Compressor and refrigeration cycle apparatus

Abstract

To provide a compressor and a refrigeration cycle device including the compressor.SOLUTION: A compressor is disclosed. A compressor (1) is provided with a fixed-side member (43) constituting a compression chamber (43a) and having a discharge opening (43q) opening to an inner surface (43u) of the fixed-side member (43), an outlet (43o) formed on a surface (43t / 43r) of the fixed-side member (43) different from the inner surface (43u), and a hole (43p) extending from the discharge opening (43q) toward the outside of the fixed-side member (43) and communicating with the outlet (43o). The compression machine (1) further includes a valving element (V) provided in the hole (43p) of the fixed-side member (43) and movable in a direction substantially perpendicular to a seating surface (S) around the discharge port (43o), and a mechanism (D) configured to bias the valving element (V) in the direction substantially perpendicular to the seating surface (S) such that the valving element (V) closes the discharge port (43q). A refrigeration cycle apparatus including the compressor (1) is also provided.SELECTED DRAWING: Figure 3

Description

[Technical Field]

[0001] The present invention relates to a compressor structure, and more particularly to a compressor and a refrigeration cycle device including the compressor. [Background technology]

[0002] Losses related to compressor performance include thermal fluid loss, mechanical loss, and electric motor loss. In particular, in rotary compressors, the proportion of thermal fluid loss, including overcompression loss and re-expansion loss, is large among the above-mentioned losses. In order to improve compressor efficiency, it is necessary to reduce these thermal fluid losses, including overcompression loss and re-expansion loss.

[0003] In recent years, there has been a demand for compressors to be compatible with refrigerants with low global warming potential (GWP). To accommodate low-GWP refrigerants, compressors are required to increase their displacement. However, this increase in displacement increases the amount of refrigerant circulating, which increases the discharge flow rate of the high-pressure gas compressed in the compression chamber. This increase in discharge flow rate results in an increase in overcompression loss (i.e., thermal fluid loss).

[0004] To address this issue, it is possible to increase the area of ​​the discharge port and the cylinder discharge notch so as to reduce the discharge flow rate in response to the increase in the discharge flow rate. However, increasing the area of ​​the discharge port and the cylinder discharge notch increases the dead volume, which in turn increases the re-expansion loss (i.e., thermal fluid loss).

[0005] In view of the above-mentioned technical background, there is a demand for the development of a compressor structure having a discharge structure in which both the over-compression loss and the re-expansion loss are small.

[0006] Furthermore, while it is possible to increase the height of the compression chamber to increase the displacement, in this case, in many rotary compressors, the path to the discharge port would become larger, which could increase over-compression loss, because in many rotary compressors, the discharge port for the high-pressure gas compressed in the compression chamber is located on the top or bottom surface of the compression chamber.

[0007] Known techniques for reducing over-compression loss and re-expansion loss are disclosed in Japanese Patent Laid-Open No. 9-112469 (Patent Document 1) and Japanese Patent Laid-Open No. 9-158878 (Patent Document 2). In the prior art disclosed in Patent Documents 1 and 2, a discharge port for high-pressure gas compressed in a compression chamber is provided on the inner diameter surface of the cylinder, and the compression chamber and the entire surface of the discharge port are directly connected, eliminating the need to provide a cylinder discharge notch, suppressing an increase in dead volume, and reducing over-compression loss and re-expansion loss.

[0008] However, both of the prior arts described in Patent Documents 1 and 2 include a reed-type discharge valve and valve guard. Therefore, high-pressure gas flowing from the compression chamber to the discharge port follows the reed-type discharge valve and valve guard. However, the flow is blocked by the vane blade housing wall, which separates the low-pressure and high-pressure sides of the compression chamber. This can result in pressure loss. While increasing the distance between the discharge port and the vane blade housing wall could reduce pressure loss, this requires locating the discharge port at a lower rotation angle. Locating the discharge port at a lower rotation angle reduces the effective rotation angle for compression, potentially resulting in a decrease in the refrigerant circulation rate. Additionally, locating a reed-type discharge valve and valve guard on the outer periphery of the cylinder bore requires a large recess. However, this increases the occupancy area, which reduces the rigidity of the cylinder that forms the compression chamber and can lead to compression problems due to pressure deformation. [Prior art documents] [Patent documents]

[0009] [Patent Document 1] Japanese Patent Application Publication No. 9-112469 [Patent Document 2] Japanese Patent Application Publication No. 9-158878 Summary of the Invention [Problem to be solved by the invention]

[0010] The present disclosure has been made in consideration of the above points, and aims to provide a highly efficient compressor and a refrigeration cycle device equipped with the compressor, which suppresses over-compression loss and re-expansion loss while suppressing a decrease in rigidity and pressure loss in the compression chamber. [Means for solving the problem]

[0011] In order to solve the above-mentioned problems, the present disclosure provides a compressor having the following features. The compressor includes a fixed-side member that defines a compression chamber. The fixed-side member has a discharge port that opens to an inner surface thereof, an outlet formed on a surface of the fixed-side member that is different from the inner surface, and a hole that extends from the discharge port toward the outside of the fixed-side member and communicates with the outlet. The compressor includes a valve element that is provided within the hole of the fixed-side member and is movable in a direction approximately perpendicular to a valve seat surface around the discharge port, and a mechanism that biases the valve element in a direction approximately perpendicular to the valve seat surface so that the valve element closes the discharge port. [Effects of the Invention]

[0012] The above configuration makes it possible to provide a highly efficient compressor and a refrigeration cycle device equipped with the compressor, which suppresses over-compression loss and re-expansion loss while suppressing a decrease in rigidity and pressure loss in the compression chamber. [Brief explanation of the drawings]

[0013] [Figure 1] FIG. 1 is a vertical cross-sectional view showing the overall configuration of a rotary compressor 1 having a one-cylinder configuration as a compressor according to an embodiment of the present disclosure. [Figure 2] FIG. 2 is a diagram illustrating a cylinder housed in a sealed container and constituting a compression chamber, and a discharge valve structure provided in the cylinder, in a compressor according to an embodiment of the present disclosure. [Figure 3] FIG. 3 is a diagram illustrating an enlarged view of a discharge valve structure in a state where the discharge valve is disposed in a compressor according to an embodiment of the present disclosure. [Figure 4]FIG. 4A is a perspective view of a cylinder in a compressor according to an embodiment of the present disclosure, in which a discharge valve is not disposed, and FIG. 4B is an enlarged view thereof. [Figure 5] FIG. 5 illustrates a perspective view of a cylinder with a discharge valve disposed therein in a compressor according to an embodiment of the present disclosure. [Figure 6] FIG. 6 is a diagram illustrating a discharge valve structure including a guide structure according to a preferred embodiment. [Figure 7] FIG. 7 is a vertical cross-sectional view showing the overall configuration of a two-cylinder rotary compressor as a compressor according to the second embodiment of the present disclosure. [Figure 8] FIG. 8 is a diagram showing an example of the configuration of an air conditioner as a refrigeration cycle apparatus including a compressor according to an embodiment of the present disclosure. DETAILED DESCRIPTION OF THE INVENTION

[0014] One or more embodiments of the present disclosure will be described below with reference to the drawings, but the embodiments of the present disclosure are not limited to the specific embodiments described below. Note that the same reference numerals throughout the drawings indicate the same or corresponding parts.

[0015] The present disclosure relates to a compressor and a refrigeration cycle apparatus including a compressor. The compressor according to an embodiment of the present disclosure includes a fixed-side member that defines a compression chamber, the fixed-side member having a discharge port that opens to an inner surface of the fixed-side member, an outlet formed on a surface of the fixed-side member different from the inner surface, and a hole that extends from the discharge port toward an outside of the fixed-side member and communicates with the outlet. The compressor also includes a valve body that is disposed within the hole of the fixed-side member and is movable in a direction substantially perpendicular to a valve seat surface around the discharge port, and a mechanism that biases the valve body in a direction substantially perpendicular to the valve seat surface so as to close the discharge port.

[0016] In the above configuration, the valve disc is configured to move in a direction substantially perpendicular to the valve seat surface around the discharge port, allowing the compressed refrigerant to flow smoothly into the hole through the gap formed between the valve disc and the valve seat surface, thereby reducing pressure loss. Furthermore, the hole in which the valve disc, which moves in a direction substantially perpendicular to the valve seat surface around the discharge port, is located extends from the discharge port toward the outside of the fixed member, preventing a decrease in the rigidity of the compression chamber compared to the configuration using the reed valve described above. Furthermore, because the discharge port is formed on the inner surface of the fixed member, it is possible to reduce over-compression loss and re-expansion loss. Consequently, it is possible to provide a highly efficient compressor and a refrigeration cycle device equipped with the compressor, thereby improving its APF (All-Year Energy Performance Factor).

[0017] Here, a poppet-type discharge valve is configured by providing a valve element within the hole that moves approximately perpendicular to the valve seat surface around the discharge port. A mechanism, such as an elastic body, biases the valve element approximately perpendicular to the valve seat surface so as to close the discharge port. Until the high-pressure compression chamber reaches discharge pressure, the high-pressure gas in the sealed container and the mechanism press the outer surface of the valve element inward, forcing the valve element into tight contact with the valve seat surface and effectively closing the discharge port. On the other hand, once the high-pressure compression chamber reaches or exceeds discharge pressure, the valve element moves approximately parallel from the inside to the outside, opening and creating a gap. Because the entire valve element moves approximately perpendicular to the valve seat surface, a large flow path can be secured for the high-pressure gas pressurized in the compression chamber after it is discharged from the discharge port, thereby reducing overcompression loss. Furthermore, compared to a reed valve type discharge valve, this discharge valve structure has a smaller area (occupied area) facing the inner surface of the fixed side member, so the area of ​​the thin-walled portion due to the structure that provides a hole on the outside to accommodate the discharge valve can be reduced, and the rigidity of the fixed side member that forms the compression chamber can be maintained high.

[0018] In a preferred embodiment, the hole in the fixed member and the valve disc are formed with a guide structure that prevents the valve disc from moving out of a substantially vertical direction. In a specific embodiment, the guide structure includes a concave shape formed on one of the side surfaces of the valve disc and the hole, and a convex shape formed on the other of these. The concave and convex shapes fit together to position the valve disc in a plane horizontal to the valve seat surface. If the valve disc is provided in a hole extending from the discharge port toward the outside of the fixed member and movable in a substantially vertical direction relative to the valve seat surface of the discharge port, gravity and a gap between the valve disc and the valve seat surface may cause the valve disc to shift downward within the hole, resulting in poor contact. While the area of ​​the valve disc can be increased to improve contact resistance to accommodate this shift, this may result in a smaller gap, making it more difficult for high-pressure gas to flow, and thus increasing overcompression loss. In contrast, the provision of the guide structure positions the valve disc in a plane horizontal to the valve seat surface, thereby preventing poor contact due to shifting and ensuring a sufficient gap when the compressor is open, resulting in a highly efficient compressor.

[0019] In a specific embodiment, the compressor is a rotary compressor, the fixed member is a cylinder whose inner surface is a cylindrical surface, and the substantially vertical direction coincides with a substantially radial direction of the cylindrical surface of the cylinder.

[0020] In a preferred embodiment, the outlet formed in the cylinder opens on a surface of the cylinder that faces approximately in the axial direction, and the recess of the recessed shape and the protrusion of the protrusion of the protrusion fit together approximately in the circumferential direction of the cylinder's cylindrical surface (or in a direction approximately perpendicular to the approximately axial and radial directions of the cylindrical surface). Here, the surface of the cylinder that faces the axial direction is, for example, the upper or lower surface, assuming that the axial direction is up or down, and the fitting direction of the recess of the recessed shape and the protrusion of the protrusion of the protrusion is a direction within a horizontal plane. With this configuration, the outlet that serves as a flow path after discharge is located approximately in the axial direction (up or down) of the cylinder's cylindrical surface, and the protrusions extend approximately in the circumferential direction (horizontal) of the cylindrical surface. This prevents interference between the outlet and the protrusion, and the fitting relationship between the protrusion and the recess is always maintained. This makes it possible to provide a highly efficient rotary compressor with a highly flexible discharge valve.

[0021] In a preferred embodiment, the discharge port has a shape elongated in the axial direction of the cylindrical surface, or includes a plurality of openings arranged in the axial direction of the cylindrical surface. By ensuring a discharge port area that is elongated in the axial direction of the cylindrical surface of the cylinder, the installation angle of the discharge port relative to the cylindrical surface of the cylinder can be reduced, and the effective rotation angle at which compression can be performed can be increased. This makes it possible to provide a rotary compressor with high volumetric efficiency while increasing the discharge port area and reducing over-compression loss.

[0022] In a preferred embodiment, the compressor further includes a sealed container that houses the cylinder, and a sealing member that seals a rear opening of a hole provided on the outer surface of the cylinder opposite the discharge port from the internal space of the sealed container. Because the rear opening of the hole is sealed from the internal space of the sealed container, oil can be prevented from flowing into the hole even when the cylinder is immersed in oil accumulated at the bottom of the sealed container. This makes it possible to provide a highly efficient rotary compressor that prevents a decrease in the responsiveness of the discharge valve structure due to oil and prevents backflow of oil from the discharge port into the compression chamber.

[0023] In certain embodiments, the compressor has a single cylinder or multiple cylinders connected in parallel, rather than multiple cylinder stages arranged in series such that the refrigerant discharged from the previous cylinder is drawn into the next cylinder stage.

[0024] In a specific embodiment, a refrigeration cycle device including a compressor having the above-described configuration is provided.

[0025] Hereinafter, the compressor according to the embodiment of the present disclosure will be described in more detail with reference to FIGS.

[0026] 1 is a longitudinal cross-sectional view showing the overall configuration of a hermetic single-cylinder rotary compressor 1 as a compressor according to an embodiment of the present disclosure. In the following, the hermetic rotary compressor 1 will be described as an example of the compressor, but the compressor is not necessarily limited to the hermetic rotary compressor 1. The present disclosure can also be applied to other types of rotary compressors, such as semi-hermetic and open types.

[0027] A rotary compressor 1 according to an embodiment of the present disclosure includes a sealed container 2, an electric motor 3, and a compression mechanism 4. The sealed container 2 houses the electric motor 3 and the compression mechanism 4 and forms the outer shell of the compressor 1. The electric motor 3 is disposed in the upper part of the sealed container 2 and drives the compression mechanism 4. The compression mechanism 4 is disposed in the lower part of the sealed container 2, below the electric motor 3, and compresses a refrigerant (working fluid). The refrigerant compressed by the compression mechanism 4 flows upward (indicated by arrow α1 in FIG. 1) and is discharged from a discharge port 2o (indicated by arrow α2 in FIG. 1).

[0028] The sealed container 2 is composed of a central cylinder 21, an upper lid 22, and a bottom 23. The cylinder 21 is a cylindrical housing that is open at the top and bottom. The lid 22 has a dish shape and is fitted to the cylinder 21 while closing the upper opening of the cylinder 21. The bottom 23 also has a dish shape and is fitted to the cylinder 21 while closing the lower opening of the cylinder 21. The cylinder 21 is made of, for example, a steel plate, and the lid 22 and bottom 23 are fixed to the cylinder 21 by welding or the like. The interior of the sealed container 2 is an enclosed space because it contains compressed refrigerant.

[0029] An oil reservoir 23t for storing refrigeration oil (hereinafter sometimes simply referred to as oil) is provided on the upper surface (inner surface) of the bottom body 23 of the sealed container 2. The oil is supplied to the compression mechanism 4 to lubricate the sliding surfaces of the compression mechanism 4 and seal gaps in the compression mechanism 4. The electric motor 3 is the drive source for the compression mechanism 4. The electric motor 3 includes a stator 31 and a rotor 32. The stator 31 is fixed to the inner wall of the sealed container 2 by shrink fitting or the like. The rotor 32 is fitted onto the upper part of the crankshaft 41 of the compression mechanism 4.

[0030] The compression mechanism 4 compresses the refrigerant gas in accordance with the rotational movement of the rotor 32 of the electric motor 3. The compression mechanism 4 then supplies the compressed refrigerant to the refrigeration cycle of the refrigeration cycle device (refrigeration air conditioner) through the discharge port 2o. The compression mechanism 4 includes a crankshaft 41, a main bearing 42, a cylinder 43, rollers 44 as movable members, vanes 45, and an auxiliary bearing 46.

[0031] The crankshaft 41 is a drive shaft that drives the rollers 44 and vanes 45 inside the cylinder 43, and includes an eccentric portion 41a. The crankshaft 41 is rotatably supported within the sealed container 2 by fitting the upper side above the eccentric portion 41a into the main bearing 42 and the lower side into the sub-bearing 46.

[0032] The main bearing 42 includes a substantially disk-shaped end plate 42a and a cylindrical portion 42b extending upward from the radial center of the end plate 42a. The main bearing 42 supports the crankshaft 41 via the cylindrical portion 42b. The outer peripheral wall surface of the end plate 42a is fixed to the inner peripheral wall surface of the cylindrical body 21 of the sealed container 2 by welding or the like.

[0033] The auxiliary bearing 46 includes an end plate 46a that closes the lower end surface of the cylinder 43, and a cylindrical portion 46b that extends downward from the radial center of the end plate 46a and supports the crankshaft 41.

[0034] The cylinder 43 has a cylindrical through-hole 43h that penetrates in the axial direction at the center in the inner diameter direction. The through-hole 43h, the main bearing 42, and the sub-bearing 46 form a compression chamber 43a. The cylinder 43 is a fixed member in the embodiment of the present disclosure, and the inner surface of the through-hole 43h of the cylinder 43 forms a cylindrical surface in the embodiment of the present disclosure.

[0035] A flow path hole 71 through which the compressed refrigerant passes is formed in the end plate 42a of the main bearing 42. A cup muffler 72 is also provided on the end plate 42a of the main bearing 42. The cup muffler 72 functions as a silencer.

[0036] Roller 44 is formed in a cylindrical shape and is disposed in compression chamber 43a. Eccentric portion 41a of crankshaft 41 is fitted into the inner diameter side of roller 44, and roller 44 is configured to be rotatable on the outer circumferential side of eccentric portion 41a. Vane 45 is disposed in a vane housing portion (not shown) so as to abut against the outer circumferential surface of roller 44. Vane 45 has a plate shape and reciprocates radially inside cylinder 43.

[0037] An accumulator 6 and a suction pipe 6a are provided on the outside of the sealed container 2 shown in Fig. 1. The accumulator 6 is a container that stores refrigerant gas. The suction pipe 6a guides the refrigerant from the refrigeration cycle to the compression mechanism 4 via the accumulator 6. The suction pipe 6a is connected to an end of the suction port 2i that communicates with the compression chamber 43a.

[0038] The overall structure of the compressor 1 has been described above, but as mentioned above, a structure having a discharge structure with small over-compression loss and small re-expansion loss is required in the development of the compressor 1. In response to this, in the compressor 1 according to the embodiment of the present disclosure, in order to improve the efficiency of the compressor 1, a discharge valve mechanism (hereinafter referred to as the discharge valve structure) having a specific structure is provided in the cylinder 43 described above, thereby reducing thermal fluid losses including over-compression loss and re-expansion loss, smoothing the flow of high-pressure gas from the compression chamber 43a to the discharge port, reducing pressure loss, and improving the rigidity of the cylinder 43.

[0039] Hereinafter, the cylinder 43 and the discharge valve structure according to the embodiment of the present disclosure will be described in more detail with reference to FIGS.

[0040] FIG. 2 illustrates a cylinder 43, which is housed in a sealed container 2 and defines a compression chamber 43a, and a discharge valve structure provided in the cylinder 43 in a compressor 1 according to an embodiment of the present disclosure. FIG. 2(A) illustrates a top view of the cylinder 43. FIG. 2(B) illustrates a side view of the cylinder 43. FIG. 2(C) illustrates a cross-sectional view of the cylinder 43 taken along the cutting plane indicated by the cutting line AA in the side view of FIG. 2(B). FIG. 2(D) illustrates an inner diameter surface 43u around a discharge port 43q of the cylinder 43, as viewed from a viewpoint O from the center in the cross-sectional view of FIG. 2(C). While FIG. 2 illustrates a state in which a discharge valve is not provided, FIG. 3 illustrates an enlarged view of the discharge valve structure when a discharge valve is provided. FIG. 3 corresponds to an enlarged view of the area indicated by the dotted rectangle in the cross-sectional view of FIG. 2(C).

[0041] Fig. 4(A) is a perspective view of the cylinder 43 without a discharge valve, and Fig. 4(B) is an enlarged perspective view showing the back side of the inner diameter surface 43u around the discharge port 43q. The perspective view shown in Fig. 4(B) is an enlarged view of the structure around the discharge port 43q when cut along the dotted line C in Fig. 4(A). Fig. 5 is a perspective view of the cylinder 43 from two directions with a discharge valve installed. Fig. 5(A) shows the discharge port 43q and valve body V as seen from above, opposite the vane 45, and Fig. 5(B) shows the discharge hole portion 43p as seen from the vane 45 side.

[0042] 2(A), 2(C), 4(A), and 5, cylinder 43 has a ring-shaped cylinder body 43b having an upper surface 43t and a lower surface 43r, a through-hole 43h formed inside cylinder body 43b and having a substantially cylindrical inner diameter surface 43u, a vane accommodating portion 43v that accommodates vane 45 shown in Fig. 1, a suction hole 43i that opens into inner diameter surface 43u and to which suction pipe 6a is connected, and a discharge hole portion 43p that opens into inner diameter surface 43u and extends substantially radially outward of cylinder 43. Cylinder 43 shown in Fig. 2 is arranged so that the axial direction of the cylindrical surface of cylinder 43 coincides with the up-down direction.

[0043] A spring hole 43w, which is a space for accommodating an elastic body such as a spring that presses the vane 45 against the roller 44, is provided behind the vane accommodating portion 43v.

[0044] The discharge hole portion 43p has a discharge port 43q that opens to an inner diameter surface 43u of the cylinder 43 and a back opening 43n that opens to an outer diameter surface 43s of the cylinder 43. The discharge port 43q extends from the discharge port 43q to the back opening 43n toward the outside of the cylinder 43, more specifically, toward the outside in the radial direction. The back opening 43n is closed as described below. The discharge hole portion 43p has an outlet 43o formed in the top surface 43t of the cylinder 43 and communicates with this outlet 43o and the discharge port 43q formed in the inner diameter surface 43u. The outlet 43o communicates with a flow path hole 71 formed in the end plate 42a of the main bearing 42, as shown in FIG. 1. The refrigerant is discharged laterally from the interior of the cylinder 43 through the discharge port 43q, directed upward, and released into the sealed container 2 from the outlet 43o in the top surface 43t through the flow path hole 71.

[0045] Elements constituting the discharge valve structure are provided within the discharge hole portion 43p. The discharge valve structure shown in FIG. 3 includes a valve element V, an elastic body D such as a spring, and a base B to which the elastic body D is fixed. As shown in FIGS. 3 and 4(B), a valve seat surface S that comes into close contact with the valve element V to close the discharge valve structure is formed on the back side of the inner diameter surface 43u around the discharge port 43q. As shown in FIGS. 3 and 5, the valve element V is provided within the discharge hole portion 43p and is configured to be movable in a direction approximately perpendicular to the valve seat surface S around the discharge port 43q. The elastic body D biases the valve element V in a direction approximately perpendicular to the valve seat surface S so that the valve element V closes the discharge port 43q. Here, the direction approximately perpendicular to the valve seat surface S coincides with the approximately radial direction of the cylindrical surface of the through-hole 43h of the cylinder 43.

[0046] A poppet-type discharge valve is configured by providing a valve element V in the discharge hole portion 43p that is movable in a direction substantially perpendicular to the valve seat surface S around the discharge port 43q. A mechanism such as an elastic body D urges the valve element V in a direction substantially perpendicular to the valve seat surface S so that the valve element V closes the discharge port 43q. Until the high-pressure compression chamber reaches discharge pressure, the high-pressure gas in the sealed container 2 and the elastic body D press the outer surface of the valve element V (the surface visible from the discharge hole portion 43p in FIG. 5B) from the outside to the inside, causing the valve element V to adhere closely to the valve seat surface S and close the discharge port 43q. On the other hand, when the high-pressure compression chamber reaches or exceeds discharge pressure, the valve element V opens by moving substantially parallel from the inside to the outside, creating a gap. In the embodiment described below, the elastic body D determines the opening degree of the discharge valve and prevents it from opening too far.

[0047] In this way, the entire valve element V is configured to be movable in a direction approximately perpendicular to the valve seat surface S, so a large flow path can be secured for the high-pressure gas pressurized in the compression chamber 43a after it is discharged from the discharge port 43q, thereby reducing over-compression loss. Also, compared to a reed valve-type discharge valve, the discharge valve structure shown in Figures 2 to 5 can reduce the area occupied by the region facing the inner diameter surface 43u of the cylinder 43 that is necessary for installation, so the area of ​​the thin-walled portion formed by providing the discharge hole 43p can be reduced, and the rigidity of the cylinder 43 that forms the compression chamber 43a can be maintained high.

[0048] 3, a rear opening 43n of the discharge hole 43p provided on the outer diameter surface 43s of the cylinder 43, facing the discharge port 43q, is filled with a sealant G for sealing against the internal space of the sealed container 2. The base B fitted into the discharge hole 43p and the sealant G filled in the gap between the discharge hole 43p and the base B together constitute a sealing member. Because the rear opening 43n of the discharge hole 43p is sealed against the internal space of the sealed container 2 in this manner, oil can be prevented from flowing into the discharge hole 43p even when the cylinder 43 is immersed in oil (oil reservoir 23t) accumulated at the bottom of the sealed container 2. This makes it possible to provide a highly efficient rotary compressor 1 that suppresses a decrease in the responsiveness of the discharge valve structure due to oil and a backflow of oil from the discharge port 43q to the compression chamber 43a.

[0049] As shown in FIGS. 2(D), 4, and 5, the shape of the discharge port 43q is elongated in the approximate axial direction of the cylindrical surface of the cylinder 43. In the embodiments shown in FIGS. 2(D), 4, and 5, the opening constituting the discharge port 43q is a single opening. By ensuring the area of ​​the discharge port 43q so that it is elongated in the axial direction of the cylindrical surface of the cylinder 43, the installation angle of the discharge port 43q with respect to the cylindrical surface of the cylinder 43 can be reduced, thereby increasing the effective rotation angle at which compression is possible. This makes it possible to provide a rotary compressor 1 with high volumetric efficiency while increasing the discharge port area and reducing over-compression loss. In the described embodiment, the opening constituting the discharge port 43q includes only a single opening. However, in other embodiments, the discharge port 43q may include multiple openings. In this case, the discharge port 43q may include multiple openings arranged in the approximate axial direction of the cylindrical surface of the cylinder 43.

[0050] A preferred embodiment including a guide structure will be described below with reference to Fig. 6. Fig. 6 is a diagram illustrating a discharge valve structure including a guide structure in a preferred embodiment. When a poppet-type discharge valve is provided in the radial direction of the cylinder 43 in the cylinder 43 whose axial direction is the up-down direction as described above, gravity acts on the movement of the valve element V. Therefore, in a preferred embodiment, as shown in Fig. 6, the discharge hole portion 43p and the valve element V are provided with guide structures (T, R) that restrict the movement of the valve element V from deviating from the approximately vertical direction. This is to address poor contact caused by gravity and gaps causing the valve element V to shift downward within the discharge hole portion 43p.

[0051] FIG. 6(A) is a diagram illustrating poor contact between the valve disc V and the valve seat surface S due to gravity. As shown in FIG. 6(A), the valve disc V is generally manufactured to be slightly smaller than the discharge hole portion 43p. As shown in FIG. 8(A), the contact between the valve disc V and the valve seat surface S may be affected by the action of gravity due to the presence of a space, the flow path P, which is the gap between the valve disc V and the discharge hole portion 43p, causing the valve disc V to be displaced downward and also in the rotational direction. Such displacement causes the overlap between the valve disc V and the valve seat surface S to shift, resulting in an area M of poor contact. Area M indicates a portion of the valve seat surface S where the valve disc V is not in close contact, and the presence of such area M indicates insufficient contact between the valve disc V and the valve seat surface S.

[0052] Furthermore, instead of providing a guide structure, the area of ​​the valve body V can be increased to improve adhesion against misalignment, in which case the valve body V is manufactured to a size that reduces the gap between it and the discharge hole 43p, but this reduces the area of ​​the flow path P. By providing a guide structure instead of increasing the area of ​​the valve body V, it is possible to maintain a large gap (P) between the valve body V and the wall surface of the discharge hole 43p, while reducing overcompression loss caused by difficulty in flowing high-pressure gas.

[0053] As described above, in the preferred embodiment shown in FIG. 6, the discharge hole 43p and the valve element V are provided with a guide structure that prevents the valve element from moving out of the substantially vertical direction. More specifically, this guide structure includes a concave shape formed on one of the side surfaces of the valve element V and the discharge hole 43p, and a convex shape formed on the other. In the embodiment shown in FIGS. 6(B) and 6(C), a convex shape T is formed on the left and right side surfaces of the valve element V, and a concave shape R is formed on the left and right side surfaces Z of the discharge hole 43p. As shown in FIG. 6(C), the side surface Z of the discharge hole 43p is slightly smaller than the rear opening 43n, and is connected to the rear opening 43n at the position of the concave shape R. The concave shape R and convex shape T of the valve element V and the discharge hole 43p fit together, positioning the valve element V in a plane horizontal to the valve seat surface S.

[0054] Furthermore, the outlet 43o opens on the upper surface 43t, which is approximately in the axial direction of the cylindrical surface of the cylinder 43, and the concave portion of the concave shape and the convex portion of the convex shape fit together in the approximately circumferential direction of the cylindrical surface of the cylinder 43 (or in a direction approximately perpendicular to the approximately axial and approximately radial directions of the cylindrical surface), that is, in the horizontal direction. As a result, the outlet 43o, which serves as a flow path after discharge, is in the approximately axial direction (vertical direction) of the cylindrical surface of the cylinder 43, and the convex and concave portions extend in the approximately circumferential direction (horizontal direction) of the cylindrical surface. Therefore, the outlet 43o does not interfere with the convex portion T and the concave portion R, and the fit between the convex portion T and the concave portion R is always maintained. This makes it possible to provide a highly efficient rotary compressor 1 with good discharge valve mobility.

[0055] Thus, in a preferred embodiment, a concave shape is provided on one of the side surfaces of the valve body V and the discharge hole portion 43p, and a convex shape is provided on the other, and positioning in the vertical and horizontal directions is performed using the concave and convex shapes, thereby suppressing poor adhesion due to misalignment and ensuring a gap, thereby enabling the application of a highly efficient rotary compressor.

[0056] In the above-described embodiment, the outlet 43o is described as being provided on the upper surface 43t of the cylinder 43, but the location of the outlet 43o is not limited as long as it is provided on a surface of the cylinder 43 different from the inner diameter surface 43u on which the discharge port 43q is formed. For example, in another embodiment, the outlet 43o may be provided on the lower surface 43r of the cylinder 43, which is opposite the upper surface 43t in the approximately axial direction. In this case, the refrigerant is discharged laterally from inside the cylinder 43 through the discharge port 43q and directed downward to be released into the sealed container 2 from the outlet 43o on the lower surface 43r.

[0057] In the above-described embodiment, a rotary compressor having a single cylinder has been described as an example. However, the cylinder configuration of the rotary compressor is not limited to a single cylinder configuration. In other embodiments, a configuration including multiple cylinders may be adopted, as described below.

[0058] The overall configuration of a rotary compressor 1 according to a second embodiment of the present disclosure will be described below with reference to Fig. 7. Fig. 7 is a vertical cross-sectional view showing the overall configuration of a rotary compressor 1 according to the second embodiment of the present disclosure. Hereinafter, components similar to those shown in Fig. 1 will basically be given the same reference numerals, and detailed description thereof will be omitted.

[0059] As shown in FIG. 7, the rotary compressor 1 of the second embodiment includes a sealed container 2, an electric motor 3, a compression mechanism 4, and a crankshaft 41, similar to the embodiment shown in FIG. 1. The sealed container 2 houses the electric motor 3, the compression mechanism 4, the crankshaft 41, a main bearing 42, and an auxiliary bearing 46, as well as a partition plate 47, similar to the configuration shown in FIG. 1. The electric motor 3 is a drive source that rotates the crankshaft 41 and eccentrically drives the eccentric portions 41a and 41b of the crankshaft 41. The crankshaft 41 eccentrically drives the upper roller 52 and the upper vane 53 of the compression mechanism 4, and also eccentrically drives the lower roller 62 and the lower vane 63 of the compression mechanism 4. The main bearing 42 rotatably supports the middle portion of the crankshaft 41. The auxiliary bearing 46 rotatably supports the lower portion of the crankshaft 41. The partition plate 47 is a plate-shaped member that separates the upper cylinder 51 and the lower cylinder 61 of the compression mechanism portion 4 .

[0060] In the second embodiment to be described, the rotary compressor 1 is configured such that, of the upper cylinder 51 and the lower cylinder 61, a spring hole 64a is formed only in the lower cylinder 61, and a spring 64 is disposed inside the spring hole 64a. However, in other embodiments, a spring and a spring hole may also be provided in the upper cylinder 51, and the spring may be disposed in the spring hole formed inside the upper cylinder 51.

[0061] The sealed container 2 has the same configuration as that shown in Fig. 1. Oil stored in an oil reservoir on the upper surface (inner surface) of the bottom body 23 of the sealed container 2 is supplied to the compression mechanism 4 to lubricate the sliding surfaces of the compression mechanism 4 and seal the gaps of the compression mechanism 4. Here, the sliding surfaces of the compression mechanism 4 mean the upper and lower surfaces of the upper roller 52 and the upper and lower inner wall surfaces of the upper cylinder 51 facing thereto, as well as the upper and lower surfaces of the lower roller 62 and the upper and lower inner wall surfaces of the lower cylinder 61 facing thereto.

[0062] An accumulator 6 and two suction pipes 6a are provided outside the sealed container 2. One of the two suction pipes 6a is connected to the accumulator 6 and an end of an upper suction port 51d that communicates with the upper compression chamber 51b of the compression mechanism 4. The other is connected to the accumulator 6 and an end of a lower suction port 61d that communicates with the lower compression chamber 61b of the compression mechanism 4.

[0063] The crankshaft 41 includes an upper eccentric portion 41a and a lower eccentric portion 41b that are eccentrically driven as the crankshaft 41 rotates. The upper eccentric portion 41a and the lower eccentric portion 41b each have a substantially disk shape and are disposed eccentrically with respect to the axis of the crankshaft 41. The eccentric direction of the upper eccentric portion 41a and the eccentric direction of the lower eccentric portion 41b are opposite directions (i.e., directions that are 180° out of phase with each other). The crankshaft 41 is rotatably supported within the sealed container 2 with its upper side fitted into the main bearing 42 and its lower side fitted into the sub-bearing 46.

[0064] The compression mechanism 4 is driven by eccentric portions 41a, 41b of the crankshaft 41. The compression mechanism 4 includes two compression sections 4a, 4b for compressing the refrigerant gas. The compression section 4a is the compression section located on the upper side. The compression section 4b is the compression section located on the lower side. Hereinafter, when distinguishing between the compression section 4a and the compression section 4b, the compression section 4a will be referred to as the upper compression section 4a, and the compression section 4b will be referred to as the lower compression section 4b.

[0065] The main bearing 42 includes a substantially disk-shaped end plate 42a and a cylindrical portion 42b extending upward from the radial center of the end plate 42a. The end plate 42a closes the upper end surface of the upper cylinder 51. The main bearing 42 supports the middle portion of the crankshaft 41 with the cylindrical portion 42b. The outer peripheral wall surface of the end plate 42a and the inner peripheral wall surface of the cylindrical body 21 of the sealed container 2 are fixed in close contact with each other by fastening them at the fixing portion 5 with welding, bolts, etc.

[0066] An upper flow passage hole 71 is formed in the end plate 42a of the main bearing 42, and a cup muffler 72 that functions as a silencer is also provided.

[0067] The sub-bearing 46 includes a substantially disk-shaped end plate 46a and a cylindrical portion 46b extending downward from the radial center of the end plate 46a. The end plate 46a closes the lower end surface of the lower cylinder 61. The sub-bearing 46 supports the lower end of the crankshaft 41 with the cylindrical portion 46b.

[0068] A lower flow passage hole 73 is formed in the end plate 46a of the auxiliary bearing 46, and a cup muffler 74 that functions as a silencer is also provided.

[0069] The upper compression section 4a has an upper cylinder 51, an upper roller 52, and an upper vane 53. The upper cylinder 51 is a stationary member housing the upper roller 52 and the upper vane 53. The upper roller 52 is a member eccentrically driven by the upper eccentric portion 41a of the crankshaft 41. The upper vane 53 is a member that divides the interior of the upper compression chamber 51b into a compression-side space and a suction-side space. On the other hand, the lower compression section 4b has a lower cylinder 61, a lower roller 62, a lower vane 63, and a spring 64. The lower cylinder 61 is a stationary member housing the lower roller 62 and the lower vane 63. The lower roller 62 is a member eccentrically driven by the lower eccentric portion 41b of the crankshaft 41. The lower vane 63 is a member that divides the interior of the lower compression chamber 61b into a compression-side space and a suction-side space. The spring 64 is a biasing member that biases the vane toward the compression chamber.

[0070] As shown in Fig. 7, the rotary compressor 1 may include a plurality of cylinders connected in parallel. Note that the rotary compressor 1 shown in Fig. 7 does not include a plurality of cylinders arranged in series such that the refrigerant discharged from the cylinder in the previous stage is sucked into the cylinder in the next stage, and the discharge valve structure of the present disclosure can be suitably applied to a rotary compressor 1 including a plurality of cylinders connected in parallel.

[0071] In the two-cylinder rotary compressor 1 shown in FIG. 7 , the cylinder and discharge valve structure described with reference to FIGS. 2 to 6 can be applied to one or both of the upper cylinder 51 and the lower cylinder 61. In this case, the outlet of the discharge valve structure may be provided on the upper surface 43t of the upper cylinder 51 and on the lower surface 43r of the lower cylinder 61. The outlet provided on the upper surface 43t of the upper cylinder 51 communicates with the upper flow passage hole 71 formed in the end plate 42a of the main bearing 42 shown in FIG. 7. The outlet provided on the lower surface 43r of the lower cylinder 61 communicates with the lower flow passage hole 73 formed in the end plate 46a of the sub-bearing 46 shown in FIG. 7. Although the two-cylinder rotary compressor has been described with reference to FIG. 7 , the number of cylinders is not particularly limited and may be any number equal to or greater than three.

[0072] Hereinafter, with reference to Fig. 8, a refrigeration cycle apparatus including a compressor 1 according to an embodiment of the present disclosure will be described using an air conditioner 100 as an example. Fig. 8 is a diagram showing an example configuration of an air conditioner 100 as a refrigeration cycle apparatus including a compressor according to an embodiment of the present disclosure. The air conditioner 100 is configured to include an outdoor unit 109 that is installed outdoors, such as in a house or building, and multiple indoor units 110 that are installed indoors. The outdoor unit 109 and each indoor unit 110 are connected by two connection pipes 115, 116 through which a refrigerant circulates as a heat medium.

[0073] The refrigerant used may be a hydrofluorocarbon such as R410A or R32. During operation, the indoor unit 110 takes in indoor air, exchanges heat between the taken-in air and the refrigerant supplied from the outdoor unit 9, and blows out cooled or heated air to cool or heat the room to a set temperature. To this end, the indoor unit 110 is equipped with an indoor heat exchanger 111 that exchanges heat between the indoor air and the refrigerant, and a blower (fan) 113 that takes in indoor air into the indoor heat exchanger 111 and blows out the air that has undergone heat exchange by the indoor heat exchanger 111. The indoor unit 110 also includes an indoor expansion valve 112 that expands the refrigerant and adjusts the flow rate of the refrigerant flowing through the indoor heat exchanger 111. The indoor unit 110 is equipped with a temperature sensor 114.

[0074] When operating in the cooling cycle, the indoor heat exchanger 111 functions as an evaporator, and refrigerant in a two-phase flow state, a mixture of liquid and gas, flows into the indoor heat exchanger 111. The liquid component of the refrigerant evaporates as it exchanges heat with air taken in by the fan 113 in the indoor heat exchanger 111, and the refrigerant is discharged from the indoor heat exchanger 111 as gas refrigerant and sent to the outdoor unit 109. The liquid component evaporates at a certain temperature (saturation temperature) that corresponds to the pressure inside the indoor heat exchanger 111, and is discharged from the indoor heat exchanger 111 at the saturation temperature or a temperature higher than the saturation temperature. The flow of refrigerant in the cooling cycle is indicated by solid arrows.

[0075] In the heating cycle, the indoor heat exchanger 111 functions as a condenser, and refrigerant gas flows into the indoor heat exchanger 111 from the outdoor unit 109. The refrigerant exchanges heat with air taken in by the fan 113 inside the indoor heat exchanger 111, becomes liquid refrigerant, and is sent to the outdoor unit 109. Note that the flow of refrigerant in the heating cycle is opposite to the flow in the cooling cycle, as indicated by the solid arrows.

[0076] The outdoor unit 109 starts up upon receiving instructions from a control device (not shown) and begins operation in an operation mode set by a remote control or the like. The operation modes include cooling mode, heating mode, fan mode, etc. The outdoor unit 109 stops operation upon receiving a command from the remote control or the like.

[0077] The outdoor unit 109 is connected to a plurality of indoor units 110a to 110c and circulates a refrigerant. The outdoor unit 109 is equipped with a compressor 1 to circulate the refrigerant. In the cooling cycle, the refrigerant gas compressed by the compressor 1 exchanges heat with air taken in by the fan 105 in the outdoor heat exchanger 103 and becomes a liquid refrigerant. The liquid refrigerant is sent to the indoor unit 110. The gas refrigerant flows from the indoor unit 110 into the outdoor unit 109 and is returned to the compressor 1.

[0078] The outdoor unit 109 is also equipped with a four-way valve 102 for reversing the direction of refrigerant flow to enable heating operation. In the heating cycle, the four-way valve 102 has a different path from that shown in FIG. 8, and the refrigerant gas compressed by the compressor 1 is sent to the indoor unit 110. Liquid refrigerant from the indoor unit 110 flows into the outdoor unit 109, evaporates by exchanging heat with air taken in by the fan 15 in the outdoor heat exchanger 13, is discharged as gas refrigerant from the indoor heat exchanger 111, and is returned to the compressor 1. The outdoor expansion valve 104 is provided to convert the high-pressure refrigerant into a low-temperature, low-pressure refrigerant in the heating cycle, and to adjust the flow rate of the refrigerant.

[0079] 8, the outdoor unit 109 may further include a subcooling mainstream pipe 106a and a subcooling heat exchanger 107 that subcools the refrigerant passing through the subcooling mainstream pipe 106a. The outdoor unit 109 is provided with a subcooling expansion valve 108, and some of the refrigerant passes through the subcooling side flow pipe 106b, is decompressed by the subcooling expansion valve 108, and enters the subcooling heat exchanger 107, where it exchanges heat with the refrigerant from the subcooling mainstream pipe 106a and evaporates, and is then returned to the compressor 1.

[0080] As described above, a compressor including a discharge valve structure according to an embodiment of the present disclosure can be suitably applied to a refrigeration cycle device such as the air conditioner 100.

[0081] In the above-described embodiment, the air conditioner 100 has been described as an example of a refrigeration cycle apparatus according to an embodiment of the present disclosure. However, the refrigeration cycle apparatus is not limited to an air conditioner and may include what is also called a refrigeration air conditioning apparatus. Here, the term refrigeration air conditioning apparatus collectively refers to devices that use a refrigerant and a refrigeration cycle, such as the air conditioner described above, a refrigerator, a refrigeration unit, etc. More specifically, examples of refrigeration air conditioning apparatus include the above-described air conditioners such as package air conditioners and multi-air conditioners for buildings, heat source equipment such as freezers and chilling units, commercial freezers such as showcases, refrigerator-freezers, unit coolers, and ice makers, transportation refrigeration equipment such as car air conditioners, and heat pump water heaters.

[0082] According to the embodiment described above, it is possible to provide a highly efficient compressor and a refrigeration cycle device equipped with the compressor, which suppresses over-compression loss and re-expansion loss while suppressing a decrease in rigidity and pressure loss in the compression chamber.

[0083] The prior arts described in Patent Documents 1 and 2 both feature a reed-type discharge valve and valve guard. Therefore, high-pressure gas flowing from the compression chamber to the discharge port follows the reed-type discharge valve and valve guard, but is immediately stopped by the vane blade housing wall that separates the low-pressure and high-pressure sides of the compression chamber, potentially resulting in pressure loss. While increasing the distance between the discharge port and the vane blade housing wall could potentially reduce pressure loss due to the vane blade housing wall, locating the discharge port at a low rotation angle reduces the effective rotation angle at which compression is possible, potentially resulting in a decrease in the amount of refrigerant circulating. Additionally, providing a reed-type discharge valve and valve guard on the outer periphery of the cylinder bore requires a large recess, which reduces the rigidity of the cylinder that forms the compression chamber and can lead to compression problems due to pressure deformation.

[0084] In contrast, in the discharge valve configuration according to one or more embodiments of the present disclosure, the valve element V is configured to move in a direction substantially perpendicular to the valve seat surface S around the discharge port 43q. The compressed refrigerant flows smoothly into the hole through the gap formed between the valve element V and the valve seat surface S, thereby reducing pressure loss. Furthermore, the discharge port 43p, in which the valve element V, which moves in a direction substantially perpendicular to the valve seat surface S around the discharge port 43q, is provided, extends from the discharge port 43q toward the outside of the cylinder 43. This prevents a decrease in the rigidity of the compression chamber 43a compared to the configuration using the reed valve described above. Furthermore, because the discharge port 43q is formed directly on the inner diameter surface 43u of the cylinder 43, it is possible to reduce overcompression loss and re-expansion loss. Consequently, it is possible to provide a highly efficient compressor 1 and a refrigeration cycle apparatus (air conditioner 100) including the compressor 1, thereby improving its APF (All-Year Energy Performance Factor).

[0085] It should be noted that the embodiments of the present invention are not limited to the above-described embodiments and may include various modifications. For example, the above-described embodiments have been described in detail for ease of understanding, and are not necessarily limited to those including all of the described features. Furthermore, some of the features of one embodiment may be replaced with features of another embodiment, or features of one embodiment may be added to features of another embodiment. Furthermore, some of the features of each embodiment may be added to, deleted from, or replaced with other features. [Explanation of symbols]

[0086] 1...compressor, 2...sealed container, 3...electric motor, 4...compression mechanism, 21...cylindrical body, 22...lid body, 23...bottom body, 31...stator, 32...rotor, 41...crankshaft, 41a, 41b...eccentric part, 42...main bearing, 42a...end plate, 42b...cylindrical part, 43, 51, 61...cylinder, 43a...compression chamber, 43b...cylinder body, 43h...through hole, 43i...suction hole, 43n...rear opening, 43o...outlet, 43p...discharge Outlet hole portion, 43q...discharge port, 43r...lower surface, 43s...outer diameter surface, 43t...upper surface, 43u...inner diameter surface, 43v...vane accommodating portion, 43w, 64a...spring hole, 44, 52, 62...roller, 45, 53, 63...vane, 46...auxiliary bearing, 46a...end plate, 46b...cylindrical portion, 47...partition plate, 6...accumulator, 6a...suction pipe, 64...spring, V...valve disc, S...valve seat surface, D...elastic body, B...base,

Claims

1. A compressor, a fixed-side member that constitutes a compression chamber, the fixed-side member having a discharge port that opens to an inner surface of the fixed-side member, an outlet that is formed on a surface of the fixed-side member that is different from the inner surface, and a hole that extends from the discharge port toward an outside of the fixed-side member and communicates with the outlet; a valve body provided in the hole of the fixed member and movable in a direction substantially perpendicular to a valve seat surface around the discharge port; a mechanism for urging the valve body in the substantially perpendicular direction relative to the valve seat surface so that the valve body closes the discharge port; A compressor comprising:

2. The compressor according to claim 1 , wherein the hole and the valve body are formed with a guide structure that restricts movement of the valve body from the substantially vertical direction.

3. 3. The compressor according to claim 2, wherein the compressor is a rotary compressor, the fixed-side member is a cylinder having a cylindrical inner surface, and the substantially vertical direction coincides with a substantially radial direction of the cylindrical surface of the cylinder.

4. 4. The compressor according to claim 3, wherein the guide structure includes a concave shape formed on one of a side surface of the valve disc and a side surface of the hole, and a convex shape formed on the other of the side surface of the valve disc and the side surface of the hole, and the concave shape and the convex shape are fitted together to position the valve disc in a plane horizontal to the valve seat surface.

5. 5. The compressor according to claim 4, wherein the outlet opens in an approximately axial direction of the cylindrical surface of the cylinder, and the concave portion of the concave shape and the convex portion of the convex shape are fitted together in an approximately circumferential direction of the cylindrical surface of the cylinder, or in a direction approximately perpendicular to the approximately axial direction of the cylindrical surface and the approximately radial direction.

6. The compressor according to claim 3 , wherein the discharge port has a shape elongated in a substantial axial direction of the cylindrical surface, or includes a plurality of openings arranged in a substantial axial direction of the cylindrical surface.

7. The compressor is a sealed container that accommodates the cylinder; a sealing member that seals a rear opening of the hole provided on the outer surface of the cylinder, facing the discharge port, from the inner space of the sealed container; The compressor of claim 3 further comprising:

8. The compressor is The compressor according to claim 3 , comprising one cylinder or a plurality of cylinders connected in parallel.

9. The compressor according to any one of claims 1 to 8. A refrigeration cycle device comprising:

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