JP2013050038A - Vane-type compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a vane-type compressor that can relatively reduce the coating amount of a solid lubricant used for forming a solid lubricant film on the outer peripheral surface of a rotor.SOLUTION: The vane-type compressor 1 includes at least a cylinder 8a having a perfect circle inner circumferential surface stored in a housing 2, a perfect circle rotor 4 stored in the cylinder 8a with its center P2 disposed at a position offset from the center P1 of the cylinder 8a, and a shaft 3 press-fit into a through-hole 4a of the perfect circle rotor 4. A solid lubricant film 30 is formed on the outer peripheral surface 4b and the side surface 4c of the perfect circle rotor 4. The thickness L of the solid lubricant film 30 is in a range of 10-20 μm in the initial stage without application of a finish process so that the coating amount of the solid lubricant is reduced relatively.

Description

  The present invention relates to a vane compressor used in a refrigeration cycle of a vehicle air conditioner, for example.

  In a vane type compressor used in a refrigeration cycle of a vehicle air conditioner, in order to achieve both performance and reliability, the clearance between the inner peripheral surface of the cylinder and the outer peripheral surface of the rotor is in an appropriate state. In order to manage so that it becomes, various devices have been conventionally performed.

  For example, in the case of a vane type compressor in which an odd-numbered vane rotor is combined with an elliptic cylinder as shown in FIG. 1 of Patent Document 1, it is positioned on both sides in the radial direction with the shaft as the center. Since the compression action is performed alternately in the compression section, even if the clearance between the shaft and the bearing that supports this shaft is made as small as possible, the rotor assembly can move in the elliptical minor axis direction of the elliptic cylinder within this clearance. It will vibrate alternately along. Specifically, the clearance between the rotor outer peripheral surface on the top dead center side and the cylinder inner peripheral surface is increased, and the clearance increases, and the rotor outer surface on the side opposite to the top dead center and the cylinder inner peripheral surface approach each other. Thus, the rotor assembly vibrates so that the clearance is reduced.

  Therefore, in order to reduce the leakage of working fluid (refrigerant gas) from between the rotor outer peripheral surface and the cylinder inner peripheral surface, it is preferable to make the clearance between the rotor outer peripheral surface and the cylinder inner peripheral surface as small as possible. Thus, if the clearance between the rotor outer circumferential surface and the cylinder inner circumferential surface in the elliptical minor axis direction of the elliptical cylinder is too small, the rotor in the elliptical minor axis direction of the elliptical cylinder There is a risk of contact between the outer peripheral surface and the cylinder inner peripheral surface.

  In order to ensure the reliability of the vane compressor while allowing contact between the rotor outer peripheral surface and the cylinder inner peripheral surface, either or both of the inner peripheral surface of the elliptic cylinder and the outer peripheral surface of the rotor are provided. It is conceivable to form a solid lubricant film by applying a solid lubricant such as polytetrafluoroethylene (hereinafter referred to as PTFE). In the gas compressor shown in Patent Document 1, although the purpose is different, a solid lubricant film made of fluororesin or the like is formed on one or both of the inner peripheral surface of the elliptic cylinder and the outer peripheral surface of the rotor. A formed configuration is disclosed.

  When a rotor having such a solid lubricant film formed on the entire circumference is used, the thickness of the solid lubricant film is added in addition to the shape accuracy of each part, and the variation in the clearance between the cylinder inner peripheral surface and the rotor outer peripheral surface is relative. Become bigger. For this reason, a so-called matching process is generally used in which the clearance is managed by processing the other of the cylinder inner peripheral surface and the rotor outer peripheral surface in accordance with the actually measured dimension so that the clearance has an appropriate value.

JP 2004-211161 A

  However, in the case where the above matching process is adopted in forming a vane type compressor employing an elliptic cylinder as shown in Patent Document 1, an elliptical shape is formed with sufficient accuracy by polishing or lathe processing. Therefore, the matching process is usually performed by polishing the outer peripheral surface of the cylindrical rotor on the rotor assembly side.

  Along with this, the solid lubricant film formed at the initial stage on the outer peripheral surface of the rotor includes a surplus of, for example, about 100 μm in consideration of the deformation of the rotor at the time of shaft press-fitting and the margin for finishing. Because of the thickness, when expensive PTFE is applied as a solid lubricant, there is a disadvantage that a large amount of PTFE must be used even though it is removed by finishing. In addition, when the solid lubricant is PTFE, the solid lubricant film has a relative thickness of, for example, about 100 μm unless the operation of coating and dividing and baking and hardening is repeated a plurality of times, for example, three times. There is also a disadvantage that the thickness is not large.

  Then, this invention aims at providing the vane type compressor which can reduce relatively the application quantity of the solid lubricant used in order to form a solid lubricant film on the outer peripheral surface of a rotor. .

  A vane type compressor according to the present invention includes a housing having a suction port and a discharge port, forming an outer shell, a cylinder formed integrally with or separate from the housing, and having a perfect circular inner peripheral surface, A perfectly circular rotor housed in the cylinder so that its center is arranged at a position deviated from the center of the cylinder, a vane groove opened in an outer peripheral surface of the rotor, and the inner periphery of the cylinder A vane that is slidably contacted with a surface and is retractably stored in the vane groove; a rotor assembly that is press-fitted into the rotor and integrated with the rotor; and a shaft that transmits external power to the rotor; and A bearing portion that is formed and held in a housing and rotatably supports the shaft. The rotor has a solid lubricant film formed on the outer peripheral surface, and the rotor Nburi is characterized in that it is housed in the cylinder without finishing to the solid lubricant coating is applied (claim 1). The clearance between the rotor assembly and the cylinder is controlled by processing only the inner peripheral surface of the cylinder based on the size of a predetermined portion of the rotor assembly. 7). Here, for example, PTFE or the like is used as the solid lubricant. The solid lubricant film is formed by applying a solid lubricant or the like.

  Thereby, since the cylinder which has a perfect circular internal peripheral surface is used, it becomes possible to match-process using a lathe about the cylinder internal peripheral surface. As a result, it is not necessary to polish and match the outer peripheral surface and side surfaces of the rotor, and it is not necessary to apply excess solid lubricant to the rotor assembly in consideration of the allowance in finishing processing. It is possible to relatively reduce the amount of the coating.

  Further, the cylinder includes a circular inner peripheral surface, and a circular rotor housed in the cylinder so that the center is arranged at a position deviated from the center of the cylinder. Therefore, the rotor is always pushed to the side opposite to the top dead center by the pressure in the cylinder. For this reason, since there is no possibility that the rotor assembly vibrates even if the clearance between the shaft and the bearing portion is large, it is not necessary to perform matching processing on the bearing portion to manage a suitable clearance between the shaft and the bearing portion. A suitable clearance can be managed only by matching the cylinder inner peripheral surface based on the numerical value from one point of the surface to the outer peripheral surface of the shaft opposite to the one side of the rotor outer peripheral surface of the shaft.

  In the vane type compressor according to the present invention, the rotor has a solid lubricant film formed on a side surface where a through hole into which the shaft of the rotor is inserted is opened, and the rotor assembly includes the rotor of the rotor. It is characterized in that it is accommodated in the cylinder without being subjected to a finishing process on the solid lubricant film on the side surface (Claim 2). In this way, the solid lubricant is applied simultaneously to the outer peripheral surface and the side surface of the rotor by forming the solid lubricant film on the side surface of the rotor without finishing as well as the outer peripheral surface of the rotor. It becomes possible to do.

  The thickness of the solid lubricant film of the rotor is in the range of 10 μm to 20 μm without finishing. (Claim 3) The thickness of the solid lubricant film is optimally 15 μm, for example.

  In the vane type compressor according to the present invention, the bearing portion is a plain bearing (claim 4). Thereby, the clearance between the bearing portion and the shaft can be made relatively larger than when a needle bearing is used as the bearing portion. Further, unlike the case where a needle bearing is used as the bearing portion, direct measurement is possible when measuring a certain point of the bearing portion located on the opposite side of the certain point located on the inner circumference of the cylinder.

  In the vane type compressor according to the present invention, the side block constituting the housing is formed integrally with the cylinder (Claim 5). As described above, when the side block is formed integrally with the cylinder, the side block is applied by matching processing that matches the length of the rotor after the solid lubricating film is formed with the bottom surface of the cylinder (the thrust surface of the rotor). The thrust clearance between the rotor and the rotor can be easily managed.

  The vane compressor according to the present invention is characterized in that a concave portion that is recessed in the axial direction of the through hole is formed on an opening periphery of the through hole on a side surface of the rotor. Thereby, this recessed part can be utilized as a site | part which does not need to consider about sliding and interference with the components which oppose.

  As described above, according to the first to seventh aspects of the invention, since the cylinder having the perfect circular inner peripheral surface is used, the inner peripheral surface of the cylinder can be matched using a lathe. It becomes. Along with this, the outer peripheral surface and side surfaces of the rotor have been polished and matched on the rotor assembly side, so that matching processing can be performed on the cylinder side. Since the solid lubricant film needs only to have a necessary and sufficient thickness, it is not necessary to apply an excess solid lubricant to the rotor assembly, and the amount of solid lubricant applied can be relatively reduced. It becomes possible to reduce the manufacturing cost of a compressor.

  In addition, since the solid lubricant film formed on the rotor assembly conventionally cuts off the surplus, it is suitable for a finished product, that is, a thickness in the range of 10 μm to 20 μm, more preferably 15 μm. For example, the thickness of the solid lubricant film formed on the rotor assembly is surely in the range of 10 μm to 20 μm, more preferably 15 μm. The thickness can be set.

  In particular, according to the second aspect of the present invention, the outer peripheral surface and the side surface of the rotor are formed by forming the solid lubricant film on the side surface of the rotor without finishing the same as the outer peripheral surface of the rotor. In addition, the solid lubricant can be applied simultaneously, and the application of the fixed lubricant to the rotor can be performed efficiently and quickly.

  In particular, according to the fourth aspect of the present invention, unlike the case where a needle bearing is used as the bearing portion, it is possible to directly measure the position of a certain point on the inner periphery of the bearing portion. Furthermore, since plain bearings can be used with a relatively large clearance compared to needle bearings, when a needle bearing is used as a bearing portion, the clearance between the bearing portion and the shaft is set to a predetermined clearance. In order to manage the value, it was necessary to match the outer diameter of the shaft in accordance with the inner diameter of the bearing portion. By using a plain bearing for the bearing portion, it is no longer necessary to manage the clearance between the bearing portion and the shaft. The matching process on the rotor assembly side can be dispensed with in combination with the inner peripheral surface of the cylinder described in claim 1 being perfectly circular.

  Moreover, as shown in claim 5, when the side block is formed integrally with the cylinder, the matching process is performed so that the bottom surface of the cylinder (the thrust surface of the rotor) matches the length of the rotor after the formation of the solid lubricant film. As a result, the thrust clearance between the rear side block and the rotor can be easily managed.

  Further, according to the invention described in claim 6, since the concave portion formed in the periphery of the opening of the through hole into which the shaft is inserted is formed on the side surface of the rotor, the concave portion slides with the facing component. And can be used as a site that does not need to consider interference. For example, when the shaft is press-fitted into the rotor, the recess on the side surface of the rotor is used as a support part, so that even if the periphery of the support part is damaged or raised due to the press-fitting load, it slides on the side block. There is no need to consider defects or interference. For this reason, it is not necessary to apply extra solid lubricant to the rotor side surface and remove it by finishing in consideration of deformation of the rotor side surface and damage to the solid lubricant film that occur during press-fitting of the shaft. The amount can be further reduced.

FIG. 1 is a cross-sectional view showing an example of a vane type compressor according to the present invention. FIG. 1 (a) is a cross-sectional view cut so that a discharge port can be seen, and FIG. 1 (b) shows a suction port. It is sectional drawing cut | disconnected. FIG. 2 is a cross-sectional view taken along line AA in FIG. FIG. 3 is a cross-sectional view of a part of the vane type compressor according to the present invention, showing a part thereof. FIG. 4 is an explanatory view showing the structure of the rotor assembly constituting the vane type compressor according to the present invention and a part of the rotor assembly. FIG. 4 (a) is a perspective view of the rotor assembly. (B) is a perspective view of a rotor, FIG.4 (c) is explanatory drawing which shows the thickness of the solid lubricant film formed in the outer surface of a rotor. FIG. 5 is an explanatory diagram showing a reference for setting a clearance between the outer peripheral surface of the rotor and the inner peripheral surface of the cylinder.

  Embodiments of the present invention will be described below with reference to the accompanying drawings.

  1 to 4 show an example of a vane compressor used in a refrigeration cycle of a vehicle air conditioner, for example. The vane compressor 1 includes a shaft 3, a rotor 4 that is fixed to the shaft 3 and rotates as the shaft 3 rotates, and a first housing member that defines a compression space 18 described later by the rotor 4. 8 and the second housing member 9, and the first housing member 8 and the second housing member 9 constitute the housing 2. The part A shown in FIG. 4A in which the rotor 4 is assembled to the shaft 3 is also referred to as a rotor assembly.

  In this embodiment, the first housing member 8 is a cylinder 8a that houses the rotor 4, and the cylinder 8a is positioned on the rear side in the axial direction of the shaft 3 and is integrally formed with the cylinder 8a. The rear side block 8b closes the rear side. Although not shown, the cylinder 8a may be separated from the rear side block 8b, that is, may not be a part of the first housing member 8, or may be integrated with the front side block 9a.

  The rotor 4 accommodated in the cylinder 8a has a cylindrical shape with a perfect cross section, and the shaft 3 can be press-fitted into the center P1 of the perfect circle as shown in FIG. 4B. A hole 4a is provided. As shown in FIG. 4B, the rotor 4 is inserted into a plurality of (two in this embodiment) vane grooves 5 opened in the outer peripheral surface (two in this embodiment). It has a vane 6. The vane groove 5 is opened not only in the cylinder 8a but also in the front side block 9a side and the rear side block 8b side, and the back pressure chamber 5a is provided at the bottom of the vane groove 5 on the back side in the sliding direction of the vane 6. Is defined. Therefore, the back pressure chamber 5a is also opened to the front side block 9a side and the rear side block 8b side. As shown in FIG. 2, the vane 6 has a side surface that slides on the inner surface of the vane groove 5, and a tip that protrudes and retracts from the vane groove 5 and slides on the inner peripheral surface of the cylinder 8 a. The concave portion 4d formed on the side surface 4c of the rotor 4 will be described later.

  Further, as shown in FIG. 2, the inner peripheral surface of the cylinder 8a has a perfect circle shape having an inner diameter larger than the outer diameter of the rotor 4, and the center P2 of the cylinder 8a and the center P1 of the rotor 4 The outer peripheral surface of the rotor 4 and the inner peripheral surface of the cylinder 8a are biased to form a minute clearance (portion where the cylinder 8a and the rotor 4 are closest to each other: top dead center P3) at one place in the circumferential direction. The rotor 4 is accommodated in the cylinder 8a. The deviation between the center P2 of the cylinder 8a and the center P1 of the rotor 4 is, for example, about ½ of the difference between the inner diameter dimension of the cylinder 8a and the outer diameter dimension of the rotor 4. Thus, by accommodating the rotor 4 in the cylinder 8 a, a compression space 18 is defined between the inner peripheral surface of the cylinder 8 a and the outer peripheral surface of the rotor 4. The compression space 18 is divided into a plurality of compression chambers 19 by being divided by the vanes 6 accommodated in the plurality of vane grooves 5 formed in the rotor 4, and the volume of each compression chamber 19 changes according to the rotation of the rotor 4. It is like that.

  The second housing member 9 includes a front side block 9a that contacts the front end surface of the cylinder 8a, and extends from the front side block 9a in the axial direction of the shaft 3 so as to surround the outer peripheral surfaces of the cylinder 8a and the rear side block 8b. The shell 9b formed so as to be integrated with each other. The second housing member 9 is connected to the first housing member 8 via a connector 7 such as a bolt. Then, by inserting the first housing member 8 from the rear side opening 9d of the shell 9b and fitting with the shell 9b, the front side of the cylinder 8a is closed by the front side block 9a and the rear of the shell 9b. The side opening 9d is closed by the rear side block 8b.

  The second housing member 9 is a pulley in which rotational power is transmitted from a power source (not shown) of a vehicle to a boss portion 9c integrated with the front side block 9a via a belt (not shown). 20 is rotatably mounted, and rotational power is transmitted from the pulley 20 to the shaft 3 via the electromagnetic clutch 21. The second housing member 9 is formed with a suction port 11 and a discharge port 12 for working fluid (refrigerant gas). The suction port 11 is connected to the space 14 a and the cylinder 8 a formed in the second housing member 9. It communicates with the suction space 14 formed by the formed recess 14b.

  The shaft 3 is rotatably supported via plain bearings 23 and 24 which are bearing parts formed to be held by the front side block 9a of the second housing member 9 and the rear side block 8b of the first housing member 8. . In the shaft 3, a seal member 13 is interposed between the shaft 3 and the inner peripheral surface of the second housing member 9 in the vicinity of the proximal end of the boss portion 9 c of the second housing member 9. Leakage from the opening of the portion 9c is prevented.

  A suction port 25 communicating with the suction space 14 corresponding to the compression space 18 and a discharge port 26 communicating with the discharge space 15 are provided on the peripheral surface of the cylinder 8a. Therefore, when the cylinder 8a is fitted into the shell 9b, the suction space 14 communicates with the compression chamber 19 via the suction port 25, and both end sides are flanged between the outer peripheral surface of the cylinder 8a and the inner peripheral surface of the shell 9b. A discharge space 15 partitioned by the portions 8 c and 8 d is formed, and the discharge space 15 can communicate with the compression chamber 19 via a discharge port 26. The discharge port 26 is opened and closed by a discharge valve 27 accommodated in the discharge space 15. The discharge space 15 communicates with the oil separator 16 through a through hole 28 formed in the flange portion 8d. The oil separator 16 further communicates with the discharge port 12.

  According to the above configuration, in the vane type compressor 1, rotational power from a power source (not shown) is transmitted to the shaft 3 through the pulley 20 and the electromagnetic clutch 21, and when the rotor 4 rotates, the suction port 11 The working fluid that has flowed into the suction space 14 is sucked into the compression space 18 via the suction port 25. Since the volume of the compression chamber 19 partitioned by the vanes 6 in the compression space 18 changes with the rotation of the rotor 4, the working fluid confined between the vanes 6 is compressed and is discharged from the discharge port 26 through the discharge valve 27. And discharged into the discharge space 15. The working fluid discharged into the discharge space 15 moves in the circumferential direction along the outer peripheral surface of the cylinder 8a (the inner peripheral surface of the shell 9b), and passes around the periphery of the cylinder 8a so as to be formed in the flange portion 8d. The oil is introduced into the oil separation chamber of the oil separator 16 formed in the rear side block 8b through the hole 28. Thereafter, the oil is separated from the working fluid in the process of turning in the oil separation chamber of the oil separator 16 and discharged from the discharge port 12 to the external circuit.

  Incidentally, as shown in FIG. 4C, a solid lubricant film 30 is formed on the outer peripheral surface 4b and the side surface 4c of the rotor 4 shown in FIG. 4B. As the solid lubricant for forming the solid lubricant film 30, for example, PTFE is used.

The clearance value W between the outer peripheral surface of the rotor 4 and the inner peripheral surface of the cylinder 8a is suitably managed by the following method as shown in FIG.
First, the rotor assembly side dimension R from the point S1 located on the outer peripheral surface 4b of the rotor 4 to the point S2 located on the opposite side of the outer peripheral surface 4b of the rotor 4 from the point S1 side of the side circumferential surface of the shaft 3. Measure.
On the other hand, the cylinder 8a is located on the opposite side of the inner peripheral surface of the cylinder 8a before finishing from the side where the center P2 of the cylinder 8a is eccentric with respect to the center P1 of the rotor 4 (downward in FIG. 5). The cylinder side dimension C from the point S3 to the point S4 located on the opposite side to the point S3 located on the inner peripheral surface of the cylinder 8a in the plain bearing 24 is measured.
Since the numerical value of C-R is the numerical value of the clearance W between the outer peripheral surface of the rotor 4 in operation and the inner peripheral surface of the cylinder 8a, the numerical value of W is a suitable value (for example, 20 μm). As described above, an optimal numerical value C ′ (not shown) is determined based on the numerical values of R and C measured in advance, and the numerical value of C is the optimal value for the dimensions from point S3 to point S4 of the cylinder 8a. The cylinder 8a is subjected to matching processing so that the numerical value C ′ is obtained.

  The reason why the clearance W can be managed by the matching processing of the cylinder 8a is that the inner peripheral surface of the cylinder 8a is formed into a perfect circle, and the cylinder 8a side is finished using a lathe. This is due to the fact that it can be done. As described above, the center P1 of the inner peripheral surface of the cylinder 8a is eccentric with respect to the center P2 of the outer peripheral surface of the cylinder 8a. However, when the cylinder 8a is held and rotated by eccentric chucking, the center P1 is offset. The inner peripheral surface of the centered cylinder 8a can be turned. When measuring the cylinder side dimension C, if the bearing part is a needle bearing, a plurality of needles (rollers) are exposed on the inner peripheral surface of the bearing part, so the S4 point is directly measured. However, in the present embodiment, since the bearing portion is the plain bearing 24, the reference S4 point can be directly measured.

  In addition, when a needle bearing is used for the bearing portion, it is necessary to manage the clearance between the inner diameter of the bearing portion and the shaft within a predetermined clearance range in consideration of the reliability of the needle. For this reason, after measuring the inner diameter dimension of the actual bearing portion, it is necessary to perform matching processing for adjusting the finishing margin of the outer diameter dimension of the shaft so that a predetermined clearance is obtained. In the present embodiment, since the bearing portions are the plain bearings 23 and 24, the management of the clearance between the bearings 23 and 24 and the shaft 3 becomes unnecessary.

  As a result, since it is no longer necessary to perform matching processing on the rotor 4 and thus on the rotor assembly A side as in the prior art, the thickness L of the solid lubricant film 30 formed on the outer peripheral surface and side surfaces of the rotor 4 can be finished. For example, it is no longer necessary to have a thickness including an excess of about 100 μm.

  Furthermore, in this embodiment, as shown in FIGS. 4A and 4B, a recess 4 d that is recessed in the axial direction of the through hole 4 a is formed on the opening periphery of the through hole 4 a on the side surface 4 c of the rotor 4. ing. The concave portion 4d serves as a support portion for supporting the press-fitting load when the shaft 3 is press-fitted into the rotor 4 on which the solid lubricant film 30 is formed to form the rotor assembly A. Depending on the press-fit load when the shaft 3 is press-fitted into the rotor 4, there is a possibility that the periphery of the support portion rises or the solid lubricating film is damaged, but these damages can be confined in the recess 4d. There is no risk of causing interference or sliding failure with the side blocks 8b and 9a. For this reason, even if the solid lubricant film 30 is formed before the shaft 3 is press-fitted into the rotor 4, it is not necessary to consider the damage of the solid lubricant film 30. It is no longer necessary to have a thickness that includes minutes.

  However, since the thickness of the solid lubricant film 30 can be set to a suitable dimension from the beginning, for example, 10 μm to 20 μm (for example, 15 μm of the optimum dimension) on the outer peripheral surface 4 b and the side surface 4 c of the rotor 4. The manufacturing amount of the vane type compressor 1 is reduced because the amount of the lubricant applied is relatively reduced and the finishing process for setting the thickness of the solid lubricant film to a suitable dimension is not necessary.

  As shown in FIG. 1, the first housing member 8 may be configured by integrally forming the cylinder 8 a and the rear side block 8 b. As a result, both the thrust and radial clearances can be continuously processed from the cylinder 8a to the rear side block 8b according to the actual size of the rotor assembly A, so that the processing time can be shortened and the process can be reduced. In other words, an error may occur each time the part is held by the tool. However, the possibility of such an error due to process differentiation is reduced, and the accuracy can be improved.

DESCRIPTION OF SYMBOLS 1 Vane type compressor 2 Housing 3 Shaft 3a Press-fit part 4 Rotor 4a Through-hole 4b Outer peripheral surface 4c Side surface 4d Recessed part 5 Vane groove 6 Vane 8 First housing member 8a Cylinder 8b Rear side block 9 Second housing member 9a Front side block 9b Shell 23 Plain bearing (bearing part)
24 Plain bearing (bearing part)
30 Solid lubricant film A Rotor assembly P1 Center of rotor P2 Center of cylinder P3 Top dead center

The reason why the clearance W can be managed by the matching processing of the cylinder 8a is that the inner peripheral surface of the cylinder 8a is formed into a perfect circle, and the cylinder 8a side is finished using a lathe. This is due to the fact that it can be done. As described above, the center P1 of the rotor 4 is eccentric with respect to the center P2 of the cylinder 8a . However, by holding and rotating the cylinder 8a by eccentric chucking, the inner circumference of the eccentric cylinder 8a is maintained. The surface can be turned. When measuring the cylinder side dimension C, if the bearing is a needle bearing, the S4 point is directly measured because a plurality of needles (rollers) are exposed on the inner peripheral surface of the bearing. However, in the present embodiment, since the bearing portion is the plain bearing 24, the reference S4 point can be directly measured.

Claims (7)

A housing in which an inlet and an outlet are formed and which forms an outer shell;
A cylinder formed integrally or separately with the housing, and having a perfect circular inner peripheral surface;
A perfectly circular rotor housed in the cylinder so that the center is arranged at a position deviated from the center of the cylinder;
A vane groove opened in the outer peripheral surface of the rotor, and a vane stored in the vane groove so as to protrude and retract while being in sliding contact with the inner peripheral surface of the cylinder;
A shaft that is press-fitted into the rotor and integrated with the rotor to transmit power from the outside to the rotor;
A bearing portion that is formed and held in the housing and rotatably supports the shaft;
The rotor has a solid lubricant film formed on the outer peripheral surface, and the rotor assembly is housed in the cylinder without being subjected to a finishing process to the solid lubricant film. A vane type compressor.   In the rotor, a solid lubricant film is formed on a side surface of the rotor where the shaft into which the shaft is inserted is opened, and the rotor assembly is processed into a solid lubricant film on the side surface of the rotor. The vane type compressor according to claim 1, wherein the compressor is housed in the cylinder without being applied.   3. The vane compressor according to claim 1, wherein the thickness of the solid lubricant film is in a range of 10 μm to 20 μm without finishing. 4.   The vane compressor according to claim 1, 2 or 3, wherein the bearing is a plain bearing.   The vane compressor according to any one of claims 1, 2, 3 and 4, wherein the side block constituting the housing is formed integrally with the cylinder.   6. The vane compressor according to claim 2, wherein a concave portion that is recessed in an axial direction of the through hole is formed on a side surface of the rotor on an opening peripheral edge of the through hole. . The clearance between the rotor assembly and the cylinder is managed by processing only the inner peripheral surface of the cylinder based on the size of a predetermined portion of the rotor assembly. The vane type compressor according to 3, 4, 5 or 6.

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