Compressors and refrigeration cycle equipment

Abstract

To provide a compressor and refrigeration cycle system that have excellent gas-liquid separation capabilities while also being able to improve maximum capacity through supercharging. [Solution] The compressor comprises a cylindrical sealed container 13, a compression mechanism capable of compressing a refrigerant, an electric motor for driving the compression mechanism, a crankshaft for transmitting the rotational driving force of the electric motor to the compression mechanism, and an accumulator 25 located outside the sealed container and connected to the suction side of the compression mechanism. The accumulator comprises a container 61 and at least one outlet pipe 69 having an outlet opening 69o connected to the suction side of the compression mechanism. The container is positioned in the circumferential direction of the sealed container, in a direction different from the opening direction of the outlet opening of at least one outlet pipe when viewed from the rotation center of the crankshaft.

Description

Technical Field

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[0001] Embodiments according to the present invention relate to a compressor and a refrigeration cycle apparatus.

Background Art

[0002] A multi-cylinder rotary compressor is known that aims to improve volumetric efficiency and ensure the storage capacity (liquid storage capacity) of liquid refrigerant in an accumulator that is a gas-liquid separator. This compressor includes a compressor body that houses a rotating shaft having an axial center in the vertical direction, a motor unit connected to the upper end side of the rotating shaft, and an upper compression mechanism unit and a lower compression mechanism unit that are connected to the lower end side of the rotating shaft and are vertically positioned, within a sealed case. Further, the compressor has an accumulator installed beside the compressor body, an upper suction pipe that penetrates the bottom of the accumulator and has one end opening above the accumulator and the other end connected to the upper compression mechanism unit, and a lower suction pipe that has one end opening above the accumulator and the other end connected to the lower compression mechanism unit. The accumulator is arranged in the circumferential direction of the sealed case, in the same direction as the opening direction of each other end of the upper suction pipe and the lower suction pipe, when viewed from the center of rotation of the rotating shaft.

Prior Art Documents

Patent Documents

[0003]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0004] However, in conventional compressors, the liquid storage capacity in the accumulator is determined by the position of the suction pipe opening. Therefore, if one attempts to secure sufficient liquid storage capacity, it may not be possible to design the suction pipe to the desired length. In other words, if one attempts to secure sufficient liquid storage capacity, it may not be possible to freely adjust the length of the suction pipe so that the compressor's supercharging effect is obtained when the compressor is operated at a predetermined rotational speed. Consequently, there is room for improvement in compressors to achieve both the excellent gas-liquid separation capability obtained by securing sufficient liquid storage capacity and the improvement of maximum capacity through supercharging.

[0005] Therefore, the present invention aims to provide a compressor and a refrigeration cycle device that have excellent gas-liquid separation capabilities by securing liquid storage capacity, while also being able to improve maximum capacity through a supercharging effect. [Means for solving the problem]

[0006] To solve the aforementioned problems, a compressor according to an embodiment of the present invention comprises a cylindrical sealed container, a compression mechanism housed in the sealed container and capable of compressing a refrigerant, an electric motor housed in the sealed container and driving the compression mechanism, a crankshaft that transmits the rotational driving force of the electric motor to the compression mechanism, and an accumulator disposed outside the sealed container and connected to the suction side of the compression mechanism, wherein the accumulator comprises a container and at least one outlet pipe having an outlet opening connected to the suction side of the compression mechanism, and the container of the accumulator is provided in the circumferential direction of the sealed container in a direction different from the opening direction of the outlet opening of the at least one outlet pipe when viewed from the rotation center of the crankshaft.

[0007] Furthermore, in order to solve the above-mentioned problems, the refrigeration cycle apparatus according to an embodiment of the present invention comprises a compressor, a heat sink, an expansion device, a heat absorber, and a refrigerant pipe connecting the compressor, the heat sink, the expansion device, and the heat absorber for circulating the refrigerant. [Brief explanation of the drawing]

[0008] [Figure 1] A schematic diagram of a refrigeration cycle device and compressor according to an embodiment of the present invention. [Figure 2] A longitudinal cross-sectional view of a compressor according to an embodiment of the present invention. [Figure 3] A longitudinal cross-sectional view of the accumulator of a compressor according to an embodiment of the present invention. [Figure 4] A cross-sectional view of a compressor according to an embodiment of the present invention. [Figure 5] A cross-sectional view of another example of a compressor according to an embodiment of the present invention. [Figure 6] A longitudinal cross-sectional view of another example of a compressor accumulator according to an embodiment of the present invention. [Modes for carrying out the invention]

[0009] Embodiments of the compressor and refrigeration cycle device according to the present invention will be described with reference to Figures 1 to 6. Note that the same or corresponding components are denoted by the same reference numerals in multiple drawings.

[0010] Figure 1 is a schematic diagram of a refrigeration cycle device and compressor according to an embodiment of the present invention.

[0011] As shown in Figure 1, the refrigeration cycle device 1 according to this embodiment includes a rotary compressor 3, a heat radiator 5, an expansion device 7, a heat absorber 9, and a refrigerant pipe 11. The rotary compressor 3 may hereafter be simply referred to as "compressor 3". The refrigerant pipe 11 sequentially connects the compressor 3, the heat radiator 5, the expansion device 7, and the heat absorber 9 to circulate the refrigerant. The refrigerant circulating in the refrigeration cycle device 1 can be various refrigerants such as carbon dioxide, R32, or a mixed refrigerant containing R32. The heat radiator 5 may also be called a condenser, and the heat absorber 9 may also be called an evaporator.

[0012] Figure 2 is a longitudinal cross-sectional view of a compressor according to an embodiment of the present invention. Note that Figure 2 is a cross-sectional view that allows you to understand the internal structure of the sealed container 13 of the compressor 3, for example, a cross-sectional view taken along the line A1-A1 in Figure 1.

[0013] As shown in Figure 2 in addition to Figure 1, the compressor 3 comprises a vertically positioned cylindrical sealed container 13, an electric motor 15 housed in the upper half of the sealed container 13, a compression mechanism 17 housed in the lower half of the sealed container 13, a crankshaft 19 that transmits the rotational driving force of the electric motor 15 to the compression mechanism 17, a main bearing 21 and a sub-bearing 23 that rotatably cooperate to support the crankshaft 19, and an accumulator 25 located outside the sealed container 13 and connected to the suction side of the compression mechanism 17.

[0014] The sealed container 13 comprises a cylindrical body 13a extending vertically, a hemispherical or elliptical upper end plate 13b that closes the upper end of the body 13a, and a hemispherical or elliptical lower end plate 13c that closes the lower end of the body 13a.

[0015] The shell 13a supports multiple suction pipes 11a that lead the refrigerant to the compressor 3. The multiple suction pipes 11a are connected to the accumulator 25. The multiple suction pipes 11a are part of the refrigerant pipe 11.

[0016] The upper end plate 13b supports the discharge pipe 11b that discharges the refrigerant compressed by the compressor 3. The discharge pipe 11b is connected to the refrigerant pipe 11.

[0017] The electric motor 15 generates a driving force to rotate the compression mechanism 17. The electric motor 15 is, for example, a permanent magnet synchronous motor (PMSM). The electric motor 15 comprises a cylindrical stator 27 fixed to the inner wall of the sealed container 13, and a rotor 29 positioned inside the stator 27 and fixed to the crankshaft 19.

[0018] The rotor 29 comprises a rotor core having magnet housing holes and permanent magnets housed in the magnet housing holes. The rotor 29 is rotatable relative to the stator 27 and is fixed to the crankshaft 19 in a rotational manner. The rotational centerlines C of the rotor 29 and the crankshaft 19 substantially coincide with the centerline P of the stator 27.

[0019] The crankshaft 19 connects the electric motor 15 and the compression mechanism 17. The crankshaft 19 transmits the driving force generated by the electric motor 15 to the compression mechanism 17.

[0020] The intermediate portion 19a of the crankshaft 19 connects the electric motor 15 and the compression mechanism 17 and is rotatably supported by the main bearing 21. The lower end portion 19b of the crankshaft 19 is rotatably supported by the auxiliary bearing 23. The main bearing 21 and the auxiliary bearing 23 are also part of the compression mechanism 17. In other words, the crankshaft 19 penetrates the compression mechanism 17.

[0021] Further, the crankshaft 19 has a plurality of eccentric portions 31a, 31b between the intermediate portion 19a supported by the main bearing 21 and the lower end portion 19b supported by the auxiliary bearing 23. Among the plurality of eccentric portions 31, the side closer to the main bearing 21 is called the first eccentric portion 31a, and the side closer to the auxiliary bearing 23 is called the second eccentric portion 31b. Each of the eccentric portions 31a, 31b is a disk or a cylinder having a center that does not coincide with the center of the crankshaft 19. The centers of the respective eccentric portions 31a, 31b are eccentric with a phase difference of about 180 degrees around the crankshaft 19. The first eccentric portion 31a is disposed on the upper side closer to the electric motor 15, and the second eccentric portion 31b is disposed on the lower side farther from the electric motor 15.

[0022] The upper main bearing 21 is fixed to the frame 32 via the compression mechanism 17 by a plurality of fastening members (not shown), such as bolts. The frame 32 is fixed to the sealed container 13 by welding at a plurality of locations, such as spot welding. That is, the frame 32 supports the compression mechanism 17, the crankshaft 19, and the rotor 29 of the electric motor 15 in a state fixed to the sealed container 13.

[0023] The compression mechanism 17 sucks gaseous refrigerant from a plurality of suction pipes 11a when the electric motor 15 connected via the crankshaft 19 rotates and drives, compresses the sucked refrigerant, and discharges the compressed refrigerant into the sealed container 13. The lower part of the sealed container 13 is filled with refrigeration oil, and most of the compression mechanism 17 is immersed in this refrigeration oil.

[0024] The compression mechanism 17 comprises multiple cylinders, for example, two cylinders 33 and 35. In other words, the compressor 3 is a multi-cylinder rotary compressor. The compression mechanism 17 comprises a first cylinder 33 provided in a sealed container 13, a second cylinder 35 provided in the sealed container 13, and a partition plate 37 provided between the first cylinder 33 and the second cylinder 35.

[0025] The compressor 3 may be a multi-cylinder rotary compressor with three or more cylinders, or a single-cylinder rotary compressor. The compressor 3 and the accumulator 25 are connected via suction pipes 11a, the same number as the number of cylinders.

[0026] The first cylinder 33 has a cylindrical first cylinder chamber 39 that penetrates the first cylinder 33 in the vertical direction.

[0027] The second cylinder 35 has a cylindrical second cylinder chamber 41 that penetrates the second cylinder 35 in the vertical direction.

[0028] The compression mechanism 17 also includes an annular first roller 43 positioned in the first cylinder chamber 39, an annular second roller 45 positioned in the second cylinder chamber 41, and vanes 46 (see Figure 4) positioned in the radial direction of the first cylinder chamber 39 in the first cylinder 33 and in the radial direction of the second cylinder chamber 41 in the second cylinder 35. Each vane 46 reciprocates, moving closer to and further away from the rotational centerline C of the crankshaft 19 while remaining in contact with the outer circumferential surface of the corresponding rollers 43 and 45, thereby dividing the corresponding cylinder chambers 39 and 41 into an intake chamber and a compression chamber. The first roller 43 and the second roller 45 are rolling pistons, respectively.

[0029] The first cylinder 33 and the second cylinder 35 compress the refrigerant by changing the volume of the compression chamber, which is partitioned by corresponding rollers 43 and 45 and corresponding vanes 46, by the rotation of the rollers 43 and 45.

[0030] The first cylinder 33 and the second cylinder 35 are arranged to stack on top of each other in the axial direction of the crankshaft 19. The upper first cylinder 33 is located closer to the electric motor 15. The lower second cylinder 35 is located further away from the electric motor 15.

[0031] Each cylinder 33, 35 has an inner circumferential surface that defines the corresponding cylinder chambers 39, 41. Each cylinder 33, 35 has an annular, plate-like shape with the corresponding cylinder chambers 39, 41 inside. Each cylinder 33, 35 has an end face closer to the electric motor 15 and an end face further away from the electric motor 15.

[0032] The centers of the first cylinder chamber 39 and the second cylinder chamber 41 substantially coincide with the rotational centerline C of the crankshaft 19. These cylinder chambers 39 and 41 have substantially the same diameter and height dimensions, i.e., the longitudinal dimensions of the crankshaft 19. The first cylinder chamber 39 is the inner space of the first cylinder 33 and is closed by the main bearing 21 and the partition plate 37. The first cylinder chamber 39 houses the first eccentric portion 31a of the crankshaft 19. The second cylinder chamber 41 is the inner space of the second cylinder 35 and is closed by the partition plate 37 and the sub-bearing 23. The second cylinder chamber 41 houses the second eccentric portion 31b of the crankshaft 19.

[0033] Furthermore, the compression mechanism 17 includes a first suction port 47 provided in the first cylinder 33 for drawing refrigerant into the first cylinder chamber 39, and a second suction port 48 provided in the second cylinder 35 for drawing refrigerant into the first cylinder chamber 39. Each of the suction ports 47 and 48 is connected to the suction pipe 11a.

[0034] The compression mechanism 17 includes a first discharge valve mechanism having a discharge port provided on the main bearing 21 for discharging the refrigerant compressed in the first cylinder chamber 39 to the outside of the first cylinder chamber 39, and a discharge valve provided on the main bearing 21 for opening and closing the discharge port, and a first discharge muffler 49 provided on the main bearing 21 and covering the first discharge valve mechanism.

[0035] The discharge port of the first discharge valve mechanism is connected to the first cylinder chamber 39.

[0036] The discharge valve of the first discharge valve mechanism opens its discharge port when the differential pressure inside and outside the first cylinder chamber 39 reaches a predetermined differential pressure value due to the compression action of the compression mechanism 17, thereby discharging the compressed refrigerant into the first discharge muffler 49.

[0037] The first discharge muffler 49 covers the first discharge valve mechanism. The first discharge muffler 49 has a discharge hole that penetrates it. The compressed refrigerant discharged into the first discharge muffler 49 is discharged into the sealed container 13 through the discharge hole.

[0038] The first discharge muffler 49 and the first cylinder 33 are fixed to the main bearing 21 by a plurality of fastening members, such as bolts, which are not shown in the figure. The bolts pass through the first discharge muffler 49 and the main bearing 21 to reach the first cylinder 33.

[0039] Furthermore, the compression mechanism 17 includes a second discharge valve mechanism having a discharge port provided on the sub-bearing 23 for discharging the refrigerant compressed in the second cylinder chamber 41, and a discharge valve provided on the sub-bearing 23 for opening and closing the discharge port, and a second discharge muffler 50 provided on the sub-bearing 23 and covering the second discharge valve mechanism.

[0040] The discharge port of the second discharge valve mechanism is connected to the second cylinder chamber 41.

[0041] The discharge valve of the second discharge valve mechanism opens its discharge port when the differential pressure inside and outside the second cylinder chamber 41 reaches a predetermined differential pressure value due to the compression action of the compression mechanism 17, and discharges the compressed refrigerant into the second discharge muffler 50.

[0042] The second discharge muffler 50 covers the second discharge valve mechanism. The compressed refrigerant discharged into the second discharge muffler 50 is guided to the first discharge muffler 49 through the sub-bearing 23, the second cylinder 35, the partition plate 37, and a hole that penetrates the first cylinder 33, and is discharged into the sealed container 13.

[0043] The second discharge muffler 50, the sub-bearing 23, the second cylinder 35, and the partition plate 37 are fixed to the first cylinder 33 by a plurality of fastening members, such as bolts, which are not shown in the figure. The bolts penetrate the second discharge muffler 50, the sub-bearing 23, the second cylinder 35, and the partition plate 37 to reach the first cylinder 33.

[0044] The first roller 43 is fitted onto the circumferential surface of the first eccentric portion 31a and housed within the first cylinder chamber 39. As the crankshaft 19 rotates, the first roller 43 performs eccentric motion, with a portion of its outer surface making line contact with the inner surface of the first cylinder chamber 39.

[0045] The second roller 45 is fitted onto the circumferential surface of the second eccentric portion 31b and housed within the second cylinder chamber 41. As the crankshaft 19 rotates, the second roller 45 performs eccentric motion, with a portion of its outer surface making line contact with the inner surface of the second cylinder chamber 41.

[0046] Note that the contact between the first roller 43 and the first cylinder 33, and the contact between the second roller 45 and the second cylinder 35 are not direct contacts but indirect contacts mediated by an oil film (not shown). However, for the sake of explanation, these contacts mediated by the oil film will simply be referred to as "contact." The same applies to the contacts between the first roller 43 and the first eccentric part 31a, between the second roller 45 and the second eccentric part 31b, between the first roller 43 and the main bearing 21, between the second roller 45 and the sub-bearing 23, between the first roller 43 and the partition plate 37, and between the second roller 45 and the partition plate 37.

[0047] The accumulator 25 is a gas-liquid separator that separates gaseous refrigerant from liquid refrigerant and sends the gaseous refrigerant to the compressor 3. The accumulator 25 is fixed to the sealed container 13 of the compressor 3 via a holder 51 provided on the shell 13a of the sealed container 13. In other words, the accumulator 25 is located on the outside of the sealed container 13. The accumulator 25 is fixed to the sealed container 13 of the compressor 3 by, for example, welding to the holder 51, or by a clamp band (not shown) provided on the holder 51 so as to cover the outer circumference of the accumulator 25.

[0048] Figure 3 is a longitudinal cross-sectional view of the accumulator of a compressor according to an embodiment of the present invention. Note that Figure 3 is, for example, a cross-sectional view taken along the line A2-A2 in Figure 1. The same applies to Figure 6, which will be described later.

[0049] As shown in Figure 3 in addition to Figures 1 and 2, the accumulator 25 according to this embodiment includes a cylindrical container 61 supported in an upright position, a partition plate 63 provided inside the container 61 to divide the internal space of the container 61 into a refrigerant introduction chamber IR and a refrigerant discharge chamber OR, an inlet pipe 65 fixed to the container 61 and having an inlet passage IP connected to the refrigerant introduction chamber IR, a connecting pipe 67 having a connecting passage CP that penetrates the partition plate 63 and connects the refrigerant introduction chamber IR and the refrigerant discharge chamber OR, and a plurality of outlet pipes 69 fixed to the container 61 and having outlet passages OP connected to the refrigerant discharge chamber OR.

[0050] Furthermore, the accumulator 25 includes a strainer 71 positioned between the inlet pipe 65 and the connecting pipe 67 to filter foreign matter from the refrigerant introduced into the accumulator 25, a separation plate 73 positioned between the strainer 71 and the connecting pipe 67 to separate the refrigerant that has passed through the strainer 71 into gaseous refrigerant and liquid refrigerant, and a support plate 75 positioned between the separation plate 73 and the partition plate 63 to support the connecting pipe 67 together with the partition plate 63.

[0051] The container 61 is fixed to the sealed container 13 of the compressor 3 via a holder 51. The container 61 is cylindrical. The container 61 comprises a cylindrical body 61a extending in the vertical direction, a hemispherical or elliptical upper end plate 61b that closes the upper end, which is one end of the body 61a, and a hemispherical or elliptical lower end plate 61c that closes the lower end, which is the other end of the body 61a.

[0052] The body 61a supports the strainer 71, the separation plate 73, the support plate 75, and the partition plate 63 in the order of the refrigerant flow.

[0053] The upper end plate 61b supports the inlet pipe 65 that allows the refrigerant, compressed by the compressor 3 and circulated through the refrigeration cycle device 1, to flow into the accumulator 25. The inlet pipe 65 is connected to the refrigerant pipe 11.

[0054] The inlet pipe 65 is fixed to the upper end plate 61b and connected to the refrigerant pipe 11. The inlet pipe 65 is a straight pipe extending along the centerline of the shell 61a. The centerline of the shell 61a coincides with the centerline Q of the container 61.

[0055] The refrigerant flowing from the inlet pipe 65 into the accumulator 25 first reaches the strainer 71. The strainer 71 has the required mesh size to prevent foreign matter from flowing into the compression mechanism 17 of the compressor 3.

[0056] The separation plate 73 prevents the refrigerant that has passed through the strainer 71 from flowing directly into the connecting pipe 67. The separation plate 73 is a plate with an upward-convex shape that acts like an umbrella on the connecting pipe 67. The separation plate 73 has multiple openings 73a through which the refrigerant can pass. The separation plate 73 obstructs the view directly below the inlet pipe 65 and obstructs the view directly above the connecting pipe 67. The multiple openings 73a of the separation plate 73 are positioned radially outward from the container 61 than the connecting pipe 67 when viewed from the inlet pipe 65. The refrigerant that reaches the separation plate 73 flows down to the lower side of the refrigerant introduction chamber IR of the container 61 through the multiple openings 73a of the separation plate 73.

[0057] Each opening 73a opens toward the outer periphery of the separation plate 73. In other words, each opening 73a opens toward the inner surface of the container 61. Each opening 73a is formed from a plate-like material, for example, by cutting and bending.

[0058] The support plate 75 and the partition plate 63 are fixed inside the container 61 and work together to support the connecting pipe 67.

[0059] The support plate 75 has holes to support the connecting pipe 67 and appropriate openings that do not obstruct the flow of liquid refrigerant and gaseous refrigerant, so that the refrigerant introduction chamber IR becomes a continuous space. Preferably, the support plate 75 has appropriate support strength and support rigidity so that the connecting pipe 67 extending from the partition plate 63 toward the separation plate 73 does not tip over.

[0060] The partition plate 63 has no openings other than the holes that support the connecting pipe 67, so that the internal space of the container 61 is divided into a refrigerant introduction chamber IR and a refrigerant discharge chamber OR. The partition plate 63 is liquid-tight and airtightly joined to the inner surface of the container 61, preventing the refrigerant from flowing out from the refrigerant introduction chamber IR to the refrigerant discharge chamber OR through a path other than the connecting pipe 67. The partition plate 63 only needs to have a plane 63a perpendicular to the center line Q of the container 61, and in the upright position of the accumulator 25, it defines a plane 63a that extends horizontally.

[0061] In this embodiment, there is one connecting pipe 67. However, the number of connecting pipes 67 is not limited to one, and there may be two or more. The number of connecting pipes 67 is determined by considering the pressure loss, pipe diameter, and interference of the internal structure of the connecting passage CP that connects the refrigerant inlet chamber IR and the refrigerant discharge chamber OR.

[0062] The connecting pipe 67 has an inlet opening 67i located in the refrigerant introduction chamber IR and an outlet opening 67o located in the refrigerant discharge chamber OR. The inlet opening 67i corresponds to the upstream end of the connecting flow path CP, and the outlet opening 67o corresponds to the downstream end of the connecting flow path CP.

[0063] The connecting pipe 67 is located inside the container 61 and is fixed to the support plate 75 and the partition plate 63, connecting the refrigerant inlet chamber IR and the refrigerant outlet chamber OR. The connecting pipe 67 is a straight pipe that extends parallel to the centerline of the shell 61a.

[0064] The length of the connecting pipe 67 depends on the amount of refrigerant charged into the refrigeration cycle device 1, but it is generally preferable to be at least half the total length of the accumulator 25.

[0065] Furthermore, the connecting pipe 67 has at least one refrigerant oil return hole 67h located in the refrigerant introduction chamber IR.

[0066] The inlet opening 67i of the connecting pipe 67 is closer to the upper end plate 61b than to the partition plate 63.

[0067] The outlet opening 67o of the connecting pipe 67 faces downwards towards the lower end plate 61c.

[0068] Each outlet pipe 69 is the suction pipe 11a of the compressor 3 and is connected to the cylinder chambers 39 and 41 of the corresponding cylinders 33 and 35 of the compression mechanism 17. The number of outlet pipes 69 is the same as the number of cylinders in the compressor 3. In the case of a multi-cylinder compressor 3 as shown in Figure 1, the accumulator 25 is connected to the compressor 3 by the same number of outlet pipes 69 as the number of cylinders. In the case of a single-cylinder compressor 3, the accumulator 25 only needs to be connected to the compressor 3 by one outlet pipe 69. In other words, the accumulator 25 only needs to have at least one outlet pipe 69, and it is preferable that it has the same number of outlet pipes 69 as the number of cylinders in the compressor 3.

[0069] Each outlet pipe 69 discharges gaseous refrigerant separated from the refrigerant that has flowed into the accumulator 25 from the accumulator 25. Each outlet pipe 69 has an inlet opening 69i located in the refrigerant discharge chamber OR and an outlet opening 69o connected to the corresponding cylinder chambers 39 and 41.

[0070] The inlet opening 69i corresponds to the upstream end of the outlet channel OP, and the outlet opening 69o corresponds to the downstream end of the outlet channel OP.

[0071] It is preferable that each inlet opening 69i is located radially outward of the body 61a than the outlet opening 67o of the connecting pipe 67 when viewed from the inlet opening 67i side, which is the upper end of the connecting pipe 67.

[0072] The container 61 is an assembly of two members that are divided in the middle of the body 61a and airtightly joined together. Preferably, the inlet pipe 65, strainer 71, and separation plate 73 are incorporated into the upper member before the assembly of the container 61, and the outlet pipe 69, partition plate 63, support plate 75, and connecting pipe 67 are incorporated into the lower member before the assembly of the container 61. The support plate 75 may be positioned on the dividing surface of the two members or may be fixed to the inside of the lower member.

[0073] In the accumulator 25 configured as described above, the refrigerant flowing down from the inlet pipe 65 into the refrigerant introduction chamber IR inside the container 61 is separated into gaseous refrigerant and liquid refrigerant upon contact with the separation plate 73. The separated liquid refrigerant flows further down through the refrigerant introduction chamber IR from the opening 73a of the separation plate 73 and accumulates at the bottom of the refrigerant introduction chamber IR, i.e., from the partition plate 63 side. Meanwhile, the separated gaseous refrigerant flows from the opening 73a of the separation plate 73 through the connecting pipe 67 into the refrigerant discharge chamber OR. The gaseous refrigerant that flows into the refrigerant discharge chamber OR is sucked into the outlet pipe 69 and sent to the compressor 3. The accumulator 25 has, inside the container 61, an upper space which is the refrigerant introduction chamber IR for storing liquid refrigerant, and a lower space which is the refrigerant discharge chamber OR where the inlet opening 69i of at least one outlet pipe 69 is located. Therefore, while the compressor 3 ensures storage capacity through the refrigerant introduction chamber IR, the storage capacity in the accumulator is not determined by the position of the suction pipe opening, unlike conventional compressors.

[0074] Figure 4 is a cross-sectional view of a compressor according to an embodiment of the present invention. Note that Figure 4 is a cross-sectional view that shows the arrangement of the sealed container 13, the compression mechanism 17, the holder 51, the container 61 of the accumulator 25, and the outlet pipe 69, for example, a cross-sectional view along the line A3-A3 in Figure 1.

[0075] Incidentally, in conventional compressors, the liquid storage capacity in the accumulator is determined by the position of the suction pipe opening. Therefore, if one tries to secure sufficient liquid storage capacity, there is a risk that the length of the suction pipe cannot be freely designed. In other words, there is a risk that the length of the suction pipe cannot be adjusted so that the supercharging effect of the compressor is obtained when the compressor is operated at a predetermined rotational speed. Consequently, there is room for improvement in compressors in achieving both excellent gas-liquid separation capability through securing liquid storage capacity and increased maximum capacity through the supercharging effect.

[0076] Therefore, as shown in Figure 4, the container 61 of the accumulator 25 is positioned in a direction different from the opening direction of the outlet opening 69o of at least one outlet pipe 69 when viewed from the rotation center of the crankshaft 19, in the circumferential direction of the sealed container 13. This allows the outlet pipe 69 to have, for example, an inverted U-shape (gate-type shape) that opens toward the holder 51 when viewed from the bottom. As a result, compared to the case where the opening directions of the container 61 of the accumulator 25 and the outlet opening 69o of the outlet pipe 69 are the same when viewed from the rotation center of the crankshaft 19, the compressor 3 can easily increase the length of the outlet pipe 69. Thus, the compressor 3 can easily improve its maximum capacity by optimizing the length of the outlet pipe 69 to match the peak of the supercharging effect to the maximum rotation speed of the compressor 3, while maintaining excellent gas-liquid separation capability by securing the liquid storage capacity of the accumulator 25 in the refrigerant introduction chamber IR.

[0077] Furthermore, it is preferable that the central axis of the gate-shaped outlet pipe 69 lies on a plane perpendicular to the rotational centerline C of the crankshaft 19. This allows the outlet pipe 69 to extend without compressing the space above or below it. In other words, the installation volume when installing the compressor 3 will not increase excessively due to the presence of the outlet pipe 69.

[0078] Generally, to achieve a supercharging effect, the outlet pipe (inlet pipe) must be designed according to the desired operating conditions of the compressor. In conventional compressors, the relative positional relationship between the sealed container and the accumulator needs to be significantly revised depending on the length of the outlet pipe.

[0079] Therefore, it is preferable that at least one outlet pipe 69 includes two bent pipes 81 and 83.

[0080] Specifically, the two bent pipes 81 and 83 are, for example, L-shaped. By joining the two L-shaped bent pipes 81 and 83 together, a gate-shaped outlet pipe 69 can be constructed. With two such bent pipes 81 and 83, at the design stage, the length of at least one of the two bent pipes 81 and 83 can be adjusted so that the outlet pipe 69 is of an appropriate length to produce a supercharging effect, simply by moving the container 61 of the accumulator 25 radially or circumferentially within the sealed container 13. In other words, the two bent pipes 81 and 83 make it easy to achieve a supercharging effect in various compressors with different target operating conditions.

[0081] Preferably, the compressor 3 includes a first connecting part 85 for joining two bent pipes 81 and 83, and a second connecting part 87 which is fixed to the sealed container 13 and joins the second bent pipe 83 to the sealed container 13. This ensures that the first bent pipe 81 and the second bent pipe 83 are reliably joined by brazing via the first connecting part 85. Furthermore, the second bent pipe 83 and the sealed container 13 are reliably joined by brazing via the second connecting part 87. In addition, the first connecting part 85 and the second connecting part 87 can absorb the length tolerance of the two bent pipes 81 and 83 when fixing the container 61 of the accumulator 25 to the sealed container 13 via the holder 51, allowing the container 61 to be fixed to the sealed container 13 with high precision.

[0082] Preferably, each of the two bent tubes 81 and 83 has a portion that extends in the X direction, which is parallel to the first imaginary line VL1, when viewed from the bottom, with the first imaginary line VL1 being defined as the straight line passing through the rotation center of the crankshaft 19 and the center of the container 61 of the accumulator 25.

[0083] In the bottom view, the rotation center of the crankshaft 19 refers to the point where the rotation center line C intersects with the plane perpendicular to the rotation center line C. Similarly, in the bottom view, the center of the container 61 of the accumulator 25 refers to the point where the center line Q of the container 61 intersects with the plane perpendicular to the center line Q. At this time, the first virtual line VL1 lies on the plane perpendicular to both the rotation center line C and the center line Q.

[0084] Here, for the sake of convenience in the following explanation, the bent pipe 81 may be referred to as the "first bent pipe 81" and the bent pipe 83 as the "second bent pipe 83". The first bent pipe 81 has a straight upstream section 81a including the inlet opening 69i of the outlet pipe 69, a bent section 81b that is continuous with the upstream section 81a and is bent, and a straight downstream section 81c that is continuous with the bent section 81b. The downstream section 81c of the first bent pipe 81 is the part that extends in the X direction parallel to the first imaginary line VL1. The second bent pipe 83 has a straight downstream section 83c including the inlet opening 69i of the outlet pipe 69, a bent section 83b that is continuous with the downstream section 83c and is bent, and a straight upstream section 83a that is continuous with the bent section 83b. The upstream portion 83a of the second bent pipe 83 is the part that extends in the X direction parallel to the first virtual line VL1. Therefore, during the design phase, by simply moving the container 61 of the accumulator 25 along the first virtual line VL1 located radially to the sealed container 13, the length of at least one of the downstream portion 81c and the upstream portion 83a is adjusted so that the outlet pipe 69 is of an appropriate length to produce a supercharging effect, thereby making it easy to adjust the length of the outlet pipe 69.

[0085] Furthermore, it is preferable that each of the two bent tubes 81 and 83, when viewed from below, has a portion extending in the X direction, which is parallel to the first imaginary line VL1, in addition to a portion extending in the Y direction, which is perpendicular to the first imaginary line VL1, when the straight line passing through the rotation center of the crankshaft 19 and the center of the container 61 of the accumulator 25 is defined as the first imaginary line VL1.

[0086] Specifically, the upstream portion 81a of the first bent pipe 81 and the downstream portion 83c of the second bent pipe 83 are portions that extend in the Y direction, which is perpendicular to the first virtual line VL1. Therefore, at the design stage, the length of the outlet pipe 69 can be easily adjusted by simply moving the container 61 of the accumulator 25 in the circumferential direction of the sealed container 13, thereby adjusting the length of at least one of the downstream portion 81c and the upstream portion 83a and at least one of the upstream portion 81a and the downstream portion 83c so that the outlet pipe 69 is of an appropriate length to produce a supercharging effect.

[0087] Figure 5 is a cross-sectional view of another example of a compressor according to an embodiment of the present invention. In Figure 5, the relative positional relationship between the sealed container 13 of the compressor 3 and the container 61 of the accumulator 25 differs from the relative positional relationship between the sealed container 13 and the container 61 of the accumulator 25 in Figure 4.

[0088] Furthermore, as shown in Figure 5, when viewed from below, if the first imaginary line VL1 is defined as the line passing through the rotation center of the crankshaft 19 and the center of the container 61 of the accumulator 25, and the second imaginary line VL2 is defined as the line passing through the rotation center of the crankshaft 19 and the center of the outlet opening 69o of at least one outlet pipe 69, then the angle θ between the second imaginary line VL2 and the first imaginary line VL1 may be less than 90°. Note that the center of the outlet opening 69o of the outlet pipe 69 is the intersection point of the central axis of the outlet pipe 69 and the plane containing the outlet opening 69o.

[0089] Specifically, if the length of the outlet pipe 69 is to be shortened so that it is of an appropriate length to produce a supercharging effect, the length of the outlet pipe 69 can be shortened at the design stage by making the angle θ between the second virtual line VL2 and the first virtual line VL1 less than 90°, thereby shortening the length of at least one of the two bent pipes 81 and 83. In the example in Figure 5, the length of the outlet pipe 69 is shortened by shortening the length of the first bent pipe 81 compared to the example in Figure 4. Also, by making the angle θ between the second virtual line VL2 and the first virtual line VL1 less than 90°, it is possible to reduce the installation volume required for the compressor 3 compared to the case where the angle θ is 90°.

[0090] Furthermore, as shown in Figure 3, it is preferable that at least one outlet pipe 69 is connected from the side of the container 61 of the accumulator 25 into the container 61. In other words, it is preferable that at least one outlet pipe 69 is connected from the shell 61a of the container 61 of the accumulator 25 to the refrigerant discharge chamber OR.

[0091] Generally, in a compressor equipped with an accumulator, the outlet pipe (suction pipe) connecting the accumulator container and the compressor's sealed container has a straight upstream section that extends downward and is fixed to the lower end plate of the accumulator container on the outside of the container, a bent section that is continuous with the upstream section, and a straight downstream section that is continuous with the bent section and connected to the suction side of the compression mechanism. Here, if the length of the upstream section is increased in order to increase the length of the outlet pipe, the accumulator container will be moved upward. When the container is moved upward, the space above the container is compressed, and the installation volume required when installing the compressor increases upward. In other words, the ease of installing the compressor decreases.

[0092] On the other hand, in this embodiment, the container 61 of the accumulator 25 does not need to be moved upward because the outlet pipe 69 is connected to the refrigerant discharge chamber OR from the side of the container 61. In other words, it prevents an excessive decrease in the ease of installation of the compressor 3. Also, if the number of outlet pipes 69, which are at least one outlet pipe connected to the refrigerant discharge chamber OR from the side of the container 61, is small, the volume of the refrigerant introduction chamber IR can be increased to improve the gas-liquid separation capacity. Furthermore, the inlet openings 69i of each of the multiple outlet pipes 69 can be arranged at substantially the same position in the radial direction of the shell 61a, spaced apart in the direction along the centerline of the shell 61a. In other words, compared to the outlet pipes of conventional compressors that have outlet pipes with complex structures within the accumulator, the length of each of the multiple outlet pipes 69 can be easily adjusted to the same length. Therefore, the resonance frequencies of each of the multiple outlet pipes 69 can be matched to maximize the supercharging effect.

[0093] Figure 6 is a longitudinal cross-sectional view of another example of a compressor accumulator according to an embodiment of the present invention.

[0094] As shown in Figure 6, the partition plate 63 of the accumulator 25 may have a recess 64 that is recessed downward from the flat surface 63a. Furthermore, the recess 64 may have a bottom 64a located below the inlet opening 69i of the uppermost outlet pipe 69 among at least one outlet pipe 69 inside the container 61 of the accumulator 25. Doing so increases the volume of the refrigerant introduction chamber IR of the container 61 and further improves the gas-liquid separation capacity of the accumulator 25.

[0095] The shape of the recess 64 is, for example, cylindrical. Also, if the partition plate 63 of the accumulator 25 has a bottom 64a, the connecting pipe 67 penetrates the bottom 64a. Furthermore, the outer surface of the recess 64 faces the inner surface of the container 61 at a certain distance. Moreover, the outer surface of the recess 64 is located radially inward of the body 61a than the inlet opening 69i of at least one outlet pipe 69 when viewed from the inlet opening 67i side, which is the upper end of the connecting pipe 67. Therefore, the recess 64 allows the gaseous refrigerant that has flowed into the refrigerant discharge chamber OR through the connecting pipe 67 to be sent to the compressor 3 without obstructing its suction into the outlet pipe 69.

[0096] As described above, the compressor 3 and refrigeration cycle device 1 according to this embodiment include an accumulator 25 having a container 61 that is positioned in a direction different from the opening direction of the outlet opening 69o of at least one outlet pipe 69 when viewed from the rotation center of the crankshaft 19, in the circumferential direction of the sealed container 13. Due to this relative positional relationship between the sealed container 13 and the container 61 of the accumulator 25, i.e., the accumulator 25, the length of the outlet flow path OP can be easily secured compared to the case where the opening directions of the container 61 of the accumulator 25 and the outlet opening 69o of the outlet pipe 69 are in the same direction when viewed from the rotation center of the crankshaft 19, in the circumferential direction of the sealed container 13. In other words, the outlet pipe 69 can have a high degree of design freedom regarding the length adjustment of the outlet pipe 69. Therefore, the compressor 3 and refrigeration cycle device 1 can easily adjust the length of the outlet pipe 69 due to the high degree of design freedom of the outlet pipe 69. Therefore, the compressor 3 and refrigeration cycle device 1 have excellent gas-liquid separation capabilities by ensuring the liquid storage capacity of the accumulator 25 in the refrigerant introduction chamber IR, while also being able to easily improve their maximum capacity by optimizing the length of the outlet pipe 69 to match the peak of the supercharging effect to the maximum rotational speed of the compressor 3.

[0097] The compressor 3 and refrigeration cycle device 1 according to this embodiment are equipped with at least one outlet pipe 69 including two bent pipes 81 and 83. The length of the outlet pipe 69 can be easily adjusted by adjusting the length of at least one of the two bent pipes 81 and 83 during the design phase, so that the outlet pipe 69 is of an appropriate length to produce a supercharging effect simply by moving the container 61 of the accumulator 25 radially or circumferentially within the sealed container 13. Therefore, the compressor 3 and refrigeration cycle device 1 can easily obtain a supercharging effect in various compressors with different target operating conditions.

[0098] Furthermore, with two such bent pipes 81 and 83, the length of the outlet pipe 69 can be easily adjusted by adjusting the length of at least one of the two bent pipes 81 and 83 while fixing the relative positions of the sealed container 13 and the container 61 during the design phase. This allows for a common installation location for the compressor 3, which may vary depending on the relative positions of the sealed container 13 and the container 61. Therefore, the compressor 3 and the refrigeration cycle device 1 can improve the manufacturability of the compressor 3.

[0099] The compressor 3 and refrigeration cycle device 1 according to this embodiment include two bent pipes 81 and 83, each having a portion that extends in the X direction, which is parallel to the first imaginary line VL1, when viewed from below, the straight line passing through the rotation center of the crankshaft 19 and the center of the container 61 of the accumulator 25 is defined as the first imaginary line VL1. The downstream portion 81c of the first bent pipe 81 and the upstream portion 83a of the second bent pipe 83, which extend in the X direction, allow for easy adjustment of the length of the outlet pipe 69 so that it becomes the appropriate length to produce a supercharging effect simply by moving the container 61 of the accumulator 25 along the first imaginary line VL1 located radially in the sealed container 13 during the design phase. Therefore, the compressor 3 and refrigeration cycle device 1 can more easily obtain a supercharging effect in various compressors with different target operating conditions.

[0100] The compressor 3 and refrigeration cycle device 1 according to this embodiment, when viewed from below, have two bent pipes 81 and 83, each having a portion extending in the X direction, which is parallel to the first imaginary line VL1, and a portion extending in the Y direction, which is perpendicular to the first imaginary line VL1, when the straight line passing through the rotation center of the crankshaft 19 and the center of the container 61 of the accumulator 25 is defined as the first imaginary line VL1. The downstream portion 81c of the first bent pipe 81 and the upstream portion 83a of the second bent pipe 83, which are the portions extending in the X direction, and the upstream portion 81a of the first bent pipe 81 and the downstream portion 83c of the second bent pipe 83, which are the portions extending in the Y direction, allow for easy adjustment of the length of the outlet pipe 69 so that the outlet pipe 69 becomes the appropriate length to produce a supercharging effect simply by moving the container 61 of the accumulator 25 in the circumferential direction of the sealed container 13. Therefore, the compressor 3 and the refrigeration cycle device 1 can more easily achieve the supercharging effect in various compressors with different target operating conditions.

[0101] In this embodiment, the compressor 3 and refrigeration cycle device 1 are equipped with an accumulator 25 positioned such that, when viewed from below, a first imaginary line VL1 is defined as the straight line passing through the rotation center of the crankshaft 19 and the center of the container 61 of the accumulator 25, and a second imaginary line VL2 is defined as the straight line passing through the rotation center of the crankshaft 19 and the center of the outlet opening 69o of at least one outlet pipe 69, the angle θ between the first imaginary line VL1 and the second imaginary line VL2 is less than 90°. Therefore, when it is desired to shorten the length of the outlet pipe 69 so that it becomes an appropriate length for generating a supercharging effect, the compressor 3 and refrigeration cycle device 1 can easily adjust the length of the outlet pipe 69 by making the angle θ less than 90°, thereby shortening the length of at least one of the two bent pipes 81 and 83 during the design phase. Furthermore, by making the angle θ of the compressor 3 and the refrigeration cycle device 1 smaller than 90°, the installation volume required for the compressor 3 can be reduced compared to the case where the angle θ is 90°.

[0102] The compressor 3 and refrigeration cycle device 1 according to this embodiment are provided with at least one outlet pipe 69 connected to the side of the container 61 of the accumulator 25, that is, from the body 61a of the container 61 to the inside of the container 61. Therefore, the compressor 3 and refrigeration cycle device 1 can adjust the length of at least one outlet pipe 69 without moving the container 61 upward, compared to the case where at least one outlet pipe 69 is connected to the bottom surface of the container 61 of the accumulator 25, that is, from the lower end plate 61c to the inside of the container 61.

[0103] Furthermore, if the number of outlet pipes 69 is small, it is not necessary to secure the area on the side of the container 61 that separates the refrigerant discharge chamber OR. In other words, the volume of the refrigerant discharge chamber OR can be reduced. Therefore, if the number of outlet pipes 69 is small, the compressor 3 and the refrigeration cycle device 1 can increase the volume of the refrigerant introduction chamber IR in the container 61, thereby improving the gas-liquid separation capacity.

[0104] Furthermore, the inlet openings 69i of each of the multiple outlet pipes 69 can be positioned at substantially the same radial position on the shell 61a, spaced apart along the centerline of the shell 61a. In other words, compared to conventional compressors with outlet pipes that have a complex structure within the accumulator, the compressor 3 can easily adjust the length of each of the multiple outlet pipes 69 to be the same length. As a result, the compressor 3 and the refrigeration cycle device 1 can match the resonance frequencies of each of the multiple outlet pipes 69 to maximize the supercharging effect.

[0105] Furthermore, the compressor 3 and the accumulator 25 of the refrigeration cycle device 1 according to this embodiment are equipped with a partition plate 63 having a recess 64 that is recessed downwards. The recess 64 has a bottom portion 64a located below the inlet opening 69i of the uppermost outlet pipe 69 among at least one outlet pipe 69 inside the container 61 of the accumulator 25. The partition plate 63 increases the volume of the refrigerant introduction chamber IR of the container 61 of the accumulator 25 by the amount that the recess 64 is recessed downwards. As a result, the compressor 3 and the refrigeration cycle device 1 can increase the volume of the refrigerant introduction chamber IR of the container 61 compared to the case where the partition plate 63 does not have a recess 64, thereby improving the gas-liquid separation capacity of the accumulator 25, that is, the gas-liquid separation capacity of the compressor 3. In particular, even when the inlet opening 69i of the outlet pipe 69 is provided on the side of the container 61, as in this embodiment, the compressor 3 and the refrigeration cycle device 1 can ensure sufficient gas-liquid separation capacity while suppressing an increase in the overall size of the accumulator 25.

[0106] Therefore, according to the compressor 3 and refrigeration cycle device 1 of this embodiment, the compressor 3 can achieve both excellent gas-liquid separation capability by securing liquid storage capacity and improved maximum capacity by supercharging effect.

[0107] In this embodiment, the compressor 3 is a rotary compressor. However, it is not limited to this; the compressor 3 may be, for example, a swing compressor or a sliding vane compressor, and the same effects as when it is a rotary compressor can be obtained.

[0108] While several embodiments of the present invention have been described, these embodiments are presented as examples only and are not intended to limit the scope of the invention. These novel embodiments can be carried out in a variety of other forms, and various omissions, substitutions, and modifications can be made without departing from the spirit of the invention. These embodiments and their variations are included in the scope and spirit of the invention, as well as in the claims of the invention and its equivalents. [Explanation of symbols]

[0109] 1...Refrigeration cycle unit, 3...Rotary compressor (compressor), 5...Radiator, 7...Expansion device, 9...Heat absorber, 11...Refrigerant pipe, 11a...Suction pipe, 11b...Discharge pipe, 13...Sealed container, 13a...Body, 13b...Upper end plate, 13c...Lower end plate, 15...Electric motor, 17...Compression mechanism, 19...Crankshaft, 19a...Intermediate section, 19b...Lower end section, 21...Main bearing, 23...Sub-bearing, 25...Accumulator, 27...Stator, 29...Rotor, 31...Eccentric section, 31a...First eccentric section, 31b...Second eccentric section, 32...Frame, 33...First cylinder, 35...Second cylinder, 37...Partition plate, 39...First cylinder chamber, 41...Second cylinder chamber, 43...First roller, 45...Second roller, 46...Vane 47...First suction port, 48...Second suction port, 49...First discharge muffler, 50...Second discharge muffler, 51...Holder, 61...Container, 61a...Body, 61b...Upper end plate, 61c...Lower end plate, 63...Partition plate, 63a...Flat surface, 64...Recess, 64a...Bottom, 65...Inlet pipe, 67...Connecting pipe, 67i...Inlet opening, 67o...Outlet opening, 67d...Refrigeration Machine oil return hole, 69... Outlet pipe, 69i... Inlet opening, 69o... Outlet opening, 71... Strainer, 73... Separation plate, 75... Support plate, 81... Bent pipe (first bent pipe), 81a... Upstream section, 81b... Bent section, 81c... Downstream section, 83... Bent pipe (second bent pipe), 83a... Upstream section, 83b... Bent section, 83c... Downstream section, 85... First connection section, 87... Second connection section.

Claims

1. A cylindrical airtight container, A compression mechanism housed in the aforementioned sealed container and capable of compressing a refrigerant, An electric motor housed in the sealed container and driving the compression mechanism, A crankshaft that transmits the rotational driving force of the electric motor to the compression mechanism, The system comprises an accumulator located outside the sealed container and connected to the suction side of the compression mechanism, The accumulator is Container and The compression mechanism comprises at least one outlet pipe having an outlet opening connected to the suction side, The container of the accumulator is a compressor provided in the circumferential direction of the sealed container, in a direction different from the opening direction of the outlet opening of the at least one outlet pipe when viewed from the rotation center of the crankshaft.

2. The compressor according to claim 1, wherein the at least one outlet pipe includes two bent pipes.

3. The compressor according to claim 2, wherein each of the two bent pipes has a portion that extends in a direction parallel to the first imaginary line VL1, when viewed from the bottom, the straight line passing through the rotation center of the crankshaft and the center of the container of the accumulator is defined as the first imaginary line VL1.

4. The compressor according to claim 3, wherein each of the two bent pipes has a portion that extends in a direction perpendicular to the first virtual line VL1.

5. In a bottom view, if a straight line passing through the rotation center of the crankshaft and the center of the container of the accumulator is defined as a first imaginary line VL1, and a straight line passing through the rotation center of the crankshaft and the center of the outlet opening of the at least one outlet pipe is defined as a second imaginary line VL2, then the angle θ between the first imaginary line VL1 and the second imaginary line VL2 is less than 90°, the compressor according to claim 1.

6. The compressor according to any one of claims 1 to 5, wherein the at least one outlet pipe is connected to the inside of the container from the side of the container of the accumulator.

7. The accumulator is provided inside the container of the accumulator, and divides the internal space of the container into a refrigerant introduction chamber and a refrigerant discharge chamber, and includes a partition plate having a recess that is recessed downwards. The at least one outlet pipe has an inlet opening connected to the refrigerant discharge chamber, The compressor according to claim 6, wherein the recess has a bottom portion located below the inlet opening of the uppermost outlet pipe among the at least one outlet pipe.

8. The compressor according to claim 1, Heat sink and, Expansion device and Heat absorber and A refrigeration cycle device comprising a compressor, a heat sink, an expansion device, and a refrigerant pipe for circulating a refrigerant, connecting the compressor, the heat sink, the expansion device, and the heat absorber.

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