a partially conical cylindrical reinforcing member, the large-diameter side end of the reinforcing member is located on the radially outer side of the rotating side flange, and the small-diameter side end is the outer periphery of the outer ring member. In the rolling bearing unit for supporting a wheel, which is respectively locked to the axially inward portion of the rotating side flange from the surface and is stretched between the two portions, the small diameter side end of the reinforcing member The edge is rotated on the outer peripheral surface of the outer ring member. Wheel supporting rolling bearing unit, characterized in that locked in a state of abutting axially inwardly toward the locking groove or locking projection formed in a portion of the flange.   The rolling bearing unit for wheel support according to claim 1, wherein a locking step portion is provided on an inner side surface in the axial direction of the rotation side flange, and a large-diameter side end portion of the reinforcing member is locked to the locking step portion.   A locking bent part bent inward in the radial direction is provided at the large diameter side end of the reinforcing member, and a concave part is provided at the outer diameter side end of the axially outer side surface of the rotation side flange, and this locking bent part is provided. The wheel bearing rolling bearing unit according to claim 1, wherein the rolling bearing unit is sandwiched between the recess and an axially inner surface of a member coupled and fixed to an axially outer surface of the rotation side flange.   4. The honeycomb structure according to claim 1, wherein the reinforcing member is a honeycomb structure in which a partition wall is partitioned between an inner peripheral surface of an outer cylinder and a peripheral surface of the inner cylinder, each of which is a partially conical cylinder. A rolling bearing unit for supporting a wheel according to claim 1.

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