JP4998306B2 - Thrust needle bearing - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a thrust needle bearing which has a cage formed by combining two bent plates and is restrained from being damaged while being low in cost. <P>SOLUTION: A free end 166g of a second outer cylindrical part 166c and a free end 166h of a second inner cylindrical part 166d are bent so as not to interfere with a first holding member 165. Consequently, even if the radius of curvature of a first outer curved surface 165e and a first inner curved surface 165f is enlarged, the free ends 166g, 166h are restrained from interfering with the first outer curved surface 165e and the first inner curved surface 165f. The first holding member 165 is thereby restrained from being damaged to effectively suppress a stress concentration or the like while being low in cost. <P>COPYRIGHT: (C)2009,JPO&amp;INPIT

Description

  The present invention relates to a thrust needle bearing suitable for use in a compressor of a car air conditioner, a planetary gear mechanism for an automatic transmission, office equipment, and the like.

Thrust-needle bearings used in conventional swash plate compressors for car air conditioners, automatic transmissions for automobiles, and the like often use steel plate press cages from the viewpoint of cost and heat resistance. However, there are various types of general cages, such as those made of resin, formed by pressing a single plate, and those formed by combining two pressed plates, etc. Has been made. An example of a thrust needle bearing in which two pressed plates are used as a cage is disclosed in Patent Document 1.
JP 2000-266043 A JP 2006-207618 A

  By the way, when combining two press plates in a thrust needle bearing as shown in Patent Document 1, in each press plate, the outer peripheral flanges extending from the outer periphery and the inner peripheral flanges extending from the inner periphery are respectively radiused. Polymerized in the direction. However, since it is difficult to form the outer peripheral flanges and inner peripheral flanges in parallel, depending on the accuracy of the parts, the tip of one outer flange abuts the root of the other outer flange, or There is a possibility that the tip of one inner peripheral flange contacts the base of the other inner peripheral flange.

  Here, since the stress at the base of the outer peripheral flange or inner peripheral flange is relatively high, a fine scratch (notch) is caused by the tip of the outer peripheral flange or inner peripheral flange on the other side contacting the base of the outer peripheral flange or inner peripheral flange. If this occurs, there is a concern about excessive stress due to stress concentration. In order to prevent such scratches, it is necessary to take measures such as strictly controlling the dimensions of the two press plates and increasing the number of other processes such as chamfering the flange tip, which may increase the cost.

  On the other hand, Patent Document 2 is a combination of two folded plates, and the first flange portion is bent so as to form a step portion with which the tip of the second flange portion abuts. A cage is formed. According to such a cage, the tip of the second flange portion does not come into contact with the root of the first flange portion, and no flaw is formed here. Stress concentration can be avoided. On the other hand, the tip of the second flange portion is in contact with the step portion of the first flange portion. However, since the stress is lower than the root of the first flange portion, excessive stress due to stress concentration is generated even if flaws are formed. The fear is low.

  However, the cage of Patent Document 2 has such excellent characteristics, but there is a problem that the bending of the first flange portion becomes complicated and the cost increases. Further, in order to make the cage thin, it is necessary to reduce the radius of curvature of the bent portion of the first flange portion. However, if the radius of curvature is excessively small, stress concentration may easily occur. .

  The present invention has been made in view of the above-described problems, and has a cage formed by combining two bent plate materials, and is a low-cost thrust needle bearing capable of suppressing scratches. The purpose is to provide.

The thrust needle bearing of the present invention is a thrust needle bearing comprising a roller and a cage for holding the roller.
The cage is a combination of a first holding member and a second holding member formed by bending a plate material,
The first holding member includes an annular first holding portion formed with a first pocket portion for holding the rollers, a first outer cylindrical portion extending in an axial direction from an outer peripheral edge of the first holding portion, The first inner cylindrical portion extending in the axial direction from the inner peripheral edge of the first holding portion, the first holding portion and the first outer cylindrical portion, and the joining of the first holding portion and the first inner cylindrical portion. And an R portion having a predetermined radius of curvature in the axial cross section ,
The second holding member includes an annular second holding portion formed with a second pocket portion for holding the roller, a second outer cylindrical portion extending in an axial direction from an outer peripheral edge of the second holding portion, A second inner cylindrical portion extending in the axial direction from the inner peripheral edge of the second holding portion;
When the first holding member and the second holding member are combined to face each other, the second outer cylindrical portion is disposed radially inside the first outer cylindrical portion, and the second inner cylindrical portion is Disposed radially outward of the first inner cylindrical portion,
A free end of the second outer cylindrical portion is bent radially inward so as not to interfere with the R portion between the first holding portion and the first outer cylindrical portion, and the first outer cylindrical portion Is not in contact with
The free end of the second inner cylindrical part is bent radially outward so as not to interfere with the R part between the first holding part and the first inner cylindrical part, and the first inner cylindrical part It is characterized by not contacting .

Since the first holding member is formed by bending a plate material, a curved surface (R) must be provided at the joint between the first holding portion, the first outer cylindrical portion, and the first inner cylindrical portion. ) Part occurs. According to the present invention, the free end of the second outer cylindrical part is bent radially inward so as not to interfere with the R part between the first holding part and the first outer cylindrical part, The second outer cylindrical portion is not in contact with the first outer cylindrical portion, and the free end of the second inner cylindrical portion has a radius so as not to interfere with the R portion between the first holding portion and the first inner cylindrical portion. Since it is bent outward in the direction and is not in contact with the first inner cylindrical part, even when the radius of curvature of the R part is increased, the free end is prevented from interfering with the R part, and the cost is low. However, it is possible to effectively suppress stress concentration and the like by suppressing scratching of the first holding member.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. FIG. 1 is a cross-sectional view of a compressor of a car air conditioner in which a thrust needle bearing according to the present embodiment is incorporated, and FIG. 2 is a view of the configuration of FIG. 1 viewed in the direction of arrow II.

  In FIG. 1, a housing 6 constituting the compressor 1 includes a central short cylindrical body 7 sandwiched between a head case 8 and a swash plate case 9 from both sides in the axial direction (left-right direction in FIG. 1). It is united by coupling bolts (not shown). Inside the head case 8, low-pressure chambers 10 and 10 and a high-pressure chamber 11 are provided. Note that not only the inside of the high pressure chamber 11 but also the inside of the low pressure chambers 10 and 10 are positive. A flat partition plate 12 is sandwiched between the main body 7 and the head case 8. The low-pressure chambers 10 and 10 represented as being divided into a plurality of parts in FIG. 1 communicate with each other and communicate with a single suction port 13 (FIG. 2) provided on the outer surface of the head case 8. . The high pressure chamber 11 communicates with a discharge port (not shown) provided in the head case 8. The suction port 13 communicates with the outlet of an evaporator (not shown), and the discharge port (not shown) communicates with the inlet of a condenser (not shown).

  A shaft 14 is rotatably supported in the housing 6 in a state of being spanned between the main body 7 and the swash plate case 9. More specifically, both ends of the shaft 14 are rotatably supported with respect to the main body 7 and the swash plate case 9 by a pair of radial needle bearings 15A and 15B, and a pair of thrust needle bearings 16A and 160. Thus, the thrust load applied to the shaft 14 can be supported freely.

  The thrust needle bearing 16A has a plurality of rollers 16a, raceways 16b and 16c that clamp the rollers 16a in the axial direction (left and right in FIG. 1), and a cage 16d that holds the rollers 16a. A thrust needle bearing 160 according to the present embodiment includes a plurality of rollers 161, race rings 162 and 163 that sandwich the rollers 161 in the axial direction (left and right direction in FIG. 1), and a cage 164 that holds the rollers 161. is doing.

  The radial needle bearing 15A has a plurality of rollers 15a, a shell-type outer ring 15b, and a cage 15c that holds the rollers 15a. The radial needle bearing 15B includes a plurality of rollers 15d, an outer ring (track ring) 15e, and a cage 15f that holds the rollers 15d.

  The thrust needle bearing 16A is provided via a disc spring 18 between a part of the main body 7 and a step portion 17 formed at one end portion (right end side in FIG. 1) of the shaft 14. The thrust needle bearing 160 is disposed between the disc portion 19 and the swash plate case 9 that are fitted and fixed to the outer peripheral surface of the intermediate portion of the shaft 14. A plurality of (for example, six in the example shown in the figure in the circumferential direction) cylinder holes 20, 20 are formed in the periphery of the shaft 14 inside the main body 7 constituting the housing 6. Sliding portions 22, 22 provided in the front half (right half in FIG. 1) of the pistons 21, 21 are respectively provided inside the plurality of cylinder holes 20, 20 formed in the main body 7 in this manner. It is fitted so that it can be displaced in the direction.

  Here, a space provided between the bottom surfaces of the cylinder holes 20 and 20 and the tip surfaces (right end surfaces in FIG. 1) of the pistons 21 and 21 is referred to as a compression chamber 23. The space existing inside the swash plate case 9 is a swash plate chamber 24. A swash plate 25 is fixed at a predetermined inclination angle with respect to the shaft 14 at a portion located in the swash plate chamber 24 on the outer peripheral surface of the intermediate portion of the shaft 14, and the swash plate 25 rotates together with the shaft 14. I try to do it. A plurality of locations in the circumferential direction of the swash plate 25 and the pistons 21 and 21 are connected by a pair of sliding shoes 26 and 26, respectively. For this reason, the inner side surfaces (surfaces facing each other) of these sliding shoes 26 and 26 are flat surfaces so as to be in sliding contact with portions on both side surfaces of the swash plate 25 that are also flat surfaces. Further, the outer side surfaces of these sliding shoes 26, 26 (side surfaces opposite to the mating sliding shoe 26) are spherical convex surfaces. Further, the outer surfaces of the sliding shoes 26 and 26 are positioned on a single spherical surface with the inner surface thereof being in contact with both side surfaces of the swash plate 25. On the other hand, a driving force transmission mechanism is constructed with sliding shoes 26 and 26 and a swash plate 25 at the base end of each piston 21 and 21 (the end far from the partition plate 12 and the left end in FIG. 1). The connecting portions 27 and 27 are formed integrally with the pistons 21 and 21, respectively. The connecting portions 27 and 27 are formed with holding portions 28 and 28 for holding the pair of sliding shoes 26 and 26. The holding portions 28 and 28 are formed with spherical concave surfaces that are in close sliding contact with the outer surfaces of the sliding shoes 26 and 26 so as to face each other.

  Further, a pair of guide surfaces (not shown) for each piston 21, 21 is provided on the part of the inner peripheral surface of the main body 7 that is aligned with the outer end of each connecting portion 27, 27. They are spaced apart in the circumferential direction. The outer end portions of the connecting portions 27 and 27 are guided by the guide surfaces, and can only be displaced in the axial direction of the pistons 21 and 21 (left and right direction in FIG. 1). Therefore, the pistons 21 and 21 are also prevented from rotating around the central axis of the pistons 21 and 21 in the cylinder holes 20 and 20 due to the rotation of the swash plate 25, and can only be displaced in the axial direction (non-rotatable). ). As a result, the connecting portions 27 and 27 push and pull the pistons 21 and 21 in the axial direction as the swash plate 25 is oscillated and displaced by the rotation of the shaft 14. , 20 to reciprocate in the axial direction.

  On the other hand, in order to partition the low-pressure chamber 10 and the high-pressure chamber 11 from the cylinder holes 20, 20, the partition plate 12 sandwiched between the abutting portions of the main body 7 and the head case 8 includes the low-pressure chamber 10 and the cylinder holes 20. , 20 and the discharge holes 30, 30 communicating with the high-pressure chamber 11 and the cylinder holes 20, 20 are formed in a state of penetrating in the axial direction. Accordingly, the opening on the cylinder hole 20, 20 side at one end (the left end in FIG. 1) of each suction hole 29, 29 and each discharge hole 30, 30 is opposed to the tip surface of each piston 21, 21. In addition, a reed valve type suction that allows refrigerant gas to flow only from the low-pressure chamber 10 toward each cylinder hole 20, 20 in a part of each cylinder hole 20, 20 facing one end of each suction hole 29, 29. Valves 31 are provided. Further, in the high-pressure chamber 11, the refrigerant gas is allowed to flow only from the cylinder holes 20, 20 toward the high-pressure chamber 11 in the portion facing the other end (right end in FIG. 1) opening of each discharge hole 30, 30. A reed valve type discharge valve 32 is provided. The discharge valve 32 is provided with a stopper 33 that restricts displacement in a direction away from the discharge holes 30.

  The shaft 14 of the compressor 1 configured as described above is rotationally driven via an endless belt 42 by a vehicle engine (not shown). For this reason, in the case of the illustrated example, the driven pulley 35 around the support cylinder portion 34 provided in the center of the outer surface (left side surface in FIG. 1) of the swash plate case 9 constituting the housing 6 is connected to a double row radial ball. The bearing 36 is rotatably supported. The driven pulley 35 has a U-shaped cross section and is formed in an annular shape as a whole. A solenoid 37 fixed to the outer surface of the swash plate case 9 is disposed in the internal space of the driven pulley 35. On the other hand, a mounting bracket 38 is fixed to a portion protruding from the support cylinder portion 34 at the end of the shaft 14, and an annular plate 39 made of a magnetic material is supported around the mounting bracket 38 via a plate spring 40. is doing. When the solenoid 37 is not energized, the annular plate 39 is separated from the driven pulley 35 by the elastic force of the leaf spring 40 as shown in the figure. However, when the solenoid 37 is energized, the annular plate 39 is attracted toward the driven pulley 35. The rotational force from the driven pulley 35 to the shaft 14 can be freely transmitted. That is, the solenoid 37, the annular plate 39, and the leaf spring 40 constitute an electromagnetic clutch 41 for engaging and disengaging the driven pulley 35 and the shaft 14. Further, an endless belt 42 is stretched between a driving pulley and a driven pulley 35 fixed to an end of a crankshaft (not shown) of a vehicle engine.

  The operation of the compressor of the car air conditioner according to the present embodiment will be described. When the car air conditioner is operated to cool or dehumidify the passenger compartment, the electromagnetic clutch 41 is operated to engage the driven pulley 35 and the shaft 14, thereby causing the vehicle to pass through the endless belt 42. The power of the engine is transmitted to the shaft 14 and is driven to rotate. As a result, the swash plate 25 rotates to reciprocate the sliding portions 22 and 22 constituting the plurality of pistons 21 and 21 in the cylinder holes 20 and 20, respectively. As the sliding portions 22 and 22 reciprocate, the refrigerant gas sucked from the suction port 13 is sucked into the compression chamber 23 from the low pressure chambers 10 and 10 through the suction holes 29 and 29. . The refrigerant gas is compressed in each of the compression chambers 23 and then sent to the high-pressure chamber 11 through the discharge holes 30 and 30 and is discharged from the discharge port. After that, the high-temperature and high-pressure refrigerant gas is cooled by a condenser to become a liquid refrigerant, and then rapidly expanded to flow into the evaporator as a low-temperature and low-pressure mist refrigerant, where the air supplied to the passenger compartment After cooling, the refrigerant gas is sucked into the compressor.

  FIG. 3 is a front view of the thrust needle bearing 160 with the raceway removed. It is sectional drawing of the thrust needle bearing 160 concerning this Embodiment. In FIG. 3, the cage 164 is formed by combining a first holding member 165 and a second holding member 166 that are formed by bending a single plate material by pressing.

  The first holding member 165 includes an annular first holding portion 165b in which first pocket portions 165a for holding the rollers 161 are formed at equal intervals in the circumferential direction, and an axial direction extending from the outer periphery of the first holding portion 165b. The first outer cylindrical portion 165c is present, and the first inner cylindrical portion 165d extends in the axial direction from the inner peripheral edge of the first holding portion 165b. A joint portion between the first holding portion 165b and the first outer cylindrical portion 165c is a first outer curved surface portion 165e having a predetermined radius of curvature R in cross section, and the first holding portion 165b and the first inner cylindrical portion 165d. Is a first inner curved surface portion 165f having a predetermined radius of curvature R in cross section.

  On the other hand, the second holding member 166 includes an annular second holding portion 166b in which second pocket portions 166a for holding the rollers 161 are formed at equal intervals in the circumferential direction, and an axial direction from the outer peripheral edge of the second holding portion 166b. And a second outer cylindrical portion 166c extending in the axial direction from the inner peripheral edge of the second holding portion 166b. The joint between the second holding portion 166b and the second outer cylindrical portion 166c is a second outer curved surface portion 166e having a predetermined radius of curvature R in cross section, and the second holding portion 166b and the second inner cylindrical portion 166d. Is a second inner curved surface portion 166f having a predetermined radius of curvature R in cross section. Here, the free end 166g of the second outer cylindrical portion 166c is angled and bent radially inward, and the free end 166h of the second inner cylindrical portion 166d is bent and bent radially outward. Each of them is not in contact with the first holding member 165.

  The free end 165h of the first inner cylindrical portion 165d is plastically deformed radially outward by caulking after assembling the first holding member 165 and the second holding member 166, thereby forming the second inner curved surface portion 166f. It goes around and comes into close contact. Thereby, separation of the first holding member 165 and the second holding member 166 is prevented. However, even if the free end 165g of the first outer cylindrical portion 165c is plastically deformed radially inward by caulking instead of the free end 165h, the first holding member 165 and the second holding member 166 are similarly separated. Needless to say, is blocked. In such a caulking, the cage can be deformed, but interference can be suppressed by bending the free end of the second holding member 166 as in the present invention.

  FIG. 4 is a cross-sectional view similar to FIG. 3 of a thrust needle bearing 160 'shown as a comparative example. The thrust needle bearing 160 ′ is different from the embodiment shown in FIG. 3 in that the free end 166g ′ of the second outer cylindrical portion 166c ′ and the second inner cylindrical portion 166d of the second holding member 166 ′ of the cage 164 ′. The only difference is that the 'free end 166h' is not bent and is straight. According to this comparative example, the free end 166g ′ of the straight-shaped second outer cylindrical portion 166c ′ and the free end 166h ′ of the second inner cylindrical portion 166d ′ have broken surfaces due to cutting, so that an edge or the like is formed. If formed, the first outer curved surface portion 165e and the first inner curved surface portion 165f of the first holding member 165 facing each other may be damaged, which may cause stress concentration.

  On the other hand, according to the present embodiment, the free end 166g of the second outer cylindrical portion 166c and the free end 166h of the second inner cylindrical portion 166d are bent so as not to interfere with the R portion of the first holding member 165, respectively. Therefore, even if there is interference, in this case, the straight portion 165b is formed, so that the stress concentration and the like can be effectively suppressed by suppressing the scratch of the R portion of the first holding member 165 while being low in cost. .

  The present invention has been described above with reference to the embodiments. However, the present invention is not limited to the above-described embodiments, and can of course be changed or improved within the scope of the invention. For example, simply bending one of the free end 166g of the second outer cylindrical portion 166c and the free end 166h of the second inner cylindrical portion 166d is effective. Furthermore, the present invention is applicable not only to a car cooler compressor but also to various machines such as an automobile transmission and office equipment.

It is sectional drawing of the compressor of the car air conditioner in which the needle bearing concerning this Embodiment was integrated. It is the figure which looked at the structure of FIG. 1 in the arrow II direction. It is a front view of the thrust needle bearing 160 shown in the state where a bearing ring was removed. FIG. 4 is a cross-sectional view similar to FIG. 3 of a thrust needle bearing 160 ′ shown as a comparative example.

Explanation of symbols

1 Car Air Conditioner Compressor 6 Housing 14 Shaft 15A, 15B Radial Needle Bearing 16A, 160 Thrust Needle Bearing

Claims (1)

In a thrust needle bearing comprising a roller and a cage for holding the roller,
The cage is a combination of a first holding member and a second holding member formed by bending a plate material,
The first holding member includes an annular first holding portion formed with a first pocket portion for holding the rollers, a first outer cylindrical portion extending in an axial direction from an outer peripheral edge of the first holding portion, The first inner cylindrical portion extending in the axial direction from the inner peripheral edge of the first holding portion, the first holding portion and the first outer cylindrical portion, and the joining of the first holding portion and the first inner cylindrical portion. And an R portion having a predetermined radius of curvature in the axial cross section ,
The second holding member includes an annular second holding portion formed with a second pocket portion for holding the roller, a second outer cylindrical portion extending in an axial direction from an outer peripheral edge of the second holding portion, A second inner cylindrical portion extending in the axial direction from the inner peripheral edge of the second holding portion;
When the first holding member and the second holding member are combined to face each other, the second outer cylindrical portion is disposed radially inside the first outer cylindrical portion, and the second inner cylindrical portion is Disposed radially outward of the first inner cylindrical portion,
A free end of the second outer cylindrical portion is bent radially inward so as not to interfere with the R portion between the first holding portion and the first outer cylindrical portion, and the first outer cylindrical portion Is not in contact with
The free end of the second inner cylindrical part is bent radially outward so as not to interfere with the R part between the first holding part and the first inner cylindrical part, and the first inner cylindrical part A thrust needle bearing characterized in that it is not in contact with the thrust needle bearing.

Images