JP2018031296A - Compressor and method of manufacturing compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a method of manufacturing a cylinder rotation type compressor 1 ensuring the reproducibility of concentricity.SOLUTION: A compressor 1 includes the steps of: machining a shaft body 24A and a bush 24B so as to match an axis of a tapered portion 300 of the shaft body 24A with an axis of the bush 24B while deciding a position in a rotating direction of the bush 24B to the shaft body 24A with a positioning key 330; disassembling the shaft body 24A and the bush 24B after the machining step and fitting the shaft body 24A in through-holes of rotors 22a and 22b; and fitting the tapered portion 300 of the shaft body 24A in a hollow portion of the bush 24B and deciding the position in the rotating direction of the bush 24B to the shaft body 24A with the positioning key 330, while fitting the shaft body 24A in the through-holes of the rotors 22a and 22b.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a compressor and a method for manufacturing the compressor.

  Conventionally, in a cylinder rotary compressor, a shaft mounted on a casing, a cylinder rotatably supported on the shaft, and a cylinder installed in the cylinder and rotatably supported on an eccentric part of the shaft. And a rotor that rotates about a second rotation center that is eccentric with respect to the first rotation center of the cylinder (see, for example, Patent Document 1).

  The cylinder rotary compressor includes a transmission mechanism that connects the cylinder and the rotor so as to rotate at a constant speed, and a partition vane that partitions a working chamber formed between the inner peripheral surface of the cylinder and the outer peripheral surface of the rotor. The rotor has a structure in which one end of the vane can freely enter and exit.

  An intake refrigerant flow path extending in the axial direction is formed in the shaft. The rotor is provided with an introduction refrigerant channel that guides the low-pressure refrigerant from the refrigerant channel to the space. When the cylinder rotates together with the rotor, the refrigerant is sucked into the working chamber through the suction refrigerant passage and the introduction refrigerant passage, and is compressed and discharged in the working chamber.

  A first bearing portion that is rotatably supported on the outer peripheral surface of one side in the axial direction of the shaft is provided on one side in the axial direction of the cylinder. A second bearing portion that is rotatably supported on the outer peripheral surface of the other side in the axial direction of the shaft is provided on the other side in the axial direction of the cylinder.

  Here, in order to fit the rotor from one side in the axial direction of the shaft, the radial dimension on one side in the axial direction of the shaft is smaller than the radial dimension on the other side in the axial direction of the shaft.

JP 2014-238023 A

  In the compressor, the diameter D2 on one side in the axial direction of the shaft 1 is smaller than the diameter D1 on the other side in the axial direction of the shaft 1. For this reason, the area of the axial direction other side end surface 2b among cylinders 2 becomes larger than the area of the axial direction one side end surface 2a among cylinders 2 (refer to Drawing 28).

  Here, the one axial end surface 2a and the other axial end surface 2b of the cylinder 2 function as pressure receiving surfaces that receive the refrigerant pressure. For this reason, the thrust force which presses the cylinder 2 to the other side in the axial direction is generated by the product of the difference in the area between the one end surface 2a in the axial direction and the second end surface 2b in the axial direction. Therefore, there is a possibility that the second bearing portion 2c of the cylinder may be worn due to the other side in the axial direction (the portion indicated by X in the figure) being in contact with the casing 3.

  On the other hand, when the diameter D2 on one side in the axial direction of the shaft 1 and the diameter D1 on the other side in the axial direction of the shaft 1 are the same (see FIG. 29), the thrust force that presses the cylinder 2 toward the other side in the axial direction is Does not occur. Therefore, the problem that the other axial side of the cylinder 2 is worn against the casing 3 does not occur.

  However, in order to fit the rotors 4a and 4b to the eccentric portion 1b of the shaft 1, it is necessary to reduce the diameter D2 on one side in the axial direction of the shaft 1 and the diameter D1 on the other side in the axial direction. For this reason, the cross-sectional area of the suction refrigerant flow path 1a provided in the shaft 1 has to be reduced, and the suction refrigerant causes a pressure loss, resulting in deterioration of efficiency.

  Therefore, the present inventors have made use of a shaft main body and a bush assembled to one side of the shaft main body in order to make the diameter dimension on one side and the other side in the axial direction of the shaft larger than the diameter dimension of the eccentric portion. We considered the construction of a shaft.

  According to the study by the present inventors, the shaft body and the bush are finished and the shaft body and the bush are aligned with each other, and then the shaft body and the bush are disassembled. When the shaft is configured by reassembling the shaft, the axis of the shaft main body and the axis of the bush are displaced.

  For this reason, before the shaft main body and the bush are disassembled and after the bush is reassembled to the shaft main body, the coaxiality of the shaft is different, and the reproducibility of the coaxiality may not be ensured. The coaxiality of the shaft is a degree indicating how close the axis of the shaft body and the axis of the bush are.

  An object of this invention is to provide the compressor and the manufacturing method of a compressor which ensured the reproducibility of the coaxiality in view of the said point.

In order to achieve the above object, in the invention according to claim 1, the housing (10) constituting the refrigerant chamber (10a),
A shaft (24) disposed within and supported by the housing;
A cylinder (21) disposed in the housing and formed in a cylindrical shape and rotatably supported with respect to the shaft and rotating about the first axis (C1);
A rotor (22a, 22b) disposed within the housing, rotatably supported with respect to the shaft, and rotated about a second axis (C2) eccentric with respect to the first axis;
A transmission mechanism (251a, 251b) for connecting the cylinder and the rotor and rotating the cylinder and the rotor in synchronization;
Vanes (23a, 23b) for partitioning working chambers (Va, Vb) between the inner peripheral surface of the cylinder and the outer peripheral surface of the rotor,
The shaft is provided with an intake refrigerant flow path (24d) through which refrigerant flows, and the rotor is provided with introduction refrigerant flow paths (224a, 224b) that guide the refrigerant from the intake refrigerant flow path to the working chamber. ,
The working chamber is deformed by the rotation of the cylinder, the rotor, and the vane, the refrigerant is sucked into the working chamber through the suction refrigerant flow path and the introduction refrigerant flow path, and compressed in the working chamber to discharge the high-pressure refrigerant through the refrigerant chamber ( A compressor discharging from 11a),
The shaft
A shaft body formed so as to extend in the axial direction of the first axis, a tapered portion (300 provided on one side in the axial direction and having a smaller radial dimension toward one end (24a) in the axial direction. And a shaft body (24A) formed so that the radial dimension on one axial side is smaller than the radial dimension on the other axial side;
A bush that is disposed in the housing and has an inner peripheral surface (301) having a radial dimension centered on the first axis that decreases from the other side in the axial direction toward the one side to form a hollow portion (301a). (24B)
A first positioning portion (330) for determining a position of the bushing in the rotation direction with respect to the shaft main body in a state where the taper portion of the shaft main body is fitted in the hollow portion of the bush.

  According to the first aspect of the present invention, the coaxiality after reassembling the bushing to the shaft body can be brought closer to the coaxiality before the shaft body and the bushing are disassembled. Therefore, it is possible to provide a compressor in which reproducibility of the coaxiality is ensured after the bush is reassembled on the shaft body. The coaxiality of the shaft is a degree indicating how close the axis of the shaft body and the axis of the bush are.

In the invention according to claim 27, the housing (10) constituting the refrigerant chamber (10a);
A shaft (24) disposed within and supported by the housing;
A cylinder (21) disposed in the housing and formed in a cylindrical shape and rotatably supported with respect to the shaft and rotating about the first axis (C1);
A rotor (22a, 22b) disposed within the housing, rotatably supported with respect to the shaft, and rotated about a second axis (C2) eccentric with respect to the first axis;
A transmission mechanism (251a, 251b) for connecting the cylinder and the rotor and rotating the cylinder and the rotor in synchronization;
Vanes (23a, 23b) for partitioning the working chamber between the inner peripheral surface of the cylinder and the outer peripheral surface of the rotor,
The shaft is provided with an intake refrigerant flow path (24d) through which refrigerant flows, and the rotor is provided with introduction refrigerant flow paths (224a, 224b) that guide the refrigerant from the intake refrigerant flow path to the working chamber. ,
The working chamber is deformed by the rotation of the cylinder, the rotor, and the vane, the refrigerant is sucked into the working chamber through the suction refrigerant flow path and the introduction refrigerant flow path, and compressed in the working chamber to discharge the high-pressure refrigerant through the refrigerant chamber ( 11a), a method of manufacturing a compressor for discharging,
The shaft
A shaft body formed so as to extend in the axial direction of the first axis, a tapered portion (300 provided on the other axial side and having a smaller radial dimension toward the other axial side end (24a). And a shaft body (24A) formed so that the radial dimension on the other axial side is smaller than the radial dimension on the one axial side;
A bush (24B) having an inner peripheral surface (301) having a radial dimension centered on the first axis that decreases as it approaches the other side from one side in the axial direction, forming a hollow portion (301a). ,
A first positioning step (S110) in which the taper portion of the shaft body is fitted in the hollow portion of the bush and the position of the bush in the rotation direction with respect to the shaft body is determined by the positioning portion (330);
A processing step (S120) of processing the shaft main body and the bush so that the axis of the bush is brought close to the first axis of the tapered portion of the shaft main body in a state where the position of the bush in the rotation direction with respect to the shaft main body is determined by the first positioning portion; ,
A disassembling step (S130) for disassembling the shaft body and the bush after the processing step;
After the disassembling process, in a state where the shaft main body is fitted in the through hole of the rotor, a second positioning process (positioning the rotational direction of the bush with respect to the shaft main body by fitting the tapered portion of the shaft main body into the hollow portion of the bush) S150).

  According to the twenty-seventh aspect of the present invention, the coaxiality after reassembling the bushing to the shaft body can be made closer to the coaxiality before the shaft body and the bushing are disassembled. Therefore, it is possible to provide a compressor in which reproducibility of the coaxiality is ensured after the bush is reassembled on the shaft body. The coaxiality of the shaft is a degree indicating how close the axis of the shaft body and the axis of the bush are.

  In addition, the code | symbol in the bracket | parenthesis of each means described in this column and the claim shows the correspondence with the specific means as described in embodiment mentioned later.

It is a figure showing the section composition of the cylinder rotation type compressor in a 1st embodiment of the present invention. It is II-II sectional drawing in FIG. FIG. 2 is an exploded view of main components of the cylinder rotary compressor in FIG. 1. FIG. 3 is a cross-sectional view of a rotor and a cylinder in FIG. 2. (A) is a cross-sectional view showing the periphery of the bush in FIG. 1, (b) is an enlarged view of the wedge ring in FIG. 1, (c) is a Z arrow view in (a), (d) is V in (a). -V sectional view. It is a schematic diagram which shows the action | operation of the cylinder rotation type compressor in 1st Embodiment. It is a flowchart about the manufacturing process of the cylinder rotation type compressor in a 1st embodiment. It is a figure which shows the dimensional relationship of the shaft main body of the cylinder rotation type compressor which is proportional. It is a figure which shows the dimensional relationship of the shaft main body of the cylinder rotation type compressor in 1st Embodiment. It is a figure which shows a part of shaft main body and bush of a cylinder rotary compressor which is the 1st modification of 1st Embodiment. It is a figure which shows a part of shaft main body of a cylinder rotary compressor which is a 2nd modification of 1st Embodiment, and a bush. It is sectional drawing of the cylinder rotary compressor of 2nd Embodiment of this invention. It is a figure which shows the bush periphery in FIG. It is sectional drawing of the cylinder rotation type compressor of the 1st modification of 2nd Embodiment of this invention. It is a figure which shows the periphery of the bush of the 2nd modification of 2nd Embodiment of this invention. It is a figure which shows the periphery of the bush of the 3rd modification of 2nd Embodiment of this invention. It is a figure which shows the periphery of the bush of the 4th modification of 2nd Embodiment of this invention. It is sectional drawing which shows the periphery of a bush among the shafts in 3rd Embodiment of this invention. It is sectional drawing which shows the periphery of a bush among the shafts in 3rd Embodiment. It is sectional drawing which shows the periphery of a bush among the shafts in 3rd Embodiment. It is sectional drawing to which the periphery of the bush was expanded among the shafts in 3rd Embodiment. It is sectional drawing which shows the periphery of a bush among the shafts in 3rd Embodiment. FIG. 20B is a sectional view taken along the line III-III in FIG. 20A. It is IV-IV sectional drawing in FIG. 20A. It is sectional drawing which shows the periphery of a bush among the shafts in 4th Embodiment of this invention. It is VV sectional drawing in FIG. 21A. It is sectional drawing which shows the periphery of a bush among the shafts in the 1st modification of 5th Embodiment of this invention. It is VI-VI sectional drawing in FIG. 22A. It is sectional drawing which shows the periphery of a bush among the shafts in the 1st modification of 5th Embodiment of this invention. It is a perspective view which shows the side plate in 6th Embodiment of this invention. It is a perspective view which shows the side plate in the 1st modification of 6th Embodiment of this invention. It is a perspective view which shows the periphery of a bush among the shafts of 7th Embodiment of this invention. It is a X1 arrow line view in FIG. 26A. It is a perspective view which shows the periphery of a bush among the shafts of the 1st modification of 7th Embodiment of this invention. It is a X2 arrow line view in FIG. 27A. It is sectional drawing of the cylinder rotation type compressor in a 1st proportionality. It is sectional drawing of the cylinder rotation type compressor in the 2nd proportionality.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. In the following embodiments, parts that are the same or equivalent to each other are given the same reference numerals in the drawings in order to simplify the description.

(First embodiment)
The present embodiment will be described with reference to FIGS. In the present embodiment, an example in which the cylinder rotary compressor 1 is applied to a vapor compression refrigeration cycle that cools blown air that is blown into a vehicle interior by a vehicle air conditioner will be described. Hereinafter, the cylinder rotary compressor 1 may be simply referred to as the compressor 1.

  The compressor 1 has a function of sucking, compressing and discharging refrigerant of the refrigeration cycle. In this embodiment, the refrigerant of the refrigeration cycle corresponds to the fluid to be compressed. In the refrigeration cycle of the present embodiment, an HFC refrigerant (for example, R134a) is adopted as the refrigerant. The refrigerant is mixed with refrigerating machine oil which is a lubricating oil for lubricating the sliding portion of the compressor 1. A part of the refrigerating machine oil circulates in the cycle together with the refrigerant.

  Hereinafter, after describing the basic configuration and basic operation of the compressor 1, the characteristic configuration of the compressor 1 of the present embodiment will be described. As shown in FIG. 1, the compressor 1 includes an electric motor 30 in which a compression mechanism 20 that compresses and discharges a refrigerant and an electric motor 30 that drives the compression mechanism 20 are housed in a housing 10 that forms an outer shell thereof. It is configured as a compressor.

  The housing 10 of this embodiment is configured by combining a plurality of metal members. The housing 10 of the present embodiment has a sealed container structure that forms a substantially cylindrical space therein.

  Specifically, the housing 10 includes a bottomed cylindrical (that is, cup-shaped) main housing 11, a bottomed cylindrical sub-housing 12 that closes an opening of the main housing 11, and an opening of the sub-housing 12. It has a disk-shaped lid member 13 that closes. The housing 10 has a sealed container structure by combining the main housing 11, the sub-housing 12, and the lid member 13.

  The main housing 11 and the sub housing 12 constitute a refrigerant chamber 10a as a space for accommodating the compression mechanism 20 and the electric motor 30. The sub-housing 12 and the lid member 13 constitute a space 10b that houses the drive circuit 30a.

  It should be noted that a seal member (not shown) made up of an O-ring or the like is disposed at the contact portion of the main housing 11, the sub housing 12, and the lid member 13 in order to prevent refrigerant leakage from each contact portion. .

  A discharge port 11 a for discharging the refrigerant compressed by the compression mechanism 20 to the outside of the housing 10 is formed on the side surface of the main housing 11. The discharge port 11a is connected to the refrigerant flow upstream side of a condenser of a refrigeration cycle (not shown).

  Further, a suction port 12 a for sucking a refrigerant compressed by the compression mechanism 20 from the outside of the housing 10 is formed on the side surface of the sub housing 12. The suction port 12a is connected to the refrigerant flow downstream side of the evaporator of the refrigeration cycle.

  Furthermore, a housing-side suction passage 13a for guiding the refrigerant sucked from the suction port 12a to the working chamber Va and the working chamber Vb of the compression mechanism 20 is formed between the sub housing 12 and the lid member 13. .

  In addition, a driving circuit 30 a that controls electric power supplied to the electric motor 30 is attached to the lid member 13 on a surface opposite to the surface on the sub housing 12 side (that is, a surface exposed to the outside).

  The electric motor 30 has a stator 31 that is a stator. The stator 31 includes a cylindrical stator core 31a formed of a metallic magnetic material, and a stator coil 31b wound around the stator core 31a.

  The stator 31 is fixed to the inner peripheral surface of the main housing 11 by means such as press fitting, shrink fitting, and bolt fastening. The stator 31 is disposed on the outer peripheral side of the cylinder 21 of the compression mechanism 20.

  The stator coil 31b is connected to the drive circuit 30a via a sealed terminal 30b disposed in the sub housing 12. The sealing terminal 30b is a hermetic seal terminal that seals between the refrigerant chambers 10a and 10b.

  When electric power is supplied from the drive circuit 30a to the stator coil 31b via the sealed terminal 30b, the electric motor 30 generates a rotating magnetic field that rotates the cylinder 21 disposed on the inner peripheral side of the stator 31.

  The cylinder 21 is a cylindrical member formed of a metallic magnetic material. The cylinder 21 is a member that forms working chambers Va and Vb of the compression mechanism 20 between a rotor 22a and a rotor 22b described later.

As shown in the sectional views of FIGS. 1 and 2, a plurality of permanent magnets 32 are embedded in the cylinder 21. The plurality of permanent magnets 32 are arranged in the circumferential direction of the cylinder 21, respectively.
A rotational force that rotates about the axis C <b> 1 is generated in the plurality of permanent magnets 32 of the cylinder 21 based on the rotating magnetic field generated from the stator 31. Thereby, the cylinder 21 also has a function as a rotor of the electric motor 30.

  Thus, in the compressor 1 of the present embodiment, the rotor of the electric motor 30 and the cylinder 21 of the compression mechanism 20 are configured as an integrally molded product. Of course, the rotor of the electric motor 30 and the cylinder 21 of the compression mechanism 20 may be configured as separate members and integrated by means such as press-fitting.

  Next, the compression mechanism 20 including the aforementioned cylinder 21 will be described. The compression mechanism 20 of this embodiment is comprised by compression mechanism part 20a, 20b. The basic structures of the compression mechanism portions 20a and 20b are equivalent to each other. Further, the compression mechanism portions 20 a and 20 b are connected in parallel to the refrigerant flow inside the housing 10.

  Furthermore, the compression mechanism parts 20a and 20b are arranged side by side in the axial direction of the axis C1 of the cylinder 21, as shown in FIG. In the present embodiment, among the compression mechanism portions 20a and 20b, the compression mechanism portion 20a is disposed on the bottom surface side of the main housing 11, and the compression mechanism portion 20b is disposed on the sub housing 12 side.

  Moreover, in each drawing, the code | symbol of the thing corresponding to the equivalent structural member of the compression mechanism part 20a among the structural members of the compression mechanism part 20b is changed and shown from "a" to "b". . For example, among the constituent members of the compression mechanism portion 20b, the second rotor corresponding to the rotor 22a of the compression mechanism portion 20a is denoted by the symbol “22b”.

  For this reason, the compression mechanism part 20a is comprised by the cylinder 21, the rotor 22a, the vane 23a, the shaft main body 24A, etc. The compression mechanism portion 20b includes a cylinder 21, a rotor 22b, a vane 23b, a shaft body 24A, and the like.

  The compression mechanism part 20a and the compression mechanism part 20b of this embodiment are comprised including the common cylinder 21 and the shaft main body 24A. Specifically, as shown in FIG. 1, in the cylinder 21 and the shaft main body 24A, a part on the bottom surface side of the main housing 11 constitutes a compression mechanism portion 20a, and a part on the sub housing 12 side is a compression mechanism. Part 20b is configured.

  As described above, the cylinder 21 rotates around the axis C1 as a rotor of the electric motor 30, and has a cylindrical shape that forms the working chamber Va of the compression mechanism portion 20a and the working chamber Vb of the compression mechanism portion 20b therein. It is a member.

  A side plate 25 a that closes an opening that opens to one side in the axial direction is fixed to the cylinder 21 by means such as bolting. Further, a side plate 25b that closes an opening that opens to the other side in the axial direction is fixed to the cylinder 21 by the same means. The side plates 25 a and 25 b constitute a closing member that closes the openings that open at both ends of the cylinder 21.

  The side plates 25a and 25b have a disc-shaped portion that extends in a direction perpendicular to the axis C1 of the cylinder 21, and a boss portion that is disposed at the center of the disc-shaped portion and projects in the axial direction of the axis C1. . Furthermore, through holes 250a and 250b are formed in the boss portions of the side plates 25a and 25b so as to penetrate in the axial direction of the axis C1.

  The shaft body 24A is inserted into the through holes 250a and 250b. Thereby, the cylinder 21 is rotatably supported with respect to the shaft main body 24A via the side plates 25a and 25b.

  A disc-shaped intermediate side plate 25c is disposed inside the cylinder 21 of the present embodiment. The inside of the cylinder 21 is partitioned into a working chamber Va and a working chamber Vb by an intermediate side plate 25c. In the present embodiment, the intermediate side plate 25 c is disposed at a substantially central portion in the axial direction of the cylinder 21.

  Subsequently, the shaft main body 24A, together with the bush 24B, constitutes a substantially cylindrical shaft 24 that rotatably supports the side plates 25a, 25b, 25c fixed to the cylinder 21 and the rotors 22a, 22b.

  One end and the other end of the shaft main body 24A in the axial direction are fixed to the main housing 11 and the sub housing 12 of the housing 10, respectively. The bush 24B is fitted into one end portion in the axial direction of the shaft body 24A. A specific structure of the bush 24B will be described later. Therefore, the shaft body 24A and the bush 24B do not rotate with respect to the housing 10.

  Further, an eccentric portion 24c having an outer diameter smaller than that of the other end portion in the axial direction is provided at the central portion in the axial direction of the shaft main body 24A. The central axis of rotation of the eccentric portion 24 c is an eccentric shaft C 2 that is eccentric with respect to the axis C 1 of the cylinder 21. That is, the eccentric portion 24c is formed in a columnar shape having the eccentric axis C2 as an axis.

  The rotor 22a and the rotor 22b are rotatably supported on the eccentric portion 24c of the shaft main body 24A via a bearing mechanism (not shown). In the present embodiment, the eccentric shaft of the rotor 22a and the eccentric shaft of the rotor 22b are arranged so as to coincide with each other so that the rotors 22a and 22b rotate around the common eccentric shaft C2.

  As shown in FIG. 1, a shaft side suction passage 24d is formed in the shaft main body 24A so as to communicate with the refrigerant flowing in from the outside to the working chambers Va and Vb. A plurality of (for example, four) first and second shaft side outlet holes 240a and 240b through which the refrigerant flowing through the shaft side suction passage 24d flows out are opened on the outer peripheral surface of the shaft body 24A. In the present embodiment, the shaft side suction passage 24d constitutes a supply passage for supplying fluid from the outside.

  Subsequently, the rotor 22 a is a cylindrical member that is disposed inside the cylinder 21 and extends in the axial direction of the axis C <b> 1 of the cylinder 21. The rotor 22a is rotatably supported by the eccentric portion 24c of the shaft body 24A. For this reason, the rotor 22a rotates around the eccentric shaft C2 that is eccentric with respect to the axis C1 of the cylinder 21.

  As shown in FIG. 1, the length of the rotor 22 a in the axial direction is formed to have substantially the same dimension as the length of the shaft main body 24 </ b> A and the portion constituting the compression mechanism 20 a of the cylinder 21 in the axial direction. Further, the outer diameter dimension of the rotor 22 a is smaller than the inner diameter dimension of the columnar space formed inside the cylinder 21. As shown in FIG. 1, the outer diameter dimension of the rotor 22a of this embodiment is set so that the outer peripheral surface 225a of the rotor 22a and the inner peripheral surface 21a of the cylinder 21 are close to each other at one proximity portion C3. This point will be described in detail later.

  A power transmission mechanism 251a is disposed between the rotor 22a and the intermediate side plate 25c and between the rotor 22a and the side plate 25a.

  The power transmission mechanism 251a transmits a rotational driving force from the cylinder 21 to the rotor 22a so that the rotor 22a rotates in synchronization with the cylinder 21.

  The power transmission mechanism 251a of this embodiment is configured by a mechanism equivalent to a transmission mechanism that connects the cylinder and the roller so as to rotate at a constant speed in Patent Document 1. That is, the power transmission mechanism 251a includes a plurality of circular first holes formed on the surface of the rotor 22a on the intermediate side plate 25c side, and a plurality of drive pins protruding from the intermediate side plate 25c toward the rotor 22a. It consists of Each drive pin protrudes in the axial direction toward the rotor 22a side, and is fitted in the first hole. The same applies to the power transmission mechanism 251a provided between the rotor 22a and the side plate 25a.

  On the outer peripheral surface 225a of the rotor 22a, as shown in FIG. 2, a groove 222a that is recessed toward the inner peripheral side over the entire region in the axial direction is formed. A vane 23a described later is slidably fitted in the groove 222a.

  The groove part 222a is formed in a shape extending in a direction inclined with respect to the radial direction of the rotor 22a in a cross section orthogonal to the axial direction of the eccentric shaft C2. For this reason, the vane 23a fitted in the groove 222a is displaced in a direction inclined with respect to the radial direction of the rotor 22a.

  Further, as shown in FIG. 3, the rotor 22a extends at an incline with respect to the radial direction as in the groove portion 222a, and communicates the outer peripheral surface 225a side and the inner peripheral surface 226a side of the rotor 22a. A passage 224a is formed.

  The fluid outlet of the rotor side suction passage 224a opens immediately after the rotation direction of the groove 222a. As a result, the refrigerant flowing from the outside into the shaft side suction passage 24d is guided to the rotor side suction passage 224a side.

  The vane 23a has a working chamber Va formed between the outer peripheral surface 225a of the rotor 22a and the inner peripheral surface 21a of the cylinder 21. The first suction space Va_IN that sucks the refrigerant and the first compression space Va_OUT that compresses the refrigerant. It is a plate-shaped partition member partitioned into two.

  The length of the vane 23a in the axial direction is substantially the same as the length of the rotor 22a in the axial direction. Furthermore, the outer peripheral side end of the vane 23 a is arranged to be slidable with respect to the inner peripheral surface 21 a of the cylinder 21.

  Further, as shown in FIG. 1, the side plate 25 a is formed with a discharge hole 252 a through which the refrigerant compressed in the working chamber Va is discharged to the internal space of the housing 10. Further, the side plate 25a is provided with a first discharge valve 26a that opens the discharge hole 252a when the refrigerant pressure in the first compression space Va_OUT of the working chamber Va exceeds a predetermined discharge pressure.

  The first discharge valve 26a of the present embodiment is constituted by, for example, a reed valve that suppresses the refrigerant in the internal space of the housing 10 from flowing back to the working chamber Va through the discharge hole 252a.

  Next, the compression mechanism unit 20b will be described. As described above, the basic configuration of the compression mechanism 20b is the same as that of the compression mechanism 20a. Therefore, as shown in FIG. 1, the rotor 22 b is configured by a cylindrical member having a dimension substantially the same as the axial length of the parts constituting the shaft main body 24 </ b> A and the compression mechanism portion 20 b of the cylinder 21.

  Furthermore, the eccentric shaft C2 of the rotor 22b and the eccentric shaft C2 of the rotor 22a coincide. For this reason, the outer peripheral surface 225b of the rotor 22b and the inner peripheral surface 21a of the cylinder 21 are close to each other at the proximity portion C3 shown in FIG. 2 in the same manner as the rotor 22a.

  Between the rotor 22b and the intermediate side plate 25c and between the rotor 22b and the side plate 25a, a power transmission mechanism 251b that transmits the rotational driving force from the cylinder 21 to the rotor 22b is provided. In the power transmission mechanism 251b, a plurality of circular second holes into which a plurality of drive pins are fitted are formed in the rotor 22b, similarly to the power transmission mechanism 251a. A ring member similar to the first hole portion is fitted into the second hole portion.

  Further, as shown by a broken line in FIG. 2, a groove 222b that is recessed toward the inner periphery over the entire area in the axial direction is formed on the outer peripheral surface 225b of the rotor 22b. A vane 23b is slidably fitted in the groove 222b.

  Similarly to the groove portion 222a, the groove portion 222b is formed in a shape extending in a direction inclined with respect to the radial direction of the rotor 22b in a cross section orthogonal to the axial direction of the eccentric shaft C2.

  Further, as shown by a broken line in FIG. 3, the rotor 22b extends at an angle with respect to the radial direction as in the case of the groove portion 222b, and communicates the outer peripheral surface 225b side and the inner peripheral surface 226b side of the rotor 22b. A side suction passage 224b is formed.

  The vane 23b has a working chamber Vb formed between the outer peripheral surface 225b of the rotor 22b and the inner peripheral surface 21a of the cylinder 21. The second suction space Vb_IN that sucks the refrigerant and the second compression space Vb_OUT that compresses the refrigerant. It is a plate-shaped partition member partitioned into two. The length of the vane 23b in the axial direction is formed to have substantially the same dimension as the length of the rotor 22b in the axial direction. Furthermore, the outer peripheral side end of the vane 23 b is slidably disposed with respect to the inner peripheral surface 21 a of the cylinder 21.

  Further, the side plate 25b is formed with a discharge hole 252b through which the refrigerant compressed in the working chamber Vb is discharged into the internal space of the housing 10. Further, the side plate 25b is provided with a discharge valve 26b that opens the discharge hole 252b when the refrigerant pressure in the second compression space Vb_OUT of the working chamber Vb exceeds a predetermined discharge pressure. The discharge valve 26b of the present embodiment is a reed valve that suppresses the refrigerant in the internal space of the housing 10 from flowing back to the working chamber Vb through the discharge hole 252b.

  As shown by the broken line in FIG. 3, the compression mechanism portion 20b of the present embodiment has components such as the vane 23b, the rotor-side suction passage 224b, the discharge hole 252b, and the like approximately 180 with respect to the components of the compression mechanism portion 20a. ° Arranged at out-of-phase positions.

  Next, details of the structure of the shaft main body 24A and the bush 24B of the present embodiment will be described with reference to FIG.

  The shaft main body 24A is formed so that the radial dimension on one axial side is smaller than the radial dimension on the other axial side.

On one side in the axial direction of the shaft main body 24A, a tapered portion 300 having a radial dimension that decreases toward the one end 24a in the axial direction is provided. An eccentric portion 24c is provided on the other side in the axial direction with respect to the tapered portion 300 in the shaft main body 24A. For this reason, the end surface 310 is provided in the taper part 300 side among the eccentric parts 24c. The end face 310 is
It is a surface part exposed to one axial direction side, Comprising: The base part which supports the bush 24B from the axial direction other side of the axis line C1 is comprised.

The bush 24B is provided with a hollow portion 301a as a space penetrating in the axial direction of the axis C1. As a result, the bush 24B forms an inner peripheral surface 301 whose radial dimension around the axis C1 decreases as it approaches the one side from the other side in the axial direction. The inner peripheral surface 301 is a surface that forms the hollow portion 301a in the bush 24B.
A concave portion 320 is provided on the outer peripheral surface of the tapered portion 300 so as to be recessed radially inward. On the other hand, the inner peripheral surface 301 of the bush 24B is provided with a recess 335 that is recessed radially inward. The recess 335 is opened on the other side in the axial direction of the axis C1.

  The concave portion 320 on the outer peripheral surface of the tapered portion 300 and the concave portion 335 on the inner peripheral surface of the bush 24B face each other to constitute a region in which the positioning key 330 is fitted. The positioning key 330 contacts the concave portion 320 of the tapered portion 300 and the concave portion 335 of the bush 24B, thereby restricting the bush 24B from rotating about the axis C1 with respect to the shaft main body 24A. That is, the positioning key 330 plays a role of a determining part for determining the position of the bush 24B in the rotational direction with respect to the shaft body 24A.

  A concave portion 323 that is recessed radially inward is provided on one side in the axial direction with respect to the concave portion 320 of the tapered portion 300. The concave portion 323 is provided in the tapered portion 300 over the circumferential direction centering on the axis C1. The recess 323 is open radially outward on one side in the axial direction with respect to the bush 24B.

  A wedge ring 340 is fitted in the recess 323. The wedge ring 340 is a ring formed in a C shape with the axis C1 as the center.

  Specifically, the wedge ring 340 is formed such that the thickness dimension K1 on the radially outer side gradually becomes larger than the thickness dimension K2 on the radially inner side. A radially inner side of the wedge ring 340 is fitted into the recess 323, and a radially outer side of the wedge ring 340 supports the bush 24B from one side in the axial direction. Thus, the wedge ring 340 serves as a C-shaped wedge that determines the axial position of the bush 24B with respect to the shaft body 24A.

  Next, the basic operation of the compressor 1 of the present embodiment will be described with reference to FIG.

  FIG. 6 is an explanatory view continuously showing changes in the working chamber Va accompanying the rotation of the cylinder 21 in order to explain the operating state of the compressor 1. In the cross-sectional view corresponding to each rotation angle θ of the cylinder 21 in FIG. 6, the positions of the rotor-side suction passage 224a, the vane 23a, and the like in the cross-sectional view equivalent to FIG. 2 are indicated by solid lines. In FIG. 6, the positions of the rotor-side suction passage 224b and the vane 23b at each rotation angle θ are indicated by broken lines. Further, in FIG. 6, for clarity of illustration, the reference numerals of the respective constituent members are attached to the sectional views corresponding to the rotation angle θ = 0 ° of the cylinder 21, and the reference numerals of the respective constituent members in the other sectional views are omitted. doing. In FIG. 6, the rotation angle θ of the cylinder 21 in a state where the proximity portion C3 and the outer peripheral end portion of the vane 23a overlap each other is set to 0 °.

  As shown in FIG. 6, when the rotation angle θ of the cylinder 21 is 0 °, the first compression space Va_OUT having the maximum volume is formed on the front side in the rotation direction of the vane 23a, and at the rear side in the rotation direction of the vane 23a. A first suction space Va_IN having a minimum volume is formed. Note that the first suction space Va_IN is a space in which the volume of the working chamber Va is increased. In addition, the first compression space Va_OUT is a space that is a stroke for reducing the volume in the working chamber Va.

  When the rotation angle θ of the cylinder 21 increases from 0 °, the cylinder 21, the rotor 22a, and the vane 23a are displaced as shown in the rotation angle θ = 45 ° to 315 ° in FIG. The volume of the space Va_IN increases.

  Thereby, the refrigerant sucked from the suction port 12a formed in the sub housing 12 flows in the order of the housing side suction passage 13a → the first shaft side outlet hole 240a of the shaft side suction passage 24d → the rotor side suction passage 224a, It flows into the first suction space Va_IN.

  At this time, the centrifugal force associated with the rotation of the rotor 22a acts on the vane 23a, so that the outer peripheral end of the vane 23a is pressed against and contacts the inner peripheral surface of the cylinder 21. Accordingly, the working chamber Va is maintained in a state of being divided into the first suction space Va_IN and the first compression space Va_OUT by the vane 23a.

  When the rotation angle θ of the cylinder 21 reaches 360 ° (that is, when the rotation angle θ returns to 0 °), the first suction space Va_IN becomes the maximum volume. Further, when the rotation angle θ of the cylinder 21 is increased from 360 °, the communication between the first suction space Va_IN and the rotor side suction passage 224a is blocked. Thereby, the first compression space Va_OUT is formed on the front side in the rotation direction of the vane 23a.

  Further, when the rotation angle θ of the cylinder 21 is increased from 360 °, the first compression space formed on the front side in the rotation direction of the vane 23a as shown by the point hatching at the rotation angle θ = 405 ° to 675 ° in FIG. The volume of Va_OUT is reduced.

  As a result, the refrigerant pressure in the first compression space Va_OUT increases. When the refrigerant pressure in the first compression space Va_OUT reaches a discharge pressure equal to or higher than the refrigerant pressure in the internal space of the housing 10, the first discharge valve 26a is opened. Thereby, the refrigerant in the first compression space Va_OUT is discharged into the internal space of the housing 10 through the discharge hole 252a.

  In the above description of the operation, the change in the working chamber Va while the rotation angle θ of the cylinder 21 changes from 0 ° to 720 ° has been described in order to clarify the operation mode of the compression mechanism portion 20a. Actually, the refrigerant suction process described when the rotation angle θ of the cylinder 21 changes from 0 ° to 360 ° and the refrigerant described above when the rotation angle θ of the cylinder 21 changes from 360 ° to 720 °. The compression stroke is performed simultaneously when the cylinder 21 makes one rotation.

  The compression mechanism 20b operates in the same manner as the compression mechanism 20a, and compresses and sucks refrigerant. In the compression mechanism unit 20b, the vanes 23b and the like are arranged at positions that are 180 ° out of phase with respect to the vanes 23a and the like of the compression mechanism unit 20a. That is, in the present embodiment, the rotation angle θ of the cylinder 21 at which the refrigerant pressure in the second compression space Vb_OUT reaches the discharge pressure becomes the rotation angle θ of the cylinder 21 at which the refrigerant pressure in the first compression space Va_OUT reaches the discharge pressure. On the other hand, it is shifted by 180 °.

  Therefore, in the second compression space Vb_OUT, the refrigerant is compressed and sucked at a rotation angle that is 180 degrees out of phase with respect to the first compression space Va_OUT. The refrigerant discharged from the compression mechanism portion 20b into the internal space of the housing 10 merges with the refrigerant discharged from the compression mechanism portion 20a, and is discharged from the discharge port 11a of the housing 10.

  Next, the assembly process of this embodiment is demonstrated with reference to FIG.

  First, in the preparation process, the main housing 11, the sub-housing 12, the lid member 13, the shaft body 24A, the bush 24B, the rotors 22a and 22b, the vanes 23a and 23b, the cylinder 21 and the like are separately prepared (step 100).

  In the next step, the positioning key 330 is fitted into the recess 320 of the tapered portion 300 of the shaft body 24A. With the positioning key 330 fitted in the concave portion 320 of the taper portion 300, the taper portion 300 of the shaft body 24A is inserted into the hollow portion 301a of the bush 24B, and the taper portion 300 is brought into contact with the end surface 310 (step 110). .

  At this time, the positioning key 330 is in contact with the inner wall of the recess 335 of the bush 24B. Thereby, the positioning key 330 can determine the position of the rotation direction of the bush 24B with respect to the shaft main body 24A.

  At this time, the wedge ring 340 is fitted into the recess 323 of the bush 24B. At this time, the bush 24B is sandwiched between the wedge ring 340 and the end surface 310 of the eccentric portion 24c in a state where the wedge ring 340 is elastically deformed. Accordingly, the axial position of the axis C1 of the bush 24B relative to the shaft main body 24A can be determined in a state where the shaft main body 24A and the bush 24B are integrated.

  In the next step, the outer shape of the bush 24B is formed by cutting or the like, and the axis line of the bush 24B is made to coincide with the axis line C1 of the shaft body 24A (step 120). As a result, the shaft 24 is formed.

  In the next step, the shaft 24 is disassembled, and the bush 24B, the wedge ring 340, the shaft main body 24A, and the positioning key 330 are separately arranged (step 130).

  In the next step, one side in the axial direction of the shaft body 24A is fitted into the respective through holes of the rotors 22a and 22b to fix the rotors 22a and 22b to the eccentric portion 24c of the shaft body 24A (step 140).

  In the next step, the positioning key 330 is fitted into the concave portion 320 of the tapered portion 300 of the shaft body 24A, and the tapered portion 300 of the shaft main body 24A is moved in a state where the positioning key 330 is fitted into the concave portion 320 of the tapered portion 300. The bush 24B is inserted into the hollow portion 301a (step 150).

  At this time, the positioning key 330 fits into the recess 335 of the bush 24B, and the positioning key 330 can determine the position of the bush 24B in the rotational direction with respect to the shaft body 24A.

  In addition, the wedge ring 340 is fitted into the recess 330 of the bush 24B. At this time, the axial position of the axis C1 of the bush 24B relative to the shaft body 24A can be determined with the wedge ring 340 elastically deformed.

  As a result, the rotors 22 a and 22 b are fixed to the shaft 24.

  In the next step, with the vanes 23a and 23b fitted into the grooves 222a and 222b of the rotors 22a and 22b, the rotors 22a and 22b and the vanes 23a and 23b are passed through the cylinder 21 to form side plates 25a and 25b. , 25c are fixed to the cylinder 21. Thereby, the assembly of the compression mechanism portions 20a and 20b is completed.

  Further, the compression mechanisms 20 a and 20 b and the stator 31 are accommodated in the main housing 11, and the sub-housing 12 is assembled to the main housing 11. At this time, one axial direction side of the shaft 24A is fitted into the recess 11c of the main housing.

  The other axial side of the shaft 24 </ b> A is fitted into the recess 11 d of the sub housing 12. In addition to this, the lid 13 is fixed to the sub-housing 12 with the drive circuit 30a and the like housed in the sub-housing 12 and the sub-housing 12 closed by the lid 13. This completes the assembly of the compressor 1 (step 160).

  According to this embodiment described above, in the compressor 1, the shaft 24 includes the shaft body 24A and the bush 24B. The shaft main body 24A is a shaft main body formed so as to extend in the axial direction of the axis C1, and is provided on one side in the axial direction and becomes a tapered portion whose radial dimension decreases toward the one end 24a in the axial direction. 300, and is formed so that the radial dimension on one side in the axial direction is smaller than the radial dimension on the other side in the axial direction. The bush 24B has a hollow portion 301a having an inner peripheral surface 301 whose radial dimension about the axis C1 decreases from the other side in the axial direction toward one side.

In the method for manufacturing the compressor 1 according to the present embodiment, the taper portion 300 of the shaft main body 24A is fitted into the hollow portion 301a of the bush 24B, and the position in the rotation direction of the bush 24B with respect to the shaft main body 24A is determined by the positioning key 330. A process (step 110);
Processing in which the shaft main body 24A and the bush 24B are processed so that the axis of the bush 24B is aligned with the axis of the tapered portion 300 of the shaft main body 24A in a state where the positioning key 330 determines the position of the bush 24B in the rotation direction with respect to the shaft main body 24A. A process (step 120), and a fitting process (step 140) in which the shaft main body 24A and the bush 24B are disassembled after the processing process and then one side in the axial direction of the shaft main body 24A is fitted into the through holes of the rotors 22a and 22b; With the shaft main body 24A fitted in the through holes of the rotors 22a and 22b, the taper portion 300 of the shaft main body 24A is fitted into the hollow portion of the bush 24B, and the position of the bush 24B in the rotational direction with respect to the shaft main body 24A is determined by the positioning key 330. Second positioning step for positioning ( Includes a 150), the.

  Therefore, the coaxiality after reassembling the bush 24B to the shaft main body 24A can be made closer to the coaxiality before the shaft main body 24A and the bush 24B are disassembled. Therefore, after the shaft main body 24A and the bush 24B are once disassembled, it is possible to reproduce a state in which the axis of the bush 24B matches the axis of the tapered portion 300 of the shaft main body 24A.

  As described above, it is possible to provide the compressor 1 in which the reproducibility of the coaxiality is ensured after the bush 24B is reassembled to the shaft main body 24A. The coaxiality of the shaft 24 is a degree indicating how close the axis of the shaft body 24A and the axis of the bush 24B are.

  In the manufacturing process of the cylinder rotary compressor 1 of the present embodiment, the position of the bushing 24B in the rotation direction with respect to the shaft body 24A is determined by the positioning key 330 in the first positioning process and the second positioning process, and the shaft is formed by the wedge ring 340. The position of the bush 24B in the axial direction with respect to the main body 24A is determined. Thereby, the state which made the axis line of the bush 24B correspond to the axis line of the taper part 300 of the shaft main body 24A can be reproduced with high accuracy.

  In the present embodiment, the outer diameter dimension of the shaft body 24A on the other side in the axial direction is D1, and the outer diameter dimension of the eccentric portion 24c that rotatably supports the rotors 22a and 22b of the shaft body 24A is D2. If the distance between the axis of the shaft body 24A and the axis of the eccentric portion 24c is d and the outer diameter of the bush 24B is D3, D1 ≧ D2 + 2 × d, D3 ≧ D2 + 2 × d, and D1 = D3 are satisfied. Yes.

On the other hand, as shown in FIG. 8A, when D1 <D2 + 2 × d and D3 <D2 + 2 × d are satisfied, when assembling the side plate 25b and the shaft main body 24A, If you try to insert the side into the side plate 25b,
The other side in the axial direction of the shaft main body 24A hits the side plate 25b, and the shaft main body 24A cannot be passed through the through hole 250b of the side plate 25b. Therefore, it is necessary to penetrate the shaft body 24A from the other side in the axial direction into the through hole 250b of the side plate 25b. For this reason, the freedom degree of the method of assembling the side plate 25b and the shaft main body 24A is low.

  On the other hand, in this embodiment, D1 ≧ D2 + 2 × d, D3 ≧ D2 + 2 × d, and D1 = D3 are satisfied (see FIG. 8B). Therefore, the shaft main body 24A can be passed through the through hole 250b of the side plate 25b from one axial direction side or the other axial direction side. For this reason, the freedom degree of the method of assembling side plate 25b and shaft main part 24A can be made high.

(First modification of the first embodiment)
In the first embodiment, the example in which the tapered portion 300 of the shaft main body 24A is in contact with the inner peripheral surface forming the hollow portion 301a in the bush 24B in the axial direction has been described, but in the first modified example, As shown in FIG. 9, the tapered portion 300 contacts the other axial side 124 and the one axial side 126 of the inner peripheral surface forming the hollow portion 301 a of the bush 24 </ b> B.

  In the first modified example, the inner diameter dimension of the axial direction other side 124 and the axial direction one side 126 of the inner circumferential surface of the bush 24B forming the hollow portion 301a is larger than the inner diameter dimension of the intermediate portion 125. It ’s getting smaller.

  Thereby, the taper part 300 is non-contacting with respect to the intermediate part 125 between the axial direction other side 124 and the axial direction one side 126 among the internal peripheral surfaces which form the hollow part 301a among the bushes 24B.

  For this reason, the tapered portion 300 is made to conform by plastically deforming the other axial side 124 and the one axial side 126 of the inner peripheral surface of the bush 24B, and the tapered portion 300 of the shaft main body 24A of the shaft at the time of reassembly. And the axis of the bush 24B can be minimized.

(Second modification of the first embodiment)
In the first embodiment, the example in which the tapered portion 300 of the shaft main body 24A is in direct contact with the inner peripheral surface forming the hollow portion 301a of the bush 24B has been described, but in the second modified example, FIG. As shown, the membrane 127 is disposed on the inner peripheral surface 123 that forms the hollow portion 301a of the bush 24B, and the tapered portion 300 contacts the inner peripheral surface 123 that forms the hollow portion 301a of the bush 24B via the membrane 127. Let

  As a material of the film 127, a material softer than the tapered portion 300 and the bush 24B is used. When the material of the taper portion 300 and the bush 24B is stainless steel, copper or aluminum can be used as the material of the film 127.

(Second Embodiment)
In the first embodiment, the example in which the wedge ring 340 determines the position of the bush 24B in the axial direction with respect to the shaft main body 24A has been described, but instead of this, the position of the bush 24B in the axial direction of the bush 24B with respect to the shaft main body 24A by bolts and male screws. The second embodiment for determining the above will be described.

  FIG. 11 is a cross-sectional view of the cylinder rotary compressor 1 of the present embodiment, and FIG. 12 is a partially enlarged view of the periphery of the bush 24B in the shaft 24 in FIG.

  The shaft main body 24A of the present embodiment is provided with a male screw 128 that protrudes from the taper portion 300 to one side in the axial direction. The bush 24B is provided with a side wall 131 that is disposed on one side in the axial direction with respect to the hollow portion 301a and that forms a through hole portion 131a through which the male screw 128 passes. The nut 130 is disposed on one side in the axial direction with respect to the side wall 131 and is fastened to the male screw 128 in a state where the side wall 131 is pushed in the other side in the axial direction, whereby the axial direction of the bush 24B with respect to the shaft body 24A is increased. Determine the position.

  In addition, in this embodiment, since it is the same as that of the said embodiment except the structure which determines the position of the axial direction of the bush 24B with respect to the shaft main body 24A, the description is abbreviate | omitted.

(First Modification of Second Embodiment)
In the second embodiment, the example in which the male screw 128 is formed on the shaft main body 24A has been described. Instead, the female screw 151 is formed on the tapered portion 300 of the shaft main body 24A, and the female screw 151 and the male screw 150 are formed. A first modified example for determining the position of the bush 24B in the axial direction relative to the shaft body 24A will be described.

FIG. 13 is a cross-sectional view of the cylinder rotary compressor 1 according to the first modification. In FIG. 13, the configuration other than the female screw 151 and the male screw 150 is the same as that in FIG.

  The female screw 151 of the first modification is formed in a hole that is recessed from the one axial end surface of the tapered portion 300 of the shaft main body 24A to the other axial direction side. The male screw 150 passes through the through hole 131a and is fastened to the female screw 151 with the head 150a pushing the side wall 131 to the other side in the axial direction, whereby the position of the bush 23B in the axial direction with respect to the shaft main body 24A. Decide.

(Second Modification of Second Embodiment)
In the bush 24B of the second modified example, as shown in FIG. 14, surfaces 140a and 140b are formed on the outer periphery of the bush 24B of the first embodiment so as to be parallel to each other with the axis line therebetween. The surfaces 140a and 140b serve as rotation stoppers for the jig to grip the bush 24B.

  Therefore, the jig grasps the surfaces 140a and 140b in the step of determining the axial position of the bush 24B with respect to the shaft body 24A (step 150) using the male screw 128 (or the male screw 150 and the female screw 151). Thus, the rotation of the bush 24B can be stopped. Therefore, the bush 24B can be fixed to the shaft body 24A using the male screw 128 (or the male screw 150 and the female screw 151) in a state where the rotation of the bush 24B is stopped. Thereby, the position of the axial direction of the bush 24B with respect to the shaft main body 24A can be easily determined.

  Further, in the step of disassembling the shaft main body 24A and the bush 24B (step 130), when the male screw 150 is removed from the female screw 151, the jig grasps the bush 24B and stops the bush 24B from rotating. Can do. Thereby, the external thread 150 can be easily removed from the bush 24B.

(Third Modification of Second Embodiment)
In the third modified example, in the bush 24B, as shown in FIG. 15A, grooves 161a and 161b to be gripped by a jig are formed instead of the surfaces 140a and 140b serving as rotation stoppers. The groove portions 161a and 161b are formed in parallel on the outer periphery of the bush 24B with the axis line therebetween.

  Therefore, as in the second modification of the second embodiment, the bushing 24B is removed by the jig 160 when the male screw 150 is removed from the female screw 151 in the step of disassembling the shaft body 24A and the bushing 24B (step 130). To hold the bush 24B from rotating. Thereby, the external thread 150 can be easily removed from the bush 24B.

(Fourth modification of the second embodiment)
In the third modified example, as shown in FIG. 15B, the example in which the grooves 161a and 161b are provided on the outer periphery of the bush 24B has been described. Instead, in the fourth modified example, the step portion of the shaft body 24A is provided. A groove 162 is formed between 311 and the bush 24B.

  The step portion 311 of the shaft body 24A is a portion that is formed on the other side in the axial direction with respect to the bush 24B in the shaft body 24A and serves as a base portion of the taper portion 300. The groove 162 is formed in an annular shape centered on the axis. The groove 162 serves as a rotation stopper that is gripped by the jig 160A.

(Third embodiment)
In the third embodiment, an example in which a lubricating oil separation mechanism 400 that separates lubricating oil from high-pressure refrigerant discharged from the discharge ports 252a and 252b in the cylinder rotary compressor 1 of the first embodiment is added is shown in FIG. Description will be given with reference to FIG.

  As shown in FIG. 16, the lubricating oil separation mechanism 400 is disposed on one side in the axial direction with respect to the main housing 11. An oil storage chamber 415 that temporarily stores the lubricating oil separated from the high-pressure refrigerant by the lubricating oil separating mechanism 400 is formed below the lubricating oil separating mechanism 400 in the vertical direction.

  An oil storage chamber 411 that stores lubricating oil supplied from the lubricating oil separation mechanism 400 through the oil storage chamber 415 is formed below the main housing 11 in the vertical direction.

  A lubricating oil supply passage 101 for supplying the lubricating oil from the oil storage chamber 411 between the outer peripheral surface of the bush 24B and the inner peripheral surface of the side plate 25a is formed in the lid portion on one axial side of the main housing 11. ing. The lid on one side in the axial direction of the main housing 11 is a lid that closes the opening on one side in the axial direction of the main housing 11.

  Here, the outer peripheral surface of the bush 24B and the inner peripheral surface of the side plate 25a each constitute a sliding surface. The outer peripheral surface of the bush 24B and the inner peripheral surface of the side plate 25a are respectively lubricated with lubricating oil. A space between the outer peripheral surface of the bush 24B and the inner peripheral surface of the side plate 25a communicates with the working chamber Va.

  The bush 24B is provided with a lubricating oil supply path 102 that supplies the lubricating oil from the lubricating oil supply path 101 between the outer peripheral surface of the bush 24B and the inner peripheral surface of the side plate 25a.

  The sub-housing 12 is formed with a lubricating oil supply path 103 that supplies the lubricating oil from the oil storage chamber 411 between the outer peripheral surface on the other axial side of the shaft main body 24A and the inner peripheral surface of the side plate 25b. .

  The shaft main body 24A is formed with a lubricating oil supply path 104 that supplies the lubricating oil from the lubricating oil supply path 103 between the outer peripheral surface on the other axial side of the shaft main body 24A and the inner peripheral surface of the side plate 25b. ing.

  Here, the outer peripheral surface on the other side in the axial direction of the shaft main body 24A and the inner peripheral surface of the side plate 25b each constitute a sliding surface. The outer peripheral surface on the other side in the axial direction of the shaft main body 24A and the inner peripheral surface of the side plate 25b are respectively lubricated with lubricating oil. The shaft body 24A communicates with the working chamber Vb between the outer peripheral surface on the other side in the axial direction and the inner peripheral surface of the side plate 25b.

  In FIG. 16, the configuration other than the lubricating oil separation mechanism 400, the oil storage chambers 415 and 411, and the lubricating oil supply passages 101, 102, 103, and 104 is the same as that in FIG.

  In the present embodiment configured as above, the compression mechanisms 20a and 20b are sucked into the working chambers Va and Vb through the suction port 12a and the shaft-side suction passage 24d, respectively, and compressed in the working chambers Va and Vb. The refrigerant is discharged from the discharge holes 252a and 252b to the refrigerant chamber 10a. The high-pressure refrigerant flows from the refrigerant chamber 10a to the lubricating oil separation mechanism 400 through the discharge port 11b.

  The lubricating oil separation mechanism 400 removes lubricating oil from the high-pressure refrigerant from the discharge port 11b, and supplies the refrigerant from which the lubricating oil has been removed to the condenser from the discharge port 11a.

  On the other hand, the lubricating oil separated from the high-pressure refrigerant from the discharge port 11 b in the lubricating oil separation mechanism 400 flows into the oil storage chamber 411 through the oil storage chamber 415. The lubricating oil that has flowed into the oil storage chamber 411 flows into the working chamber Va through the lubricating oil supply paths 101 and 102 and between the outer peripheral surface of the bush 24B and the inner peripheral surface of the side plate 25a. Thereby, the outer peripheral surface of the bush 24B and the inner peripheral surface of the side plate 25a are lubricated.

  Further, the lubricating oil from the oil storage chamber 411 flows into the working chamber Vb through the lubricating oil supply paths 103 and 104 and between the outer peripheral surface of the bush 24B and the inner peripheral surface of the side plate 25b. Thereby, the outer peripheral surface of the bush 24B and the inner peripheral surface of the side plate 25b are each lubricated.

  Here, when the compression mechanism parts 20a and 20b are located in the middle between the support parts 110 and 120, the gap 200 between the support part 110 and the side plate 25a, and between the support part 120 and the side plate 25b. The gaps 210 are approximately the same (see FIG. 17).

  At this time, the refrigerant pressure of the high-pressure refrigerant discharged from the discharge ports 11a and 11b (hereinafter referred to as discharge pressure Ya) acts on the other side in the axial direction on the side plate 25a as a thrust force. On the other hand, the discharge pressure Ya acts on the side plate 25b on one side in the axial direction as a thrust force. For this reason, the discharge pressure Ya acting on the side plate 25a and the discharge pressure Ya acting on the side plate 25b cancel each other. For this reason, the gap 200 between the support part 110 and the side plate 25a and the gap 210 between the support part 120 and the side plate 25b are maintained in the same level.

  On the other hand, when the compression mechanism portions 20a and 20b of the cylinder rotary compressor 1 move to one side in the axial direction due to vibration or the like, the gap 200 between the support portion 110 and the side plate 25a becomes small, and the support portion 120 and the side plate The gap 210 between the two 25b increases (see FIG. 18).

  At this time, an oil film of lubricating oil is formed between the support portion 110 and the side plate 25a. Therefore, the combined pressure Yb of the discharge pressure Ya and the lubricating oil pressure (hereinafter referred to as oil pressure Pm) acts on the side plate 25a as the thrust force on the other side in the axial direction.

  Here, the oil pressure Pm is lower than the discharge pressure Ya due to pressure loss generated in the lubricant separation mechanism 400, the oil storage chambers 415 and 411, and the lubricant supply paths 101 to 104. For this reason, the combined pressure Yb is lower than the discharge pressure Ya. Accordingly, the discharge pressure Yb as the thrust force acting on the side plate 25a is lower than the discharge pressure Ya as the thrust force acting on the side plate 25b. For this reason, the clearance gap 200 between the support part 110 and the side plate 25a becomes small, and the state where the clearance gap 210 between the support part 120 and the side plate 25b is large is maintained.

  For this reason, the frictional force between the support part 110 and the side plate 25a increases, and the power loss increases.

  On the other hand, in this embodiment, in the lubricating oil supply path 102, the oil supply start position 102a (see FIG. 18) connected between the outer peripheral surface of the bush 24B and the inner peripheral surface of the side plate 25a is a gap. It is offset in the axial direction with respect to 200 (see FIG. 19). FIG. 19 shows an example in which the refueling start position 102a is separated from the gap 200 by the distance Lb.

  Therefore, it becomes difficult for the lubricating oil from the lubricating oil supply path 102 to reach the gap 200. For this reason, it is difficult for the oil pressure of the lubricating oil from the lubricating oil supply passage 102 to reach the gap 200, and the pressure Yb as the thrust force acting on the side plate 25a is the discharge pressure Ya even when the gap 200 is small. A value close to.

  Therefore, even when the gap 200 is small and the gap 210 is large, the difference between the thrust force acting on the side plate 25a and the thrust force acting on the side plate 25b is small. Thereby, the frictional force between the support part 110 and the side plate 25a becomes small, and the power loss becomes small.

  In the present embodiment, an oil supply start position 104 a (see FIG. 18) connected between the outer peripheral surface of the shaft body 24 </ b> A and the inner peripheral surface of the side plate 25 b in the lubricating oil supply path 104 is relative to the gap 210. It is offset in the axial direction. Therefore, it becomes difficult for the lubricating oil from the lubricating oil supply path 102 to reach the gap 210.

  For this reason, it is difficult for the oil pressure of the lubricating oil from the lubricating oil supply path 102 to reach the gap 210, and even when the gap 210 is small, the pressure Yb as the thrust force acting on the side plate 25b is the discharge pressure Ya. A value close to. For this reason, even if the gap 200 is large and the gap 210 is small, the difference between the thrust force acting on the side plate 25b and the thrust force acting on the side plate 25b is small. Thereby, the frictional force between the support part 120 and the side plate 25a becomes small, and the power loss becomes small.

  According to the present embodiment described above, the oil supply start position 102 a in the lubricating oil supply path 102 is offset with respect to the gap 200 in the axial direction. For this reason, it becomes difficult for the lubricating oil from the lubricating oil supply path 102 to reach the gap 200. For this reason, even if the gap 200 is large and the gap 210 is small, the difference in thrust force acting on the side plates 25a and 25b is small.

  On the other hand, the oil supply start position 104 a in the lubricant supply path 104 is offset in the axial direction with respect to the gap 210. Therefore, it becomes difficult for the lubricating oil from the lubricating oil supply path 102 to reach the gap 210. For this reason, even if the gap 200 is large and the gap 210 is small, the difference in thrust force acting on the side plates 25a and 25b is small.

  As described above, the frictional force between the support portion 110 (or 120) and the side plate 25a (or 25b) is reduced, and the power loss is reduced.

(First Modification of Third Embodiment)
In the first modified example, in the gap between the inner peripheral surface of the side plate 25a and the outer peripheral surface of the bush 24B of the third embodiment, the cross-sectional area on the other side in the axial direction from the oil supply start position 102a is the oil supply start. It is larger than the cross-sectional area on one side in the axial direction than the position 102a.

  Specifically, on the other side in the axial direction of the bushing 24B from the refueling start position 102a, as shown in FIGS. 20A and 20B, a surface 102d extending in the axial direction is formed on the outer peripheral surface and the cross section is D-shaped. Is formed. For this reason, a lubricating oil flow path is formed between the outer peripheral surface of the bush 24B and the inner peripheral surface of the side plate 25a to flow the lubricating oil supplied from the oil supply start position 102a. Accordingly, the lubricating oil can be satisfactorily supplied between the outer peripheral surface of the bush 24B and the inner peripheral surface of the side plate 25a. On the other hand, as shown to FIG. 20A and FIG. 20C, the cross section is circularly formed in the axial direction other side from the oil supply start position 102a among bush 24B.

  As described above, in the gap between the inner peripheral surface of the side plate 25a and the outer peripheral surface of the bush 24B, the cross-sectional area on one side in the axial direction from the oil supply start position 102a is the region on the other side in the axial direction from the oil supply start position 102a. It is smaller than the cross-sectional area of 102c. Therefore, it becomes difficult for the pressure of the lubricating oil to be transmitted to the gap 200 from the oil supply start position 102a through the gap between the inner peripheral surface of the side plate 25a and the outer peripheral surface of the bush 24B. Therefore, the pressure acting as the thrust force on the side plate 25a can be brought close to the discharge pressure Ya.

  Furthermore, in the first modification, one of the outer peripheral surfaces of the shaft main body 24A on the one axial side from the refueling start position 104a has a flat surface extending in the axial direction and has a D-shaped cross section. And a side plate 25b is formed with a lubricating oil flow path through which the lubricating oil supplied from the oil supply start position 104a flows. On the other hand, of the outer peripheral surface of the shaft main body 24A, the cross section is formed in a circular shape on the other side in the axial direction from the oil supply start position 104a.

  Thereby, in the gap between the inner peripheral surface of the side plate 25b and the outer peripheral surface of the shaft main body 24A, the cross-sectional area of the region on the other side in the axial direction from the oil supply start position 104a is one in the axial direction from the oil supply start position 104a. It is smaller than the cross-sectional area of the side region.

  That is, in the gap between the inner peripheral surface of the side plate 25b and the outer peripheral surface of the shaft body 24A, the cross-sectional area of the region on the one axial side from the oil supply start position 104a is the other axial side from the oil supply start position 104a. It is larger than the cross-sectional area of the region.

  Therefore, it becomes difficult for the pressure of the lubricating oil to be transmitted to the gap 210 from the oil supply start position 104a through the gap between the inner peripheral surface of the side plate 25b and the outer peripheral surface of the shaft body 24A. Therefore, the pressure acting as the thrust force on the side plate 25b can be brought close to the discharge pressure Ya.

(Fourth embodiment)
In the fourth embodiment, as shown in FIG. 21A and FIG. 21B, in the side plate 25a of the cylinder rotary compressor 1 of the first embodiment, it is recessed from the gap 200 side to the other axial direction and radially outward. A plurality of grooves 410 that are open are provided.

  As shown in FIG. 21B, the plurality of grooves 410 according to the present embodiment are arranged in a radial pattern around the axis. For this reason, even when the gap 210 is large and the gap 200 is narrow, the lubricating oil from the refrigerant chamber 10 a enters the plurality of grooves 410. For this reason, the oil pressure Ya of the lubricating oil acts on the side plate 25a as a thrust force.

  The side plate 25b of the present embodiment is provided with a plurality of grooves (not shown) that are recessed from the gap 210 side to one side in the axial direction and open radially outward. The plurality of grooves of the side plate 25b are arranged radially with the axis as the center. For this reason, even when the gap 200 is large and the gap 210 is narrow, the lubricating oil from the refrigerant chamber 10a enters the plurality of grooves. Therefore, the oil pressure Ya of the lubricating oil acts on the side plate 25b as a thrust force.

(Fifth embodiment)
In the fourth embodiment, the example in which the plurality of grooves 410 of the side plate 25a are arranged radially has been described. Instead, the plurality of grooves 410 are arranged in the rotation direction, and the plurality of grooves 410 are arranged in the rotation direction. A fifth embodiment that is inclined will be described with reference to FIGS. 22A and 22B.

  In the side plate 25a of the present embodiment, the plurality of grooves 410a are formed such that the radially outer side of each of the plurality of grooves 410a is positioned in the rotational direction rather than the radially inner side of each of the plurality of grooves 410a. Yes. For this reason, with the rotation of the side plate 25a, the discharged refrigerant from the refrigerant chamber 10a easily enters and becomes cheaper on the radially inner side of the plurality of grooves 410a. Therefore, the discharge pressure Ya is easily applied as a thrust force on the side plate 25a on the radially inner side of the plurality of grooves 410a.

  In the side plate 25b of the present embodiment, the plurality of grooves are arranged in the rotational direction, and the radially outer side of each of the plurality of grooves is positioned in the rotational direction rather than the radially inner side of each of the plurality of grooves. A plurality of grooves are formed. For this reason, with the rotation of the side plate 25b, the refrigerant discharged from the refrigerant chamber 10a easily enters the radially inner side of the plurality of grooves. Therefore, the discharge pressure Ya is likely to act as a thrust force on the inner side in the radial direction of the plurality of grooves 410a with respect to the side plate 25b.

(First Modification of Fifth Embodiment)
In the fifth embodiment, the example in which the plurality of grooves 410 are inclined in the rotation direction in the side plate 25a has been described, but instead, in the first modification, as shown in FIG. 23, the side plate 25a In FIG. 5, the plurality of grooves 410b are arranged in the rotation direction, and the plurality of grooves 410b are formed in a “<” shape so as to protrude rearward in the rotation direction.

  In this case, the refrigerant discharged from the refrigerant chamber 10a can easily enter the convex portions of the plurality of grooves 410b. Therefore, the discharge pressure Ya is easily applied as a thrust force to a convex portion (specifically, in the radial center) of the plurality of grooves 410b with respect to the side plate 25a.

  In the first modification, a plurality of grooves are arranged in the rotation direction in the side plate 25b, and the plurality of grooves are each formed in a “<” shape and protruded rearward in the rotation direction. In this case, the refrigerant discharged from the refrigerant chamber 10a can easily enter the convex portions of the plurality of grooves. Therefore, the discharge pressure Ya is likely to act as a thrust force on the convex portion (specifically, the radial center side) of the plurality of grooves with respect to the side plate 25b.

(Sixth embodiment)
In the sixth embodiment, as shown in FIG. 24, a groove 420 is formed in a spiral shape around the axis of the shaft body 24A on the inner peripheral surface 260 of the side plate 25a of the first embodiment. .

  The groove 420 guides the lubricating oil supplied from the lubricating oil supply path 102 to the other side in the axial direction in the gap between the side plate 25a and the bush 24B. For this reason, the space between the side plate 25a and the bush 24B can be lubricated in the axial direction.

  In the present embodiment, a groove is formed in a spiral shape around the axis of the shaft main body 24A on the inner peripheral surface of the side plate 25b. The groove guides the lubricating oil supplied from the lubricating oil supply path 104 to one side in the axial direction in the gap between the side plate 25b and the shaft body 24A. For this reason, the space between the side plate 25b and the shaft body 24A can be lubricated in the axial direction.

(First Modification of Sixth Embodiment)
In the sixth embodiment, the example in which one groove 420 is spirally formed on the inner peripheral surface 260 of the side plate 25a has been described. Instead, in the first modified example, FIG. As shown, two grooves 420 and 421 are formed in a spiral shape around the axis of the shaft main body 24A on the inner peripheral surface 260 of the side plate 25a.

(Seventh embodiment)
In the seventh embodiment, as shown in FIGS. 26A and 26B, the lubricating oil supply path 102 is radially outward on one side 501 in the axial direction from the oil supply start position 102a in the bush 24B of the first embodiment. It is opened over the axial direction.

  For this reason, the lubricating oil from the lubricating oil supply path 102 can be supplied between the support part 110 and the bush 24B. Therefore, an oil film of lubricating oil can be formed between the support portion 110 and the bush 24 </ b> B to seal between the lubricating oil supply path 101 and the gap 200.

  The lubricating oil supply path 104 of the shaft main body 24B of the present embodiment is opened in the axial direction outside in the radial direction. For this reason, the lubricating oil from the lubricating oil supply path 103 can be supplied between the support portion 120 and the shaft main body 24A. Therefore, an oil film of lubricating oil can be formed between the support portion 120 and the shaft main body 24A to seal between the lubricating oil supply path 103 and the gap 210.

(First Modification of Seventh Embodiment)
In the first modified example, as shown in FIGS. 27A and 27B, the bush 24B communicates with the lubricating oil supply passage 102 on the axial direction one side 501 from the oil supply start position 102a and extends in the circumferential direction. An opening groove 520 is provided.

  The groove portion 520 constitutes a lubricating oil passage that supplies the lubricating oil from the lubricating oil supply passage 102 between the support portion 110 and the bush 24B. For this reason, the lubricating oil from the lubricating oil supply path 102 can be reliably supplied between the support portion 110 and the bush 24B. Therefore, an oil film of lubricating oil can be reliably formed between the support portion 110 and the bush 24B, and the gap between the lubricating oil supply path 101 and the gap 200 can be sealed with high accuracy.

  A groove portion that communicates with the lubricating oil supply passage 104 and opens in the circumferential direction is provided on the other axial side of the shaft main body 24B of the first modification from the oil supply start position 104a. For this reason, the lubricating oil from the lubricating oil supply path 103 can be reliably supplied between the support portion 120 and the shaft body 24A. Therefore, an oil film of lubricating oil can be reliably formed between the support portion 120 and the shaft body 24A, and the space between the lubricating oil supply path 103 and the gap 210 can be reliably sealed.

(Other embodiments)
(1) In the first to seventh embodiments and the modifications, the example in which the cylinder rotary compressor 1 is applied to a vehicle air conditioner has been described, but instead of this, an installation type other than the vehicle air conditioner is used. The cylinder rotary compressor 1 may be applied to an air conditioner, an air conditioner for a moving body such as an airplane or a train, or various refrigeration cycle apparatuses.

  (2) It should be noted that the present invention is not limited to the embodiment described above, and can be appropriately changed within the scope described in the claims. Further, the above embodiments are not irrelevant to each other, and can be combined as appropriate unless the combination is clearly impossible. In each of the above-described embodiments, it is needless to say that elements constituting the embodiment are not necessarily indispensable except for the case where it is clearly indicated that the element is essential and the case where the element is clearly considered essential in principle. Yes. Further, in each of the above embodiments, when numerical values such as the number, numerical value, quantity, range, etc. of the constituent elements of the embodiment are mentioned, it is clearly limited to a specific number when clearly indicated as essential and in principle. The number is not limited to the specific number except for the case. Further, in each of the above embodiments, when referring to the shape, positional relationship, etc. of the component, etc., the shape, unless otherwise specified and in principle limited to a specific shape, positional relationship, etc. It is not limited to the positional relationship or the like.

(Summary)
According to the first aspect described in the first to seventh embodiments, each modified example, and part or all of the other embodiments, the housing (10) constituting the refrigerant chamber (10a), and the housing A shaft (24) disposed in the housing and supported by the housing; and a shaft (24) disposed in the housing and formed in a cylindrical shape and rotatably supported with respect to the shaft, the first axis (C1) being centered. And a rotor (22a, which is disposed in the housing, is rotatably supported with respect to the shaft, and rotates about the second axis (C2) eccentric with respect to the first axis. 22b), a transmission mechanism (251a, 251b) for connecting the cylinder and the rotor to rotate the cylinder and the rotor in synchronization, and a working chamber (Va, between the inner peripheral surface of the cylinder and the outer peripheral surface of the rotor). V ), And the shaft is provided with an intake refrigerant channel (24d) through which the refrigerant flows, and the rotor guides the refrigerant from the intake refrigerant channel to the working chamber. Introducing refrigerant channels (224a, 224b) are provided,
The working chamber is deformed by the rotation of the cylinder, the rotor, and the vane, the refrigerant is sucked into the working chamber through the suction refrigerant flow path and the introduction refrigerant flow path, and compressed in the working chamber to discharge the high-pressure refrigerant through the refrigerant chamber ( A compressor discharging from 11a),
The shaft is a shaft body formed so as to extend in the axial direction of the first axis, and is provided on one side in the axial direction so that the radial dimension decreases toward the one end (24a) in the axial direction. A shaft body (24A) having a portion (300) and formed so that a radial dimension on one axial side is smaller than a radial dimension on the other axial side; A bush (24B) having an inner peripheral surface (301) having a radial dimension centered on one axis that decreases as it approaches one side from the other side in the axial direction, and a hollow of the bush A first positioning portion (330) for determining a position of the bushing in the rotation direction with respect to the shaft main body in a state where the taper portion of the shaft main body is fitted into the portion.

  According to the second aspect, the outer peripheral surface of the tapered portion of the shaft body is provided with the first concave portion (320) that is recessed radially inward, and the inner peripheral surface of the bush is opposed to the first concave portion. And a second recess (335) that is recessed radially outward is provided, and the first positioning portion is disposed in a region formed by the first recess and the second recess, and the bush with respect to the shaft body is provided. Determine the position in the direction of rotation.

  Thereby, the position of the rotation direction of the bush with respect to the shaft body can be determined satisfactorily.

  According to the third aspect, the outer diameter of the axially other side portion formed on the other side in the axial direction of the shaft main body and formed in a columnar shape centering on the first axis is D1, and the shaft main body The outer diameter dimension of the eccentric portion (24c) disposed between the other axial side portion and the tapered portion and having the first axis as the axis is D2, and the first axis and the second axis Is d, and the outer diameter of the bush is D3, D1> D2 + 2 × d and D3> D2 + 2 × d are satisfied.

  According to a fourth aspect, D1 = D3.

  According to the 5th viewpoint, the 2nd positioning part (340,130,150) which determines the position of the axial direction of a bush with respect to a shaft main body is provided with the taper part of the shaft main body being fitted in the hollow part of the bush.

  Thereby, the coaxiality after reassembling the bushing on the shaft body can be made closer to the coaxiality before the shaft body and the bushing are disassembled.

  According to the sixth aspect, the outer periphery of the tapered portion of the shaft main body is formed with a groove portion (323) recessed inward in the radial direction, and the second positioning portion is fitted into the groove portion, and the axial direction of the bush A C-shaped wedge (340) is formed which contacts one side and determines the axial position of the bush relative to the shaft body.

  According to the seventh aspect, the groove portion includes first and second side surfaces (321 and 322) formed on one axial side and the other axial side of the shaft body, and the first and second side surfaces. And the second side surface is inclined with respect to the first side surface so that the distance between the first and second side surfaces becomes smaller toward the inner side in the radial direction. doing.

  According to the eighth aspect, the male screw (128) formed so as to protrude from the tapered portion to the one axial direction side is provided on one side in the axial direction with respect to the tapered portion of the shaft body. The bush is provided with a side wall (131) that is disposed on one side in the axial direction with respect to the hollow portion and that forms a through hole portion (131a) that penetrates the male screw. The second positioning portion The nut (130) which is disposed on one side in the axial direction with respect to the side wall and is fastened to the male screw in a state where the side wall is pushed in the other side in the axial direction, thereby determining the axial position of the bush with respect to the shaft body. Configure.

  Thereby, the position of the axial direction of the bush with respect to the shaft body can be determined satisfactorily.

  According to the ninth aspect, the tapered portion of the shaft body is provided with a female screw portion (151) formed in a hole that is recessed in one axial direction and opened in the other axial direction. The bush is provided with a side wall (131) which is disposed on the other side in the axial direction with respect to the hollow portion and forms a penetrating portion (131a) penetrating in the axial direction. A male screw (150) that determines the position of the bush in the axial direction of the bush with respect to the shaft main body is configured by passing through the penetrating portion and being fastened to the female screw portion with the head pushing the side wall in one axial direction.

  Thereby, the position of the axial direction of the bush with respect to the shaft body can be determined satisfactorily.

  According to the 10th viewpoint, the lubricating oil separation mechanism (400) which isolate | separates lubricating oil from the high pressure refrigerant | coolant discharged from the discharge outlet is provided.

  According to an eleventh aspect, disposed in the housing, rotatably supported with respect to the other axial side of the bush, formed so as to close the opening on the one axial side of the cylinder, and The housing includes a first side plate (25a) that rotates together with the cylinder, and the housing is provided with a first support portion (110) that supports one side of the bush in the axial direction. The first support portion and the first side plate A first gap (200) communicating with the refrigerant chamber is formed between the bush and the lubricant oil separated from the high-pressure refrigerant by the lubricant oil separation mechanism is supplied between the bush and the first side plate. A first lubricating oil path (102) is provided, and a first oil supply start position (102a) communicated between the bush and the first side plate in the first lubricating oil path is provided. It is offset with respect to 1 gap.

  This makes it difficult for the hydraulic pressure of the lubricating oil from the first oil supply start position to reach the first gap.

  According to the twelfth aspect, the first lubricating oil path is communicated with the working chamber through the bush and the first side plate, and is more axial than the first oil supply start position between the bush and the first side plate. The cross-sectional area on the other side in the direction is larger than the cross-sectional area on the one side in the axial direction from the first oil supply start position.

  According to the thirteenth aspect, each of the first side plates has a plurality of grooves (410) that are recessed from the first gap side to the other side in the axial direction and are formed radially. ing.

  As a result, the lubricating oil enters the plurality of grooves. For this reason, the oil pressure Ya of the lubricating oil acts on the first side plate as a thrust force.

  According to the fourteenth aspect, each of the first side plates includes a plurality of grooves (410a) that are recessed from the first gap side to the other side in the axial direction and are formed in the radial direction. Each of the plurality of grooves is inclined such that the radially outer side is positioned on the front side in the rotational direction than the radially inner side.

  According to the fifteenth aspect, each of the first side plates has a plurality of grooves (410b) that are recessed from the first gap side to the other side in the axial direction and are formed in the radial direction. Each of the plurality of grooves is formed in a dogleg shape projecting forward in the rotational direction.

  According to the sixteenth aspect, on the inner peripheral surface that slides on the outer peripheral surface of the bush of the first side plate, a groove that is formed in a spiral shape and flows the lubricating oil from the first lubricating oil path ( 420, 421) are formed.

  According to the seventeenth aspect, the other axial side of the outer peripheral surface of the bush than the first oil supply start position has a flat surface (102d) extending in the axial direction and the cross section is formed in a D-shape. A lubricating oil passage is formed between the first side plate and the lubricating oil supplied from the first oil supply start position.

  According to the eighteenth aspect, one side of the bush in the axial direction from the first oil supply start position communicates with the first lubricating oil path and opens in the circumferential direction so that the first lubricating oil path is opened. A lubricating oil passage (520) is provided for supplying lubricating oil from between the bush and the first support portion.

  According to a nineteenth aspect, the housing is provided with a second support portion (120) that supports the other axial side of the shaft body, and one axial direction of the second support portion in the housing is provided. A second side plate (25b) that is disposed on the side, is rotatably supported with respect to the shaft body, is formed to close the other axial side opening of the cylinder, and rotates together with the cylinder; A second gap (210) communicating with the refrigerant chamber is formed between the second support portion and the second side plate, and the lubricating oil separated from the high-pressure refrigerant by the lubricating oil separation mechanism is applied to the shaft body. A second lubricating oil path (104) is provided between the shaft main body and the second side plate, and is connected between the shaft main body and the second side plate in the second lubricating oil path. The second oil supply start position (104a) is offset relative to the second clearance portion.

  According to the twentieth aspect, the second lubricating oil path is communicated with the working chamber through the shaft body and the second side plate, and is located between the bush and the second side plate than the second oil supply start position. The cross-sectional area on one side in the axial direction is larger than the cross-sectional area on the other side in the axial direction from the second oil supply start position.

  According to the twenty-first aspect, a plurality of grooves (410) that are recessed from the second gap side to the one side in the axial direction and are formed in the radial direction are arranged radially on the second side plate. ing.

  According to the twenty-second aspect, a plurality of grooves (410a) that are recessed from the second gap side to the one side in the axial direction and are formed in the radial direction are arranged radially on the second side plate. Each of the plurality of grooves is inclined such that the radially outer side is positioned on the front side in the rotational direction than the radially inner side.

  According to the twenty-third aspect, each of the second side plates includes a plurality of grooves (410b) that are recessed from the second gap side to one side in the axial direction and are formed in the radial direction. Each of the plurality of grooves is formed in a dogleg shape projecting forward in the rotational direction.

  According to the twenty-fourth aspect, the groove formed in the inner peripheral surface that slides on the outer peripheral surface of the shaft body of the second side plate is formed in a spiral shape and flows the lubricating oil from the second lubricating oil path. (420, 421) are formed.

  According to the twenty-fifth aspect, the axially one side of the outer peripheral surface of the shaft body has a flat surface extending in the axial direction from the second refueling start position, and the cross section is formed in a D-shape. A lubricating oil flow path is formed between the two side plates to flow lubricating oil supplied from the second oil supply start position.

  According to the twenty-sixth aspect, the second lubricating oil communicates with the second lubricating oil path on the other axial side of the shaft body from the second oiling start position and opens in the circumferential direction. A second lubricating oil passage for supplying lubricating oil from the path between the shaft body and the second support portion is provided.

According to the twenty-seventh aspect, the housing (10) constituting the refrigerant chamber (10a), the shaft (24) disposed in the housing and supported by the housing, and disposed in the housing in a cylindrical shape A cylinder (21) formed and rotatably supported with respect to the shaft and rotating about the first axis (C1); and disposed within the housing and rotatably supported with respect to the shaft; A rotor (22a, 22b) that rotates about a second axis (C2) that is eccentric with respect to the first axis, and a transmission mechanism (251a, 22) that connects the cylinder and the rotor and rotates the cylinder and the rotor synchronously. 251b) and vanes (23a, 23b) for partitioning the working chambers (Va, Vb) between the inner peripheral surface of the cylinder and the outer peripheral surface of the rotor, and a suction flow through which refrigerant flows in the shaft Nakadachiryuro (24d) is provided, the rotor, the coolant introducing refrigerant flow path for guiding the working chamber from the suction refrigerant flow path (224a, 224b) is provided,
The working chamber is deformed by the rotation of the cylinder, the rotor, and the vane, the refrigerant is sucked into the working chamber through the suction refrigerant flow path and the introduction refrigerant flow path, and compressed in the working chamber to discharge the high-pressure refrigerant through the refrigerant chamber ( 11a) is a method for manufacturing a compressor that discharges from a shaft,
A shaft body formed so as to extend in the axial direction of the first axis, a tapered portion (300 provided on the other axial side and having a smaller radial dimension toward the other axial side end (24a). And a shaft body (24A) formed so that the radial dimension on the other axial side is smaller than the radial dimension on the one axial side, and the radial dimension about the first axis is A bush (24B) having an inner peripheral surface (301) that decreases as it approaches the other side from one side in the axial direction to form a hollow portion (301a), and the taper portion of the shaft body is a hollow portion of the bush A first positioning step (S110) in which the position of the bushing relative to the shaft body is determined by the positioning portion (330), and the position of the bushing relative to the shaft body. With the first positioning portion determined, a processing step (S120) for processing the shaft main body and the bush so that the axis of the bush approaches the first axis of the tapered portion of the shaft main body, and the shaft main body and the bush after the processing step The disassembling step (S130) for disassembling the shaft, and after the disassembling step, with the shaft main body fitted in the through hole of the rotor, the taper portion of the shaft main body is fitted into the hollow portion of the bush and the rotation direction of the bush relative to the shaft main body And a second positioning step (S150) for positioning the position.

  According to the twenty-eighth aspect, there is provided a third positioning step (S150) for positioning the position of the bush in the rotational direction with respect to the shaft body and positioning the position of the bush in the axial direction with respect to the shaft body.

  According to the twenty-ninth aspect, in the third positioning step, the jig holds the rotation stoppers (140a, 140b) of the bush, and the bush stops rotating with respect to the shaft body by the jig. Position the bush in the axial direction relative to the shaft body.

  According to the thirtieth aspect, in the disassembling process, the groove (162) formed between the step (311) formed on the other side in the axial direction with respect to the bush in the shaft main body and the bush is cured. The bush is removed from the shaft main body by the jig while being held by the tool, and the shaft main body and the bush are disassembled.

  According to the thirty-first aspect, in the disassembling step, the bushing is removed from the shaft body with the jig while the grooves (161a, 161b) formed in the bush are gripped by the jig, and the shaft body and the bush are disassembled. .

DESCRIPTION OF SYMBOLS 1 Compressor 10 Housing 20 Compression mechanism 21 Cylinder 22a, 22b Rotor 24 Shaft 24A Shaft main body 24B Bushing 25a, 25b Side plate 30 Electric motor

Claims (31)

A housing (10) constituting a refrigerant chamber (10a);
A shaft (24) disposed within the housing and supported by the housing;
A cylinder (21) disposed in the housing, formed in a cylindrical shape and rotatably supported with respect to the shaft, and rotating about a first axis (C1);
A rotor (22a, 22b) disposed within the housing, rotatably supported with respect to the shaft, and rotated about a second axis (C2) eccentric with respect to the first axis;
A conduction mechanism (251a, 251b) for connecting the cylinder and the rotor to rotate the cylinder and the rotor synchronously;
Vanes (23a, 23b) for partitioning working chambers (Va, Vb) between the inner peripheral surface of the cylinder and the outer peripheral surface of the rotor,
The shaft is provided with an intake refrigerant flow path (24d) through which refrigerant flows, and the rotor has introduction refrigerant flow paths (224a, 224b) that guide the refrigerant from the intake refrigerant flow path to the working chamber. Provided,
The cylinder, the rotor, and the vane rotate to deform the working chamber, suck the refrigerant into the working chamber through the suction refrigerant flow path and the introduction refrigerant flow path, and compress the high pressure by compressing in the working chamber. A compressor that discharges refrigerant from the discharge port (11a) through the refrigerant chamber,
The shaft is
A shaft main body formed so as to extend in the axial direction of the first axis, wherein the tapered body is provided on one side in the axial direction and decreases in radial direction toward the one end (24a) in the axial direction. (300), and a shaft main body (24A) formed so that a radial dimension on one side in the axial direction is smaller than a radial dimension on the other side in the axial direction;
A hollow portion (301a) having an inner peripheral surface (301) disposed in the housing and having a radial dimension centered on the first axis that decreases from the other side in the axial direction toward the one side. A bush (24B) to be formed;
A compressor comprising: a first positioning portion (330) that determines a position of the bushing in a rotation direction with respect to the shaft main body in a state where the tapered portion of the shaft main body is fitted in the hollow portion of the bush. A first recess (320) that is recessed radially inward is provided on the outer peripheral surface of the tapered portion of the shaft body,
The inner peripheral surface of the bush is provided with a second recess (335) facing the first recess and recessed outward in the radial direction,
2. The compressor according to claim 1, wherein the first positioning portion is disposed in a region formed by the first recess and the second recess, and determines a position of the bush in a rotation direction with respect to the shaft body. The outer diameter dimension of the axial direction other side part formed in the columnar shape centering on the 1st axis which is formed in the other side of the axial direction among the shaft main parts is set to D1,
Outer diameter dimension of the eccentric part (24c) which is arranged between the axial direction other side part and the taper part among the shaft main bodies and is formed so that the first axis line is an axis line is D2.
The distance between the first axis and the second axis is d,
If the outer diameter of the bush is D3,
The compressor according to claim 1, wherein D1> D2 + 2 × d and D3> D2 + 2 × d are satisfied.   The compressor according to claim 3, wherein D1 = D3.   2. A second positioning portion (340, 130, 150) that determines the axial position of the bush relative to the shaft main body in a state where the tapered portion of the shaft main body is fitted in the hollow portion of the bush. The compressor as described in any one of thru | or 4. On the outer periphery of the tapered portion of the shaft body, a groove portion (323) that is recessed radially inward is formed,
The second positioning portion is fitted into the groove portion, and constitutes a C-shaped wedge (340) that contacts one side in the axial direction of the bush and determines the position of the bush in the axial direction with respect to the shaft body. The compressor according to claim 5. The groove is formed between the first and second side surfaces (321 and 322) formed on one side in the axial direction and the other side in the axial direction of the shaft body, and the first and second side surfaces. And a bottom surface (323)
The compressor according to claim 6, wherein the second side surface is inclined with respect to the first side surface so that the distance between the first and second side surfaces becomes smaller as it approaches the radially inner side. . A male screw (128) formed so as to protrude from the tapered portion to the one axial direction side is provided on the one axial side with respect to the tapered portion of the shaft body,
The bush is provided with a side wall (131) that is disposed on one side in the axial direction with respect to the hollow portion and that forms a through hole portion (131a) that penetrates the male screw.
The second positioning portion is disposed on one side in the axial direction with respect to the side wall, and is fastened to the male screw in a state in which the side wall is pushed to the other side in the axial direction, thereby the bush against the shaft body. The compressor according to claim 5, comprising a nut (130) that determines a position in the axial direction. The tapered portion of the shaft body is provided with a female thread portion (151) formed in a hole that is recessed on one side in the axial direction and opened on the other side in the axial direction.
The bush is provided with a side wall (131) which is disposed on the other side in the axial direction with respect to the hollow portion and forms a penetrating part (131a) penetrating in the axial direction.
The second positioning portion is fastened to the female screw portion through the penetration portion with the head pushing the side wall in the axial direction, and is thus fastened to the female screw portion. 6. A compressor according to claim 5, comprising a male thread (150) for determining the position in the direction.   The compressor according to any one of claims 1 to 9, further comprising a lubricating oil separation mechanism (400) that separates lubricating oil from the high-pressure refrigerant discharged from the discharge port. Arranged in the housing, rotatably supported with respect to the other axial side of the bush, formed so as to close the opening on the one axial side of the cylinder, and rotated together with the cylinder A first side plate (25a),
The housing is provided with a first support portion (110) that supports one side in the axial direction of the bush.
A first gap (200) communicating with the refrigerant chamber is formed between the first support portion and the first side plate,
The bush is provided with a first lubricating oil path (102) for supplying the lubricating oil separated from the high-pressure refrigerant by the lubricating oil separation mechanism between the bush and the first side plate,
The compression according to claim 10, wherein a first oil supply start position (102a) communicated between the bush and the first side plate in the first lubricating oil path is offset with respect to the first gap. Machine. The first lubricating oil path is in communication with the working chamber through the bush and the first side plate;
The cross-sectional area on the other side in the axial direction from the first oil supply start position between the bush and the first side plate is larger than the cross-sectional area on the one axial side from the first oil supply start position. Item 12. The compressor according to Item 11.   The plurality of grooves (410) that are recessed from the first gap side to the other side in the axial direction and that are formed in the radial direction are radially arranged in the first side plate, respectively. The compressor described. In the first side plate, a plurality of grooves (410a) that are recessed from the first gap side to the other side in the axial direction and are formed in the radial direction are arranged in the circumferential direction,
The compressor according to claim 11, wherein each of the plurality of grooves is inclined such that a radially outer side is positioned on a front side in a rotational direction than a radially inner side. Each of the first side plates has a plurality of grooves (410b) that are recessed in the axial direction from the first gap side and formed in the radial direction, and are arranged in the circumferential direction.
The compressor according to claim 11, wherein each of the plurality of grooves is formed in a dogleg shape protruding toward the front side in the rotation direction.   Grooves (420, 421) that are formed in a spiral shape and flow lubricating oil from the first lubricating oil path are formed on the inner peripheral surface that slides on the outer peripheral surface of the bush of the first side plate. The compressor according to any one of claims 10 to 15, wherein the compressor is formed.   Of the outer peripheral surface of the bush, the other side in the axial direction from the first oil supply start position has a flat surface (102d) extending in the axial direction and is formed in a D-shaped cross section so that the bush and the first side plate The compressor of Claim 11 which forms the lubricating oil flow path through which the lubricating oil supplied from the said 1st oil supply start position flows.   One side of the bush in the axial direction from the first oil supply start position communicates with the first lubricating oil path and opens in the circumferential direction to lubricate from the first lubricating oil path. The compressor according to claim 11, wherein a lubricating oil passage (520) for supplying oil between the bush and the first support portion is provided. The housing is provided with a second support portion (120) for supporting the other axial side of the shaft body,
The inside of the housing is disposed on one side in the axial direction with respect to the second support portion, and is rotatably supported with respect to the shaft body, and is formed so as to close the opening on the other side in the axial direction of the cylinder. And a second side plate (25b) that rotates together with the cylinder,
A second gap (210) communicating with the refrigerant chamber is formed between the second support portion and the second side plate,
The shaft main body is provided with a second lubricating oil path (104) for supplying the lubricating oil separated from the high-pressure refrigerant by the lubricating oil separation mechanism between the shaft main body and the second side plate,
The second oil supply start position (104a) communicated between the shaft body and the second side plate in the second lubricating oil path is offset with respect to the second gap. Compressor. The second lubricating oil path is in communication with the working chamber through the shaft body and the second side plate;
A cross-sectional area on one side in the axial direction from the second oil supply start position between the bush and the second side plate is larger than a cross-sectional area on the other axial side from the second oil supply start position. Item 20. The compressor according to Item 19.   The plurality of grooves (410) that are recessed in the axial direction from the second gap side to the one side in the axial direction and are formed in the radial direction are radially arranged in the second side plate, respectively. The compressor described. Each of the second side plates has a plurality of grooves (410a) that are recessed in the axial direction from the second gap side and formed in the radial direction, and are arranged radially.
The compressor according to claim 11, wherein each of the plurality of grooves is inclined such that a radially outer side is positioned on a front side in a rotational direction than a radially inner side. Each of the second side plates has a plurality of grooves (410b) that are recessed in the axial direction from the second gap side and formed in the radial direction, and are arranged in the circumferential direction.
The compressor according to claim 11, wherein each of the plurality of grooves is formed in a dogleg shape protruding toward the front side in the rotation direction.   Grooves (420, 421) formed in a spiral shape on the inner peripheral surface of the second side plate that slides on the outer peripheral surface of the shaft main body and through which the lubricating oil from the second lubricating oil passageway flows. The compressor according to any one of claims 11 to 23, wherein the compressor is formed.   Of the outer peripheral surface of the shaft main body, one side in the axial direction from the second oil supply start position has a flat surface extending in the axial direction and has a D-shaped cross section, and the shaft main body, the second side plate, The compressor according to any one of claims 11 to 23, wherein a lubricating oil flow path through which lubricating oil supplied from the second oil supply start position flows is formed.   In the shaft body, on the other side in the axial direction from the second oil supply start position, the shaft body communicates with the second lubricating oil path and opens in the circumferential direction from the second lubricating oil path. The compressor according to any one of claims 11 to 23, wherein a second lubricating oil passage for supplying the lubricating oil is provided between the shaft body and the second support portion. A housing (10) constituting a refrigerant chamber (10a);
A shaft (24) disposed within the housing and supported by the housing;
A cylinder (21) disposed in the housing, formed in a cylindrical shape and rotatably supported with respect to the shaft, and rotating about a first axis (C1);
A rotor (22a, 22b) disposed within the housing, rotatably supported with respect to the shaft, and rotated about a second axis (C2) eccentric with respect to the first axis;
A conduction mechanism (251a, 251b) for connecting the cylinder and the rotor to rotate the cylinder and the rotor synchronously;
Vanes (23a, 23b) for partitioning working chambers (Va, Vb) between the inner peripheral surface of the cylinder and the outer peripheral surface of the rotor,
The shaft is provided with an intake refrigerant flow path (24d) through which refrigerant flows, and the rotor has introduction refrigerant flow paths (224a, 224b) that guide the refrigerant from the intake refrigerant flow path to the working chamber. Provided,
The cylinder, the rotor, and the vane rotate to deform the working chamber, suck the refrigerant into the working chamber through the suction refrigerant flow path and the introduction refrigerant flow path, and compress the high pressure by compressing in the working chamber. A method of manufacturing a compressor for discharging refrigerant from a discharge port (11a) through the refrigerant chamber,
The shaft is
A shaft main body formed so as to extend in the axial direction of the first axis, wherein the tapered body is provided on the other side in the axial direction and decreases in a radial dimension toward the other end (24a) in the axial direction. (300), and a shaft body (24A) formed so that a radial dimension on the other axial side is smaller than a radial dimension on the one axial side;
A bush (24B) having an inner peripheral surface (301) having a radial dimension about the first axis as it approaches the other side from one side in the axial direction to form a hollow portion (301a); With
A first positioning step (S110) in which a taper portion of the shaft body is fitted into a hollow portion of the bush, and a position of the bushing in the rotation direction with respect to the shaft body is determined by a positioning portion (330);
The shaft main body and the bush are processed so that the axis of the bush approaches the first axis of the tapered portion of the shaft main body in a state where the position of the bush in the rotation direction with respect to the shaft main body is determined by the first positioning portion. Processing step (S120) to be performed;
A disassembling step (S130) for disassembling the shaft body and the bush after the processing step;
After the disassembling step, with the shaft main body fitted in the through hole of the rotor, the tapered portion of the shaft main body is fitted into the hollow portion of the bush so that the position of the bush in the rotation direction with respect to the shaft main body is set. A second positioning step (S150) for positioning;
The manufacturing method of a compressor provided with.   28. The method of manufacturing a compressor according to claim 27, further comprising a third positioning step (S150) of positioning a position of the bush in a rotation direction with respect to the shaft body and positioning a position of the bush in an axial direction with respect to the shaft body. .   In the third positioning step, the shaft main body in a state in which a jig holds the rotation stoppers (140a, 140b) of the bush and the bush stops rotation with respect to the shaft main body by the jig. The method for manufacturing a compressor according to claim 28, wherein a position of the bush in an axial direction relative to the bush is positioned.   In the disassembling step, a step (311) formed on the other side in the axial direction with respect to the bush in the shaft body and a groove (162) formed between the bush are gripped by a jig. 28. The method for manufacturing a compressor according to claim 27, wherein the bush is removed from the shaft main body by the jig in a state where the shaft main body and the bush are disassembled.   The disassembling step disassembles the shaft main body and the bush by removing the bush from the shaft main body with the jig in a state where the grooves (161a, 161b) formed in the bush are gripped by the jig. Item 28. A method for manufacturing a compressor according to Item 27.

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