JP2007010159A - Sliding bearing - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To firmly fix a sleeve member and a cap member by adhesive and to prevent extrusion of the adhesive to the external. <P>SOLUTION: This sliding bearing comprises the sleeve member, a shaft member having a flange and relatively rotatably fitted to the sleeve member, and the cap member fitted and fixed to a circumferential step portion formed on an opening portion of the sleeve member. The circumferential step portion of the sleeve member is composed of a first step portion having an inner diameter larger than an outer diameter of the cap member, and a second step portion guiding and fitting the cap member, a required clearance having a radial width narrower than an axial length, or a required clearance of a width capable of allowing the adhesive to penetrate by capillary phenomenon, is formed between an inner peripheral face of the first step portion of the sleeve member and an outer peripheral face of the cap member, and the inner peripheral face of the first step portion of the sleeve member and the outer peripheral face of the cap member are adhered by the adhesive. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a slide bearing in which, for example, a shaft member is supported on a cylindrical member so as to be relatively rotatable at a dynamic pressure bearing portion.

  In general, a sliding bearing, for example, a dynamic pressure bearing, is known from a shaft member having a flange formed at a shaft end and a cylindrical member that accommodates the shaft member (see Patent Document 1).

  The structure of a conventional hydrodynamic bearing is shown in FIG. 1 or FIG. In the dynamic pressure bearing of FIG. 1, dynamic pressure generating grooves 3 and 4 as axial bearing portions are formed on both axial end surfaces of the flange 2 formed at the shaft end of the shaft member 1. The shaft member 1 has dynamic pressure generating grooves 5 and 6 as radial bearing portions. The shaft member 1 and the flange 2 are accommodated in the tubular member 7, and the lid member 8 in which the axial through hole is not formed is fitted in the opening 9 of the tubular member 7, so that the opening 9 of the tubular member 7 is formed. It is blocked.

  2 has an axial through hole 8a formed at the center of the lid member 8, and an end 1a of the shaft member 1 having the flange 2 formed in the through hole 8a. It is inserted. Other configurations are the same as those in FIG. 1, and the same reference numerals are given to omit redundant description.

  In the dynamic pressure bearings of FIGS. 1 and 2, the cylindrical member 7 and the lid member 8 are fitted by a press-fitting or bonding method, but the fixing by press-fitting is easy to handle and has a relatively high fixing force. However, since there is a problem that it is easy to influence the dimensions of the bearing portion, fixing by adhesion without affecting the dimensions of the bearing portion is performed.

That is, conventionally, as shown in FIG. 7, a circumferential step portion 71 is formed in the opening of the cylindrical member 7, and the lid member 8 having an outer diameter substantially the same as the inner diameter of the circumferential step portion 71 is formed on the circumference. It is guided by the stepped portion 71 and fitted, and in this state, the adhesive B is applied from the outside of the fitting surface of the tubular member 7 and the lid member 8 to bond the both members 7 and 8 together. Other configurations are the same as those in FIG. Further, the structure of FIG. 7 is of the dynamic pressure bearing type of FIG. 1, but the fitting of the cylindrical member 7 and the lid member 8 in the dynamic pressure bearing type of FIG. 2 is exactly the same as FIG.
JP 7-317765 A

  In the conventional bonding structure shown in FIG. 7, there is almost no fitting gap between the circumferential step portion 71 of the cylindrical member 7 and the lid member 8 in order to prevent the guide after the lid member 8 is fitted and rattling after being assembled. For this reason, even if the adhesive B is applied from the outside of the fitting surface, the tubular member 7 and the lid member 8 are fixed in a state where the adhesive B does not sufficiently permeate between the fitting surfaces and protrudes to the outside. The Therefore, there is a problem that the fixing force of the adhesive B is small, and at the same time, the adhesive B needs to be protruded and removed.

  An object of the present invention is to provide a sliding bearing that obtains a high fixing force by an adhesive on the fitting surface of a cylindrical member and a lid member and prevents the adhesive from protruding to the outside.

  As means for solving the above-mentioned problems, in the invention of claim 1, a cylindrical member, a shaft member having a flange fitted to the cylindrical member so as to be relatively rotatable, and a circumferential step formed in an opening of the cylindrical member A lid member that is fitted to the flange and is axially opposed to the flange, forms an axial bearing portion with the flange, and abuts against a step surface that extends inward in the axial direction of the circumferential step portion The circumferential step portion of the cylindrical member includes a first step portion having an inner diameter larger than the outer diameter of the lid member on the opening end side, and an outer diameter of the lid member on the inner side. The inner diameter is the same as that of the second step portion that guides and fits the lid member, and is formed between the inner peripheral surface of the first step portion of the cylindrical member and the outer peripheral surface of the lid member. The axial length of the required gap is longer than the radial width of the required gap, and the first step of the cylindrical member is And inner and outer circumferential surfaces of the lid member is characterized in that it is bonded by an adhesive.

  In the invention of claim 2, the cylinder member, the shaft member having a flange that is fitted to the cylinder member so as to be relatively rotatable, and the circumferential step formed in the opening of the cylinder member are adhesive. And a lid member that is axially opposed to the flange and is formed with an axial bearing portion between the flange and the lid member that is in contact with the step surface that extends inward in the axial direction of the circumferential step portion. The circumferential step portion of the cylindrical member has a first step portion whose inner diameter is larger than the outer diameter of the lid member on the opening end side, and an inner diameter that is substantially the same as the outer diameter of the lid member on the inner side. A radial direction of a required gap formed between the inner peripheral surface of the first step portion of the cylindrical member and the outer peripheral surface of the lid member. The width is set to a width that allows the adhesive to penetrate by capillary action, and the width of the first step portion of the cylindrical member is set. And the outer peripheral surface of the peripheral surface and the lid member is characterized by being bonded with the adhesive.

  Furthermore, in the invention of claim 3, in the slide bearing according to claim 1 or 2, a recess is formed on at least one of the inner peripheral surface of the first step portion of the cylindrical member and the outer peripheral surface of the lid member. It is characterized by that.

  Furthermore, in the invention according to claim 4, in the sliding bearing according to any one of claims 1 to 3, the axial length of the adhesive layer that has penetrated and hardened between the cylindrical member and the lid member. Is longer than the radial width of the layer.

  In the present invention, since the adhesive is reliably infiltrated between the required gaps between the circumferential step portion of the cylindrical member and the lid member, a high fixing force is obtained and the adhesive is prevented from protruding.

  The dynamic pressure bearing shown in FIGS. 1 and 3 will be described. As a plain bearing, for example, a dynamic pressure bearing, there is one shown in FIG. In this dynamic pressure bearing, dynamic pressure generating grooves 3 and 4 as axial bearing portions are formed on both axial end surfaces of the flange 2 formed at the shaft end of the shaft member 1. The shaft member 1 has dynamic pressure generating grooves 5 and 6 as radial bearing portions. Further, the shaft member 1 and the flange 2 are accommodated in the cylindrical member 7, and the lid member 8 is fitted into the opening 9 of the cylindrical member 7 so that the opening 9 of the cylindrical member 7 is closed.

  The opening 9 of the cylindrical member is a circumferential step 10, and the circumferential step 10 is a first step whose opening end is set to have an inner diameter larger than the diameter of the outer peripheral surface 15 of the lid member 8. 11 and a second step portion 12 whose inner side has an inner diameter substantially the same as the outer diameter of the lid member 8. That is, the lid member 8 is guided by the second step portion 12 of the circumferential step portion 10 of the cylindrical member 7 to prevent rattling after fitting. Furthermore, the required clearance S which is equal on the circumference is formed between the first step portion 11 of the cylindrical member 7 and the lid member 8 by the guide of the lid member 8 of the second step portion 12. Therefore, when the cylinder member 7 and the lid member 8 are fixed by applying the adhesive B from the outside of the fitting surface, the gap S between the first step portion 11 and the lid member 8 is large. The fitting surface is surely penetrated by the own weight and capillary action in the direction of the arrow, and the two members 7 and 8 are firmly bonded. Further, the protrusion of the adhesive B is also eliminated.

  Further, in another embodiment of FIG. 4, circumferential grooves as concave portions 13 and 14 are formed on both the inner peripheral surface of the first step portion 11 of the cylindrical member 7 and the outer peripheral surface 15 of the lid member 8. Yes. As a result, the adhesive B that has penetrated into the gap S between the first step portion 11 and the lid member 8 in the direction of the arrow enters the circumferential grooves 13 and 14 and hardens. Power is obtained. The circumferential grooves 13 and 14 may be formed in at least one of the first step portion 11 or the lid member 8, and may be not only the circumferential groove but also a plurality of circumferential recesses.

  Furthermore, FIG. 5 shows another embodiment. Contrary to the embodiment of FIG. 3, the outer peripheral surface 15 of the lid member 8 has an outer diameter substantially the same as the inner diameter of the circumferential step portion 10 of the cylindrical member 7. In addition, the outer peripheral side circumferential surface of the lid member 8 is a circumferential step portion 16 having an outer diameter smaller than the inner diameter of the circumferential step portion 10 of the cylindrical member. Thereby, the clearance gap S similar to FIG. 2 is formed between the circumferential step part 16 of the cover member 8 and the circumferential step part 10 of the cylindrical member, and the same effect as FIG. 2 is produced.

  Moreover, you may apply the structure of the recessed parts 13 and 14 shown to embodiment of FIG. 4 to embodiment of FIG.

  Furthermore, the hydrodynamic bearing of FIGS. 2 and 6 is another embodiment. 1 and 3, the lid member 8 fitted to the cylindrical member 7 is not formed with an axial through hole, whereas the end of the shaft member 1 is formed on the lid member 8. The only difference is that the axial through-hole 8a into which the portion 1a is inserted is formed in the central portion, and the other configurations are exactly the same, and are given the same reference numerals. The configuration of the circumferential step portion 10 formed on the cylindrical member 7 in FIG. 6 is the same as the configuration in FIG. 3, but the other embodiments in FIGS. Naturally, it is applied to the pressure bearing type.

It is sectional drawing of a general dynamic pressure bearing. It is sectional drawing of another common dynamic pressure bearing. It is a principal part enlarged view of one Embodiment of this invention. It is a principal part enlarged view of another embodiment of this invention. It is a principal part enlarged view of another embodiment of this invention. It is a principal part enlarged view of another embodiment of this invention. It is a principal part enlarged view of the conventional dynamic pressure bearing.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Shaft member 2 Flange 3 Dynamic pressure generating groove 4 Dynamic pressure generating groove 5 Dynamic pressure generating groove 6 Dynamic pressure generating groove 7 Cylindrical member 8 Lid member 9 Opening part 10 Circumferential step part 11 First step part 12 Second step part 13 Circumferential groove 14 circumferential groove 15 outer peripheral surface 16 circumferential step B adhesive S gap

Claims (4)

A tubular member;
A shaft member having a flange fitted to the tubular member so as to be relatively rotatable;
Fitted to a circumferential step formed in the opening of the cylindrical member, fixed with an adhesive, opposed to the flange in the axial direction, and formed an axial bearing portion between the flange and the circumferential step A lid member that comes into contact with a stepped surface that extends inward in the axial direction;
In a plain bearing comprising:
The circumferential step portion of the cylindrical member has a first step portion whose inner diameter is larger than the outer diameter of the lid member on the opening end side, and an inner diameter that is substantially the same as the outer diameter of the lid member on the inner side. A second step portion for guiding and fitting the lid member;
The axial length of the required gap formed between the inner peripheral surface of the first step portion of the cylindrical member and the outer peripheral surface of the lid member is longer than the radial width of the required gap,
A sliding bearing, wherein an inner peripheral surface of the first step portion of the cylindrical member and an outer peripheral surface of the lid member are bonded with an adhesive. A tubular member;
A shaft member having a flange fitted to the tubular member so as to be relatively rotatable;
Fitted to a circumferential step formed in the opening of the cylindrical member, fixed with an adhesive, opposed to the flange in the axial direction, and formed an axial bearing portion between the flange and the circumferential step A lid member that comes into contact with a stepped surface that extends inward in the axial direction;
In a plain bearing comprising:
The circumferential step portion of the cylindrical member has a first step portion whose inner diameter is larger than the outer diameter of the lid member on the opening end side, and an inner diameter that is substantially the same as the outer diameter of the lid member on the inner side. A second step portion for guiding and fitting the lid member;
The radial width of the required gap formed between the inner peripheral surface of the first step portion of the cylindrical member and the outer peripheral surface of the lid member is set to a width that allows the adhesive to penetrate by capillary action,
A sliding bearing, wherein an inner peripheral surface of the first step portion of the cylindrical member and an outer peripheral surface of the lid member are bonded by the adhesive.   The slide bearing according to claim 1 or 2, wherein a concave portion is formed on at least one of an inner peripheral surface of the first step portion of the cylindrical member and an outer peripheral surface of the lid member.   The axial length of the adhesive layer that has permeated and hardened between the cylindrical member and the lid member is longer than the radial width of the layer. The plain bearing described in 1.

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