JP2006057678A - Supporting structure of bearing - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a supporting structure of a bearing capable of successfully supporting a bearing on a knuckle, and making the supporting structure which is light-weighted and inexpensive. <P>SOLUTION: The supporting structure of the bearing is provided with a bearing bush 10 of double structure comprising a male bush 10A to support the bearing 20, and a female bush 10B fitted into the male bush 10A and retained in a bearing support 2, and a fastening means 30 to fasten the bearing bush 10 in the bearing support 2. The bearing bush 10 is formed in such a tapered shape that male and femal fitting parts 14a, 14b of both the bushes 10A, 10B fitting inside and outside are fitted in the fastening direction by the fastening means 30. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a bearing support structure for supporting a bearing for supporting an axle on a bearing support portion of an automobile knuckle.

Conventionally, spheroidal graphite cast iron (FCD) is generally used for automobile knuckles (hereinafter simply referred to as “knuckles”), and a bearing for supporting an axle is press-fitted into a bearing support portion of the knuckle. The support structure of being supported was taken (for example, refer patent document 1).
Such a bearing support structure requires various measures such as management of bearing tightening allowance, response to fretting wear, and a structure for preventing slipping, but the structure is simple, inexpensive and lightweight. Had the advantage of being.

A bearing support structure is also known in which a bearing is integrated with a hub and attached to the knuckle for the purpose of enhancing the assembly of the bearing to the knuckle and the rigidity of the drive system (see, for example, Patent Document 2). .
JP-A-2-190226 (page 2, lower left column, third line to page 4, upper left column, fourth line, FIGS. 2 to 3) JP 2001-199202 A (paragraphs 0018 to 0023, FIG. 1)

  Incidentally, in recent years, aluminum alloy knuckles have come to be used with the weight reduction of automobile bodies. Since these knuckles are made of an aluminum alloy, in order to have the function as a knuckle, it is necessary to respond to fretting wear, to improve strength and to cope with electric corrosion or thermal expansion. It becomes.

  In particular, an aluminum alloy knuckle has a large difference in thermal expansion from the outer ring of the bearing and is likely to cause fretting wear. Therefore, when the bearing is press-fitted into the knuckle, it is necessary to make a large press-fitting allowance. The press-fitting allowance can be specified from the proof stress and sag resistance predicted by the material of the aluminum alloy, but if it is too small, fretting wear or tapping wear tends to occur, which is a big problem in terms of durability. Become.

For this reason, in the past, it is difficult to cause such a problem, and it is the current situation that many of the above-mentioned bearings integrated with a hub are used, but such a support structure has an integrated structure. As a result, the weight increases and the cost increases.
Moreover, in such an integrated structure, the material of the knuckle is made of an aluminum alloy for the purpose of reducing the weight, but conversely, it becomes necessary to increase the strength of the hub itself, resulting in an increase in weight. It had the disadvantage that it would end up.

  In particular, development of a lightweight and inexpensive bearing support structure has been desired for automobiles that have improved fuel efficiency through weight reduction of vehicles.

  Therefore, an object of the present invention is to provide a bearing support structure that can favorably support a bearing on a knuckle and that can be a lightweight and inexpensive support structure.

  In order to solve the above problems, a bearing support structure according to the present invention is a bearing support structure for supporting a bearing that supports an axle on a bearing support portion of a knuckle, and a male bush that holds the bearing; A double-structured bearing bush fitted with the male bush and held by the bearing support, and fastening means for fastening the bearing bush to the bearing support. The bearing bush is characterized in that the male and female fitting portions of the bushes fitting inside and outside are tapered so as to fit in the fastening direction by the fastening means.

According to such a bearing support structure, the bearing can be supported via the bearing bush having a double structure including the male bush and the female bush, and the bearing support is achieved by using the fastening means. A bearing bush can be fastened to the part.
The bearing bush has a tapered shape in which the male and female fitting portions of both bushes that fit inside and outside fit in the fastening direction by the fastening means, so that the male bush and the female bush using the fastening means As a result, the mating force between the male bush and the female bush at the male / female fitting portion increases, generating a component force, and the stress in the direction holding the bearing is male. And a stress in a direction fitting with the bearing support portion is generated in the female bush.

  Accordingly, the bearing is held by the bearing bush and the bearing bush is held by the bearing support portion.

  Moreover, since the bearing bush is fastened to the bearing support portion by the fastening means, it is not necessary to use press fitting to fix the bearing bush to the bearing support portion. As a result, the fretting wear and tapping wear that occurs when the press-fitting allowance is set to a large value or when the press-fitting allowance is too small, as in the conventional case where the bearing is directly press-fitted into the bearing support. This eliminates the need for strict mounting in consideration of the above, and makes it possible to favorably support the bearing on the knuckle.

  Furthermore, since it can be a simple support structure in which the bearing is supported by the bearing support portion via the bearing bush, there is no need to use a conventional weight structure in which the hub and the bearing are integrated, and the weight is reduced. An inexpensive support structure can be obtained.

  The fastening means is a bolt, and the bolt is formed in the female bush from a bolt insertion hole of a flange portion formed in the male bush through an insertion hole provided in the bearing support portion. It is good to set it as the structure engaged with the internal thread of the made flange part.

  According to such a bearing support structure, the male bush and the female bush can be easily and reliably fastened via the bearing support portion by the fastening means using bolts.

  Further, it is preferable that a seal member is interposed between the male bush or the female bush and the bearing support portion.

According to such a bearing support structure, since the seal member is interposed between the male bush or the female bush and the bearing support portion, the male bush or the female bush and the bearing support portion are provided. It is possible to prevent moisture and the like from entering through the gap.
Thereby, electrolytic corrosion between the male bush or the female bush and the bearing support portion can be effectively prevented.

  A bearing support structure according to the present invention is a bearing support structure for supporting a bearing supporting an axle on a bearing support portion of a knuckle, the bearing bush holding the bearing, and the bearing bush being the bearing. Fastening means for fastening to the support portion, and the bearing bush mounting surface of the bearing support portion is formed in a tapered shape having a small diameter along the fastening direction by the fastening means, and the outer peripheral surface of the bearing bush is the bearing It is characterized by being formed in a tapered shape that fits to the bush mounting surface.

According to such a bearing support structure, the bearing can be supported via the bearing bush, and the bearing bush can be fastened to the bearing support portion using the fastening means.
The bearing bush mounting surface of the bearing support portion is formed in a tapered shape having a small diameter along the fastening direction by the fastening means, and the outer peripheral surface of the bearing bush is formed in a tapered shape that fits the bearing bush mounting surface. Therefore, when the bearing bush is fastened to the bearing support portion using the fastening means, the mutual fitting force between the bearing bush mounting surface of the bearing support portion and the outer peripheral surface of the bearing bush is increased. Then, stress in the direction of holding the bearing is generated in the bearing bush. Thereby, a bearing is hold | maintained at a bearing bush.

  Moreover, since the bearing bush is attached to the bearing support portion by fastening by the fastening means, it is not necessary to press-fit the bearing bush into the bearing support portion. Therefore, as in the conventional case, when the bearing is directly press-fitted into the bearing support portion, the press-fitting allowance is set to be large, or the fretting wear or the tapping wear that occurs when the press-fitting allowance is too small. This eliminates the need for rigorous mounting and allows the knuckle to better support the bearing.

  Furthermore, since it can be a simple support structure in which the bearing is supported by the bearing support portion via the bearing bush, there is no need to use a conventional weight structure in which the hub and the bearing are integrated, and the weight is reduced. An inexpensive support structure can be obtained.

  The fastening means may be a bolt, and the bolt may be screwed into a female screw portion provided in the bearing support portion through a bolt insertion hole of a flange portion formed in the bearing bush.

  According to such a bearing support structure, the bearing bush can be easily and securely fastened to the bearing support portion by the fastening means using bolts.

  Between at least one of the bearing support portion and an end surface of the bearing bush on the insertion port side, and at least one of the bearing support portion and an end surface of the bearing bush on the non-insertion port side, or A seal member may be interposed between the bearing support portion and the outer ring of the bearing facing the bearing support portion.

According to such a bearing support structure, it is possible to prevent moisture and the like from entering between the bearing support portion and the bearing bush due to the presence of the seal member.
Thereby, the electrolytic corrosion between a bearing support part and a bearing bush can be prevented effectively.

  According to the bearing support structure of the present invention, the bearing can be satisfactorily supported by the knuckle, and a lightweight and inexpensive support structure can be obtained.

Hereinafter, the best mode for carrying out the present invention will be described in detail with reference to the accompanying drawings. In the description, the same reference numerals are used for the same elements, and duplicate descriptions are omitted.
<First Embodiment>
In the drawings to be referred to, FIG. 1 is a schematic view showing a wheel portion of an automobile to which a bearing support structure according to a first embodiment of the present invention is applied, and FIG. 2 is also for explaining the bearing support structure. FIG. 3 is a partially sectional view for explaining the bearing support structure, and FIG. 4 is an enlarged sectional view showing the main part for explaining the bearing support structure. .

  As shown in FIG. 1, a front wheel (drive side wheel) portion of an automobile to which the bearing support structure of the present embodiment is applied includes a knuckle 1, an axle S supported by the knuckle 1, and the axle S And an attached wheel hub H. The knuckle 1 is provided with a knuckle arm 4 having a connecting portion 3 connected to a plurality of suspension arms A. Further, a tire wheel TW with a tire T attached thereto is attached to the wheel hub H by bolts (not shown). Further, a shock absorber K is disposed in the vicinity of the knuckle 1 and the suspension arm A.

  The knuckle 1 is made of an aluminum alloy casting, and as shown in FIG. 2, a cylindrical bearing support portion 2 is formed at the center. A bearing 20 is supported on the bearing support 2 via a bearing bush 10, and the fastening described later is provided around the hole along the axial direction of the axle S (see FIG. 1). A total of four insertion holes 2A for inserting bolts 30 (see FIG. 3) as means are formed at intervals of 90 degrees. The insertion hole 2A may be formed at least at one place, and may be formed at five or more places. Moreover, the formation interval of 2 A of insertion holes can be set arbitrarily.

  The bearing bush 10 has a double structure in which a male bush 10A and a female bush 10B are combined. As shown in FIG. 3, the bearing bush 10 is attached to the bearing support portion 2 with the bearing 20 held inside. It is supposed to be retained. The bearing bush 10 is formed using a material having a thermal expansion coefficient close to that of an aluminum alloy material, for example, an aluminum MMC (Metal Matrix Composite) material or a stainless steel material. Therefore, the bearing bush 10 having higher strength and better sag resistance than the aluminum alloy material can be obtained. The bearing bush 10 may be formed using a steel material or the like, or may be formed using an aluminum alloy material.

  As shown in FIG. 2, the male bush 10 </ b> A includes a cylindrical portion 11 a and a flange portion 12 a formed integrally with an end portion (non-insertion port side of the bearing 20) of the cylindrical portion 11 a. The bearing 20 is inserted and held in the cylindrical portion 11a. As shown in FIG. 3, a stopper 13 a that contacts the end of the inserted bearing 20 is provided in the cylindrical portion 11 a. In addition, you may comprise the bearing 20 so that it may be press-fitted and hold | maintained in the cylindrical part 11a.

  As shown in FIG. 4, the cylindrical portion 11 a has an outer peripheral surface 14 a formed in a tapered shape having a small diameter from the flange portion 12 a side toward the insertion port side of the bearing 20, and the outer peripheral surface 14 a has a female shape. An inner peripheral surface 14b described later of the bush 10B is fitted.

  As shown in FIG. 2, a total of four bolt insertion holes 15 a (partially shown) are formed in the flange portion 12 a at positions corresponding to the insertion holes 2 </ b> A formed in the bearing support portion 2. In this embodiment, the flange portion 12a is formed in an annular shape. However, the present invention is not limited to this, and a tongue-like portion (not shown) is formed only at a position where the bolt insertion hole 15a is formed. Also good.

  As shown in FIG. 2, the male bush 10A is inserted into the bearing support 2 from the side of the knuckle 1 (not shown) (see FIG. 1). As shown in FIG. 3, a stepped portion 2 a into which the flange portion 12 a of the male bush 10 </ b> A is fitted flush is formed on the side opening edge.

As shown in FIGS. 2 and 3, the female bush 10B includes a cylindrical portion 11b and a flange portion 12b integrally formed at the end of the cylindrical portion 11b.
As shown in FIG. 4, the cylindrical portion 11b has an inner peripheral surface 14b formed in a tapered shape having a large diameter from the flange portion 12b side toward the flange portion 12a side of the male bush 10A. The outer peripheral surface 14a of the male bush 10A is fitted to the inner peripheral surface 14b.
That is, the bearing bush 10 has a male / female fitting portion (a contact portion between the outer circumferential surface 14a and the inner circumferential surface 14b) of both bushes 10A and 10B that fit inside and outside, and a fastening direction by a bolt 30 as fastening means described later. It has a tapered shape that fits in (fitting direction).

  As shown in FIG. 2, a bolt 30 (see FIG. 3) as a fastening means can be screwed into the flange portion 12b at a position corresponding to the insertion hole 2A formed in the bearing support portion 2. A female screw 18b is formed. In this embodiment, the flange portion 12b is formed in an annular shape. However, the present invention is not limited to this, and a tongue-like portion (not shown) may be formed only at a position where the female screw 18b is formed. .

  Further, as shown in FIG. 4, a circumferential groove 16b is formed on the outer peripheral edge portion of the flange portion 12b on the surface facing the step portion 2b described later, and a seal is formed on the circumferential groove 16b. A member 17b (O-ring) is attached.

Such a female bush 10B is inserted into the bearing support 2 from the tire T side (see FIG. 1) of the knuckle 1, as shown in FIG. As shown in FIGS. 3 and 4, a step portion 2b into which the flange portion 12b fits flush is formed on the entire opening edge.
Here, as shown in FIG. 4, with the flange 12b aligned with the step 2b of the bearing support 2, the flange 12b and the outer ring 22 of the bearing 20 and the flange 12b A gap is formed between the end surface of the cylindrical portion 11a of the bush 10A and between the flange portion 12b and the stepped portion 2b of the bearing support portion 2 (to be used for tightening bolts 30 described later). It has become.

  As shown in FIG. 3, the bearing 20 is a ball bearing made of steel or the like. In the present embodiment, the bearing 20 has two rows of balls 21, and an outer ring 22 of the ball 20 is fastened by fastening a bolt 30 described later. It is formed in a size that is held in the cylindrical portion 11a of the bush 10A of the mold.

As shown in FIG. 4, the bolt 30 is for fastening the bearing bush 10 in the axial direction of the axle S (see FIG. 1), and from the bolt insertion hole 15a in the flange portion 12a of the male bush 10A. It is inserted into the insertion hole 2A of the bearing support portion 2 and is screwed into the female screw 18b in the flange portion 12b of the female bush 10B.
As the bolt 30, it is desirable to use a material having a high coefficient of thermal expansion or a low spring constant, for example, a material made of stainless steel, titanium, or the like. By using the bolt 30 formed of such a material, it is possible to improve the followability to the thermal expansion of the knuckle 1.

Next, assembly of the bearing 20 in such a support structure for the bearing 20 will be described with reference to FIGS.
First, as shown in FIG. 5A, the bearing 20 is inserted into the cylindrical portion 11a of the male bush 10A. At this time, the bearing 20 is held by the cylindrical portion 11a in either a loose state or a light press-fit state. The bearing 20 is inserted to a position where it abuts against a stopper 13a formed in the cylindrical portion 11a of the male bush 10A.

  Thereafter, as shown in FIG. 5B, in order to hold the male bush 10A on the bearing support portion 2 of the knuckle 1, the cylindrical portion 11a is inserted into the hole of the bearing support portion 2, and the male bush 10A is inserted. The flange portion 12a of 10A is fitted into the step portion 2a of the bearing support portion 2.

Then, as shown in FIG. 5 (c), the female bush 10B is inserted into the hole of the bearing support portion 2 from the side opposite to the side where the male bush 10A is inserted, and the male bush 10A is inserted into the male bush 10A. Assemble it. That is, the male bush 10A is brought into contact with the tapered inner peripheral surface 14b of the cylindrical portion 11b of the female bush 10B on the tapered outer peripheral surface 14a of the cylindrical portion 11a of the male bush 10A. The female bush 10B is fitted.
Further, at the time of this assembly, the seal member 17b is attached to the circumferential groove 16b of the flange portion 12b of the female bush 10B.

Thereafter, the four bolts 30 are inserted from the bolt insertion hole 15a of the flange portion 12a of the male bush 10A into the insertion hole 2A of the bearing support portion 2, and screwed into the female screw 18b of the flange portion 12b of the female bush 10B. Then, the male bush 10A and the female bush 10B are tightened.
At this time, when the bolt 30 is tightened, the male and female fitting portions (the contact portions between the outer peripheral surface 14a and the inner peripheral surface 14b) of the bushes 10A and 10B that fit inside and outside are directed in the fastening direction by the bolt 30. As shown in FIG. 5D, the male bush 10A and the female die at the male / female fitting portion (the contact portion between the outer peripheral surface 14a and the inner peripheral surface 14b) are formed. The mating force F1, F1 ′ with the bush 10B increases, the component forces F2, F2 ′ are generated, and the stress in the direction of holding the bearing 20 is generated in the male bush 10A, and the bearing support 2 Stress in the direction of fitting into the female bush 10B is generated in the female bush 10B.

  As a result, the bearing 20 inserted into the male bush 10A of the bearing bush 10 in a loose or light press-fit state is clamped and strongly held by the male bush 10A, and is inserted into the bearing support portion 2 in a loose state. The female bush 10 </ b> B thus formed is tightened and strongly held by the bearing support portion 2, and the bearing 20 is supported by the knuckle 1 via the bearing bush 10.

According to such a support structure of the bearing 20, the bearing 20 is attached to the bearing support portion 2 of the knuckle 1 via the bearing bush 10 having a double structure including the male bush 10 </ b> A and the female bush 10 </ b> B. Since the structure is attached, the bearing 20 is not directly press-fitted into the knuckle 1, and it is not necessary to strictly adjust the press-fitting allowance as in the prior art. And since each member can be assembled | attached in a loose state, the advantage that an assembly operation | work is easy is also acquired.
In addition, the bearing 20 is held against the bearing bush 10 which has higher strength and better sag resistance than the aluminum alloy material, compared to the case where the bearing 20 is directly attached to the aluminum alloy knuckle 1, so that the state is stable. The advantage of being supported by is obtained.

  Moreover, since the bearing bush 10 is attached to the bearing support portion 2 by fastening with the bolts 30, it is not necessary to use press fitting to fix the bearing bush 10 to the bearing support portion 2. Therefore, as in the conventional case, when the bearing 20 is directly press-fitted into the bearing support portion 2, the press-fitting allowance is set to be large, or the fretting wear caused by the press-fitting allowance is too small. It is not necessary to strictly perform the attachment in consideration of wear or the like, and the bearing 20 can be favorably supported on the knuckle 1.

  Furthermore, since it is possible to provide a simple support structure in which the bearing 20 is supported by the bearing support portion 2 via the bearing bush 10, it is not necessary to use a conventional weight structure in which the hub and the bearing are integrated. Thus, a light and inexpensive support structure can be obtained.

  Further, the male bush 10A and the female bush 10B can be easily and reliably fastened through the bearing support portion 2 by the fastening means using the bolts 30.

Further, since the seal member 17b is interposed between the female bush 10B and the bearing support portion 2, it is possible to prevent moisture and the like from entering between the female bush 10B and the bearing support portion 2. it can.
Thereby, the electrolytic corrosion between female bush 10B and the bearing support part 2 can be prevented effectively.

  Further, when the bearing bush 10 is formed of a material whose thermal expansion is close to that of an aluminum alloy material, such as an aluminum MMC material or a stainless steel material, there is also an advantage that a change in tightening margin can be suppressed to a small extent.

<Second Embodiment>
FIG. 6 is an enlarged cross-sectional view showing a main part for explaining the bearing support structure according to the second embodiment of the present invention.
The present embodiment differs from the bearing support structure of the first embodiment in that the bearing bush mounting surface 2 ′ of the bearing support portion 2 is formed in a tapered shape, and the bearing bush mounting surface 2 ′ is tapered. The bearing bush 40 having the outer peripheral surface 14a is fitted. That is, in this embodiment, the bearing support portion 2 of the knuckle 1 has a tapered shape corresponding to the inner peripheral surface 14b of the female bush 10B (see FIGS. 3 and 4) described in the first embodiment. A bearing bush mounting surface 2 ′ is formed, and the male bush 10A is fitted to the bearing bush mounting surface 2 ′. Since the bearing bush 40 has the same basic configuration as the male bush 10A described in the first embodiment, the same reference numerals are used and description thereof is omitted.

  The bearing bush mounting surface 2 ′ of the bearing support portion 2 is formed in a tapered shape having a small diameter along the fastening direction by the bolt 30 ′, and the tapered outer peripheral surface 14 a of the bearing bush 40 is fitted. ing.

  A circumferential groove 2c is formed between the bearing support portion 2 and the end face 40a of the bearing bush 40 on the insertion opening side of the bearing 20, and a sealing member 2d is provided in the circumferential groove 2c.

  Also in the present embodiment, a bolt 30 ′ is used as a fastening means, and this bolt 30 ′ is a female screw provided in the bearing support portion 2 through a bolt insertion hole 15 a of a flange portion 12 a formed in the bearing bush 40. It is adapted to be screwed into the part 2B.

According to such a support structure of the bearing 20, the bearing 20 can be supported via the bearing bush 40, and the bearing bush 40 can be fastened to the bearing support portion 2 using the bolt 30 ′.
Further, the bearing bush mounting surface 2 ′ of the bearing support portion 2 is formed in a taper shape having a small diameter along the fastening direction by the bolt 30 ′, and the outer peripheral surface 14 a of the bearing bush 40 is formed by the bearing bush mounting surface 2. When the bearing bush 40 is fastened to the bearing support portion 2 using the bolt 30 ', the bearing bush mounting surface 2' of the bearing support portion 2 and the bearing bush 40 are fixed. The mating force with the outer peripheral surface 14a of the bearing is increased, the bearing bush 40 is fastened to the bearing support portion 2, and the component force of the mating force acts, so that the stress in the direction of holding the bearing 20 is changed to the bearing. It will occur in the bush 40. As a result, the bearing 20 is tightened and held in the bearing bush 40.

  In addition, since the bearing bush 40 is attached to the bearing support portion 2 by fastening with the bolt 30 ', it is not necessary to use press-fitting to fix the bearing bush 40 to the bearing support portion 2, and fretting wear and the like There is no need to perform strict installation in consideration of wear and the like. Therefore, the bearing 20 can be favorably supported on the knuckle 1.

  Furthermore, in this embodiment, since the bearing 20 is supported by the bearing support portion 2 via the bearing bush 40, a simple support structure in which the hub and the bearing are integrated as in the prior art. It is not necessary to use a structure, and a lightweight and inexpensive support structure can be obtained.

  Further, the bearing bush 40 can be easily and securely fastened to the bearing support portion 2 by fastening using the bolt 30 '. In addition, since the bolt 30 'is screwed into the female thread portion 2B of the bearing support portion 2, there is also an advantage that the entire length can be shortened.

Furthermore, since the seal member 2d is interposed between the bearing support portion 2 and the end face 40a of the bearing bush 40, it is possible to prevent moisture and the like from entering between the bearing support portion 2 and the bearing bush 40. It is possible to effectively prevent electrolytic corrosion during this period.
The seal member 2d may be interposed between the bearing support portion 2 and the outer ring 22 of the bearing 20 facing the bearing support portion 2. Further, the seal member 2d is provided between a flange portion 12a (an end surface on the non-insertion port side of the bearing 20) provided on the non-insertion port side of the bearing 20 and the bearing support portion 2 facing the flange portion 12a. It may be interposed.

Although the embodiments of the present invention have been described above, the present invention is not limited to the above-described embodiments, and can be implemented with appropriate modifications.
For example, as shown in FIG. 7, a step is formed in the flange portion 12a ′ of the bearing bush 10 ′ so that the support position of the bearing 20 is shifted to the tire T (see FIG. 1) side. Good. In this case, the male-female fitting portion (the contact portion between the outer peripheral surface 14a ′ and the inner peripheral surface 14b ′) between the male bush 10A ′ and the female bush 10B ′ is also on the tire T (see FIG. 1) side. The position is shifted to. By using such a bearing bush 10 ′, the axle S (see FIG. 1) can be supported at a position close to the tire T (see FIG. 1) side.

  Further, as shown in FIG. 8, the male and female fitting portions (contact portions between the outer peripheral surface 14a ′ and the inner peripheral surface 14b ′) are further shifted to the tire T (see FIG. 1) side, and the bearing The bolt 30 may be configured to be screwed into the female screw 18b ′ on the extension of the line (center line O) passing through the center position of 20. The bearing support portion 2 is formed with an inlay portion 2C that comes into contact with the outer peripheral surface of the cylindrical portion 11b 'of the female bush 10B'.

  According to such a support structure of the bearing 20, the bolt 30 is screwed into the female screw 18 b ′ on the extension of the line (center line O) passing through the center position of the bearing 20. Therefore, stable support of the bearing 20 can be realized. It should be noted that a position slightly deviated from the extension of the line passing through the center position of the bearing 20 (center line O) is at least an extension of a line passing through the center position of the ball 21 of the bearing 20 (not shown). What is necessary is just to have the positional relationship that the volt | bolt 30 has screwed in internal thread 18b 'in the upper position.

It is the schematic diagram which showed the wheel part of the motor vehicle to which the support structure of the bearing of the 1st Embodiment of this invention is applied. FIG. 6 is an exploded perspective view (partially omitted) for explaining the bearing support structure. It is a fragmentary sectional view for demonstrating the support structure of a bearing similarly. It is the expanded sectional view which showed the principal part for demonstrating the support structure of a bearing similarly. (A)-(d) is explanatory drawing at the time of assembling a bearing. It is the expanded sectional view which showed the principal part for demonstrating the support structure of the bearing of the 2nd Embodiment of this invention. It is the expanded sectional view which showed the principal part of the modification. It is the expanded sectional view which showed the principal part of the modification.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Knuckle 2 Bearing support part 2 'Bearing mounting surface 2A Insertion hole 2B Female thread part 10 Bearing bush 10A Male type bush 10B Female type bush 11a, 11b Cylindrical part 12a, 12b Flange part 14a Outer peripheral surface 14b Inner peripheral surface 15a Bolt Insertion hole 16b Circumferential groove 17b Sealing material 18b Female thread 11 Sealing member 20 Bearing 30 Bolt (fastening means)

Claims (7)

A bearing support structure for supporting a bearing supporting an axle on a bearing support portion of an automotive knuckle,
A double-structure bearing bush comprising a male bush holding the bearing, and a female bush fitted to the male bush and held by the bearing support;
A fastening means for fastening the bearing bush to the bearing support portion;
The bearing support structure is characterized in that the male and female fitting portions of the bushes fitting inside and outside are tapered so as to fit in the fastening direction by the fastening means. The fastening means is a bolt;
The bolt is screwed into a female screw of a flange portion formed in the female bush through a through hole provided in the bearing support portion from a bolt insertion hole of the flange portion formed in the male bush. The bearing support structure according to claim 1.   The bearing support structure according to claim 1, wherein a seal member is interposed between the male bush or the female bush and the bearing support portion. A bearing support structure for supporting a bearing supporting an axle on a bearing support portion of an automotive knuckle,
A bearing bush for holding the bearing;
A fastening means for fastening the bearing bush to the bearing support portion;
While forming the bearing bush mounting surface of the bearing support portion into a tapered shape having a small diameter along the fastening direction by the fastening means,
A bearing support structure, wherein an outer peripheral surface of the bearing bush is formed in a tapered shape so as to be fitted to the bearing bush mounting surface. The fastening means is a bolt;
The bearing support structure according to claim 4, wherein the bolt is screwed into a female screw portion provided in the bearing support portion through a bolt insertion hole of a flange portion formed in the bearing bush.   A seal member is provided between at least one of the bearing support portion and an end surface of the bearing bush on the insertion port side of the bearing and between the bearing support portion and an end surface of the bearing bush on the non-insertion port side. 6. The bearing support structure according to claim 4 or 5, wherein the bearing is interposed.   The bearing support structure according to claim 4 or 5, wherein a seal member is interposed between the bearing support portion and an outer ring of the bearing facing the bearing support portion.

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