JP4051203B2 - Compressor - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a compressor mainly used in a vehicle air conditioner, and more particularly to a compressor having an improved bearing structure at a shaft end.
[0002]
[Prior art]
Conventionally, as this type of variable capacity compressor, for example, one having a configuration as shown in a side sectional view of FIG. This variable capacity compressor 1 is disclosed in Japanese Patent Application Laid-Open No. 2001-12345, and its basic configuration will be described. The front end plate 3 and the rear end are closed so as to close the front end of the cylindrical housing 2. The cylinder heads 4 are disposed so as to be closed, a valve plate 5 is inserted between the rear end of the housing 2 and the cylinder head 4, and a cylinder block 6 is disposed in the rear half of the housing 2. The cylinder block 6 is formed with a plurality of cylinder bores 7, a center bore 8 and a communication passage 9 which are arranged in the circumferential direction and spaced apart from each other, and a front half of the housing 2 is a crank chamber. 10 is formed.
[0003]
A drive shaft 11 passing through the front end plate 3 and extending back and forth extends into the housing 2, and a rear end portion of the drive shaft 11 is inserted into the center bore 8. The drive shaft 11 is rotatably supported by the front end plate 3 via a radial bearing 12 and is rotatably supported by the cylinder block 6 via a radial bearing 13. The rear end of the drive shaft 11 is supported in the axial direction by an adjustment screw 15 screwed into the center bore 8 via a thrust bearing 14. By adjusting the tightening degree of the adjusting screw 15, the axial distance between the thrust bearing 14 and a thrust bearing 17 described later is adjusted, and the axial load applied to the thrust bearings 14 and 17 is adjusted. A lip seal is disposed in front of the radial bearing 12.
[0004]
A rotor 16 disposed in the crank chamber 10 is fixed to the drive shaft 11, and the rotor 16 is supported in the axial direction by the front end plate 3 via a thrust bearing 17. One end of the rotor 16 is bent rearward to form an ear 16a, and a long hole 16b is formed in the ear 16a. A spherical bush 18 is fitted on the drive shaft 11 so as to be slidable in the axial direction behind the rotor 16. The spherical bush 18 is connected to the rotor 16 via a coil spring 19 that is fitted on the drive shaft 11. A disk-shaped swash plate 20 is slidably fitted to the spherical bush 18. The swash plate 20 is provided with ears 20a extending toward the ears 16a of the rotor 16, and the ears 20a are formed with holes 20b corresponding to the long holes 16b, and are formed in the long holes 16b and 20b. The pin 21 is inserted.
[0005]
A pair of sliding shoes 22 having a spherical surface on one side are slidably contacted with the peripheral edge of the swash plate 20 with the swash plate 20 in between, and a plurality of sliding shoes 22 are spaced apart from each other in the circumferential direction. Are arranged apart from each other. The pair of sliding shoes 22 are slidably held by shoe holding portions 23, respectively. The shoe holding portion 23 forms a piston 24 that extends rearward and is slidably inserted into the corresponding cylinder bore 7.
[0006]
A suction hole 25 and a discharge hole 26 are formed in the valve plate 5 so as to face each cylinder bore 7. The valve plate 5 controls the flow of fluid (refrigerant) to the suction hole 25 and the discharge hole 26. An intake valve and a discharge valve are attached. A suction chamber 27 communicating with the suction hole 25 and a discharge chamber 28 communicating with the discharge hole 26 are formed in the cylinder head 4. The suction chamber 27 communicates with the suction port 29, and the discharge chamber 28 communicates with the discharge port 30. A communication passage 9 formed in the cylinder bore 7 communicates with the crank chamber 10 and the suction chamber 27, and a bellows 31 sealed with respect to the surroundings is disposed in the communication passage 9. An electromagnetic clutch 32 is disposed in front of the front end plate 3.
[0007]
In the variable capacity compressor 1, when the drive shaft 11 is rotationally driven by an external drive source (not shown) via the electromagnetic clutch 32, the rotor 16 is rotated along with the rotation of the drive shaft 11, and the swash plate 20 is further moved. Rotate. As the swash plate 20 rotates, the sliding shoe 22 reciprocates back and forth while sliding on the periphery of the swash plate 20, and the shoe holding portion 23 holding the sliding shoe 22 reciprocates back and forth. A piston 24 formed at the rear end reciprocates in the cylinder bore 7 back and forth. Due to the reciprocating motion of the piston 24, the fluid (refrigerant) flowing into the suction chamber 27 through the suction port 29 is sucked into the cylinder bore 7 and compressed in the cylinder bore 7, and then passes through the discharge hole 26. After being discharged into the discharge chamber 28, it flows through the discharge port 30 to the external fluid circuit (the other part of the air conditioning circuit).
[0008]
In the variable capacity compressor 1, the bellows 31 contracts when the pressure in the communication passage 9 increases due to an increase in the heat load in the external fluid circuit and an increase in the pressure in the suction chamber 27. The communication portion between the crank chamber 10 and the communication passage 9 is opened, and blow-by gas leaked from the cylinder bore 7 to the crank chamber 10 through the sliding portion between the piston 24 and the cylinder bore 7 is sucked through the communication passage 9. The pressure in the crank chamber 10 is released to the chamber 27, so that the pressure in the crank chamber 10 becomes substantially the same as the pressure in the suction chamber 27. During the compression process, a reaction force applied to the piston 24 causes a moment M1 that causes the swash plate 20 to rotate in the clockwise direction around the pin 21. At this time, the coil spring 19 causes the swash plate 20 to move around the pin 21. A moment M2 is also generated that rotates in the clockwise direction. Therefore, if the heat load in the external fluid circuit increases and the pressure in the suction chamber 27 increases, the compression reaction force increases and M1> M2, and the swash plate 20 rotates in the clockwise direction, and the piston The stroke of 24 increases, and the compression capacity of the variable capacity compressor 1 increases.
[0009]
On the other hand, in the variable capacity compressor 1, when the pressure in the communication passage 9 decreases due to a decrease in the heat load in the external fluid circuit and a decrease in the pressure in the suction chamber 27, the bellows 31 expands. Then, the communication portion between the crank chamber 10 and the communication passage 9 is closed, and the pressure in the crank chamber 10 becomes higher than the pressure in the suction chamber 27 by blow-by gas. As a result, a moment M3 for rotating the swash plate 20 around the pin 21 in the counterclockwise direction is generated by the pressure of blow-by gas in the crank chamber 10 applied to the piston 24 during the compression process. When the heat load in the external fluid circuit decreases and the pressure in the suction chamber 27 decreases, the compression reaction force decreases and M1 <M2 + M3, and the swash plate 20 rotates counterclockwise, and the piston 24 , The compression capacity of the variable displacement compressor 1 decreases.
[0010]
By the way, in the case of this variable capacity compressor 1, the resultant force of the axial force due to the pressure of blow-by gas in the crank chamber 10 applied to the drive shaft 11 via the piston 24 when operated under a low heat load condition, and the piston 24, the time average value in the resultant force of the compression reaction force applied to the drive shaft 11 is balanced, and the rotor 16 and the thrust bearing 17 contact and disengage in synchronization with the periodic increase and decrease of the compression reaction force accompanying the suction compression process. Is repeated and the drive shaft 11 vibrates in the axial direction, thereby causing a problem of generating noise.
[0011]
Therefore, in order to prevent such noise generation, a variable displacement compressor 1 ′ having an improved bearing structure for the drive shaft 11 as shown in the side sectional view of FIG. 6 has been proposed. This variable displacement compressor 1 'is also disclosed in the same Japanese Patent Application Laid-Open No. 2001-12345 described above, and has the same configuration as that of the variable displacement compressor 1 described with reference to FIG. However, here, a disc spring 33 is inserted between the thrust bearing 14 and the adjusting screw 15 '. A recess 15'a for accommodating the disc spring 33 is formed on the end face of the adjustment screw 15 '.
[0012]
According to the variable displacement compressor 1 ′, the axial clearance between the thrust bearings 14 and 17 is adjusted by tightening the adjusting screw 15 ′, and the axial load applied to the thrust bearings 14 and 17 is adjusted. The disc spring 33 is compressed and elastically deformed, and the reaction force of the disc spring 33 is applied to the drive shaft 11 via the thrust bearing 14 and acts on the drive shaft 11 in the same direction as the compression reaction force. If the elastic coefficient 33 and the tightening degree of the adjusting screw 15 'are set to appropriate values and the reaction force of the disc spring 33 is set to an appropriate value, it is applied to the drive shaft 11 even when operated under low heat load conditions. The sum of the time average value of the resultant force of the compression reaction force and the reaction force of the disc spring 33 can be maintained at a value larger than the resultant force of the axial force due to the blow-by gas pressure in the crank chamber 10 applied to the drive shaft 11. it can. As a result, the vibration of the drive shaft 11 that occurs in synchronization with the periodic increase / decrease of the compression reaction force accompanying the suction / compression process is prevented, thereby preventing the generation of noise.
[0013]
Incidentally, the improved technology capable of preventing the occurrence of noise in such a bearing structure is a compressor other than the variable displacement compressor described above, and is supported by, for example, a cylinder block and a housing joined to the cylinder block. A fixed capacity type including an adjusting screw that adjusts the axial clearance of the thrust bearing while supporting one end of the drive shaft in the axial direction via a thrust bearing while obtaining a compression action based on rotating the driven shaft. Applicable to types.
[0014]
[Problems to be solved by the invention]
In the case of the compressor capable of preventing the noise generation described above, the bearing structure is improved and a disc spring is inserted between the thrust bearing and the adjusting screw. However, the disc is placed in the recess formed on the end surface of the adjusting screw during assembly. When assembling in a state in which the spring is accommodated, the disc spring is difficult to be successfully engaged with the concave portion of the adjusting screw, so that there is a problem that the assembly becomes complicated and difficult.
[0015]
The present invention has been made to solve such problems, and a technical problem thereof is to provide a compressor that can effectively prevent noise generation in a bearing structure and can be easily assembled. .
[0016]
[Means for Solving the Problems]
According to the present invention, a compression action is obtained based on rotation of a drive shaft supported by a cylinder block and a housing joined to the cylinder block, and one end of the drive shaft is axially connected via a thrust bearing. In a compressor including an adjusting screw that adjusts the axial clearance of the thrust bearing after being supported by the thrust bearing, the thrust bearing is in contact with the thrust bearing in the axial direction between the thrust bearing and the adjusting screw. A compressor in which an elastic member locked to a screw is interposed is obtained.
[0017]
Further, according to the present invention, in the compressor, the end face of the adjusting screw is formed with a recess capable of accommodating an elastic member, and the elastic member is located with respect to the inner peripheral wall and the bottom wall in the recess. An abutted compressor is obtained.
[0018]
Furthermore, according to the present invention, in the compressor, the recess is formed as a hollow portion having a substantially T-shaped cross section in which the small diameter portion is connected to the large diameter portion so as to include the axis of the adjusting screw, and the elastic member. Can obtain a compressor having a substantially T-shaped cross section that is brought into contact with the bottom wall in the large-diameter portion and the inner peripheral wall in the small-diameter portion. In this compressor, the hollow portion has a small-diameter portion formed as a central hole coaxial with the large-diameter portion, and the elastic member having a substantially T-shaped cross section is formed from the large-diameter portion through the small-diameter portion. The bottom wall in the diameter portion and the inner peripheral wall in the small diameter portion are in contact with each other, and a retaining portion having a diameter slightly larger than the diameter of the small diameter portion is integrally formed on the press-fitting tip side. It is preferable to have it.
[0019]
In addition, according to the present invention, in the compressor, the recess is formed in a substantially annular groove shape around the shaft core, and the elastic member is an inner peripheral edge in the substantially annular groove-shaped recess. A compressor having a substantially annular shape that comes into contact with the wall and the bottom wall is obtained. In this compressor, the concave portion has an annular groove shape continuously connected to the portion around the shaft core, and the substantially annular elastic member includes the inner peripheral wall and the bottom in the annular groove-like concave portion. A plurality of substantially arc-shaped grooves that are in an annular shape that is in contact with the wall, or that the recesses are scattered discontinuously apart from each other around the shaft core, and that form a generally annular groove shape as a whole. The elastic member having a substantially annular shape is a substantially arc shape that is in contact with the inner peripheral edge wall and the bottom wall of the plurality of substantially arc groove-like recesses. Each is preferred.
[0020]
On the other hand, according to the present invention, in the compressor, the concave portion is formed as a shape with a deformed portion in which at least the inner peripheral wall is partially deformed in the radial direction perpendicular to the axial direction. A compressor having a substantially cylindrical shape that is brought into contact with the inner peripheral edge wall and the bottom wall in the attached concave portion and is locked by the deformed portion is obtained. In this compressor, the concave portion is formed to have a concave portion that is partially recessed in the radial direction, and the elastic member having a substantially cylindrical shape is a convex portion that is partially protruded in the radial direction. And a substantially cylindrical portion with a convex portion that comes into contact with the inner peripheral wall and the bottom wall including the concave portion in the concave portion having a deformed portion in a state where the convex portion is fitted in the concave portion. It is preferable that it is a shape.
[0021]
On the other hand, in the compressor according to any one of the above, the elastic member is preferably made of a resin material or a rubber material.
[0022]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.
[0023]
FIG. 1 is a side sectional view showing a basic configuration of a variable capacity compressor 1 ″ according to an embodiment of the present invention. In the case of this variable capacity compressor 1 ″, the variable capacity shown in FIG. The bearing structure in the type compressor 1 'is improved so that the assembly is easy, and the thrust bearing 14 is brought into contact with the thrust bearing 14 in the axial direction (of the drive shaft 11) between the thrust bearing 14 and the adjusting screw 15'. In addition, a resin material 330 as an elastic member fixedly locked to the adjustment screw 15 ′ is interposed in advance, and an annular resin material 330 can be accommodated on the end face of the adjustment screw 15 ′. 6 except that the concave portion 15'a is formed and the resin material 330 is arranged so as to come into contact with the inner peripheral wall 15'b and the bottom wall in the concave portion 15'a. Because it has the same configuration as the conventional product shown The same components as compared with the conventional variable displacement compressor 1 described in FIG. 5 will not be described with the same reference numerals.
[0024]
In short, in the case of the bearing structure of the variable capacity compressor 1 ″, the resin material 330 as an elastic member is accommodated in the recess 15′a formed in advance on the end face of the adjusting screw 15 ′, and its inner peripheral wall 15′b. Is attached so as to abut against the thrust bearing 14 in a state of being integrated with the adjusting screw 15 ′, so that the tray-shaped disc spring of the variable capacity compressor 1 ′, which is a conventional product, is mounted. Compared to the bearing structure in which 33 is in contact with only the bottom wall in the recess 15'a, the resin material 330 does not have to be assembled alone, so that the assembly is simplified and the assemblability is improved. Also, the mechanical strength is stable, and noise generation in the bearing structure can be effectively prevented.
[0025]
In the variable capacity compressor 1 ″, the axial clearance between the thrust bearings 14 and 17 is adjusted by tightening the adjusting screw 15 ′, and the axial load applied to the thrust bearings 14 and 17 is adjusted. The resin material 330 is compressed and elastically deformed, and the reaction force of the resin material 330 is applied to the drive shaft 11 via the thrust bearing 14 and acts on the drive shaft 11 in the same direction as the compression reaction force. If the elastic coefficient of the screw and the tightening degree of the adjusting screw 15 'are set to appropriate values and the reaction force of the resin material 330 is set to an appropriate value, the compression applied to the drive shaft 11 even when operated under a low heat load condition. The sum of the time average value of the resultant reaction force and the reaction force of the resin material 330 is maintained at a value larger than the resultant force of the axial force due to the blow-by gas pressure in the crank chamber 10 applied to the drive shaft 11. As a result, even if the compression reaction force periodically increases or decreases with the suction compression process, a force is always applied to the drive shaft 11 in the left direction in FIG. 16 is always pressed against the thrust bearing 17, so that the drive shaft 11 generated by repeated contact and disengagement between the rotor 16 and the thrust bearing 17 is synchronized with the periodic increase and decrease of the compression reaction force. Vibration is prevented, thereby preventing noise generation.
[0026]
In the above-described embodiment, the elastic member fixed and locked to the adjusting screw 15 ′ is described as the resin material 330. However, for example, a rubber material is used as another elastic member, and the bearing structure is different. The same effect can be obtained even when configured as described above.
[0027]
FIG. 2 is a side sectional view showing a main part of a bearing structure according to another embodiment that can be substituted for the bearing structure of the above-described variable displacement compressor 1 ″. In the case of this bearing structure, the end face of the adjusting screw 150 is shown. Is formed as a hollow portion having a substantially T-shaped cross section in which the small diameter portion is connected to the large diameter portion so that the concave portion 150a capable of accommodating the resin material 331 as the elastic member includes the axis of the adjustment screw 150. The material 331 is abutted against at least the bottom wall in the large-diameter portion of the hollow portion and the inner peripheral wall in the small-diameter portion, and is formed on the tip side with a diameter slightly larger than the diameter of the small-diameter portion. It has a substantially T-shaped cross section integrally including a retaining portion 331 ′.
[0028]
That is, in this bearing structure, in the hollow portion of the recess 150a formed on the end face of the adjusting screw 150, the small diameter portion is formed as a central hole 150b coaxial with the large diameter portion, so that the resin material 331 is made large. When receiving from the diameter portion through the small diameter portion into the recess 150a by being fitted or the like, the retaining portion 331 ′ of the resin material 331 is locked to the side wall in the small diameter portion, and the other portion of the resin material 331 is in the hollow portion. It will be in the state contact | abutted with respect to the bottom wall in a large diameter part, and the inner peripheral wall in a small diameter part.
[0029]
3 is a side sectional view showing a main part of a bearing structure according to another embodiment that can be substituted for the bearing structure of the variable displacement compressor 1 ″ described above. In the case of this bearing structure, the end face of the adjusting screw 151 is shown. A recess 151a capable of accommodating a resin material 332 as an elastic member is formed in an annular groove shape continuously connected around the shaft core, and the resin material 332 is provided in the annular groove-shaped recess 151a. It has an annular shape so as to be in contact with the inner peripheral wall and the bottom wall.
[0030]
That is, in this bearing structure, since the annular groove-shaped concave portion 151a is formed around the shaft core on the end surface of the adjusting screw 151, when the annular resin material 332 is fitted into the concave portion 151a and stored. The resin material 332 is in contact with the inner peripheral wall and the bottom wall in the recess 151a.
[0031]
By the way, the annular groove-shaped concave portion 151a here is deformed and dispersed in a discontinuously spaced manner around the axial center portion of the end face of the adjustment screw 151, and a plurality of substantially annular grooves are formed as a whole. It can also be formed as an arc groove shape, but in this case, instead of the annular resin material 332 as an elastic member, the inner peripheral wall and the bottom wall in a plurality of substantially arc groove recesses In this case, the substantially arcuate shape can be used. In short, in such a bearing structure, the concave portion is formed in a substantially annular groove shape around the shaft core, and the elastic member is brought into contact with the inner peripheral wall and the bottom wall in the substantially annular groove-shaped concave portion. A substantially annular shape may be used.
[0032]
4 is a side cross-sectional view showing a main part of a bearing structure according to still another embodiment that can be substituted for the bearing structure of the capacity variable compressor 1 ″. In the case of this bearing structure, the adjustment screw 152 The end surface is formed with a recess 152a that can accommodate a resin material 333 as an elastic member, and has a recessed portion that is partially recessed in the radial direction perpendicular to the axial direction. The resin material 333 is partially in the radial direction. The convex portion 333 ′ protrudes in a convex shape, and abuts against the inner peripheral wall and the bottom wall including the concave portion in the concave portion 152a in a state where the convex portion 333 ′ is fitted in the concave portion. It has a substantially cylindrical shape with a convex portion.
[0033]
That is, in this bearing structure, the recess 152a formed on the end surface of the adjustment screw 152 is formed as a shape with a deformed portion including a partially recessed portion, and the resin material 333 having a substantially cylindrical shape with a protrusion is formed in the recess 152a. When the resin material 333 is accommodated by being fitted into the inner wall, the resin material 333 is in contact with the inner peripheral wall and the bottom wall including the recessed portion in the recessed portion 152a.
[0034]
By the way, the concavo-convex structure here has almost the same configuration even if it is reversed. In short, in such a bearing structure, the concave portion is formed as a shape with a deformed portion in which at least the inner peripheral wall is partially deformed in the radial direction perpendicular to the axial direction, and the elastic member is formed in the concave portion with the deformed portion. What is necessary is just to make it a substantially cylindrical shape which is contact | abutted with respect to a wall and a bottom wall, and is latched by a deformation | transformation part.
[0035]
Any of the resin materials 331 to 333 in these bearing structures may be replaced with a rubber material, and in any bearing structure, the resin materials 331 to 333 can be attached so as to contact the thrust bearing 14 shown in FIG. By adopting such a configuration, noise generation can be effectively prevented and assembly can be simplified as the same effect as in the previous embodiment. In addition, in the case of an improved technique that makes it possible to sufficiently prevent the occurrence of noise in such a bearing structure and is easy to assemble, as described at the end of the conventional technique, for example, a fixed compressor other than the above-described variable capacity compressor is used. The compressor of the present invention is not limited to the disclosed one because it can be applied to a capacity type.
[0036]
【The invention's effect】
As described above, according to the compressor of the present invention, the bearing structure of the conventional product is improved and the thrust bearing and the adjusting screw are brought into contact with the thrust bearing in the axial direction (of the drive shaft). In addition, since it is configured so that an elastic member fixedly locked to the adjusting screw is interposed in advance, it is in contact with only the bottom wall in the recess formed in the end face of the adjusting screw in the conventional product with a disc spring. Compared to the bearing structure, it is not necessary to assemble an elastic member made of resin material or rubber material alone. As a result, the assembly is simplified and the assemblability is improved, and the mechanical strength is stabilized. Noise generation can be effectively prevented.
[Brief description of the drawings]
FIG. 1 is a side sectional view showing a basic configuration of a variable capacity compressor according to an embodiment of the present invention.
FIG. 2 is a side cross-sectional view showing a main part of a bearing structure according to another embodiment that can be substituted for the bearing structure of the variable capacity compressor shown in FIG. 1;
3 is a side cross-sectional view showing a main part of a bearing structure according to another embodiment that can be substituted for the bearing structure of the variable capacity compressor shown in FIG. 1;
4 is a side cross-sectional view showing a main part of a bearing structure according to still another embodiment that can be substituted for the bearing structure of the variable capacity compressor shown in FIG. 1;
FIG. 5 is a side sectional view showing a basic configuration of a variable capacity compressor according to a conventional example.
FIG. 6 is a side sectional view showing a basic configuration of a variable capacity compressor according to another conventional example.
[Explanation of symbols]
1, 1 ′, 1 ″ Variable capacity compressor 2 Housing 3 Front end plate 4 Cylinder head 5 Valve plate 6 Cylinder block 7 Cylinder bore 8 Center bore 9 Communication passage 10 Crank chamber 11 Drive shaft 12, 13 Radial bearings 14, 17 Thrust Bearing 15, 15 ', 150, 151, 152 Adjustment screw 15'a, 150a, 151a, 152a Recess 15'b Inner peripheral wall 16 Rotor 16a, 20a Ear 16b Long hole 18 Spherical bush 19 Coil spring 20 Swash plate 20b Hole 21 Pin 22 Sliding shoe 23 Shoe holding part 24 Piston 25 Suction hole 26 Discharge hole 27 Suction chamber 28 Discharge chamber 29 Suction port 31 Discharge port 31 Bellows 32 Electromagnetic clutch 33 Belleville spring 150b Center holes 330.331, 332, 333 Resin material 331 ′ Without Stop portion 333 'convex portion

Claims (5)

A compression action is obtained based on rotation of a drive shaft supported by a cylinder block and a housing joined to the cylinder block, and one end of the drive shaft is supported in the axial direction via a thrust bearing. In a compressor that includes an adjustment screw that adjusts the axial clearance of the thrust bearing,
Between the thrust bearing and the adjustment screw, an elastic member that is brought into contact with the thrust bearing in the axial direction and previously locked to the adjustment screw is interposed,
A concave portion capable of accommodating the elastic member is formed on an end surface of the adjustment screw, and the elastic member is in contact with an inner peripheral wall and a bottom wall in the concave portion,
The concave portion has an annular groove shape continuously connected to a portion around the shaft core, and the elastic member is brought into contact with an inner peripheral edge wall and a bottom wall in the annular groove shape concave portion. A compressor having an annular shape. A compression action is obtained based on rotation of a drive shaft supported by a cylinder block and a housing joined to the cylinder block, and one end of the drive shaft is supported in the axial direction via a thrust bearing. In a compressor that includes an adjustment screw that adjusts the axial clearance of the thrust bearing,
Between the thrust bearing and the adjustment screw, an elastic member that is brought into contact with the thrust bearing in the axial direction and previously locked to the adjustment screw is interposed,
A concave portion capable of accommodating the elastic member is formed on an end surface of the adjustment screw, and the elastic member is in contact with an inner peripheral wall and a bottom wall in the concave portion,
The concave portion is formed as a shape with a deformed portion in which at least an inner peripheral wall is deformed in a radial direction perpendicular to the axial direction, and the elastic member is an inner portion of the concave portion with the deformed portion. A compressor having a substantially cylindrical shape that is brought into contact with the peripheral wall and the bottom wall and is locked by the deformable portion. 3. The compressor according to claim 2 , wherein the concave portion is formed so as to have a concave portion that is partially recessed in the radial direction, and the elastic member having a substantially cylindrical shape is partially in the radial direction. The inner peripheral wall and the bottom wall including the concave portion in the concave portion with the deformed portion in a state where the convex portion is fitted in the concave portion. A compressor characterized by having a substantially cylindrical shape with a convex portion that is brought into contact with the compressor. The compressor according to any one of claims 1 to 3 , wherein the elastic member is made of a resin material. The compressor according to any one of claims 1 to 3 , wherein the elastic member is made of a rubber material.

Images