JP4508591B2 - Compressor spindle support structure - Google Patents

Description

  The present invention relates to a support structure for a compressor main shaft and a needle roller bearing for the compressor main shaft.

  Some compressors for air conditioners and the like employ a support structure in which a compression operation member is operated by rotating a main shaft and a radial load of the main shaft is supported by needle roller bearings arranged in the compressor ( For example, see Patent Document 1.) Needle roller bearings have the advantage that high load capacity and high rigidity can be obtained for a small bearing projection area, and the support structure for the compressor main shaft can be designed compactly.

  The needle roller bearing employed in the compressor main shaft support structure has a thin lubrication state due to the mixture of refrigerant and the main shaft rotates at a high speed, so that the needle roller rotates on the inner diameter surface of the outer ring on which the needle roller rolls. Surface damage such as smearing and surface-origin type peeling may occur and the bearing life may be shortened. Further, in an air conditioner compressor for an automobile, it is required to reduce the noise during use of the bearing accompanying the rolling of the needle rollers.

  On the other hand, some needle roller bearings in which a plurality of needle rollers are arranged along the inner diameter surface of the outer ring use a shell-type outer ring formed by press working including a drawing process. Shell-type needle roller bearings that use this shell-type outer ring have a wide range of uses because of their economic advantage that their manufacturing costs are low, and they are also used in the support structure for compressor main shafts, including those used for automotive air conditioners. Has been.

  A schematic process for pressing a conventional shell-type outer ring is as follows. First, a circular blank is formed into a cup shape in the drawing step, and the cup bottom corner portion is determined and pushed to a predetermined corner radius in the decision pushing step. After that, the center portion of the cup bottom is punched out in the bottoming step to form one ridge of the outer ring, and the upper end portion of the cup is trimmed to a uniform height in the trimming step. An ironing process may be added after the drawing process or the final pressing process. Usually, these press processes are performed using a transfer press or a progressive press, and when a transfer press is used, a blank blank punching process is often incorporated together. The other collar of the outer ring is formed by bending the upper end of the cup inward in the assembly process after heat treatment.

  For the blank material of the shell type outer ring, a steel plate made of case-hardened steel such as SCM415 is used, and heat treatment such as carburizing and quenching and tempering is performed after press working in order to ensure a predetermined product strength. Case-hardened steel has a high carbon content compared to mild steel such as SPCC and has a low r value, which is a standard for drawability, so the number of draws in the drawing process can be divided into multiple draws. The ratio is set small.

  In this way, the shell type outer ring is formed through a number of press working processes, so the roundness of the cylindrical part, the amount of uneven thickness, etc., due to the accuracy error of the mold and the accumulation of non-uniform strain for each working process The dimensional accuracy of the bearing is inferior to that of the outer ring formed by cutting, and the life of the bearing is shortened.

  For the purpose of improving the life of such a shell type needle roller bearing, heat treatment of the shell type outer ring is performed after the assembly of the bearing, and this heat treatment is further quenched and tempered after carbonitriding. There is a manufacturing method of a shell-type needle roller bearing in which the outer diameter roundness is increased and the strength of each bearing part is increased (see, for example, Patent Document 2).

Japanese Patent No. 2997074 (2nd page, Fig. 10-12) Japanese Patent No. 3073937 (page 1-2, Fig. 1-3)

  The manufacturing method of the shell-type needle roller bearing described in Patent Literature 2 can reduce the thermal strain of the shell-type outer ring and increase its outer diameter roundness by performing heat treatment after the bearing is assembled. Since the pressing process of the shell type outer ring is the same as the conventional one, the roundness of the inner diameter and the thickness deviation of the cylindrical portion are not improved so much. Incidentally, the roundness of the inner diameter of a conventional shell type outer ring is 15 to 40 μm when the inner diameter is about 25 mm, and exceeds 10 μm even with the manufacturing method described in Patent Document 2. Further, the amount of uneven thickness of the cylindrical portion is 10 to 20 μm with an inner diameter of about 25 mm including the manufacturing method described in Patent Document 2.

  For this reason, in the case of a shell needle roller bearing used for a support structure of a compressor main shaft for an air conditioner or the like in which use conditions including lubrication are very strict, even if the manufacturing method described in Patent Document 2 is used, A sufficiently long life has not been achieved.

  In addition, the shell-type outer ring formed by press working has a surface roughness that is rougher than that of the outer ring formed by cutting. Normally, the surface roughness of the inner diameter surface of the outer ring formed by shaving is about Ra 0.05 μm, whereas the surface roughness of the inner diameter surface of the shell type outer ring is about Ra 0.4 μm. For this reason, the conventional shell-type needle roller bearings have high acoustics during use due to the rolling of the needle rollers on the inner diameter surface, and are particularly used for applications that severely dislike noise generation, such as automobile air conditioners. There is a problem that cannot be applied to the support structure of the compressor main shaft.

  Accordingly, an object of the present invention is to extend the life of a shell needle roller bearing used for a support structure for a compressor main shaft and to reduce the sound level during use.

  In order to solve the above-described problems, the compressor main shaft support structure according to the present invention is a needle roller bearing in which a compression operation member of a compressor is operated by rotation driving of the main shaft, and the radial load of the main shaft is disposed in the compressor. In the supporting structure of the supporting compressor main shaft, the needle roller bearing is a shell needle roller bearing in which a plurality of needle rollers are arranged along an inner diameter surface of a shell type outer ring formed by pressing, and the outer ring A configuration in which the circumferential surface roughness of the inner diameter surface is restricted to a numerical value range of Ra 0.05 to 0.3 μm was adopted.

  The lower limit of the circumferential surface roughness of the outer ring inner diameter surface is set to Ra 0.05 μm because the circumferential surface roughness becomes finer than this and the inner surface becomes too smooth, the elasticity of the needle roller that rolls. This is because less lubricating oil is retained in the contact area, and surface damage such as smearing is likely to occur. The reason why the upper limit of the circumferential surface roughness is set to Ra 0.3 μm is as follows.

  The present inventor conducted an acoustic measurement test using a rotary tester on a shell-type needle roller bearing in which the surface roughness of the inner surface of the shell-type outer ring was changed, and the bearing was obtained by reducing the circumferential surface roughness of the inner surface. As shown in FIG. 5 later, it has been confirmed that if this is set to Ra 0.3 μm or less, the sound level can be sufficiently applied to bearings for strictly required applications. did.

  It is considered as follows that the circumferential surface roughness of the inner diameter surface is particularly effective in reducing the sound level. That is, when the irregularities (circumferential surface roughness) in the rotation direction of the rollers with respect to the roller diameter of the needle rollers become rougher than a certain level, the vertical vibrations of the needle rollers increase and a large sound is generated. Since the roller diameter of the needle roller is relatively small, it is considered that a large sound is generated when the circumferential surface roughness exceeds Ra 0.3 μm.

  The compressor main shaft support structure according to the present invention is a compressor main shaft support structure in which a compression operation member of a compressor is operated by rotation of the main shaft, and a radial load of the main shaft is supported by a needle roller bearing disposed in the compressor. The needle roller bearing is a shell needle roller bearing in which a plurality of needle rollers are arranged along the inner diameter surface of a shell type outer ring formed by pressing, and the inner ring roundness of the outer ring is 10 μm or less. The configuration restricted to the numerical range of was also adopted.

  The numerical range of the inner ring roundness of the outer ring is set to 10 μm or less for the following reason. The present inventor conducted a bearing life test on a shell needle roller bearing in which the inner diameter roundness of the shell type outer ring was changed. As shown in FIG. 6 later, the inner diameter roundness and the bearing life have a good correlation. It was confirmed that when the inner diameter roundness was 10 μm or less, a sufficiently long life could be achieved even under severe use conditions.

  Furthermore, the compressor main shaft support structure of the present invention is a compressor main shaft support structure in which a compression operation member of the compressor is operated by rotational driving of the main shaft, and the radial load of the main shaft is supported by needle roller bearings arranged in the compressor. The needle roller bearing is a shell needle roller bearing in which a plurality of needle rollers are arranged along the inner diameter surface of the shell type outer ring formed by pressing, and the cylindrical portion thickness deviation of the outer ring is 10 μm. A configuration restricted to a numerical range of less than was also adopted.

  The reason why the numerical range of the cylindrical portion thickness deviation of the outer ring is less than 10 μm is as follows. The inventor conducted a bearing life test on the shell type needle roller bearing in which the amount of uneven thickness of the cylindrical portion of the shell type outer ring was changed, and as shown in FIG. It has been confirmed that when there is a good correlation and the axial thickness deviation is less than 10 μm, a sufficiently long life can be achieved even under severe use conditions.

  The reduction in the roundness of the inner diameter of the shell-type outer ring and the thickness deviation of the cylindrical portion is effective in extending the life of the bearing. This is considered to be because local wear and stress concentration on the inner surface due to rattling or the like is suppressed.

  As means for restricting at least one of the circumferential surface roughness, the inner diameter roundness, and the cylindrical part thickness deviation of the inner ring surface of the outer ring to the numerical range, a pressing process for forming the shell-type outer ring is performed. It is possible to employ a means for providing a lubrication condition in a substantially fluid lubrication condition on the outer diameter side ironing surface, which is the outer diameter surface of the outer ring in the ironing step.

  The inventor conducted a squeezing and ironing test of the SCM415 steel sheet using a press tester, and investigated the surface roughness, the inner diameter roundness, and the cylindrical part thickness deviation of the inner and outer diameter surfaces of the cup molded product. As a result, when high viscosity press working oil with excellent lubricity is applied to the die side (the outer diameter side ironing surface of the cup molded product), the surface roughness of the inner diameter surface of the cup molded product that becomes the inner diameter surface of the shell type outer ring is reduced. It has been found that the surface becomes finer than the outer diameter surface, and the inner diameter roundness and the cylindrical part thickness deviation are improved.

  First, an example of the surface roughness investigation results is shown in FIG. 10. The surface roughness of the blank material is about Ra 0.49 μm on both the front and back surfaces, whereas the surface roughness of the inner diameter surface of the cup molded product. The degree is very fine with Ra 0.15 μm. The surface roughness of the outer diameter surface of the cup molded product is Ra 0.44 μm, which is not much different from the surface roughness of the blank material. Note that the surface roughness of the inner and outer diameter surfaces of the cup molded product shown in FIG. 10 was measured in the axial direction, but the surface roughness measured in the circumferential direction was almost the same. This measurement result is opposite to that observed in normal drawing and ironing, and in normal drawing and ironing, the outer diameter surface of the cup product that is squeezed with a die has a finer surface roughness, The surface roughness is not much different from the surface roughness of the blank material.

  The results of these surveys are considered as follows. That is, the surface roughness of the outer diameter surface of the cup molded product was not much different from the surface roughness of the material. On the ironing surface on the outer diameter side of the cup molded product, the material to be processed and the die hardly contact each other. It is thought that it was in a state. In this way, when the lubrication condition on the die side is set to a substantially fluid lubrication state, there is almost no shearing force on the ironing surface on the outer diameter side caused by friction with the die, and the stress at the ironing part between the punch and the die is reduced by the plate thickness. As shown in FIG. 11, the material is uniformly reduced in thickness in the thickness direction.

  FIG. 11 shows a cross-sectional photograph of the thickness of the upper end of the cup molding. As the above estimation is verified, the upper end portion of the cup molded product in which the press working oil having excellent lubricity is applied to the die side is uniformly extended in the axial direction in the plate thickness direction. In this way, when the material is uniformly reduced in thickness in the plate thickness direction and stretched in the axial direction, the inner diameter surface of the cup molded product that comes in contact with the punch moves relative to the punch surface in the axial direction. It is considered that the surface roughness of the inner diameter surface became fine by sliding with the punch surface. On the other hand, the outer diameter surface side of the upper end portion of the cup molded product obtained by normal drawing ironing process is remarkably extended in the axial direction. This is because the outer diameter surface side of the cup molded product is preferentially reduced in thickness by the shearing force resulting from friction with the die, and the inner diameter surface side is not significantly reduced in thickness. In this way, in the normal drawing and ironing process in which the inner diameter surface side is not so thinly deformed, the inner diameter surface of the cup molded product hardly moves relative to the punch surface, so the surface roughness is not much different from that of the material.

  In the processing method in which the lubrication condition on the outer diameter side ironing surface is in a substantially fluid lubrication state, as shown in FIG. 11, the upper end surface of the cup molding is uniform in the plate thickness direction. Yield can be improved. Further, by reducing the blank diameter, the press load necessary for drawing is also reduced.

  Next, with respect to the inner diameter roundness and the cylindrical part thickness deviation, as shown in Table 1 below, it is confirmed that the inner diameter roundness is reduced to 10 μm or less and the cylindrical part thickness deviation is reduced to less than 10 μm. did. The results of these surveys are considered as follows. That is, as described above, when the die-side lubrication condition in the ironing process is substantially fluid lubricated, and the material is uniformly reduced in thickness in the thickness direction, the thickness of the cylindrical portion of the cup molded product is reduced. The inner diameter surface of the cup product that contacts the punch moves relative to the punch surface in the axial direction and is adapted to the shape of the outer diameter surface of the punch. It is considered to be retained. On the other hand, in the normal drawing and ironing process, the inner diameter side of the cup molded product does not undergo much thickness deformation and hardly moves relative to the punch surface. Not.

  A needle roller bearing for a compressor main shaft according to the present invention is a needle roller bearing for a compressor main shaft that supports a radial load of a main shaft that rotationally drives a compression operation member of the compressor within the compressor. The outer ring arranged in this manner was a shell-type outer ring formed by press working, and a configuration in which the circumferential surface roughness of the inner diameter surface of the outer ring was restricted to a numerical value range of Ra 0.05 to 0.3 μm was adopted.

  Further, the needle roller bearing for the compressor main shaft according to the present invention is the needle roller bearing for the main shaft of the compressor for supporting the radial load of the main shaft that rotationally drives the compression operation member of the compressor in the compressor. A configuration in which the outer ring arranged along the outer ring is a shell-type outer ring formed by pressing, and the inner ring roundness of the outer ring is regulated to a numerical range of 10 μm or less is also employed.

  Further, the needle roller bearing for a compressor main shaft according to the present invention is a needle roller bearing for a compressor main shaft that supports a radial load of a main shaft that rotationally drives a compression operation member of the compressor within the compressor. A configuration in which the outer ring arranged along the outer ring is a shell-type outer ring formed by press working, and the thickness deviation of the cylindrical portion of the outer ring is regulated to a numerical range of less than 10 μm is also employed.

  The support structure of the compressor main shaft according to the present invention is a shell-type needle in which a plurality of needle rollers are arranged along an inner diameter surface of a shell-type outer ring formed by pressing a needle roller bearing that supports a radial load of the compressor main shaft. Since the surface roughness in the circumferential direction of the inner diameter surface of the shell type outer ring is restricted to a numerical value range of Ra 0.05 to 0.3 μm, noise during compressor operation can be reduced.

  The compressor main shaft support structure of the present invention is a shell in which a plurality of needle rollers are arranged along an inner diameter surface of a shell-type outer ring formed by pressing a needle roller bearing that supports a radial load of the compressor main shaft. Since the inner diameter roundness of the shell type outer ring is restricted to a numerical value range of 10 μm or less, or the thickness deviation of the cylindrical portion is restricted to a numerical value range of less than 10 μm. Can extend the service life.

  A means for restricting at least one of the circumferential surface roughness, the inner diameter roundness and the cylindrical portion thickness deviation of the inner ring surface of the outer ring to the numerical range is provided in a pressing process for forming a shell type outer ring, By making the lubrication condition on the outer diameter side ironing surface, which is the outer diameter surface of the outer ring in this ironing process, substantially fluid lubrication, the upper end surface of the cup molded product becomes nearly uniform in the plate thickness direction. The yield can be improved by reducing the size, and the press load necessary for drawing can be reduced.

  The needle roller bearing for a compressor main shaft according to the present invention has a circumferential surface roughness of an inner diameter surface of the outer ring as an outer ring in which a plurality of needle rollers are arranged along the inner diameter surface as a shell-type outer ring formed by pressing. Since the degree is restricted to a numerical value range of Ra 0.05 to 0.3 μm, the sound level during use can be reduced.

  Further, the needle roller bearing for a compressor main shaft of the present invention has an outer ring in which a plurality of needle rollers are arranged along the inner diameter surface as a shell type outer ring formed by pressing, and the inner ring has a roundness inside diameter. Since it is restricted to a numerical value range of 10 μm or less, or the cylindrical portion thickness deviation is restricted to a numerical value range of less than 10 μm, its life can be extended.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. FIG. 1 shows a compressor for an air conditioner for an automobile that employs a support structure for a compressor main shaft according to a first embodiment of the present invention. This compressor is a double swash plate type compressor that reciprocates a piston 4 that is a compression operation member through a shoe 3 that slides on the swash plate 2 by the rotation of the swash plate 2 fixed to the main shaft 1. . The main shaft 1 that is rotationally driven at high speed is supported by two shell needle roller bearings 6 in the radial direction and a thrust needle roller bearing 7 in the thrust direction in a housing 5 in which refrigerant exists.

  A plurality of cylinder bores 8 are formed in the housing 5 at equal intervals in the circumferential direction, and double-headed pistons 4 are reciprocally accommodated in the bores 8. Each piston 4 is formed with a recess 4a so as to straddle the outer periphery of the swash plate 2, and a spherical shoe 3 is seated on a spherical seat 9 formed on the axially opposed surface of the recess 4a. Some of the shoes 3 are hemispherical and function to smoothly convert the rotational motion of the swash plate 2 into the reciprocating motion of each piston 4.

  As shown in FIG. 2, each of the shell needle roller bearings 6 that support the radial direction of the main shaft 1 has a plurality of needle-like shapes along the inner diameter surface 12 of the SCM415 shell-type outer ring 11 formed by pressing. The rollers 13 are arranged, and each needle roller 13 is held by a SPCC cage 14 that is also formed by pressing.

  FIG. 3 shows a schematic process for manufacturing the shell-type outer ring 11. First, by pressing, a circular blank of SCM415 phosphate-coated steel sheet is formed into a cup molding in one drawing and ironing process, and the cup bottom corner portion is determined and pressed into a predetermined corner radius in the final pressing process. . In the squeezing and ironing process, press working oil having excellent lubricity is applied to the die side, and the lubrication condition on the ironing surface on the outer diameter side is substantially fluid lubricated. Next, the center portion of the cup bottom is punched in the bottoming step to form one flange 11a of the outer ring 11, and the upper end portion of the cup is trimmed to a uniform height in the trimming step. After that, the press-processed outer ring 11 is subjected to carburizing and quenching and tempering in a heat treatment process, and in the final assembly process, the other flange 11b is formed by bending inward.

  In the above-described embodiment, the drawing process in the press working of the shell-type outer ring 11 is performed only once, and the ironing process is the drawing ironing process performed simultaneously with this one drawing process. The squeezing step may be performed simultaneously with the final squeezing step, or the squeezing step may be performed separately after the squeezing step or the final pressing step.

  With respect to the shell type outer ring of the example manufactured in the manufacturing process of FIG. 3, the surface roughness of the inner surface, the inner diameter roundness, and the cylindrical part thickness deviation were measured. The measured dimensions of the outer ring were an outer diameter of 28 mm, a length of 16 mm, and a wall thickness of 0.95 mm. The surface roughness of the inner diameter surface was measured by dividing the outer ring into two semicylindrical shapes.

  The surface roughness of the inner diameter surface is measured in the circumferential direction and the axial direction. The circumferential surface roughness is 3 mm from each end of the outer ring at a position of 2 mm each and a central position in the length direction. Measurements were made at four locations with a 90 ° phase in the circumferential direction. As shown in FIG. 10, the surface roughness of the blank material is about Ra 0.49 μm on both the front and back surfaces, and the surface roughness of the outer diameter surface of the outer ring is about Ra 0.44 μm.

  4A and 4B show examples of the measurement results of the surface roughness. FIG. 4A shows the circumferential surface roughness measured at the center position in the longitudinal direction of the outer ring, which is very fine as Ra 0.18 μm. Although illustration is omitted, the circumferential surface roughness measured at positions of 2 mm from both ends is also in the range of Ra 0.05 to 0.3 μm, which is finer than the surface roughness of the blank material and the outer diameter surface. FIG. 4B shows the axial surface roughness measured with one phase, which is Ra 0.15 μm. Although illustration is omitted, the surface roughness in the axial direction measured at other phases was also very fine with Ra of 0.3 μm or less.

The outer circumferential surface roughness of the outer ring inner diameter surface is the same as that of the shell type needle roller bearing in which the circumferential surface roughness of the outer ring inner diameter surface is Ra 0.05 to 0.3 μm, and the circumferential surface roughness of the outer ring inner diameter surface is Ra 0.3 μm. The comparative example shell-type needle roller bearings were prepared, and these were attached to a rotation testing machine, and an acoustic measurement test was performed. The test conditions are as follows.
・ Rotation speed: 4800 rpm
・ Radial load: 180N
・ Lubrication: Viscosity 2cSt oil application ・ Sound measurement position: Position at a distance of 100 mm in a 45 ° direction from the bearing

  FIG. 5 shows the measurement result of the sound level in the sound measurement test. From these measurement results, the examples in which the circumferential surface roughness of the inner diameter surface is Ra 0.05 to 0.3 μm all have an acoustic level of 60 dB or less, and the acoustic level is significantly reduced compared to the comparative example. You can see that.

  Table 1 shows the inner diameter roundness and cylinder of the shell type outer ring (Examples A to F) manufactured in the manufacturing process of FIG. 3 and the shell type outer ring (Comparative Examples A to F) manufactured in the conventional manufacturing process. The result of having measured the partial thickness deviation is shown. The measured dimensions of the outer ring are an outer diameter of 28 mm, a length of 16 mm, and a wall thickness of 0.95 mm. The measurement positions in the axial direction of the inner diameter roundness and the cylindrical portion thickness deviation are the same three positions as the measurement positions of the circumferential surface roughness of the inner diameter surface. The measurement was performed at a total of 12 locations at 4 locations with 90 ° phase in the circumferential direction. In all of the examples, the roundness of the inner diameter is 10 μm or less, and the thickness deviation of the cylindrical portion is less than 10 μm. In addition, Comparative Example A is manufactured by the manufacturing method described in Patent Document 2.

Bearing life tests were conducted on the shell needle roller bearings of the examples and comparative examples shown in Table 1. The number of samples in each example and comparative example was eight, and the bearing life was evaluated by L10 life (time in which 90% of the sample can be used without being damaged). The test conditions are as follows.
・ Axial load: 9.81kN
・ Rotation speed: 5000rpm
・ Lubricating oil: Spindle oil VG2

  FIG. 6 shows the relationship between the inner diameter roundness and the L10 life in the bearing life test. It can be seen that in each of the examples in which the roundness of the inner diameter of the shell type outer ring is 10 μm or less, the L10 life exceeds 200 hours, and the bearing life is significantly extended. In the comparative example having an inner diameter roundness exceeding 10 μm, even the most excellent comparative example A has an L10 life of less than 200 hours.

  FIG. 7 shows the relationship between the cylinder wall thickness deviation and the L10 life in the bearing life test. Regarding the cylindrical part thickness deviation, the L10 life of each of the examples of less than 10 μm exceeds 200 hours, and the bearing life is greatly extended.

  FIG. 8 shows an air conditioner compressor employing the compressor spindle support structure of the second embodiment. This compressor is a swash plate type compressor, and a swash plate 25 supported by a ball 23 and a thrust needle roller bearing 24 on an inclined surface 22a of the connecting member 22 by rotation of the connecting member 22 connected to the main shaft 21. The swinging motion of the swash plate 25 is converted into the reciprocating motion of the single-headed piston 27 via the piston rod 26. The main shaft 21 is supported in the housing 28 by a single shell needle roller bearing 29 in the radial direction and supported by a thrust needle roller bearing 30 in the thrust direction via a connecting member 22. As in the case of the first embodiment, the shell type needle roller bearing 29 uses a shell type outer ring manufactured by the manufacturing process shown in FIG.

  FIG. 9 shows an air conditioner compressor employing the compressor spindle support structure of the third embodiment. This compressor is a swash plate type variable displacement compressor, and the inclination angle of the connecting member 32 connected to the main shaft 31 can be changed by sliding the sleeve 33 fitted in the main shaft 31 in the axial direction. ing. The swinging motion of the swash plate 35 supported on the connecting member 32 by the thrust needle roller bearing 34 is the reciprocating motion of the one-sided piston 37 via the piston rod 36 as in the second embodiment. Converted. In the housing 38, the main shaft 31 is supported by two shell needle roller bearings 39 in the radial direction and supported by the thrust needle roller bearing 40 in the thrust direction. This shell-type needle roller bearing 39 also uses a shell-type outer ring manufactured in the manufacturing process shown in FIG. 3 as in the first embodiment.

FIG. 1 is a longitudinal sectional view showing a compressor for an air conditioner adopting the compressor spindle support structure of the first embodiment. 1 is a longitudinal sectional view showing the shell needle roller bearing of FIG. Process drawing which shows the outline manufacturing process of the shell type needle roller bearing of FIG. a and b are graphs showing the surface roughness in the circumferential direction and the axial direction of the inner surface of the shell-type outer ring manufactured in the manufacturing process of FIG. Graph showing the relationship between the circumferential surface roughness of the inner surface of the outer ring and the sound level in the sound measurement test of the shell needle roller bearing The graph which shows the relationship between the internal diameter roundness of a shell type outer ring | wheel and L10 life in the bearing life test of a shell type needle roller bearing The graph which shows the relationship between the cylindrical part thickness deviation of a shell type outer ring | wheel, and L10 life in the bearing life test of a shell type needle roller bearing The longitudinal cross-sectional view which shows the compressor for an air conditioner which employ | adopted the support structure of the compressor main shaft of 2nd Embodiment. The longitudinal cross-sectional view which shows the compressor for air conditioners which employ | adopted the support structure of the compressor main shaft of 3rd Embodiment. Graph showing the surface roughness of the inner and outer diameter surfaces of the cup molding and the surface roughness of the blank material in the drawing ironing test Thickness cross-sectional photograph of the upper end of the cup molding in the drawing ironing test

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Main shaft 2 Swash plate 3 Shoe 4 Piston 4a Recess 5 Housing 6 Shell type needle roller bearing 7 Thrust needle roller bearing 8 Bore 9 Spherical seat 11 Shell type outer ring 11a, 11b 鍔 12 Inner diameter surface 13 Needle roller 14 Cage 21 Main shaft 22 Connecting member 22a Inclined surface 23 Ball 24 Thrust needle roller bearing 25 Swash plate 26 Piston rod 27 Piston 28 Housing 29 Shell needle roller bearing 30 Thrust needle roller bearing 31 Main shaft 32 Connecting member 33 Sleeve 34 Thrust needle roller Bearing 35 Swash plate 36 Piston rod 37 Piston 38 Housing 39 Shell needle roller bearing 40 Thrust needle roller bearing

Claims (2)

In a compressor main shaft support structure in which a compression operation member of a compressor is operated by rotational driving of the main shaft and a radial load of the main shaft is supported by a needle roller bearing disposed in the compressor, the needle roller bearing is formed by pressing. A shell-type needle roller bearing in which a plurality of needle rollers are arranged along the inner diameter surface of the formed shell-type outer ring, and a pressing process for forming the shell-type outer ring is provided, and the outer ring in the pressing process is provided. By setting the lubrication condition on the outer diameter side ironing surface, which is the outer diameter surface, to a substantially fluid lubrication state, the circumferential surface roughness of the inner diameter surface of the outer ring is within a numerical range of Ra 0.05 to 0.3 μm, and the inner diameter is a perfect circle. A support structure for a compressor main shaft, wherein the degree is controlled to a numerical value range of 10 μm or less and a cylindrical portion thickness deviation is simultaneously controlled to a numerical value range of less than 10 μm. In a needle roller bearing for a compressor main shaft that supports a radial load of a main shaft that rotationally drives a compression operation member of the compressor in the compressor, an outer ring in which a plurality of needle rollers are arranged along an inner diameter surface is formed by pressing. And a pressing process for forming the shell-type outer ring is provided with a squeezing process, and the lubrication condition on the squeezing surface on the outer diameter side that is the outer diameter surface of the outer ring in this squeezing process is substantially fluid lubricated. the circumferential surface roughness of the inner surface of the outer ring in the numerical range of Ra0.05~0.3μm by the roundness of the inner diameter to the following numerical range 10 [mu] m, at the same time the cylindrical portion wall thickness deviation amount in the numerical range of less than 10 [mu] m Needle roller bearings for compressor main shafts characterized by regulation.