Rotary compressor

Abstract

To facilitate a process of manufacturing a bearing, etc.SOLUTION: A rotary compressor 1 includes: a closed housing 2 constituting an outer shell; an electric motor 5; a compression mechanism 6 accommodated in the closed housing 2 and compressing a refrigerant by using driving force from the electric motor 5; and a driving shaft 14 coupling the electric motor 5 and the compression mechanism 6 and rotating about a central axial line extending in the vertical direction. The compression mechanism 6 includes: an upper rotor 33 coupled to the driving shaft 14 and accommodated in an upper cylinder chamber 31; an upper cylinder body part 34 partitioning a radial outer side of the upper cylinder chamber 31; and an upper bearing part 35 rotatably supporting the driving shaft 14 and partitioning the vertical direction of the upper cylinder chamber 31. The refrigerant is compressed between the rotating upper rotor 33 and the upper cylinder body part 34, and the upper bearing part 35 and the upper cylinder body part 34 are formed of a composite material formed by reinforcing resin by using reinforced fiber.SELECTED DRAWING: Figure 1

Description

[Technical Field]

[0001] The present disclosure relates to a rotary compressor. [Background technology]

[0002] Rotary compressors are known as compressors used in air conditioners and the like (see, for example, Patent Document 1). Patent Document 1 discloses a rotary compressor that includes a motor housed in a sealed container, a rotary compression mechanism driven by the motor, and a drive shaft that transmits the driving force of the motor to the compression mechanism. The rotary compression mechanism compresses refrigerant by a roller connected to the drive shaft that rotates and moves within a cylinder chamber. This cylinder chamber is partitioned by a cylinder body, bearings that support the drive shaft and are provided above and below the cylinder body, and a separator. [Prior art documents] [Patent documents]

[0003] [Patent Document 1] Japanese Patent Application Laid-Open No. 2016-160911 Summary of the Invention [Problem to be solved by the invention]

[0004] In such rotary compressors, if the bearings and / or cylinder body (hereinafter referred to as "bearings, etc.") that define the cylinder chamber are made of metal, contact between the rotor rotating within the cylinder chamber and the bearings, etc., may result in damage to the components or noise. On the other hand, if a large gap is formed between the bearings, etc. and the rotor, refrigerant may leak through the gap, reducing compression efficiency. For this reason, the gap formed between the bearings, etc. and the rotor must be strictly controlled. This requires that the bearings, etc. be manufactured with high precision, which has made manufacturing the bearings, etc., difficult.

[0005] The present disclosure has been made in view of the above circumstances, and has an object to provide a rotary compressor that can simplify the process of manufacturing bearings and the like. [Means for solving the problem]

[0006] In order to solve the above problems, the rotary compressor of the present disclosure employs the following measures. A rotary compressor according to one aspect of the present disclosure includes a housing forming an outer shell, a drive source, a compression mechanism housed in the housing and compressing a refrigerant using drive force from the drive source, and a drive shaft connecting the drive source and the compression mechanism and rotating about a central axis extending along a predetermined direction, wherein the compression mechanism includes a rotor connected to the drive shaft and housed in a cylinder chamber, a cylinder defining the radially outer side of the cylinder chamber, and a bearing rotatably supporting the drive shaft and defining the predetermined direction of the cylinder chamber, and compresses the refrigerant between the rotating rotor and the cylinder, and the cylinder is formed of a composite material in which resin is reinforced with reinforcing fibers, and the cylinder has an intake port through which the refrigerant is introduced into the cylinder chamber, and an excess portion located radially outward of the intake port and protruding radially outward beyond other regions. [Effects of the Invention]

[0007] According to the present disclosure, the process of manufacturing a bearing or the like can be simplified. [Brief explanation of the drawings]

[0008] [Figure 1] FIG. 1 is a longitudinal cross-sectional view of a compressor according to an embodiment of the present disclosure. [Figure 2] 2 is a perspective view of an upper bearing cylinder portion provided in the rotary compressor of FIG. 1. FIG. [Figure 3] 2 is a vertical cross-sectional perspective view of a rotary compression mechanism provided in the rotary compressor of FIG. 1. [Figure 4] FIG. 3 is a longitudinal sectional view of the upper bearing cylinder of FIG. 2. [Figure 5] FIG. 5 is a perspective view showing the metal bush of FIG. 4. [Figure 6] 2 is a perspective view of an upper bearing cylinder portion provided in the rotary compressor of FIG. 1. FIG. [Figure 7] FIG. 7 is an enlarged view of a main part of FIG. 6. [Figure 8] FIG. 7 is an enlarged view of a main part of FIG. 6. [Figure 9] FIG. 8 is a diagram showing a modification of FIG. 7. [Figure 10] FIG. 2 is a plan view of a separator plate provided in the rotary compressor of FIG. [Figure 11] 2 is a schematic perspective view showing a bolt for fastening an upper bearing cylinder portion and a separator plate provided in the rotary compressor of FIG. 1. FIG. [Figure 12] FIG. 2 is a diagram showing a modification of FIG. 1. DETAILED DESCRIPTION OF THE INVENTION

[0009] Hereinafter, an embodiment of a rotary compressor according to the present disclosure will be described with reference to the drawings. As shown in Fig. 1, the rotary compressor 1 has a cylindrical sealed housing (casing) 2 whose upper and lower parts are sealed by covers 3 and 4, forming an outer shell. An electric motor 5 is installed in an upper part inside the sealed housing 2, and a compression mechanism 6 driven by the electric motor (drive source) 5 is installed in a lower part. The rotary compressor 1 is an electric compressor with a sealed structure. A plurality of mounting legs 7 are provided on the outer periphery of the lower part of the sealed housing 2, and a discharge pipe 8 is provided at the top of the sealed housing 2 so as to pass through the upper cover 3, so that high-pressure refrigerant gas compressed by the compression mechanism 6 and discharged into the sealed housing 2 can be sent outside the compressor (to the refrigeration cycle).

[0010] An accumulator (not shown) is integrally attached to the outer periphery of the sealed housing 2. The accumulator separates oil, liquid refrigerant, and other liquid components contained in the low-pressure refrigerant gas returned from the refrigeration cycle, and allows only the gas component to be drawn into the compression mechanism 6 through the suction pipe 10.

[0011] The electric motor 5 includes a stator 12 and a rotor 13, and the stator 12 is fixed to the inner circumferential surface of the sealed housing 2 by shrink fitting, press fitting, or the like. Meanwhile, a drive shaft 14 is integrally coupled to the rotor 13, so that its rotational driving force can be transmitted to the compression mechanism 6 via the drive shaft 14. Furthermore, an upper eccentric shaft portion 15 and a lower eccentric shaft portion 16 are provided at two positions above and below the drive shaft 14 at a predetermined interval in the axial direction, with a phase shift of 180 degrees, corresponding to an upper compression mechanism 30 and a lower compression mechanism 60 of the compression mechanism 6, which will be described later. The drive shaft 14 is a substantially cylindrical member and is disposed so that its central axis extends in the vertical direction. The drive shaft 14 connects the electric motor 5 and the compression mechanism 6. The drive shaft 14 rotates about its central axis by the driving force of the electric motor 5.

[0012] Next, the compression mechanism 6 according to this embodiment will be described in detail. The compression mechanism 6 is a two-cylinder rotary compression mechanism including an upper compression mechanism 30 and a lower compression mechanism 60. The compression mechanism 6 also includes a separator plate (separator) 50 provided between the upper compression mechanism 30 and the lower compression mechanism 60. In the following description, the term "radial direction" refers to the radial direction based on the central axis of the drive shaft 14.

[0013] The upper compression mechanism 30 includes an upper bearing cylinder portion 32 that defines an upper cylinder chamber (cylinder chamber) 31 therein, and an upper rotor (rotor) 33 that is connected to the drive shaft 14 and housed in the upper cylinder chamber 31.

[0014] 1 and 2, the upper bearing cylinder portion 32 integrally comprises an upper cylinder body portion 34 (cylinder) that defines the radially outer side of the upper cylinder chamber 31, and an upper bearing portion (bearing) 35 that rotatably supports the drive shaft 14 and defines the upper part of the upper cylinder chamber 31. In other words, the upper cylinder body portion 34 and the upper bearing portion 35 are integrally formed. The upper bearing cylinder portion 32 is entirely formed from a composite material in which resin is reinforced with short fibers (hereinafter referred to as a "short fiber composite material"). The short fibers are, for example, glass fibers or carbon fibers with fiber lengths of about 0.1 mm to several millimeters.

[0015] Note that "integrally formed" does not mean that the upper bearing portion 35 and the upper cylinder body portion 34 are formed as separate members and then integrated by fastening them with fasteners, welding, or the like, but rather that the upper bearing portion 35 and the upper cylinder body portion 34 are integrated using the same material without any seams, etc. In this embodiment, the upper bearing cylinder portion 32 is formed integrally with the upper bearing portion 35 and the upper cylinder body portion 34 by injection molding. Note that the method of forming the upper bearing cylinder portion 32 is one example and is not limited to injection molding.

[0016] As shown in Fig. 1, the upper bearing portion 35 rotatably supports the drive shaft 14. As shown in Figs. 2 to 4, the upper bearing portion 35 integrally includes a cylindrical portion 35a through which the drive shaft 14 is inserted, a plurality of plate-like ribs 35b protruding radially from the outer circumferential surface of the cylindrical portion 35a, and a plate-like annular portion 35c extending radially from the lower end of the cylindrical portion 35a. The thicknesses of the cylindrical portion 35a, the ribs 35b, and the annular portion 35c are all approximately the same.

[0017] The cylindrical portion 35a is disposed so that its central axis coincides with the central axis of the drive shaft 14. As shown in FIG. 4, a step whose inner diameter changes is formed on the inner peripheral surface of the cylindrical portion 35a. Two metal bushes (bearing wear-resistant portions) 36 are provided inside the cylindrical portion 35a so as to come into contact with the step. For ease of illustration, the metal bushes 36 are omitted from FIGS. 1 to 3. The metal bushes 36 are provided between the cylindrical portion 35a and the drive shaft 14.

[0018] As shown in FIG. 5 , each metal bushing 36 is a cylindrical member. The metal bushing 36 is made of a metal material (e.g., cast iron, aluminum alloy, or copper alloy). Two notches 36a recessed radially inward are formed on the outer circumferential surface of the metal bushing 36. The two notches 36a are arranged at equal intervals in the circumferential direction. Each notch 36a is formed from one end of the metal bushing 36 in the vertical direction to the center. A flat anti-slip portion 36b is provided at the other end of each notch 36a in the vertical direction. The cylindrical portion 35a also has an engaging portion (not shown) that engages with the notch 36a. The engagement between the notch 36a and the engaging portion restricts rotation of the metal bushing 36. Furthermore, contact between the engaging portion and the anti-slip portion 36b restricts vertical movement of the metal bushing 36, thereby preventing the metal bushing 36 from coming off the cylindrical portion 35a.

[0019] As shown in Fig. 4, the metal bushings 36 are provided at the top and bottom of the cylindrical portion 35a. That is, the metal bushings 36 are not provided in the center of the cylindrical portion 35a. The vertical length of the area where the metal bushings 36 are not provided is set to 20% to 30% of the vertical length of the cylindrical portion 35a. Note that the length of the area where the metal bushings 36 are not provided is an example and is not limited to the numerical value described above.

[0020] The metal bushing 36 can be molded integrally with the bearing cylinder portion by setting it in the mold before injecting the resin when injection molding the upper bearing cylinder portion 32. By molding them integrally in this way, manufacturing costs can be reduced.

[0021] The multiple ribs 35b are arranged side by side without significant deviation along the circumferential direction of the cylindrical portion 35a. Each rib 35b protrudes from almost the entire vertical area of ​​the outer circumferential surface of the cylindrical portion 35a. Each rib 35b is formed so that its protruding length increases as it goes downward. The lower end of each rib 35b is connected to the upper surface of the annular portion 35c. The radially outer end of the lower part of each rib 35b is connected to the inner circumferential surface of the outer frame portion 34c of the upper cylinder main body portion 34, which will be described later. Each rib 35b has a shape in which a substantially triangular member is connected to a substantially rectangular member in side view. The side surface of the rectangular member (the surface intersecting the plate surface) and the side surface of the triangular member are smoothly connected so that the connecting portion forms a curved surface.

[0022] Further, a fastening portion 37 is connected to a predetermined rib 35b. The fastening portion 37 defines a first bolt hole 37a (fastening hole) through which a bolt 38 is inserted. In other words, the first bolt hole 37a is formed on the predetermined rib 35b. A plurality of fastening portions 37 are formed. 1, the first bolt hole 37a penetrates the upper bearing cylinder portion 32. The first bolt hole 37a communicates with a second bolt hole 52 formed in a separator plate 50, which will be described later. The upper bearing cylinder portion 32 and the separator plate 50 are fastened together by a bolt 38 that passes through the first bolt hole 37a and the second bolt hole 52.

[0023] 3 and 4, the annular portion 35c is an annular member having an opening formed in its approximate center through which the drive shaft 14 is inserted. The annular portion 35c defines an area above the upper cylinder chamber 31, and also defines an area above a second flow path 42 formed in the upper cylinder body portion 34, which will be described later.

[0024] Next, the structure of the upper cylinder body 34 will be described with reference to Figures 1 to 4 and Figures 6 to 9. For ease of explanation, Figures 6 to 9 show the upper cylinder body 34 upside down. That is, in Figures 6 to 9, the bottom of the paper surface is vertically upward, and the top of the paper surface is vertically downward.

[0025] 3 and 4, the upper cylinder body 34 integrally includes a cylindrical partition portion 34a that defines the radially outer side of the upper cylinder chamber 31, a plate-shaped abutment portion 34b that extends radially outward from the lower end of the partition portion 34a, and a cylindrical outer frame portion 34c that bends at a substantially right angle from the radially outer end of the abutment portion 34b and extends upward. The thicknesses of the partition portion 34a, the abutment portion 34b, and the outer frame portion 34c are substantially the same. The thicknesses of the partition portion 34a and the like of the upper cylinder body 34 are also substantially the same as the thickness of the ribs 35b and the like of the upper bearing portion 35.

[0026] The inner circumferential surface of the partition 34a defines the upper cylinder chamber 31. The upper end of the partition 34a is connected to the lower surface of the radially outer end of the annular portion 35c. An intake port 43 is formed in the partition 34a. The intake port 43 opens to the upper cylinder chamber 31.

[0027] The lower surface of the contact portion 34b contacts the upper surface of the separator plate 50. A fastening portion 37 is provided on the upper surface of the contact portion 34b. The outer frame portion 34c is provided radially outward of the partition portion 34a and stands upright so as to face the partition portion 34a.

[0028] A second flow path 42 is formed in the upper cylinder body 34 between the partition 34a and the outer frame 34c. The second flow path 42 is connected to a first flow path 41 formed in a separator plate 50 (described later). The second flow path 42 extends in the vertical direction and has a substantially circular cross section. The downstream end of the second flow path 42 is connected to a suction port 43 (suction port) formed in the partition 34a. Therefore, the refrigerant that has flowed through the second flow path 42 flows into the upper cylinder chamber 31 via the suction port 43.

[0029] 3 and 7, the suction port 43 is formed in a rectangular shape. Specifically, the suction port 43 has a rectangular shape whose vertical length is longer than its length in a direction intersecting the vertical direction (i.e., the rotation direction of the upper rotor 33). The upper edge of the suction port 43 is defined by the upper bearing portion 35, and the lower edge is defined by the separator. The edge of the suction port 43 in the rotational direction is defined by the partition portion 34a.

[0030] As shown in FIG. 6, the upper cylinder body 34 has a blade (not shown) that divides the upper cylinder chamber 31 into a refrigerant intake side and a refrigerant discharge side, and a blade groove 44 that slidably accommodates the blade.

[0031] The blade is made of a metal material. The blade is slidably fitted into the blade groove 44. The blade groove 44 is a groove extending in the radial direction, and the blade is housed therein. The radial inner end of the blade groove 44 is connected to the upper cylinder chamber 31. The blade groove 44 is provided adjacent to the suction port 43.

[0032] As shown in FIG. 7 , the entire vertical area of ​​the sidewall surface on the suction side (the suction port 43 side) of the blade groove 44 is covered at the cylinder chamber side end (the radially inner end) by a suction-side wear-resistant portion 45. As shown in FIG. 8 , the entire radial area of ​​the sidewall surface on the discharge side (the side where the suction port 43 is not provided) of the blade groove 44 is covered by a discharge-side wear-resistant portion 46. The suction-side wear-resistant portion 45 and the discharge-side wear-resistant portion 46 are formed of a metal material (e.g., cast iron, aluminum alloy, or copper alloy). The suction-side wear-resistant portion 45 and the discharge-side wear-resistant portion 46 have protrusions 45a and 45b at their radially outer ends that engage with recesses 46a and 46b of the upper cylinder body portion 34. The engagement of the protrusions 45a and 45b with the recesses 46a and 46b restricts radial movement of the suction-side wear-resistant portion 45 and the discharge-side wear-resistant portion 46. In FIG. 6, for convenience of illustration, the suction side wear-resistant portion 45 and the discharge side wear-resistant portion 46 are omitted.

[0033] Although the above description has been given of an example in which only the radially inner end of the suction-side sidewall surface of the blade groove 44 is covered by the suction-side wear-resistant portion 45, the present disclosure is not limited to this. For example, as shown in Fig. 9, the suction-side sidewall surface of the blade groove 44 may be covered over substantially the entire radial area by the suction-side wear-resistant portion 45. In this case, by making the shape of the suction-side wear-resistant portion 45 and the shape of the discharge-side wear-resistant portion 46 the same, it is possible to standardize the parts, thereby reducing the manufacturing cost of the wear-resistant portion.

[0034] 1, the upper rotor 33 is fitted onto the outer peripheral surface of the upper eccentric shaft portion 15. The central axis of the upper eccentric shaft portion 15 is eccentric with respect to the central axis of the drive shaft 14. Therefore, the upper rotor 33 revolves within the upper cylinder chamber 31 as the drive shaft 14 rotates. The refrigerant is compressed between the revolving upper rotor 33 and the upper cylinder main body portion 34.

[0035] The separator plate 50 is a plate-like member made of a metal material (for example, cast iron). As shown in Fig. 10, the separator plate 50 is an annular member having an opening in the center through which the drive shaft 14 is inserted. The separator plate 50 is fixed to the inner peripheral surface of the sealed housing 2 by plug welding, caulking, or the like. 3 and other figures, the separator plate 50 separates the upper cylinder chamber 31 and the lower cylinder chamber. The upper surface of the separator plate 50 defines a lower area of ​​the upper cylinder chamber 31. The lower surface of the separator plate 50 defines an upper area of ​​the lower cylinder chamber.

[0036] The separator plate 50 has a suction pipe insertion hole that extends radially inward from the side surface. A suction pipe 10 that guides refrigerant to the upper cylinder chamber 31 is inserted into the suction pipe insertion hole. The separator plate 50 has a first flow path 41 that penetrates in the vertical direction. The upstream end of the first flow path 41 is connected to the suction pipe 10. The downstream end of the first flow path 41 is connected to the upstream end of the second flow path 42. The first flow path 41 and the second flow path 42 are connected to form a single linear flow path that extends in the vertical direction.

[0037] 1, second bolt holes 52 communicating with first bolt holes 37a are formed in separator plate 50. Female threads are formed on the inner circumferential surfaces of second bolt holes 52 to threadably engage with male threads of bolts 38. Upper bearing cylinder portion 32 and separator plate 50 are fastened together by bolts 38 inserted through first bolt holes 37a and second bolt holes 52.

[0038] The lower compression mechanism 60 has a structure that is vertically symmetrical to the upper compression mechanism 30 with respect to the separator plate 50. Therefore, a detailed description of the lower compression mechanism 60 will be omitted.

[0039] 3, the refrigerant that flows from the suction pipe 10 into the first flow path 41 flows through the first flow path 41 and the second flow path 42 as shown by the arrow A2, and flows into the upper cylinder chamber 31 and the lower cylinder chamber from the suction port 43. The refrigerant compressed in the upper cylinder chamber 31 and the lower cylinder chamber is discharged into the discharge chamber (not shown) via the discharge port (not shown) and the discharge valve (not shown), and is then discharged from there into the sealed housing 2, and is then guided to the upper part of the sealed housing 2 and discharged to the refrigeration cycle side via the discharge piping 8.

[0040] According to this embodiment, the following advantageous effects are achieved. Note that, although the following mainly describes the advantageous effects of the upper compression mechanism 30, it goes without saying that the same advantageous effects as those of the upper compression mechanism 30 can also be achieved with the lower compression mechanism 60. In this embodiment, the upper bearing cylinder portion 32 that defines the upper cylinder chamber 31 is made of a short fiber composite material. Short fiber composite materials are more easily deformed than metal materials, etc. As a result, when the upper rotor 33, which rotates within the upper cylinder chamber 31, comes into contact with the upper bearing cylinder portion 32 that defines the upper cylinder chamber 31, the upper bearing cylinder portion 32 is easily deformed by the load acting from the upper rotor 33. At this time, the upper bearing cylinder portion 32 deforms due to the load from the upper rotor 33, so that contact with the upper rotor 33 is suppressed. Therefore, contact between the upper bearing cylinder portion 32 and the upper rotor 33 can be suppressed. Furthermore, because the deformation of the upper bearing cylinder portion 32 is due to contact with the upper rotor 33, the upper bearing cylinder portion 32 does not deform to the extent that the gap formed between the upper rotor 33 and the upper rotor 33 becomes excessively large. As described above, in this embodiment, when manufacturing the upper compression mechanism 30, contact between the upper bearing cylinder portion 32 and the upper rotor 33 can be suppressed without strictly controlling the gap formed between the upper bearing cylinder portion 32 and the upper rotor 33. Therefore, the manufacturing of the compression mechanism 6 can be facilitated. The deformation of the upper bearing cylinder portion 32 also includes deformation caused by the upper rotor 33 and the like cutting the upper bearing cylinder portion 32.

[0041] Furthermore, if the bearing is made of a metal material, uneven contact of the drive shaft 14 with the bearing can increase localized surface pressure and reduce the reliability of the bearing. However, in this embodiment, the upper bearing cylinder portion 32 is made of a composite material, so the upper bearing cylinder portion 32 deforms in response to deformation of the drive shaft 14. This makes it possible to suppress an increase in localized surface pressure on the upper bearing cylinder portion 32 and to suppress a decrease in the reliability of the bearing function of the upper bearing portion 35.

[0042] When forming bearings and cylinders from metal materials, it is possible to consider machining them. When forming bearings and the like by machining, it is necessary to take into consideration interference with tools, etc., which can make the forming work complicated. Furthermore, when machining a component with a complex shape, such as a bearing and a cylinder integrated together, the forming work can become even more complicated. On the other hand, in this embodiment, the bearing and cylinder are formed from a composite material. When molding a bearing or the like from a composite material, it can be molded, for example, by injection molding using a mold or the like, so there is no need for complicated work such as machining. Therefore, even a component with a complex shape, such as the upper bearing cylinder portion 32 in which the bearing and cylinder are integrated, can be easily molded. In addition, in this embodiment, the bearing and the cylinder are integrally formed, which reduces the number of parts compared to when the bearing and the cylinder are separate, thereby reducing the cost and time required for assembly. Furthermore, if the bearing and cylinder are formed separately, it is necessary to align them so that they are coaxial, but by forming the bearing and cylinder as a single unit, the work of aligning the bearing and cylinder is eliminated. Furthermore, since the bearing and cylinder are integrally formed, the position of the upper rotor 33 within the upper cylinder chamber 31 is determined by supporting the drive shaft 14 on the bearing. This reduces the variation in the gap formed between the upper cylinder portion and the upper rotor 33. This eliminates the need for fitting based on the actual dimensions of the cylinder and bearing.

[0043] In this embodiment, the separator plate 50 is fixed to the upper bearing cylinder portion 32 and is also fixed to the sealed housing 2. As a result, the drive shaft 14 is supported by the sealed housing 2 via the upper bearing cylinder portion 32 and the separator plate 50. In addition, in this embodiment, the separator plate 50 is formed of a metal material. Metal materials are less likely to deform than composite materials, etc. In this way, since the drive shaft 14 is supported by the separator plate 50 made of a less deformable metal material, the drive shaft 14 is less likely to tip over compared to when the separator plate 50 is made of a short fiber composite material. Therefore, it is less likely that the rotor 13 and the stator 12 will come into contact due to deformation of the drive shaft 14. Furthermore, in this embodiment, the compression mechanism 6 is fixed to the sealed housing 2 by the separator plate 50 located in the center in the vertical direction. This shortens the distance from the fixed point with the sealed housing 2 to each cylinder chamber that compresses the refrigerant, compared to when the compression mechanism 6 is fixed to the sealed housing 2 at the ends in the vertical direction. Therefore, deformation of the upper bearing cylinder portion 32 can be suppressed.

[0044] In this embodiment, the suction pipe 10 is connected to a metal separator plate 50. This makes it possible to suppress deformation and deterioration of the connected member (separator plate 50) due to heat (for example, heat associated with brazing or welding) generated when connecting the suction pipe 10. In addition, in this embodiment, the suction pipe 10 is connected to the separator plate 50. This allows for a reduction in the number of suction pipes 10 compared to a case where multiple suction pipes 10 are provided to connect to each cylinder chamber. This reduces the number of parts, thereby reducing the cost and time required for assembly.

[0045] In this embodiment, the upper edge of the suction port 43 is defined by the upper bearing cylinder, and the lower edge of the suction port 43 is defined by the separator plate 50. That is, when looking at only the upper bearing cylinder, the lower part of the suction port 43 is open. This allows the vertical length of the suction port 43 to be longer than when a member is provided to close the lower part of the suction port 43, and therefore the area of ​​the suction port 43 can be increased accordingly. Furthermore, for example, when the area is the same as when a member that closes the lower part of the suction port 43 is provided, the length in the vertical direction can be increased, and the length in the direction intersecting the predetermined direction of the suction port 43 (i.e., the rotation direction of the upper rotor 33) can be shortened accordingly. Therefore, the time that the upper rotor 33 closes the suction port 43 can be extended, and the compression efficiency of the refrigerant in the upper cylinder chamber 31 can be improved. Furthermore, since the lower side of the suction port 43 in the upper bearing cylinder is open, when the upper bearing cylinder is formed by injection molding and is removed upward from the mold, it can be easily removed from the mold.

[0046] In this embodiment, the fastening portion 37 is connected to the rib 35b. As a result, the load acting on the upper bearing portion 35 when the drive shaft 14 tries to tilt can be transmitted to the separator plate 50 via the rib 35b and the fastening member. As a result, the drive shaft 14 can be supported by the separator plate 50, which is less likely to deform, and deformation of the drive shaft 14 can be suppressed.

[0047] In this embodiment, the rib 35b is a plate-like member with a constant thickness, and extends radially from the outer circumferential surface of the cylindrical portion 35a of the upper bearing portion 35. Therefore, when viewed from above, the circumferential length (plate thickness) of the rib 35b is constant. Therefore, for example, when the upper bearing cylinder portion 32 is formed by injection molding and is removed upward from a mold, the rib 35b does not interfere with the mold, and the mold can be easily removed. Furthermore, by providing ribs 35b extending radially from the outer peripheral surface of the cylindrical portion 35a, the rigidity in the direction in which the drive shaft 14 is inclined relative to a predetermined direction (inclination direction) can be improved while minimizing the product volume.

[0048] In this embodiment, multiple ribs 35b are arranged at equal intervals around the circumference of the cylindrical portion 35a. This improves the rigidity of the cylindrical portion 35a in the tilting direction over the entire circumference. Furthermore, by providing the ribs 35b, the ribs 35b absorb thermal expansion or contraction of the upper bearing portion 35. This makes it possible to suppress tilting of the drive shaft 14 due to thermal expansion or contraction of the upper bearing portion 35. Furthermore, for example, when forming the upper bearing cylinder portion 32 by injection molding, if a short fiber composite material is poured into a mold in a predetermined direction from the tip of the cylindrical portion 35a of the upper bearing portion 35, the ribs 35b function as an inflow path for the short fiber composite material. This makes it easier to pour the composite material uniformly throughout the entire upper bearing cylinder portion 32. Furthermore, as the short fiber composite flows radially along the ribs 35b, the fibers contained in the short fiber composite extend in the flow direction, which is substantially the same as the tilt direction of the drive shaft 14, thereby improving the rigidity of the drive shaft 14 in the tilt direction.

[0049] In this embodiment, a metal bushing 36 is provided between the upper bearing portion 35 and the drive shaft 14. This improves the limit PV value, thereby suppressing wear on the upper bearing portion 35 due to rotation of the drive shaft 14. In this embodiment, the metal bushings 36 are provided at both ends of the upper bearing portion 35 in the vertical direction. In other words, the metal bushings 36 are not provided in the center of the upper bearing portion 35. As a result, compared to a case in which the metal bushings 36 are provided over substantially the entire vertical area of ​​the upper bearing portion 35, when the drive shaft 14 deforms in the tilting direction, the upper bearing portion 35 is more likely to deform to follow the deformation of the drive shaft 14. In other words, it is more difficult for the metal bushings 36 to restrict the deformation of the upper bearing portion 35. Since the upper bearing portion 35 follows the deformation of the drive shaft 14, even when the drive shaft 14 deforms, the surface pressure acting on the upper bearing portion 35 can be reduced, and wear of the upper bearing portion 35 can be suppressed. Furthermore, compared to when the metal bushing 36 is provided over substantially the entire area of ​​the upper bearing portion 35 in the vertical direction, the volume of the metal bushing 36 is reduced, and therefore the manufacturing cost of the metal bushing 36 can be reduced.

[0050] In this embodiment, a metallic suction-side wear-resistant portion 45 and a discharge-side wear-resistant portion 46 are provided at the end of the blade groove 44 on the upper cylinder chamber 31 side, thereby suppressing wear on the upper cylinder body portion 34 due to the sliding of the blade. Furthermore, only the radially inner end of the suction-side sidewall surface of the blade groove 44 is covered by the suction-side wear-resistant portion 45. This makes it easier for the upper cylinder portion to deform in response to the load from the blade, compared to when a wear-resistant portion is provided over substantially the entire cylinder groove. In other words, the suction-side wear-resistant portion 45 is less likely to restrict the deformation of the upper cylinder portion. The deformation of the upper cylinder portion in response to the load from the blade reduces the surface pressure acting on the upper cylinder portion, thereby suppressing wear of the upper cylinder portion. Furthermore, in this case, the volume of the suction-side wear-resistant portion 45 is reduced compared to when a wear-resistant portion is provided over substantially the entire blade groove 44, thereby reducing the manufacturing cost of the suction-side wear-resistant portion 45. Because the blade mainly comes into contact with only the radially inner end of the suction-side sidewall surface, even if the wear-resistant portion covers only the inner end, wear can be suppressed effectively.

[0051] The present disclosure is not limited to the above-described embodiments, and various modifications can be made without departing from the spirit of the present disclosure.

[0052] 11, a sleeve 65 may be provided between the bolt 38 and the inner circumferential surface of the fastening portion 37. The sleeve 65 is made of a metal material (for example, cast iron, aluminum alloy, or copper alloy). By providing the sleeve 65 between the bolt 38 and the inner circumferential surface of the fastening portion 37 in this way, the stress relaxation phenomenon can be suppressed, and therefore, a decrease in the axial force of the bolt 38 can be suppressed. Furthermore, the sleeve 65 is provided from the upper end of the fastening portion 37 to a position above the lower end. In other words, it is not provided to the lower end of the fastening portion 37. This improves the sealing performance between the bolt 38 and the fastening portion 37 compared to when the sleeve 65 is provided to the lower end of the fastening portion 37. The bolt 38 may be made of aluminum without providing the sleeve 65. The linear expansion coefficient of aluminum is closer to that of short fiber composite material than that of iron. Therefore, by making the bolt 38 out of aluminum, creep can be suppressed compared to when the bolt 38 is made out of iron.

[0053] As shown by the broken line in FIG. 6, an excess material portion 66 may be provided radially outward of the intake port 43 of the upper bearing cylinder portion 32, protruding radially outward beyond other regions. A refrigerant with a low temperature before compression is introduced into the suction port 43. Therefore, the temperature of the area near the suction port 43 is lower than that of other areas. Short fiber composites have a higher thermal expansion coefficient than metals and the like. Therefore, the area near the suction port 43 of the upper bearing cylinder portion 32 made of short fiber composites may deform due to the temperature difference with other areas. If the upper bearing cylinder portion 32 deforms, adhesion with the separator plate 50 decreases, and refrigerant may leak from the upper cylinder chamber 31. On the other hand, in this embodiment, the upper bearing cylinder portion 32 is provided with an excess metal portion 66 radially outward of the suction port 43. This makes it possible to make the area near the suction port 43 less susceptible to deformation. Therefore, deformation of the upper bearing cylinder portion 32 can be suppressed, and leakage of refrigerant from the upper cylinder chamber 31 can be suppressed.

[0054] Furthermore, in the above embodiment, a so-called two-cylinder rotary compressor 1 having two cylinders has been described, but the present disclosure is not limited to this. For example, as shown in Fig. 12, a so-called one-cylinder rotary compressor 70 having only one cylinder may also be used. In the example of Fig. 12, a compression mechanism 71 includes an upper bearing 72, a lower bearing 73, and a cylinder main body 74. The upper bearing 72, the lower bearing 73, and the cylinder main body 74 are each formed as separate bodies. In the example of Fig. 12, the upper bearing 72 and / or the lower bearing 73 are made of a short fiber composite material. The cylinder body 74 is made of a metal material. The cylinder body 74 is fixed to the sealed housing 2. The upper bearing 72 and the cylinder body 74 are fastened and fixed by bolts 75. The lower bearing 73 and the cylinder body 74 are also fastened and fixed by bolts 76. In the above description, an example has been described in which the upper bearing 72, the lower bearing 73, and the cylinder body 74 are formed as separate bodies, but the present disclosure is not limited to this. For example, the upper bearing 72 and the cylinder body 74 may be integrally formed from a composite material. In this case, the lower bearing 73 is formed from a metallic material and fixed to the sealed housing 2. The lower bearing 73 and the cylinder body 74 may also be integrally formed from a composite material. In this case, the upper bearing 72 is formed from a metallic material and fixed to the sealed housing 2.

[0055] The rotary compressor according to the above-described embodiment can be understood, for example, as follows. A rotary compressor according to one embodiment of the present disclosure includes a housing (2) forming an outer shell, a drive source (5), a compression mechanism (6) housed in the housing and compressing a refrigerant by the drive force from the drive source, and a drive shaft (14) connecting the drive source and the compression mechanism and rotating around a central axis extending along a predetermined direction. The compression mechanism has a rotor (33) connected to the drive shaft and housed in a cylinder chamber (31), a cylinder (34) defining the radially outer side of the cylinder chamber, and a bearing (35) rotatably supporting the drive shaft and defining the predetermined direction of the cylinder chamber. The refrigerant is compressed between the rotating rotor and the cylinder, and the bearing and / or the cylinder are formed of a composite material in which resin is reinforced with reinforcing fibers.

[0056] In the above configuration, the bearings and / or cylinders (hereinafter referred to as "bearings, etc.") that define the cylinder chamber are formed from a composite material in which resin is reinforced with reinforcing fibers. Composite materials are more easily deformed than metal materials, etc. As a result, when the rotor that rotates within the cylinder chamber comes into contact with the bearings, etc. that define the cylinder chamber, the bearings, etc. are easily deformed by the load acting from the rotor. In this case, the bearings, etc. deform due to the load from the rotor, so they deform in a way that prevents contact with the rotor. Therefore, contact between the bearings, etc. and the rotor can be prevented. Furthermore, because the deformation of the bearings, etc. is due to contact with the rotor, the bearings, etc. do not deform to the extent that the gap formed between them and the rotor becomes excessively large. In this way, with the above configuration, contact between the bearings and the rotor can be suppressed without strictly controlling the gap between the bearings and the rotor during manufacturing of the compression mechanism, thereby facilitating manufacturing of the compression mechanism. The deformation of the bearings and the like also includes deformation caused by the rotor cutting the bearings and the like.

[0057] In addition, in a rotary compressor according to one aspect of the present disclosure, the bearing and the cylinder are formed from the composite material, and the bearing and the cylinder are integrally formed.

[0058] When forming bearings and cylinders from metal materials, it is possible to consider machining them. When forming bearings and the like by machining, it is necessary to take into consideration interference with tools, etc., which can make the forming work complicated. Furthermore, when machining a component with a complex shape, such as a bearing and a cylinder integrated together, the forming work can become even more complicated. On the other hand, in the above configuration, the bearing and cylinder are made of a composite material. When molding a bearing or the like from a composite material, it can be molded by, for example, injection molding using a mold or the like, so there is no need for complicated work such as machining. Therefore, even a component with a complex shape, such as a bearing and a cylinder integrated together, can be easily molded. Furthermore, in the above configuration, the bearing and the cylinder are integrally formed, which reduces the number of parts compared to when the bearing and the cylinder are separate, thereby reducing the cost and time required for assembly. Furthermore, if the bearing and cylinder are formed separately, it is necessary to align them so that they are coaxial, but by forming the bearing and cylinder as a single unit, the work of aligning the bearing and cylinder is eliminated. Furthermore, by forming the bearing and cylinder integrally and supporting the drive shaft on the bearing, the relative position of the cylinder and rotor is determined, which reduces the variation in the gap between the cylinder and rotor, making it unnecessary to fit the cylinder and bearing based on their actual dimensions. Note that being integrally formed does not mean that the bearing and cylinder are formed as separate components and then fixed together using fasteners or welding, etc., but rather that the bearing and cylinder are formed as an integral part by, for example, injection molding.

[0059] In addition, in a rotary compressor according to one aspect of the present disclosure, the drive source has a rotor (13) to which the drive shaft is fixed and a stator (12) surrounding the rotor, the compression mechanism has a plurality of cylinder chambers aligned in the predetermined direction and the rotor housed in each of the cylinder chambers, the cylinder chambers adjacent to each other in the predetermined direction are separated by a separator (50), the bearing and the cylinder formed integrally are fixed to the separator, and the separator is formed of a metal material and fixed to the housing.

[0060] In the above configuration, the separator is fixed to the housing, and the bearing is fixed thereto. As a result, the drive shaft is fixed to the housing via the bearing and the separator made of a metal material. In addition, in the above configuration, the separator is made of a metal material. Metal materials are less likely to deform than composite materials, etc. In this way, since the drive shaft is supported by a separator made of a less deformable metal material, the drive shaft is less likely to deform than when the separator is made of a composite material. Therefore, it is less likely that the rotor and stator will come into contact due to deformation of the drive shaft. In addition, in the above configuration, the compression mechanism is fixed to the housing by a separator located relatively toward the center in the predetermined direction. This shortens the distance from the fixed point to each cylinder chamber that compresses the refrigerant compared to when the compression mechanism is fixed to the housing at the end of the predetermined direction. This reduces deformation of the bearings, cylinders, etc.

[0061] Furthermore, a rotary compressor according to one aspect of the present disclosure includes an intake pipe (10) that guides the refrigerant to the compression mechanism, the intake pipe being connected to the separator, and the compression mechanism having a refrigerant flow path (41, 42) that guides the refrigerant supplied from the intake pipe to the cylinder chamber.

[0062] In the above configuration, the suction pipe is connected to a metallic separator, which can prevent deformation and deterioration of the connected member (separator) due to heat generated when connecting the suction pipe (for example, heat associated with brazing or welding). In addition, in the above configuration, the suction pipe is connected to the separator. This allows for a reduction in the number of suction pipes compared to when multiple suction pipes are provided to connect to each cylinder chamber. This reduces the number of parts, thereby reducing the cost and time required for assembly.

[0063] In addition, in a rotary compressor according to one aspect of the present disclosure, the refrigerant flow path is connected to an intake port (43) whose downstream end opens into the cylinder chamber, and the intake port is partitioned on one side in the predetermined direction by the bearing and on the other side in the predetermined direction by the separator.

[0064] In the above configuration, one side of the suction port in the predetermined direction is defined by the bearing, and the other side of the suction port in the predetermined direction is defined by the separator. That is, when the bearing and the cylinder are viewed as a single unit, the other side of the suction port in the predetermined direction is open. This allows the length of the suction port in the predetermined direction to be longer than when a member closing the other side of the suction port is provided, thereby increasing the area of ​​the suction port. Furthermore, for example, for the same area as when a member closing the other side of the suction port is provided, the length in the predetermined direction can be increased, thereby shortening the length of the suction port in a direction intersecting the predetermined direction (i.e., the direction of rotation of the rotor). This allows the rotor to close the suction port for a longer period of time, thereby improving the compression efficiency of the refrigerant in the cylinder chamber. Furthermore, since the other side of the suction port in the specified direction is open in the integrated bearing and cylinder, for example, when the bearing and cylinder are integrally formed by injection molding and then demolded from the mold in one direction in the specified direction, they can be easily demolded.

[0065] Furthermore, a rotary compressor according to one aspect of the present disclosure includes a fastener (38) that fixes the integrally formed bearing and cylinder to the separator, and the integrally formed bearing and cylinder have a rib (35b) that reinforces the bearing and a fastening portion (37) that defines a fastening hole through which the fastener is inserted, and the fastening portion is connected to the rib.

[0066] In the above configuration, the fastening portion is connected to the rib. This allows the load acting on the bearing when the drive shaft tries to tilt to be transmitted to the separator via the rib and the fastener. This allows the drive shaft to be supported by the separator, which is less likely to deform, thereby suppressing deformation of the drive shaft.

[0067] In addition, in the rotary compressor according to one aspect of the present disclosure, a sleeve (65) made of a metal material is provided between the inner circumferential surface of the fastening hole and the fastener.

[0068] In the above configuration, a sleeve made of a metal material is provided between the inner circumferential surface of the fastening hole and the fastener, which suppresses creep and therefore reduces the reduction in axial force of the fastener.

[0069] In addition, in a rotary compressor according to one aspect of the present disclosure, the rib is a plate-shaped member having a constant thickness, and extends radially from an outer peripheral surface of the cylindrical bearing.

[0070] In the above configuration, the rib is a plate-like member with a constant thickness that extends radially from the outer circumferential surface of the cylindrical bearing. Therefore, when viewed from a predetermined direction (the direction in which the drive shaft extends), the circumferential length (thickness) of the rib is constant. Therefore, for example, when the bearing and cylinder are integrally formed by injection molding and then removed from the mold in a predetermined direction, the rib and the mold do not interfere with each other, allowing for easy removal from the mold. Furthermore, by providing ribs extending radially from the outer peripheral surface of the bearing, it is possible to improve rigidity in the direction in which the drive shaft is inclined relative to the predetermined direction (inclination direction) while minimizing the product volume.

[0071] In addition, in the rotary compressor according to one aspect of the present disclosure, a plurality of the ribs are provided, The plurality of ribs are arranged side by side at predetermined intervals in the circumferential direction of the bearing.

[0072] In the above configuration, multiple ribs are arranged in a row at predetermined intervals around the circumferential direction of the bearing. This improves rigidity against multiple tilt directions. Furthermore, the provision of ribs allows the ribs to absorb thermal expansion or contraction of the bearing. This makes it possible to suppress tilt of the drive shaft due to thermal expansion or contraction of the bearing. Furthermore, for example, when the bearing and cylinder are integrally formed by injection molding and the composite material is poured into the mold in a predetermined direction from the tip of the bearing, the ribs function as an inflow path for the composite material, making it easier to uniformly pour the composite material into the entire integrally molded product of the bearing and cylinder. Furthermore, as the composite flows radially along the ribs, the fibers contained in the composite extend in the direction of the flow, which is approximately the same as the tilt direction of the drive shaft, thereby improving rigidity against the tilt direction of the drive shaft.

[0073] Furthermore, a rotary compressor according to one aspect of the present disclosure includes a bearing wear-resistant portion (36) formed of a metal material and provided between the bearing and the drive shaft, the bearing being formed of the composite material, and the bearing wear-resistant portion being provided at both ends of the bearing in the predetermined direction.

[0074] In the above configuration, a bearing wear-resistant portion is provided between the bearing and the drive shaft, which improves the limit PV value and suppresses bearing wear caused by rotation of the drive shaft. Furthermore, in the above configuration, the bearing wear-resistant portions are provided at both ends of the bearing in the predetermined direction. In other words, no bearing wear-resistant portion is provided in the center of the bearing. As a result, compared to a case in which the bearing wear-resistant portions are provided over substantially the entire area of ​​the bearing in the predetermined direction, when the drive shaft deforms in the tilt direction, the bearing is more likely to deform to follow the deformation of the drive shaft. In other words, it is more difficult for the bearing wear-resistant portions to restrict the deformation of the bearing. By allowing the bearing to follow the deformation of the drive shaft, the surface pressure acting on the bearing can be reduced even if the drive shaft deforms, thereby suppressing bearing wear. Furthermore, compared to when the bearing wear-resistant portion is provided over substantially the entire area of ​​the bearing in a predetermined direction, the volume of the bearing wear-resistant portion is reduced, which reduces the manufacturing cost of the bearing wear-resistant portion.

[0075] In addition, a rotary compressor according to one embodiment of the present disclosure includes a blade that divides the cylinder chamber into a refrigerant intake side and a refrigerant discharge side, the cylinder is formed from the composite material and has a blade groove (44) that slidably accommodates the blade, and a cylinder wear-resistant portion (45, 46) formed from a metal material is provided at the end of the blade groove on the cylinder chamber side.

[0076] In the above configuration, a metal cylinder wear-resistant portion is provided at the end of the blade groove on the cylinder chamber side, thereby making it possible to suppress wear of the cylinder due to sliding of the blade. Furthermore, for example, if the cylinder wear-resistant portion is provided only on the end of the cylinder groove facing the cylinder chamber, the cylinder is more likely to deform in response to the load from the blade than if the cylinder wear-resistant portion were provided over substantially the entire cylinder groove. In other words, the cylinder wear-resistant portion is less likely to restrict the cylinder deformation. By allowing the cylinder to deform in response to the load from the blade, the surface pressure acting on the cylinder can be reduced, thereby suppressing cylinder wear. Furthermore, in this case, the volume of the cylinder wear-resistant portion is reduced compared to if the cylinder wear-resistant portion is provided over substantially the entire blade groove, thereby reducing the manufacturing cost of the cylinder wear-resistant portion.

[0077] In addition, in a rotary compressor according to one aspect of the present disclosure, the cylinder is formed from the composite material, and the cylinder has an intake port (43) that guides the refrigerant into the cylinder chamber, and an excess material portion (66) that is provided radially outside the intake port and protrudes radially outward more than other regions.

[0078] The suction section receives refrigerant that is at a low temperature before compression. As a result, the area near the suction section has a lower temperature than other areas. Therefore, in a cylinder made of composite material, the area near the suction section may deform due to the temperature difference with other areas. If the cylinder deforms, refrigerant may leak from the cylinder chamber. On the other hand, in the above-mentioned configuration, the cylinder has an excess portion provided radially outward of the suction port, which makes it difficult for the area near the suction port to deform. Therefore, even if the cylinder is made of a composite material, deformation of the cylinder can be suppressed, thereby suppressing refrigerant leakage from the cylinder chamber. [Explanation of symbols]

[0079] 1: Rotary compressor 2: Sealed housing 3: Cover 4: Cover 5: Electric motor 6: Compression mechanism 7: Attached legs 8:Discharge piping 10:Suction pipe 12: Stator 13: Rotor 14: Drive shaft 15: Upper eccentric shaft part 16: Lower eccentric shaft part 30: Upper compression mechanism 31: Upper cylinder chamber 32: Upper bearing cylinder part 33: Upper rotor 34: Upper cylinder body 34a: Partition 34b: Contact part 34c: Outer frame 35: Upper bearing part 35a: Cylindrical part 35b: Rib 35c: Annular section 36: Metal bush 36a: Notch 36b: Anti-slip part 37: Fastening part 37a: First bolt hole 38: Bolt 41: First flow path 42: Second flow path 43: Intake port 44: Blade groove 45: Intake side wear-resistant part 45a:Protrusion 45b:Protrusion 46: Discharge side wear-resistant part 46a: recess 46b: recess 50: Separator plate 52: Second bolt hole 60: Lower compression mechanism 65: Sleeve 66: Excess meat part 70: Rotary compressor 71: Compression mechanism 72: Upper bearing 73: Lower bearing 74: Cylinder body 75: Bolt 76: Bolt

Claims

1. a housing forming an outer shell; A driving source; a compression mechanism housed in the housing and configured to compress a refrigerant by a driving force from the driving source; a drive shaft that connects the drive source and the compression mechanism and rotates about a central axis that extends along a predetermined direction, the compression mechanism includes a rotor connected to the drive shaft and accommodated in a cylinder chamber, a cylinder defining the radially outer side of the cylinder chamber, and a bearing rotatably supporting the drive shaft and defining the cylinder chamber in the predetermined direction, and compresses the refrigerant between the rotating rotor and the cylinder; The cylinder is formed of a composite material made of resin reinforced with reinforcing fibers, The cylinder has an intake port that introduces the refrigerant into the cylinder chamber, and an excess material portion that is provided radially outward of the intake port and protrudes radially outward beyond other regions of the cylinder.

2. the bearing and the cylinder are formed from the composite material, 2. The rotary compressor according to claim 1, wherein the bearing and the cylinder are integrally formed.

3. the drive source includes a rotor to which the drive shaft is fixed and a stator surrounding the rotor, the compression mechanism includes a plurality of the cylinder chambers arranged in the predetermined direction and the rotors accommodated in the respective cylinder chambers, The cylinder chambers adjacent to each other in the predetermined direction are separated by a separator, the bearing and the cylinder, which are integrally formed, are fixed to the separator; 3. The rotary compressor according to claim 2, wherein the separator is made of a metal material and is fixed to the housing.

4. a suction pipe for guiding the refrigerant to the compression mechanism; the suction pipe is connected to the separator, 4. The rotary compressor according to claim 3, wherein the compression mechanism has a refrigerant flow path that guides the refrigerant supplied from the suction pipe to the cylinder chamber.

5. a downstream end of the refrigerant flow path connected to a suction port that opens into the cylinder chamber; 5. The rotary compressor according to claim 4, wherein one side of the suction port in the predetermined direction is defined by the bearing, and the other side in the predetermined direction is defined by the separator.

6. a fastener for fixing the integrally formed bearing and cylinder to the separator; The bearing and the cylinder, which are integrally formed, have a rib that reinforces the bearing and a fastening portion that defines a fastening hole through which the fastener is inserted, The rotary compressor according to any one of claims 3 to 5, wherein the fastening portion is connected to the rib.

7. 7. The rotary compressor according to claim 6, wherein a sleeve made of a metal material is provided between the inner circumferential surface of the fastening hole and the fastener.

8. 8. The rotary compressor according to claim 6, wherein the rib is a plate-like member having a constant thickness and extending in a radial direction from an outer peripheral surface of the cylindrical bearing.

9. The rib is provided in plurality, 9. The rotary compressor according to claim 8, wherein the plurality of ribs are arranged side by side at predetermined intervals in the circumferential direction of the bearing.

10. a bearing wear-resistant portion formed of a metal material and provided between the bearing and the drive shaft; the bearing is formed from the composite material, 10. The rotary compressor according to claim 1, wherein the bearing wear-resistant portion is provided at both ends of the bearing in the predetermined direction.

11. a blade that divides the cylinder chamber into a suction side of the refrigerant and a discharge side of the refrigerant, the cylinder is formed of the composite material and has a blade groove for slidably receiving the blade; 11. The rotary compressor according to claim 1, wherein a cylinder wear-resistant portion made of a metal material is provided at an end of the blade groove on the cylinder chamber side.

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