JP2008247384A - Manufacturing method for rolling bearing unit - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To give a sufficient axial force by a small calking load even in a large size bearing, and to inexpensively and certainly fix the bearing 3 to a shaft body 2 in a rolling bearing unit in which the rolling bearing 3 is attached to the outer periphery of the shaft body 2 such as a vehicular hub unit. <P>SOLUTION: This rolling bearing unit is provided with a shaft body 2; an inner ring 42; an outer ring 33; and rolling bodies 34, 35. A cylinder formed at the vehicle inner side end of the shaft body 2 is bent and formed outwardly in a radial direction to form a calked part 5, and the inner ring 42 is fixed to the shaft body 2. A recess 6 is formed at the vehicle outer side end of the shaft body 2, and the recess 6 is formed from the vehicle outer side end to an axial position close to the vehicle inner side more than an end surface at the vehicle outer side of the inner ring 42. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a method for manufacturing a rolling bearing unit, such as a vehicle hub unit, in which a rolling bearing is mounted on the outer periphery of a shaft body.

  A hub unit for a vehicle generally has a structure that is mounted on the outer periphery of a hub wheel shaft body in a state in which a double row rolling bearing is prevented from coming off.

  The shaft body of the hub wheel is provided with a cylindrical portion used for retaining the bearing on the free end side. The cylindrical portion is bent and deformed radially outward using a caulking jig, and is caulked to an outer end surface of an inner ring provided in the bearing to form a caulking portion. The bearing is prevented from coming off from the hub wheel by this caulking portion. At the same time, a sufficient axial force is applied to the inner ring of the bearing from this caulking portion.

  By the way, the size of the caulking portion varies depending on the size of the bearing. That is, in the case of a large-sized bearing, the retaining of the bearing and sufficient axial force can be applied by increasing the thickness of the caulking portion or increasing the length.

  However, when the thickness of the caulking portion is increased or the length thereof is increased, it is necessary to use a large caulking machine having a strong caulking force, and there is a problem that the manufacturing cost increases. In addition, in the case of caulking, when a caulking force that exceeds the caulking load by a large caulking machine is required, there is a problem that sufficient caulking force cannot be applied and caulking cannot be performed.

  Further, when the caulking load is increased, problems such as deformation of the inner ring of the bearing and depression of the raceway occur.

  It is an object of the present invention to provide a rolling bearing unit that can apply a sufficient axial force with a small caulking load even in a large bearing, and that can be securely fixed to the shaft body at a low cost. Objective.

The rolling bearing unit of the present invention includes a shaft body having a flange portion, one inner ring raceway, and a small diameter portion formed between the inner ring raceway and a step portion on the outer circumferential surface, and an outer circumferential surface. An inner ring formed with the other inner ring raceway and externally fitted to the small-diameter portion, an outer ring having a double-row raceway disposed on the inner circumferential surface of the shaft body and the inner ring, the shaft body and the inner ring, A double-row rolling element interposed between the outer ring, a bottomed cylindrical portion is formed at a vehicle inner side end portion of the shaft body, and a concave portion is formed at a vehicle outer side end portion of the shaft body. The depth dimension from the inlet-side end surface of the recess to the vehicle inner-side end is H, and the distance from the inlet-side end surface of the recess to the vehicle outer-side end surface abutting the step of the inner ring is H _1. , the axial width of the inner ring when the _{H 2, H 1 ≦ H ≦} H 1 +0 A 9 × H ₂ and process for the preparation of the rolling bearing unit, in a state received by crimping receiving jig the inlet-side end surface of the recess, the caulking portion is bent deforming the cylindrical portion radially outward The inner ring is formed and fixed to the shaft body.

According to the rolling bearing unit of the present invention, a recess is formed at the vehicle outer side end of the shaft body,
The depth of the inlet-side end surface of the recess to the vehicle inner side end portion H, H ₁ the distance from the vehicle outer side end portion of the shaft to the end face of the inner ring of the vehicle outer _side, the axial width of the inner ring H2 Then, by setting H ₁ ≦ H ≦ H ₁ + 0.9 × H ₂ , the radial cross-sectional area of the shaft body is reduced, and as a result, the tensile force acting per unit area of the shaft body As the stress increases, the compressive stress acting on the inner ring increases, so that a large axial force can be applied to the inner ring with a small caulking load.

  According to the rolling bearing unit of the present invention, even a large-sized bearing can provide a sufficient axial force with a small caulking load, and the bearing can be securely fixed to the shaft body at a low cost.

(Embodiment 1)
Embodiment 1 of the present invention will be described with reference to FIG. 1 and FIG.

  FIG. 1 is a sectional view of a rolling bearing unit comprising a hub unit on the vehicle driven wheel side in the present embodiment, and FIG. 2 is a sectional view of the caulking process.

  1 and 2, reference numeral 1 denotes a hub wheel to which a wheel is attached, and a double row rolling bearing 3 is fitted on the outer peripheral surface of the shaft body 2 of the hub wheel 1 by press-fitting from the vehicle inner side. .

  The rolling bearing 3 is composed of a double-row angular contact ball bearing, and a pair of inner ring raceways 31 and 32, a flange 33a fixed to the vehicle body via a steering knuckle on the outer peripheral surface, and raceways 38 and 39 formed on the inner peripheral surface. A plurality of balls 34, 35 arranged along the outer ring 33, the inner ring raceways 31, 32 and the races 38, 39 of the outer ring 33, cages 36, 37 holding the balls 34, 35 in each row, and axial end portions It is comprised by the seal ring 4 which closed. The inner ring raceway portion 31 on the vehicle outer side is integrally formed on the outer peripheral surface of the shaft body 2. Further, the inner ring raceway portion 32 on the vehicle inner side is formed on the outer peripheral surface of the inner ring 42 that is externally fitted to a small diameter portion formed on the end portion on the vehicle inner side of the shaft body 2. In the present embodiment, the vehicle inner side refers to the right side in FIG. 1, the upper side in FIG. 2, the vehicle outer side refers to the left side in FIG. 1, and the lower side in FIG.

  The rolling bearing 3 is press-fitted into the outer peripheral surface of the shaft body 2 from the vehicle inner side, and then the vehicle inner side of the shaft body 2 is caulked to the end surface of the inner ring 42 and fixed to the shaft body 2 by the caulking portion 5.

  Further, a cylindrical recess 6 is formed at the end of the shaft body 2 on the side opposite to the vehicle outer side that is the caulking side. The recess 6 is formed so as not to penetrate the shaft body 2.

As shown in FIG. 2, the maximum depth of the recess 6 H, H ₁ the distance to the counter-caulking end surface 42a of the inner ring 42 from the inlet-side end surface 6a of the recess _6, the axial width of the inner ring 42 H _{2. If} the inner diameter dimension of the inlet side end surface 6a of the recess 6 is φA and the inner diameter dimension of the caulking portion 5 is φB,
H ₁ ≦ H ≦ H ₁ + 0.9 × H ₂ (1)
And φA ≦ φB (2)
Are in a relationship.

  Next, the caulking process will be described with reference to FIG.

A cylindrical portion 5 a used to prevent the rolling bearing 3 from coming off is formed at the end portion of the shaft body 2 on the vehicle inner side. After the rolling bearing 3 is press-fitted into the outer peripheral surface of the shaft body 2 from the vehicle inner side, the end portion on the vehicle outer side of the shaft body 2 is received by a caulking receiving jig 8, and the caulking tool of the caulking machine 7 is rolled to form a cylindrical portion. 5a is bent and deformed radially outward. Due to the caulking, a tensile stress acts on the shaft body 2 and the cylindrical portion 5 a, and a compressive stress acts on the inner ring 42. In this way, sufficient axial force is applied to the inner ring 42, and the rolling bearing 3 is fixed to the shaft body 2 by the caulking portion 5.

  Table 1 shows the relationship between the depth dimension H of the recess 6 and the axial force.

  In Table 1, the axial force is expressed as a ratio when the case where there is no recess 6 is 1.

From Table 1, it can be seen that the axial force is greater than 1 in the range of H ₁ ≦ H ≦ H ₁ + 0.9 × H ₂ . The maximum axial force is 1.5 when H = H ₁ + 0.5 × H ₂ . Incidentally, the axial force of 1.5 means that the tensile stress of the shaft body 2 and the compressive stress of the inner ring 42 are both suspended at a magnitude 1.5 times. The through hole is a case where the concave portion 6 is formed so as to penetrate the shaft body 2, and the shaft body 2 is deformed during caulking, so that the axial force becomes as small as 0.9.

According to the rolling bearing unit configured as described above, the concave portion 6 is formed on the vehicle outer side which is the end portion on the anti-caulking side of the shaft body 2, the depth dimension of the concave portion 6 is H, and the inlet side end face 6 a of the concave portion 6. from _{H 1} the distance to the counter-caulking end surface 42a of the inner ring 42 and the axial width dimension of the inner ring 42 and _{H 2,} by which is set such that _{H 1 ≦ H ≦ H 1 +} 0.9 × H 2 The cross-sectional area in the radial direction of the shaft body 2 is reduced. As a result, the tensile stress acting on the unit area of the radial section of the shaft body 2 during caulking increases, and the compressive stress acting on the inner ring 42 increases. Therefore, a large axial force can be applied to the inner ring 42 with a small caulking load. For this reason, even if it is a large sized bearing, it can squeeze reliably by a comparatively small caulking load, and since a large sized caulking machine is not used, cost reduction can be achieved. In addition, since the caulking load is small, the inner ring 42 of the rolling bearing 3 is not deformed and the raceway of the inner ring 42 is not recessed.

  Further, assuming that the inner diameter dimension of the inlet side end face 6a of the recess 6 is φA and the inner diameter dimension of the caulking portion is φB, the shaft body 2 is set directly below the caulking portion 5 during caulking by setting φA ≦ φB. It can be received and caulked by the caulking receiving jig 8.

  Furthermore, since the recessed part 6 was formed in the shaft body 2, the weight reduction of a rolling bearing unit can be achieved.

(Embodiment 2)
A second embodiment of the present invention will be described with reference to FIGS.

  FIG. 3 is a sectional view of a rolling bearing unit comprising a hub unit on the vehicle driven wheel side in the present embodiment, and FIG. 4 is a sectional view of the caulking process. In addition, the same code | symbol is attached | subjected to the same part as Embodiment 1, and the description is abbreviate | omitted.

  The rolling bearing unit of the present embodiment is characterized in that the concave portion 6 formed at the end portion of the shaft body 2 on the vehicle outer side has a substantially conical shape whose diameter increases toward the inlet side end surface 6a. is there. Note that the conical gradient corresponds to, for example, a draft angle during forging.

The depth dimension H of the recess 6 and the inner diameter dimension φA of the inlet side end face 6a are set to the values shown in the above formulas (1) and (2).

  Also in the rolling bearing unit configured in this way, the same effect as in the first embodiment can be obtained.

(Embodiment 3)
A third embodiment of the present invention will be described with reference to FIG.

  FIG. 5 shows a cross-sectional view of a rolling bearing unit comprising a hub unit on the vehicle driven wheel side in the present embodiment. In addition, the same code | symbol is attached | subjected to the same part as Embodiment 1, and the description is abbreviate | omitted.

  In the rolling bearing unit of the present embodiment, the hub wheel 1 is divided into a shaft body 2 and a flange 11 to which the wheel is attached, and an inner ring raceway portion 31 on the vehicle outer side is formed on the outer peripheral surface of the small diameter portion 11a of the flange 11. The inner ring raceway portion 32 on the vehicle inner side is integrally formed on the outer peripheral surface of the large diameter portion 2 a of the shaft body 2.

  Then, after the rolling bearing 3 and the flange 11 are press-fitted into the outer peripheral surface of the small diameter portion 2b of the shaft body 2 from the vehicle outer side, the vehicle inner side end portion of the shaft body 2 is crimped by a jig (not shown). The cylindrical portion 5 a of the end surface of the vehicle outer side of the shaft body 2 is caulked to the end surface of the flange 11 constituting the inner ring raceway portion 31, and the rolling bearing 3 and the flange 11 are fixed to the shaft body 2 by the caulking portion 5. .

  In addition, a cylindrical recess 6 is formed at the end of the shaft body 2 on the side opposite to the vehicle inner side which is the side that is caulked. The depth dimension H of the recess 6 and the inner diameter dimension φA of the inlet side end face 6a are set to the values shown in the above formulas (1) and (2).

  Also in the rolling bearing unit configured in this way, the same effect as in the first embodiment can be obtained.

  The recess 6 formed at the end on the vehicle inner side of the shaft body 2 may be substantially conical as shown in the second embodiment.

(Embodiment 4)
A fourth embodiment of the present invention will be described with reference to FIGS.

  FIG. 6 is a sectional view of a rolling bearing unit comprising a hub unit on the vehicle driven wheel side in the present embodiment, and FIG. 7 is a sectional view of the caulking process. In addition, the same code | symbol is attached | subjected to the same part as Embodiment 1, and the description is abbreviate | omitted.

  The rolling bearing unit of the present embodiment is characterized in that a pair of inner rings 91 and 92 that are separate from the shaft body 2 are mounted on the outer peripheral surface of the shaft body 2 along the axial direction.

  The rolling bearing 3 is press-fitted into the outer peripheral surface of the shaft body 2 from the vehicle inner side, and then the vehicle inner side of the shaft body 2 is caulked to the end surface of the inner ring 92 and fixed to the shaft body 2 by the caulking portion 5.

  Further, a cylindrical recess 6 is formed at the end of the shaft body 2 on the side opposite to the vehicle outer side that is the caulking side. The recess 6 is formed so as not to penetrate the shaft body 2.

As shown in FIG. 7, the distance from the anti-caulking side end face 91a of the inner ring 91 on the vehicle outer side to the bottom of the recess 6 is h, the axial width dimension of the inner ring 91 on the vehicle outer side is h ₁ , and the inner ring on the vehicle inner side 9
2 is the axial width dimension of h ₂ , the inner diameter dimension of the inlet side end face 6 a of the recess 6 is φA, and the inner diameter dimension of the caulking portion is φB.
h ₁ ≦ h ≦ h ₁ + 0.9 × h ₂ (3)
And φA ≦ φB (4)
Are in a relationship.

  Table 2 shows a relationship between the distance h from the anti-caulking side end surface 91a of the inner ring 91 to the bottom of the recess 6 and the axial force ratio of the pair of inner rings 91 and 92. In calculating the axial force ratio, of the inner ring 91 on the vehicle outer side and the inner ring 92 on the vehicle inner side, the larger axial force is calculated as the denominator.

From Table 2, it can be seen that in the range of h ₁ ≦ h ≦ h ₁ + 0.9 × h ₂ , the axial force ratio becomes larger than the axial force ratio 0.6 without the recess 6. That is, the axial force ratio between the pair of inner rings 91 and 92 is 0.7 or more. The maximum axial force ratio of 0.9 is when h = h ₁ + 0.5 × h ₂ . In addition, a through-hole is a case where the recessed part 6 penetrates the shaft body 2 and is formed.

According to the rolling bearing unit configured as described above, the recess 6 is formed on the vehicle outer side, which is the end of the shaft body 2 on the anti-caulking side, and the recess 6 is formed from the anti-caulking side end surface 91a of the inner ring 91 on the vehicle outer side. When the distance to the bottom is h, the axial width dimension of the inner ring 91 on the vehicle outer side is h ₁ , and the axial width dimension of the inner ring 92 on the vehicle inner side is h ₂ , h ₁ ≦ h ≦ h ₁ + 0.9 × By setting so as to be h ₂ , the cross-sectional area in the radial direction of the shaft body 2 is reduced. As a result, the tensile stress acting on the unit area of the radial section of the shaft body 2 during caulking increases, and the compressive stress acting on the inner rings 91 and 92 increases. Therefore, a large axial force can be applied to the inner rings 91 and 92 with a small caulking load. For this reason, even if it is a large sized bearing, it can squeeze reliably by a comparatively small caulking load, and since a large sized caulking machine is not used, cost reduction can be achieved. In addition, since the caulking load is small, the inner rings 91 and 92 of the rolling bearing 3 are not deformed and the raceways of the inner rings 91 and 92 are not recessed.

  Further, assuming that the inner diameter dimension of the inlet side end face 6a of the recess 6 is φA and the inner diameter dimension of the caulking portion is φB, the shaft body 2 is set directly below the caulking portion 5 during caulking by setting φA ≦ φB. It can be received and caulked by the caulking receiving jig 8.

  Moreover, since the recessed part 6 was formed in the shaft body 2, the weight reduction of a rolling bearing unit can be achieved.

  Furthermore, by setting the axial force ratio of the pair of inner rings 91 and 92 to 0.7 or more, the balance of the axial force generated in the pair of inner rings 91 and 92 is improved, and as a result, the rigidity of the entire rolling bearing 3 is improved. In addition, sufficient shaft strength can be secured, and the life of the rolling bearing 3 is improved. Therefore, for example, it is possible to prevent the shaft from becoming insufficient due to insufficient axial force of the inner ring 91 on the vehicle outer side, and the shaft from being damaged.

  The recess 6 formed at the end on the vehicle inner side of the shaft body 2 may be substantially conical as shown in the second embodiment.

  Note that the rolling bearing unit of the present invention is not limited to a hub unit composed of a combination of a hub wheel and an angular ball bearing, as shown in the above-described embodiment, and can be applied to various types of rolling bearing units.

  Moreover, the shape of the recessed part 6 is not restricted to the thing of the above-mentioned embodiment.

It is sectional drawing of the rolling bearing unit in Embodiment 1 of this invention. It is sectional drawing of the crimping process of the rolling bearing unit in Embodiment 1 of this invention. It is sectional drawing of the rolling bearing unit in Embodiment 2 of this invention. It is sectional drawing of the crimping process of the rolling bearing unit in Embodiment 2 of this invention. It is sectional drawing of the rolling bearing unit in Embodiment 3 of this invention. It is sectional drawing of the rolling bearing unit in Embodiment 4 of this invention. It is sectional drawing of the crimping process of the rolling bearing unit in Embodiment 4 of this invention.

Explanation of symbols

2 Shaft body 3 Rolling bearing 5 Caulking portion 6 Recessed portion 6a Entrance side end face 31, 32 Inner ring raceway portion 33 Outer ring 34, 35 Ball (rolling element)
42, 91, 92 Inner ring

Claims (1)

A shaft body in which a flange portion, one inner ring raceway, and a small diameter portion formed between the inner ring raceway and the step portion are formed on the outer peripheral surface in order from the vehicle outer side,
An inner ring formed on the outer peripheral surface with the other inner ring raceway and fitted on the small diameter part; and
An outer ring arranged concentrically with the shaft body and the inner ring and having a double-row track on the inner peripheral surface;
A double row rolling element interposed between the shaft body and the inner ring and the outer ring,
A bottomed cylindrical portion is formed at a vehicle inner side end portion of the shaft body,
A concave portion is formed at a vehicle outer side end portion of the shaft body,
The depth dimension from the inlet side end surface of the recess to the vehicle inner side end portion is H, and the distance from the inlet side end surface of the recess to the vehicle outer side end surface contacting the step portion of the inner ring is H ₁ . the axial width dimension when the of H _2,
A method of manufacturing a rolling bearing unit in which H ₁ ≦ H ≦ H ₁ + 0.9 × H ₂ ,
The rolling is characterized in that, with the end surface on the inlet side of the recess received by a caulking receiving jig, the cylindrical portion is bent and deformed radially outward to form a caulking portion, and the inner ring is fixed to the shaft body. Manufacturing method of bearing unit.

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