JP4206883B2 - Thrust roller bearing for swash plate compressor - Google Patents

Description

  The present invention relates to a thrust roller bearing for a swash plate compressor, and more particularly to a thrust roller bearing provided between a swash plate and a cylinder of a swash plate compressor. The swash plate compressor is used as, for example, an air conditioner compressor.

In a swash plate type compressor, there is a thrust roller bearing provided between a swash plate and a cylinder using a cage having a undulating shape in the radial direction (see, for example, Patent Document 1). This cage is manufactured by press molding or the like, and the outer peripheral surface of the outer diameter side annular portion and the inner peripheral surface of the inner diameter side annular portion of the cage are flat surfaces substantially parallel to the axis of the cage. Yes.
JP-A-11-351246

  In the swash plate compressor, when the lubricating oil is supplied to the outer diameter side or inner diameter side of the cage, the lubricating oil is rebounded by the flat surface of the outer diameter side annular portion or the inner diameter side annular portion of the cage. As a result, it becomes difficult for the lubricating oil to pass through, for example, because it tends to stay.

The present invention is a thrust roller bearing provided between a swash plate and a cylinder of a swash plate compressor, and includes a cage having pockets for holding rollers at a plurality of circumferential positions. a diameter annular portion, and the inner diameter side annular section, which has been formed in the section M-shaped by a single plate material and a pillar portion provided in the circumferential direction a plurality of locations between the two annular portions, the column portion The radial intermediate portion or both radial end portions are a race guide that is in sliding contact with a race arranged on the cylinder side or a race arranged on the swash plate side, and the outer diameter side annular portion and the inner diameter side annular portion The axial dimensions L1 and L2 are smaller than the axial width W of the column portion, and the outer peripheral surface of the outer diameter side annular portion is tapered as an inclined surface inclined with respect to the axis of the cage. It is characterized by having a surface
In another embodiment of the present invention, a tapered surface is provided on the inner peripheral surface of the inner diameter side annular portion as an inclined surface inclined with respect to the axis of the cage. In still another aspect of the present invention, the outer peripheral surface of the outer diameter side annular portion is a spherical surface that gradually decreases in diameter from the center in the axial direction toward both axial ends, or the inner peripheral surface of the inner diameter side annular portion is a shaft. The spherical surface gradually increases in diameter from the center in the direction toward both ends in the axial direction.

The tapered surface or the spherical surface may be formed in the entire axial length of the outer diameter side annular portion or the inner diameter side annular portion, or may be partially formed in a predetermined length range in the axial direction.

In this case, if a tapered surface or a spherical surface is provided on the outer peripheral surface of the outer diameter side annular portion of the cage, for example, when lubricating oil is supplied to the outer diameter side of the cage, the lubricating oil is removed from the outer diameter side annular portion. It becomes easy to go around the outer diameter side annular portion by the inclined surface and pass to the inner diameter side of the cage. If a tapered surface or a spherical surface is provided on the inner peripheral surface of the inner diameter side annular portion of the cage, when the lubricating oil is supplied to the inner diameter side of the cage, the lubricating oil is annularly formed by the inclined surface of the inner diameter side annular portion. It becomes easy to pass through the part to the outer diameter side of the cage.

  The retainer is a race guide in which a radial intermediate portion or both radial end portions of the pillar portion are in sliding contact with a race arranged on the cylinder side or a race arranged on the swash plate side, and the outer diameter The axial dimensions L1 and L2 of the side annular part and the inner diameter side annular part may be made smaller than the axial width W of the column part.

  In this case, since the cage is a race guide, it is difficult for the cage to interfere with the cage, and the rolling resistance of the rollers is reduced. Furthermore, since the axial dimension of the outer diameter side annular part and the inner diameter side annular part of the cage is smaller than the axial width of the column part, the clearance between the outer diameter side annular part and the race is widened and lubricated. It makes it easier for oil to pass through. Moreover, even if the two races that serve as the roller raceways are bent by applying preload, the outer diameter side annular portion and the inner diameter side annular portion of the cage are less likely to interfere with both races.

  Since the thrust roller bearing for the swash plate compressor according to the present invention can increase the amount of lubricating oil passing through, it can improve wear resistance and seizure resistance and contribute to stabilization of the bearing function and longer life.

  The best embodiment according to the present invention will be described with reference to the drawings. 1 is a cross-sectional view of a swash plate compressor, FIG. 2 is an enlarged view of the main part of FIG. 1, FIG. 3 is an enlarged view of part A of FIG. 2, and FIG. FIG. 5 is a sectional view showing a retainer of a thrust roller bearing, FIG. 6 is a sectional view taken along line (6)-(6) in FIG. 5, and FIG. 6 is an operation explanatory view of the cage 6; FIG.

  As shown in FIG. 1, the swash plate compressor 1 has a slant plate compressor 1 in which a single piston 4 is inserted across two cylinders 2 and 3 aligned in the axial direction, and the piston 4 is integrally attached to a rotary shaft 5. The configuration is such that the plate 6 is engaged, and the swash plate 6 reciprocates the piston 4 in the axial direction by rotating the rotary shaft 5.

  Thrust roller bearings 7 and 7 are interposed between the boss portions 2 a and 3 a of the two cylinders 2 and 3 and the boss portion 6 a of the swash plate 6.

  The thrust roller bearing 7 holds the first and second races 10 and 11 disposed opposite to each other in the axial direction, a plurality of rollers 12 interposed between the races 10 and 11, and each roller 12. And a cage 13 arranged at equal intervals around the circumference.

  The cage 13 has an M-shaped cross section, and is provided with pockets 13a for accommodating the rollers 12 at a plurality of locations in the circumferential direction, and an annular portion 13b on the outer diameter side disposed concentrically. And an annular portion 13c on the inner diameter side, and a column portion 13d that spans between the annular portions 13b and 13c. The bent portions of the annular portions 13b and 13c and the column portion 13d are rounded.

  In each pillar portion 13d, the radial intermediate portion 13d1 has a retaining projection 13e protruding in the circumferential direction, and the radial end portions 13d2 and 13d3 have a retaining projection 13f protruding in the circumferential direction. Is provided. The retaining projections 13e of the two column portions 13d adjacent to each other in the circumferential direction prevent the roller 12 from slipping out from the pocket 13a to one side in the axial direction of the cage 13, and the two column portions 13d adjacent to each other in the circumferential direction. , 13d prevents the roller 12 from slipping out of the pocket 13a to the other axial direction of the cage 13 by the retaining protrusions 13f.

  In this embodiment, the outer peripheral surface of the outer diameter side annular portion 13b in the retainer 13 has a spherical shape that gradually decreases in diameter from the center in the axial direction toward both axial ends, and the inner periphery of the inner diameter side annular portion 13c in the retainer 13 The surface has a spherical shape that gradually increases in diameter from the axial center toward both axial ends. The curvature radii R1 and R2 in the case of the spherical shape are arbitrary.

  Such a cage 13 can be manufactured, for example, by press forming a steel plate.

  Thus, if the outer peripheral surface of the outer diameter side annular portion 13b has a spherical shape, for example, when lubricating oil is supplied to the outer diameter side of the cage 13, as shown by an arrow X in FIG. Oil goes around the outer diameter side annular portion 13 b of the cage 13 and easily passes to the inner diameter side of the cage 13. On the other hand, if the inner peripheral surface of the inner diameter side annular portion 13c has a spherical shape, for example, when the lubricating oil is supplied to the inner diameter side of the cage 13, the lubricating oil is retained as shown by the arrow Y in FIG. In addition to going around the inner diameter side annular portion 13c of the vessel 13 and easily passing to the outer diameter side of the cage 13, it is advantageous for reducing the frictional resistance when sliding on the outer peripheral surface of the rotating shaft 5. Therefore, the wear resistance and seizure resistance of the thrust roller bearing 7 are improved, which can contribute to stabilization of the bearing function and longer life.

  By the way, on the inner diameter side of the inner end surfaces of the boss portions 2a, 3a of the two cylinders 2, 3, there are annular convex portions 2b, 3b as receiving seats, and outer diameters at both end surfaces of the boss portion 6a of the swash plate 6. On the side, annular protrusions 6b and 6c are provided as receiving seats. The annular protrusions 2 b and 3 b of the cylinders 2 and 3 are on the inner diameter side on the outer surface of the first race 10, and the annular protrusions 6 b and 6 c of the boss portion 6 a of the swash plate 6 are on the outer surface of the second race 11. The thrust roller bearing 7 is applied with a preload consisting of a required axial load by assembling the first race 10 and the second race 11 in a state where they are pressed against each other in the direction in which they are brought close to each other. ing.

  By applying this preload, both the races 10 and 11 are bent into a substantially conical shape. Therefore, the rollers 12 are crowned and the retainer 13 is used as a race guide, and the outer diameter of the retainer 13 is applied to the two races 10 and 11. The side annular portion 13b and the inner diameter side annular portion 13c are less likely to interfere with each other.

  First, the outer peripheral surface of the roller 12 is crowned over its entire length in the axial direction. This crowning is called full crowning. The roller 12 may be one in which both axial end portions thereof are crowned to flatten the axial intermediate portion.

  Further, the cage 13 is used as a race guide that is guided while being in contact with one of the two races 10 and 11 during the rotation operation. There are cases where the radial intermediate portion 13d1 of the column portion 13d is guided by the first race 10 and cases where both radial end portions 13d2 and 13d3 of the column portion 13d are guided by the second race 11. As shown in FIG. 7, the race guide is a state in which each retaining projection 13 e, 13 f does not contact the roller 12 from the axial direction when the cage 13 is brought into contact with one of the two races 10, 11. become. In order to obtain such a race guide, the axial width W of the column portion 13d as shown in FIG. 5, and the roller 12 and each retaining member in a state where the roller 12 is arranged in the middle of the pocket 13a as shown in FIG. Clearances d1 and d2 between the convex portions 13e and 13f are appropriately managed. The axial width W of the column portion 13d is the radial intermediate portion (guide portion for the first race 10) 13d1 of the column portion 13d and both radial end portions (guide portions for the second race 11) 13d2 and 13d3 of the column portion 13d. It is the interval between. However, with regard to the conditions for establishing the race guide, the axial width W of the column portion 13 may be increased. However, the larger the axial width W is, the more the lubricating oil passage amount is limited. Therefore, as a condition for establishing the race guide, it is preferable to set the axial width W of the cage 13 as small as possible and increase the clearances d1 and d2.

  Further, as shown in FIG. 5, in order to make it difficult for the outer race side annular portion 13 b and the inner diameter side annular portion 13 c of the cage 13 to interfere with both the races 10, 11 in the bent state, the outer diameter of the cage 13. The axial dimensions L1 and L2 of the side annular portion 13b and the inner diameter side annular portion 13c are set to be smaller than the axial width W of the column portion 13.

  If comprised in this way, as shown in FIG. 3, in the state which bent the two races 10 and 11 of the thrust roller bearing 7, it will be in the following states. First, the edge load of the roller 12 is reduced by reducing the contact pressure at both ends in the axial direction of the roller 12 with respect to both the races 10 and 11. Further, the rollers 12 are less likely to interfere with the retaining projections 13e and 13f of the cage 13, and the rolling resistance of the rollers 12 is reduced. Further, the outer diameter side annular portion 13b and the inner diameter side annular portion 13c of the retainer 13 are less likely to interfere with both the races 10 and 11 in the bent state, thereby reducing the bearing torque. However, even if the outer diameter side annular portion 13b interferes with the second race 11, since the base side bent portion of the outer diameter side annular portion 13b is rounded, generation of edge load and wear can be suppressed. .

  Hereinafter, other embodiments of the present invention will be described.

The inner peripheral surface of the outer or inner diameter side annular portion 13c of the radially outer annular portion 13b of the retainer 13 described above, or a surface inclined relative to the axis of the hold 13, from the axial center to the axial end It can be made into the V-shaped convex surface which inclines toward.

Sectional drawing of the swash plate type compressor using the thrust roller bearing which concerns on the best embodiment of this invention. Enlarged view of the main part of FIG. The figure which expanded the A section of FIG. The perspective view which isolate | separates and shows the roller and cage | basket of the thrust roller bearing of FIG. Sectional drawing which shows the retainer of the thrust roller bearing of FIG. FIG. 5 (6)-(6) cross-sectional view taken along the line Operational explanatory diagram of the cage of FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Swash plate type compressor 2, 3 Cylinder 4 Piston 6 Swash plate 7 Thrust roller bearing 10 1st race 11 2nd race 12 Roller 13 Cage 13b Outer diameter side annular part 13c Inner diameter side annular part 13d Pillar part

Claims (4)

A thrust roller bearing provided between a swash plate and a cylinder of a swash plate compressor,
A cage having pockets for holding rollers at a plurality of locations in the circumferential direction is provided, and this cage is provided at a plurality of locations in the circumferential direction between the outer diameter side annular portion, the inner diameter side annular portion, and both annular portions. The column portion is formed in an M-shaped cross section by a single plate material , and the radial intermediate portion or both radial end portions of the column portion are arranged on the race or swash plate side arranged on the cylinder side. And the axial dimensions L1 and L2 of the outer diameter side annular portion and the inner diameter side annular portion are smaller than the axial width W of the column portion, and A thrust roller bearing for a swash plate compressor, wherein a tapered surface is provided on the outer peripheral surface of the outer diameter side annular portion as an inclined surface inclined with respect to the axis of the cage. A thrust roller bearing provided between a swash plate and a cylinder of a swash plate compressor,
A cage having pockets for holding rollers at a plurality of locations in the circumferential direction is provided, and this cage is provided at a plurality of locations in the circumferential direction between the outer diameter side annular portion, the inner diameter side annular portion, and both annular portions. The column portion is formed in an M-shaped cross section by a single plate material , and the radial intermediate portion or both radial end portions of the column portion are arranged on the race or swash plate side arranged on the cylinder side. And the axial dimensions L1 and L2 of the outer diameter side annular portion and the inner diameter side annular portion are smaller than the axial width W of the column portion, and A thrust roller bearing for a swash plate compressor, wherein a taper surface is provided as an inclined surface inclined with respect to the axis of the cage on an inner peripheral surface of the inner diameter side annular portion. A thrust roller bearing provided between a swash plate and a cylinder of a swash plate compressor,
A cage having pockets for holding rollers at a plurality of locations in the circumferential direction is provided, and this cage is provided at a plurality of locations in the circumferential direction between the outer diameter side annular portion, the inner diameter side annular portion, and both annular portions. The column portion is formed in an M-shaped cross section by a single plate material , and the radial intermediate portion or both radial end portions of the column portion are arranged on the race or swash plate side arranged on the cylinder side. And the axial dimensions L1 and L2 of the outer diameter side annular portion and the inner diameter side annular portion are smaller than the axial width W of the column portion, and An oblique surface characterized in that a spherical surface that gradually decreases in diameter from the axial center to both axial ends is provided on the outer peripheral surface of the outer diameter side annular portion as an inclined surface that is inclined with respect to the axis of the cage. Thrust roller bearing for plate compressor. A thrust roller bearing provided between a swash plate and a cylinder of a swash plate compressor,
A cage having pockets for holding rollers at a plurality of locations in the circumferential direction is provided, and this cage is provided at a plurality of locations in the circumferential direction between the outer diameter side annular portion, the inner diameter side annular portion, and both annular portions. The column portion is formed in an M-shaped cross section by a single plate material , and the radial intermediate portion or both radial end portions of the column portion are arranged on the race or swash plate side arranged on the cylinder side. And the axial dimensions L1 and L2 of the outer diameter side annular portion and the inner diameter side annular portion are smaller than the axial width W of the column portion, and An inclined surface characterized in that a spherical surface that gradually increases in diameter from the center in the axial direction toward both ends in the axial direction is provided on the inner peripheral surface of the annular portion on the inner diameter side as an inclined surface that is inclined with respect to the axis of the cage. Thrust roller bearing for plate compressor.

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