Compressor and refrigeration cycle device

Abstract

The invention provides a compressor and a refrigeration cycle device which have excellent gas-liquid separation capability and can improve maximum capability based on supercharging effect. A compressor (3) is provided with: a cylindrical sealed container (13); a compression mechanism (17) capable of compressing the refrigerant; an electric motor (15) for driving the compression mechanism (17); a crankshaft (19) that transmits the rotational driving force of the electric motor (15) to the compression mechanism (17); and a reservoir (25) disposed outside the sealed container (13) and connected to the suction side of the compression mechanism (17). The liquid storage device (25) is provided with at least one outlet pipe (69). The outlet pipe (69) is provided with a container (61) and an outlet opening (69o) connected with the suction side of the compression mechanism (17). The container (61) is provided in the circumferential direction of the sealed container (13) in a direction different from the opening direction of the outlet opening (69o) of the at least one outlet pipe (69) when viewed from the center of rotation of the crankshaft (19).

Description

Technical Field

[0001] Embodiments of the present invention relate to compressors and refrigeration cycle devices. Background Technology

[0002] A multi-cylinder rotary compressor is known, aiming to improve volumetric efficiency and ensure the storage capacity (liquid capacity) of the liquid refrigerant in the receiver, which acts as a gas-liquid separator. The compressor has a compressor body within a sealed housing. This compressor body houses a rotating shaft with an axis in the vertical direction, an electric motor connected to the upper end of the rotating shaft, and an upper compression mechanism and a lower compression mechanism connected to the lower end of the rotating shaft and positioned vertically. Furthermore, the compressor includes: a receiver located beside the compressor body; an upper suction pipe extending through the bottom of the receiver, with one end opening at the top inside the receiver and the other end connected to the upper compression mechanism; and a lower suction pipe, with one end opening at the top inside the receiver and the other end connected to the lower compression mechanism. When viewed from the center of rotation of the rotating shaft, the receiver is circumferentially positioned in the same direction as the openings of the other ends of the upper and lower suction pipes within the sealed housing.

[0003] Existing technical documents Patent documents Patent Document 1: Japanese Patent No. 6037563 Summary of the Invention

[0004] The problem that the invention aims to solve However, in conventional compressors, the liquid storage capacity within the receiver is determined by the position of the suction pipe opening. Therefore, to ensure sufficient liquid storage capacity, the suction pipe may not be designed to the desired length. In other words, to ensure sufficient liquid storage capacity, the length of the suction pipe may not be freely adjustable to achieve the desired compressor boosting effect when the compressor operates at a specified speed. Therefore, there is room for improvement in compressor design, balancing excellent gas-liquid separation capabilities achieved by ensuring sufficient liquid storage capacity with maximum boosting capacity.

[0005] Therefore, the object of the present invention is to provide a compressor and a refrigeration cycle device that have excellent gas-liquid separation capability based on the guaranteed liquid storage capacity, and can improve the maximum capacity based on the pressurization effect.

[0006] Methods for solving problems To address the aforementioned problem, the 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 a liquid receiver disposed outside the sealed container and connected to the suction side of the compression mechanism, the liquid receiver comprising: a container; and at least one outlet pipe having an outlet opening connected to the suction side of the compression mechanism, wherein the container of the liquid receiver is arranged circumferentially in 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] In addition, to solve the aforementioned problem, the refrigeration cycle apparatus of the present invention includes: the compressor; the radiator; the expansion device; the heat absorber; and the refrigerant pipe, connecting the compressor, the radiator, the expansion device, and the heat absorber to allow the refrigerant to circulate. Attached Figure Description

[0008] Figure 1 This is a schematic diagram of a refrigeration cycle device and a compressor according to an embodiment of the present invention.

[0009] Figure 2 This is a longitudinal sectional view of the compressor according to an embodiment of the present invention.

[0010] Figure 3 This is a longitudinal cross-sectional view of the liquid receiver of the compressor according to an embodiment of the present invention.

[0011] Figure 4 This is a cross-sectional view of the compressor according to an embodiment of the present invention.

[0012] Figure 5 This is a cross-sectional view of another example of a compressor according to an embodiment of the present invention.

[0013] Figure 6 This is a longitudinal sectional view of another example of the liquid receiver of the compressor according to an embodiment of the present invention. Detailed Implementation

[0014] Reference Figures 1 to 6 Embodiments of the compressor and refrigeration cycle device of the present invention will be described. Furthermore, in several drawings, the same or equivalent components are labeled with the same reference numerals.

[0015] Figure 1 This is a schematic diagram of a refrigeration cycle device and a compressor according to an embodiment of the present invention.

[0016] like Figure 1As shown, the refrigeration cycle apparatus 1 of this embodiment includes a rotary compressor 3, a radiator 5, an expansion device 7, a heat absorber 9, and a refrigerant pipe 11. Hereinafter, the rotary compressor 3 will sometimes be simply referred to as "compressor 3". The refrigerant pipe 11 connects the compressor 3, the radiator 5, the expansion device 7, and the heat absorber 9 in sequence, allowing refrigerant to flow. The refrigerant flowing in the refrigeration cycle apparatus 1 includes various refrigerants such as carbon dioxide, R32, and mixed refrigerants of R32. The radiator 5 is sometimes referred to as a condenser, and the heat absorber 9 is sometimes referred to as an evaporator.

[0017] Figure 2 This is a longitudinal sectional view of the compressor according to an embodiment of the present invention. Furthermore, Figure 2 It is a cross-section that allows us to understand the internal structure of the sealed container 13 of the compressor 3, for example... Figure 1 A cross-sectional view of line A1-A1.

[0018] exist Figure 1 On the basis of, such as Figure 2 As shown, the compressor 3 includes: a vertically arranged 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 secondary bearing 23 that rotatably support the crankshaft 19; and a liquid reservoir 25 disposed outside the sealed container 13 and connected to the suction side of the compression mechanism 17.

[0019] The sealed container 13 has a cylindrical tube 13a extending in the vertical direction, a hemispherical or elliptical upper end plate 13b at the upper end of the blocking tube 13a, and a hemispherical or elliptical lower end plate 13c at the lower end of the blocking tube 13a.

[0020] Cylinder 13a supports multiple suction pipes 11a that guide refrigerant to compressor 3. The multiple suction pipes 11a are connected to receiver 25. The multiple suction pipes 11a are part of refrigerant pipe 11.

[0021] The upper end plate 13b supports the spray pipe 11b from which the refrigerant compressed by the compressor 3 is ejected. The spray pipe 11b is connected to the refrigerant pipe 11.

[0022] The electric motor 15 generates a driving force that rotates the compression mechanism 17. The electric motor 15 is, for example, a permanent magnet synchronous motor (PMSM). The electric motor 15 has a cylindrical stator 27 fixed to the inner wall of the sealed container 13, and a rotor 29 disposed inside the stator 27 and fixed to the crankshaft 19.

[0023] The rotor 29 has a rotor core with a magnet receiving hole and a permanent magnet housed in the magnet receiving hole. The rotor 29 is rotatable relative to the stator 27 and is integrally fixed to the crankshaft 19. The rotation center line C of the rotor 29 and the crankshaft 19 is substantially aligned with the center line P of the stator 27.

[0024] The crankshaft 19 connects the electric motor 15 to the compression mechanism 17. The crankshaft 19 transmits the driving force generated by the electric motor 15 to the compression mechanism 17.

[0025] The middle portion 19a of the crankshaft 19 connects the electric motor 15 to the compression mechanism 17 and is rotatably supported on the main bearing 21. The lower end portion 19b of the crankshaft 19 is rotatably supported on the auxiliary bearing 23. Both the main bearing 21 and the auxiliary bearing 23 are also part of the compression mechanism 17. In other words, the crankshaft 19 passes through the compression mechanism 17.

[0026] Furthermore, the crankshaft 19 has multiple eccentric portions 31a, 31b between the middle portion 19a supported by the main bearing 21 and the lower end portion 19b supported by the auxiliary bearing 23. The side of the multiple eccentric portions 31 closest to the main bearing 21 is referred to as the first eccentric portion 31a, and the side closest to the auxiliary bearing 23 is referred to as the second eccentric portion 31b. Each eccentric portion 31a, 31b is a disk or cylinder having a center that is not aligned with the center of the crankshaft 19. The centers of each eccentric portion 31a, 31b are eccentricated about the crankshaft 19 with a phase difference of approximately 180 degrees. The first eccentric portion 31a is positioned on the upper side closer to the motor 15, and the second eccentric portion 31b is positioned on the lower side farther from the motor 15.

[0027] The upper main bearing 21 is fixed to the frame 32 via a compression mechanism 17 by several fastening components (omitted in the figure), such as bolts. The frame 32 is fixed to the sealed container 13 at multiple locations by welding, such as spot welding. That is, the frame 32 supports the compression mechanism 17, the crankshaft 19, and the rotor 29 of the motor 15 while fixed to the sealed container 13.

[0028] The compression mechanism 17 is driven to rotate by an electric motor 15 connected via a crankshaft 19. It draws in gaseous refrigerant from multiple suction pipes 11a, compresses the drawn-in refrigerant, and sprays the compressed refrigerant into a 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 the refrigeration oil.

[0029] The compression mechanism 17 has multiple cylinders, such as two cylinders 33 and 35. In other words, the compressor 3 is a multi-cylinder rotary compressor. The compression mechanism 17 has a first cylinder 33 disposed within a sealed container 13, a second cylinder 35 disposed within a sealed container 13, and a partition plate 37 disposed between the first cylinder 33 and the second cylinder 35.

[0030] Furthermore, the compressor 3 can be a multi-cylinder rotary compressor with three or more cylinders, or it can be a single-cylinder rotary compressor. The compressor 3 and the liquid receiver 25 are connected via suction pipes 11a, which are the same number as the number of cylinders.

[0031] The first cylinder block 33 has a cylindrical first cylinder block chamber 39 that runs through the first cylinder block 33 in the vertical direction.

[0032] The second cylinder block 35 has a cylindrical second cylinder block chamber 41 that runs through the second cylinder block 35 in the vertical direction.

[0033] Additionally, the compression mechanism 17 includes: an annular first roller 43 disposed within the first cylinder chamber 39; an annular second roller 45 disposed within the second cylinder chamber 41; and blades 46 (see reference). Figure 4 The first cylinder 43 and the second cylinder 45 are respectively arranged radially in the first cylinder chamber 39 in the first cylinder 33 and radially in the second cylinder chamber 41 in the second cylinder 35. Each blade 46, in contact with the outer peripheral surface of its corresponding roller 43, 45, reciprocates towards or away from the rotational center line C of the crankshaft 19, dividing the corresponding cylinder chambers 39, 41 into an intake chamber and a compression chamber. Furthermore, the first roller 43 and the second roller 45 are rotating pistons.

[0034] The first cylinder 33 and the second cylinder 35 compress the refrigerant by changing the volume of the compression chambers divided by the corresponding rollers 43 and 45 and the corresponding blades 46 through the rotation of rollers 43 and 45.

[0035] The first cylinder block 33 and the second cylinder block 35 are arranged in a manner that stacks axially on the crankshaft 19. The upper first cylinder block 33 is located on the side closer to the electric motor 15. The lower second cylinder block 35 is located on the side farther away from the electric motor 15.

[0036] Each cylinder block 33, 35 has an inner circumferential surface that defines a corresponding cylinder chamber 39, 41. Each cylinder block 33, 35 has an annular and plate-like shape with a corresponding cylinder chamber 39, 41 on its inner side. Each cylinder block 33, 35 has an end face close to the motor 15 and an end face away from the motor 15.

[0037] The centers of the first cylinder block 39 and the second cylinder block 41 substantially overlap with the rotation center line C of the crankshaft 19. These cylinder blocks 39 and 41 have the same height dimension as their substantially identical diameter, i.e., the dimension along the length of the crankshaft 19. The first cylinder block 39 is the space inside the first cylinder block 33, enclosed by the main bearing 21 and the partition plate 37. The first cylinder block 39 houses the first eccentric portion 31a of the crankshaft 19. The second cylinder block 41 is the space inside the second cylinder block 35, enclosed by the partition plate 37 and the auxiliary bearing 23. The second cylinder block 41 houses the second eccentric portion 31b of the crankshaft 19.

[0038] Additionally, the compression mechanism 17 includes: a first suction port 47 disposed in the first cylinder 33 for drawing refrigerant into the first cylinder chamber 39; and a second suction port 48 disposed in the second cylinder 35 for drawing refrigerant into the first cylinder chamber 39. Each suction port 47, 48 is connected to the suction pipe 11a.

[0039] The compression mechanism 17 includes: a first ejection valve mechanism having an ejection outlet and an ejection valve, the ejection outlet being disposed on the main bearing 21 to eject the refrigerant compressed in the first cylinder chamber 39 to the outside of the first cylinder chamber 39, the ejection valve being disposed on the main bearing 21 to open and close the ejection outlet; and a first ejection muffler 49 being disposed on the main bearing 21 and covering the first ejection valve mechanism.

[0040] The nozzle of the first ejection valve mechanism is connected to the first cylinder chamber 39.

[0041] When the pressure difference between the inside and outside of the first cylinder chamber 39 reaches a predetermined pressure difference value due to the compression action of the compression mechanism 17, the discharge valve of the first discharge valve mechanism opens the discharge outlet and discharges the compressed refrigerant into the first discharge silencer 49.

[0042] The first ejection silencer 49 covers the first ejection valve mechanism. The first ejection silencer 49 has an ejection port that extends through the first ejection silencer 49. Compressed refrigerant ejected into the first ejection silencer 49 is ejected into the sealed container 13 through the ejection port.

[0043] The first ejection muffler 49 and the first cylinder 33 are secured to the main bearing 21 by several fastening components, such as bolts, which are omitted from the illustration. The bolts pass through the first ejection muffler 49 and the main bearing 21 to reach the first cylinder 33.

[0044] Additionally, the compression mechanism 17 includes: a second injection valve mechanism having an injection outlet and an injection valve, the injection outlet being disposed on the secondary bearing 23 to inject refrigerant compressed within the second cylinder chamber 41, the injection valve being disposed on the secondary bearing 23 to open and close the injection outlet; and a second injection muffler 50 being disposed on the secondary bearing 23 and covering the second injection valve mechanism.

[0045] The nozzle of the second injection valve mechanism is connected to the second cylinder chamber 41.

[0046] The second ejection valve mechanism opens the ejection outlet when the pressure difference between the inside and outside of the second cylinder chamber 41 reaches a specified pressure difference value due to the compression action of the compression mechanism 17, and ejects the compressed refrigerant into the second ejection silencer 50.

[0047] The second ejection silencer 50 covers the second ejection valve mechanism. The compressed refrigerant ejected into the second ejection silencer 50 is guided to the first ejection silencer 49 through the holes passing through the sub-bearing 23, the second cylinder 35, the partition plate 37, and the first cylinder 33, and is ejected into the sealed container 13.

[0048] The second ejection muffler 50, the auxiliary bearing 23, the second cylinder 35, and the partition plate 37 are fixed to the first cylinder 33 by several fastening components, such as bolts, which are omitted from the illustration. The bolts pass through the second ejection muffler 50, the auxiliary bearing 23, the second cylinder 35, and the partition plate 37 to reach the first cylinder 33.

[0049] The first roller 43 is fitted into 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 an eccentric motion while a portion of its outer circumferential surface contacts the inner circumferential surface line of the first cylinder chamber 39.

[0050] The second roller 45 is fitted into 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 an eccentric motion while a portion of its outer circumferential surface contacts the inner circumferential surface line of the second cylinder chamber 41.

[0051] Furthermore, 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 contact, but indirect contact through the presence of an oil film (not shown). However, for ease of explanation, the contact through these oil films will be simply described as "contact". The same applies to the contact between the first roller 43 and the first eccentric portion 31a, the second roller 45 and the second eccentric portion 31b, the first roller 43 and the main bearing 21, the second roller 45 and the auxiliary bearing 23, the first roller 43 and the partition plate 37, and the second roller 45 and the partition plate 37.

[0052] The receiver 25 is a gas-liquid separator that separates gaseous refrigerant from liquid refrigerant and delivers the gaseous refrigerant to the compressor 3. The receiver 25 is fixed to the sealed container 13 via a bracket 51 provided on the cylinder 13a of the sealed container 13 of the compressor 3. That is, the receiver 25 is disposed on the outside of the sealed container 13. The receiver 25 is fixed to the sealed container 13 of the compressor 3, for example, by welding to the bracket 51 or by a clamping strap (not shown) provided on the bracket 51 to cover the outer periphery of the receiver 25.

[0053] Figure 3 This is a longitudinal cross-sectional view of the liquid receiver of the compressor according to an embodiment of the present invention.

[0054] also, Figure 3 For example is Figure 1 A cross-sectional view of line A2-A2. (To be explained later.) Figure 6 The same applies to China.

[0055] exist Figure 1 as well as Figure 2 On the basis of, such as Figure 3 As shown, the liquid receiver 25 of this embodiment includes: a cylindrical container 61 supported in an upright state; a partition plate 63 disposed inside the container 61, dividing the internal space of the container 61 into a refrigerant inlet chamber IR and a refrigerant outlet chamber OR; an inlet pipe 65 fixed to the container 61, having an inlet flow path IP connected to the refrigerant inlet chamber IR; a connecting pipe 67 having a connecting flow path CP that passes through the partition plate 63 and connects the refrigerant inlet chamber IR and the refrigerant outlet chamber OR; and a plurality of outlet pipes 69 fixed to the container 61, having an outlet flow path OP connected to the refrigerant outlet chamber OR.

[0056] In addition, the receiver 25 includes: a filter 71 disposed between the inlet pipe 65 and the connecting pipe 67 to filter foreign matter from the refrigerant introduced into the receiver 25; a separator 73 disposed between the filter 71 and the connecting pipe 67 to separate the refrigerant that has passed through the filter 71 into gaseous refrigerant and liquid refrigerant; and a support plate 75 disposed between the separator 73 and the partition plate 63 to support the connecting pipe 67 together with the partition plate 63.

[0057] The container 61 is fixed to the sealed container 13 of the compressor 3 via the bracket 51. The container 61 is cylindrical. The container 61 has a cylindrical tube 61a extending in the vertical direction, a hemispherical or elliptical upper end plate 61b at one end of the blocking tube 61a, i.e., the upper end, and a hemispherical or elliptical lower end plate 61c at the other end of the blocking tube 61a, i.e., the lower end.

[0058] The cylinder 61a supports the filter 71, the separator plate 73, the support plate 75, and the partition plate 63 in the order of refrigerant flow.

[0059] The upper end plate 61b supports the inlet pipe 65 through which the refrigerant, compressed by the compressor 3 and circulating in the refrigeration cycle unit 1, flows into the receiver 25. The inlet pipe 65 is connected to the refrigerant pipe 11.

[0060] 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 cylinder 61a. The centerline of the cylinder 61a coincides with the centerline Q of the container 61.

[0061] The refrigerant flowing from the inlet pipe 65 into the receiver 25 initially reaches the filter 71. The filter 71 has the required mesh size and grid size to prevent foreign matter from flowing into the compression mechanism 17 of the compressor 3.

[0062] The separator plate 73 prevents refrigerant that has passed through the filter 71 from flowing directly into the connecting pipe 67. The separator plate 73 is an upwardly convex plate that acts like an umbrella on the connecting pipe 67. The separator plate 73 has multiple openings 73a through which the refrigerant can pass. The separator plate 73 blocks the view directly below the inlet pipe 65 and the view directly above the connecting pipe 67. Viewed from the inlet pipe 65 side, the multiple openings 73a of the separator plate 73 are positioned radially outward from the connecting pipe 67 within the container 61. The refrigerant reaching the separator plate 73 flows through the multiple openings 73a of the separator plate 73 towards the lower side of the refrigerant inlet chamber IR of the container 61.

[0063] Each opening 73a opens toward the outer periphery of the separating plate 73. In other words, each opening 73a opens toward the inner surface of the container 61. Each opening 73a is formed into a plate-shaped raw material, for example, by punching and bending.

[0064] The support plate 75 and the partition plate 63 are fixed inside the container 61, and the connecting pipe 67 is supported in conjunction with the support plate 75.

[0065] The support plate 75 has holes for supporting the connecting pipe 67 and suitable openings that do not obstruct the flow of liquid and gaseous refrigerant, so that the refrigerant inlet chamber IR becomes a continuous space. The support plate 75 preferably has suitable support strength and rigidity to prevent the connecting pipe 67 extending from the partition plate 63 toward the separation plate 73 from tipping over.

[0066] The partition plate 63 has no openings other than the hole supporting the connecting pipe 67, which divides the internal space of the container 61 into a refrigerant inlet chamber IR and a refrigerant outlet chamber OR. The partition plate 63 is liquid-tightly and gas-tightly attached to the inner surface of the container 61, preventing refrigerant from flowing out of the refrigerant inlet chamber IR to the refrigerant outlet chamber OR through a path other than the connecting pipe 67. The partition plate 63 only needs to have a plane 63a orthogonal to the centerline Q of the container 61, and in the upright state of the receiver 25, the plane 63a extends horizontally.

[0067] Furthermore, in this embodiment, the number of connecting pipes 67 is one. However, it is not limited to this; the number of connecting pipes 67 may also be two or more. The number of connecting pipes 67 is determined by taking into account the pressure loss, piping diameter, and interference from the internal structure of the connecting flow path CP connecting the refrigerant inlet chamber IR and the refrigerant outlet chamber OR.

[0068] The connecting pipe 67 has an inlet opening 67i disposed in the refrigerant inlet chamber IR and an outlet opening 67o disposed in the refrigerant outlet 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.

[0069] The connecting pipe 67 is disposed inside the container 61 and 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 extending parallel to the centerline of the cylinder 61a.

[0070] The length of the connecting pipe 67 depends on the amount of refrigerant sealed in the refrigeration cycle device 1, but is preferably approximately more than half the total length of the receiver 25.

[0071] In addition, the connecting pipe 67 has at least one refrigerant oil return hole 67h disposed in the refrigerant inlet chamber IR.

[0072] The inlet opening 67i of the connecting pipe 67 is closer to the upper end plate 61b than the partition plate 63.

[0073] The outlet opening 67o of the connecting pipe 67 faces the lower end plate 61c downwards.

[0074] Each outlet pipe 69 is the suction pipe 11a of the compressor 3, connected to the corresponding cylinder chambers 39 and 41 of the cylinders 33 and 35 of the compression mechanism 17. The number of outlet pipes 69 is the same as the number of cylinders, i.e., the number of cylinder blocks, of the compressor 3. Figure 1 In the case of the multi-cylinder compressor 3 shown, the receiver 25 is connected to the compressor 3 through a number of outlet pipes 69 equal to the number of cylinders, i.e., the number of cylinder bodies. In the case of the single-cylinder compressor 3, the receiver 25 only needs to be connected to the compressor 3 through one outlet pipe 69. In other words, the receiver 25 only needs to have at least one outlet pipe 69, and preferably has a number of outlet pipes 69 equal to the number of cylinders, i.e., the number of cylinder bodies, of the compressor 3.

[0075] Each outlet pipe 69 allows gaseous refrigerant separated from the refrigerant flowing into the receiver 25 to flow out of the receiver 25. Each outlet pipe 69 has an inlet opening 69i disposed in the refrigerant discharge chamber OR and an outlet opening 69o connected to the corresponding cylinder chambers 39, 41.

[0076] The inlet opening 69i corresponds to the upstream end of the outlet flow path OP, and the outlet opening 69o corresponds to the downstream end of the outlet flow path OP.

[0077] When viewed from the inlet opening 67i at the upper end of the connecting pipe 67, each inlet opening 69i is preferably located radially outward of the cylinder 61a than the outlet opening 67o of the connecting pipe 67.

[0078] Container 61 is an assembly of two parts that are split midway through cylinder 61a and then airtightly joined. Preferably, the inlet pipe 65, filter 71, and separator plate 73 are assembled into the upper part before assembling container 61, and the outlet pipe 69, separator plate 63, support plate 75, and connecting pipe 67 are assembled into the lower part before assembling container 61. The support plate 75 can be disposed at the split surface of the two parts or fixed to the inside of the lower part.

[0079] In the receiver 25 configured as described above, the refrigerant flowing from the inlet pipe 65 into the refrigerant inlet chamber IR inside the container 61 comes into contact with the separator plate 73 and separates into gaseous refrigerant and liquid refrigerant. The separated liquid refrigerant flows further into the refrigerant inlet chamber IR from the opening 73a of the separator plate 73 and accumulates at the bottom of the refrigerant inlet chamber IR, i.e., on the side of the separator plate 63. On the other hand, the separated gaseous refrigerant flows from the opening 73a of the separator plate 73 into the refrigerant discharge chamber OR through the connecting pipe 67. The gaseous refrigerant flowing into the refrigerant discharge chamber OR is drawn into the outlet pipe 69 and delivered to the compressor 3. The receiver 25 has a refrigerant inlet chamber IR, which serves as the upper space for storing liquid refrigerant, and a refrigerant discharge chamber OR, which serves as the lower space where the inlet opening 69i of at least one outlet pipe 69 is located, inside the container 61. Therefore, while ensuring the storage capacity through the refrigerant inlet chamber IR, the compressor 3 does not have the liquid storage capacity in the receiver determined by the position of the opening of the suction pipe, as is the case with conventional compressors.

[0080] Figure 4 This is a cross-sectional view of the compressor according to an embodiment of the present invention. Furthermore, Figure 4 It is a cross-section that allows us to understand the configuration relationship between the sealed container 13, the compression mechanism 17, the support 51, the liquid reservoir 25, the container 61, and the outlet pipe 69, for example, Figure 1 A cross-sectional view of line A3-A3.

[0081] However, in conventional compressors, the liquid storage capacity within the receiver is determined by the position of the suction pipe opening. Therefore, to ensure sufficient liquid storage capacity, the length of the suction pipe may not be freely adjustable. In other words, to achieve the desired compressor boosting effect when operating at a specified speed, the length of the suction pipe may not be adjustable. Therefore, there is room for improvement in compressors that balance excellent gas-liquid separation capabilities based on ensuring sufficient liquid storage capacity with maximum boosting capacity.

[0082] Therefore, as Figure 4As shown, the container 61 of the receiver 25 is positioned circumferentially 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. Thus, the outlet pipe 69 can have an inverted U-shape (gate-shaped) relative to the opening of the support 51 when viewed from below. Therefore, compared to the case where the container 61 of the receiver 25 is positioned circumferentially in the same direction as the opening direction of the outlet opening 69o of the outlet pipe 69 when viewed from the rotation center of the crankshaft 19, the compressor 3 can easily extend the length of the outlet pipe 69. Therefore, the compressor 3 has excellent gas-liquid separation capability by ensuring the liquid storage capacity of the receiver 25 in the refrigerant inlet chamber IR, and by optimizing the length of the outlet pipe 69, the peak pressure effect is made consistent with the maximum speed of the compressor 3, making it easy to increase the maximum capacity.

[0083] Furthermore, the central axis of the outlet pipe 69, which is preferably in the shape of a gate, is located on a plane orthogonal to the rotation center line C of the crankshaft 19. This allows the outlet pipe 69 to extend in a manner that does not compress the space extending above or below it. In other words, the installation volume of the compressor 3 will not increase excessively due to the presence of the outlet pipe 69.

[0084] Typically, to achieve a pressurization effect, the outlet pipe (suction pipe) needs to be designed according to the target operating state of the compressor. In conventional compressors, the relative positional relationship between the sealed container and the liquid receiver needed to be reconsidered significantly depending on the length of the outlet pipe.

[0085] Therefore, it is preferred that at least one outlet pipe 69 includes two bends 81, 83.

[0086] Specifically, the two bent tubes 81 and 83 are, for example, L-shaped. Furthermore, by joining the two L-shaped bent tubes 81 and 83 together, a gate-shaped outlet pipe 69 can be formed. With such two bent tubes 81 and 83, during the design phase, the length of at least one of the two bent tubes 81 and 83 can be adjusted to make the outlet pipe 69 the appropriate length to produce a pressurizing effect simply by moving the container 61 of the reservoir 25 radially or circumferentially along the sealed container 13, thus allowing for easy adjustment of the length of the outlet pipe 69. That is, the two bent tubes 81 and 83 can easily achieve a pressurizing effect in various compressors with different target operating states.

[0087] Furthermore, the compressor 3 preferably includes a first connecting portion 85 for joining the two curved tubes 81, 83 and a second connecting portion 87 fixed to the sealed container 13 for joining the second curved tube 83 to the sealed container 13. Thus, the first curved tube 81 and the second curved tube 83 can be reliably joined by brazing via the first connecting portion 85. Furthermore, the second curved tube 83 can be reliably joined to the sealed container 13 via brazing via the second connecting portion 87. Additionally, when the container 61 of the reservoir 25 is fixed to the sealed container 13 via the bracket 51, the first connecting portion 85 and the second connecting portion 87 can accommodate the length tolerances of the two curved tubes 81, 83, and fix the container 61 to the sealed container 13 with high precision.

[0088] When viewed from below, the two curved tubes 81 and 83 preferably have portions extending in the X direction, which is parallel to the first imaginary line VL1, with the straight line passing through the rotation center of the crankshaft 19 and the center of the container 61 of the reservoir 25 as the first imaginary line VL1.

[0089] Furthermore, when viewed from below, the center of rotation of the crankshaft 19 is the point where the rotation center line C intersects with a plane orthogonal to the rotation center line C. Similarly, when viewed from below, the center of the container 61 of the reservoir 25 is the point where the center line Q of the container 61 intersects with a plane orthogonal to the center line Q. At this time, the first imaginary line VL1 lies on a plane orthogonal to both the rotation center line C and the center line Q.

[0090] For ease of explanation later, the curved pipe 81 is sometimes referred to as the "first curved pipe 81," and the curved pipe 83 as the "second curved pipe 83." The first curved pipe 81 has: a straight upstream portion 81a including the inlet opening 69i of the outlet pipe 69; a curved portion 81b, continuous and curved with respect to the upstream portion 81a; and a straight downstream portion 81c, continuous with the curved portion 81b. The downstream portion 81c of the first curved pipe 81 extends in the X direction parallel to the first imaginary line VL1. Similarly, the second curved pipe 83 has: a straight downstream portion 83c including the inlet opening 69i of the outlet pipe 69; a curved portion 83b, continuous and curved with respect to the downstream portion 83c; and a straight upstream portion 83a, continuous with the curved portion 83b. The upstream portion 83a of the second curved pipe 83 extends in the X direction parallel to the first imaginary line VL1. Therefore, during the design phase, the length of at least one of the downstream portion 81c and the upstream portion 83a can be adjusted by simply moving the container 61 of the reservoir 25 along the first imaginary line VL1 located in the radial direction of the sealed container 13, so that the outlet pipe 69 becomes the appropriate length to produce a pressurizing effect, thereby making it easy to adjust the length of the outlet pipe 69.

[0091] Furthermore, when viewed from below, the two curved tubes 81 and 83 preferably have, in addition to a portion extending in the X direction parallel to the first imaginary line VL1, a portion extending in the Y direction orthogonal 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 reservoir 25 is designated as the first imaginary line VL1.

[0092] Specifically, the upstream portion 81a of the first curved pipe 81 and the downstream portion 83c of the second curved pipe 83 are respectively located in the Y direction, which is orthogonal to the first imaginary line VL1. Therefore, during the design phase, by simply moving the container 61 of the reservoir 25 circumferentially within the sealed container 13, the lengths of at least one of the downstream portion 81c and the upstream portion 83a, as well as the length of at least one of the upstream portion 81a and the downstream portion 83c, can be adjusted to make the outlet pipe 69 the appropriate length to produce a pressurizing effect, thereby allowing for easy adjustment of the length of the outlet pipe 69.

[0093] Figure 5 This is a cross-sectional view of another example of a compressor according to an embodiment of the present invention. Figure 5 In the middle, the relative positional relationship between the sealed container 13 of the compressor 3 and the container 61 of the liquid receiver 25 is as follows: Figure 4 The relative positions of the sealed container 13 and the container 61 of the liquid storage tank 25 are different.

[0094] In addition, such as Figure 5 As shown, when viewed from below, if the straight line passing through the center of rotation of crankshaft 19 and the center of container 61 of reservoir 25 is designated as the first imaginary line VL1, and the straight line passing through the center of rotation of crankshaft 19 and the center of outlet opening 69o of at least one outlet pipe 69 is designated as the second imaginary line VL2, the angle θ between the second imaginary line VL2 and the first imaginary line VL1 can also be less than 90°. Furthermore, the center of outlet opening 69o of outlet pipe 69 is the intersection of the central axis of outlet pipe 69 and the plane including outlet opening 69o.

[0095] Specifically, when it is desired to shorten the length of the outlet pipe 69 to make it an appropriate length for generating a pressurizing effect, by making the angle θ between the second imaginary line VL2 and the first imaginary line VL1 less than 90°, the length of at least one of the two curved pipes 81 and 83 can be shortened during the design phase, thereby adjusting the length of the outlet pipe 69 to be shorter. Figure 5 In the example, with Figure 4Compared to the previous example, by shortening the length of the first curved pipe 81, the length of the outlet pipe 69 is adjusted to be shorter. Furthermore, by making the angle θ between the second imaginary line VL2 and the first imaginary line VL1 less than 90°, compared to the case where the angle θ is 90°, the required installation volume for the compressor 3 can be reduced.

[0096] Additionally, if returning Figure 3 As shown, preferably at least one outlet pipe 69 is connected from the side of the container 61 of the receiver 25 to the inside of the container 61. That is, preferably at least one outlet pipe 69 is connected from the cylinder 61a of the container 61 of the receiver 25 to the refrigerant discharge chamber OR.

[0097] Typically, in a compressor equipped with a receiver, the outlet pipe (suction pipe) connecting the receiver container to the compressor's sealed container has the following characteristics on the outside of the receiver container: a straight upstream section fixed to the lower end plate of the container and extending downwards; a curved section continuously curved from the upstream section; and a straight downstream section continuous from the curved section, connected to the suction side of the compression mechanism. Here, when the length of the upstream section is increased to extend the length of the outlet pipe, the receiver container is positioned upwards. If the container is positioned upwards, the space extending upwards from the container is compressed, and the required installation volume for the compressor increases upwards. That is, the compressor's installation capacity is reduced.

[0098] On the other hand, in this embodiment, the outlet pipe 69 of the container 61 of the receiver 25 is connected to the refrigerant discharge chamber OR from the side of the container 61, so it is not necessary to move the container 61 upwards. That is, excessive reduction in the installation capability of the compressor 3 is prevented. In addition, when the number of at least one outlet pipe 69 connected to the refrigerant discharge chamber OR from the side of the container 61 is small, the volume of the refrigerant inlet chamber IR can be increased, improving the gas-liquid separation capability. Furthermore, the inlet openings 69i of each of the plurality of outlet pipes 69 can be arranged substantially at the same radial position in the cylinder 61a, spaced apart in the direction along the centerline of the cylinder 61a. That is, compared with the outlet pipes of conventional compressors that have complex structures in the receiver, the lengths of the plurality of outlet pipes 69 can be easily adjusted to be the same. Therefore, the resonant frequencies of the outlet pipes 69 in each of the plurality of outlet pipes can be made consistent, maximizing the pressurization effect.

[0099] Figure 6 This is a longitudinal sectional view of another example of the liquid receiver of the compressor according to an embodiment of the present invention.

[0100] like Figure 6As shown, the partition plate 63 of the receiver 25 may also have a recess 64 that is recessed downward from the plane 63a. Furthermore, the recess 64 may also have a bottom 64a inside the container 61 of the receiver 25, which is located below the inlet opening 69i of the uppermost outlet pipe 69 in at least one outlet pipe 69. As a result, the volume of the refrigerant inlet chamber IR of the container 61 becomes larger, and the gas-liquid separation capability of the receiver 25 is further improved.

[0101] Furthermore, the recess 64 is, for example, cylindrical. Additionally, when the separator 63 of the reservoir 25 has a bottom 64a, the connecting pipe 67 extends through the bottom 64a. Furthermore, the outer surface of the recess 64 faces the inner surface of the container 61 at a certain interval. Moreover, viewed from the inlet opening 67i at the upper end of the connecting pipe 67, the outer surface of the recess 64 is located radially inward of the cylinder 61a than the inlet opening 69i of at least one outlet pipe 69. Therefore, the recess 64 allows gaseous refrigerant flowing into the refrigerant discharge chamber OR through the connecting pipe 67 to be drawn into the outlet pipe 69 and delivered to the compressor 3 without obstructing its flow.

[0102] As described above, the compressor 3 and refrigeration cycle device 1 of this embodiment include a liquid receiver 25, which has a container 61. This container 61 is positioned circumferentially around the sealed container 13 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. Based on this relative positional relationship between the sealed container 13 and the container 61 of the liquid receiver 25, i.e., the liquid receiver 25, compared to the case where the opening directions of the container 61 of the liquid receiver 25 and the outlet opening 69o of the outlet pipe 69 are the same circumferentially around the sealed container 13 when viewed from the rotation center of the crankshaft 19, the length of the outlet flow path OP of the outlet pipe 69 can be easily ensured. That is, the length adjustment of the outlet pipe 69 can have a high degree of design freedom. 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 the refrigeration cycle unit 1 have excellent gas-liquid separation capabilities by ensuring the liquid storage capacity of the liquid receiver 25 in the refrigerant inlet chamber IR, and by optimizing the length of the outlet pipe 69, the peak value of the boosting effect is made consistent with the maximum speed of the compressor 3, which can easily improve the maximum capacity.

[0103] The compressor 3 and refrigeration cycle device 1 of this embodiment include at least one outlet pipe 69 comprising two bends 81 and 83. During the design phase, the length of at least one of the two bends 81 and 83 can be easily adjusted so that the outlet pipe 69 becomes the appropriate length for generating a pressurization effect simply by moving the container 61 of the liquid receiver 25 radially or circumferentially along the sealed container 13. Therefore, the compressor 3 and refrigeration cycle device 1 can easily achieve a pressurization effect in various compressors with different target operating states.

[0104] Furthermore, if the two bent pipes 81 and 83 are such, then during the design phase, with the relative positions of the sealed container 13 and the container 61 fixed, 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, thus making the installation location of the compressor 3, which may change depending on the relative positions of the sealed container 13 and the container 61, common. Therefore, the manufacturability of the compressor 3 and the refrigeration cycle device 1 can be improved.

[0105] The compressor 3 and refrigeration cycle device 1 of this embodiment include two curved pipes 81 and 83. When viewed from below, these two curved pipes 81 and 83, with a first imaginary line VL1 connecting the rotation center of the crankshaft 19 and the center of the container 61 of the liquid receiver 25, each have a portion extending in the X direction parallel to the first imaginary line VL1. The downstream portion 81c of the first curved pipe 81 and the upstream portion 83a of the second curved pipe 83, which are portions extending in the X direction, allow for easy adjustment of the length of the outlet pipe 69 during the design phase simply by moving the container 61 of the liquid receiver 25 along the first imaginary line VL1 located radially in the sealed container 13, thus making the outlet pipe 69 an appropriate length for generating a pressurization effect. Therefore, the compressor 3 and refrigeration cycle device 1 can more easily achieve a pressurization effect among various compressors with different target operating states.

[0106] When viewed from below, the compressor 3 and refrigeration cycle device 1 of this embodiment, with a first imaginary line VL1 connecting the rotation center of the crankshaft 19 and the center of the container 61 of the receiver 25, have, in addition to a portion extending in the X direction parallel to the first imaginary line VL1, two curved pipes 81 and 83, each having a portion extending in the Y direction orthogonal to the first imaginary line VL1. As the downstream portion 81c of the first curved pipe 81 extending in the X direction and the upstream portion 83a of the second curved pipe 83, and as the downstream portion 83c of the first curved pipe 81 extending in the Y direction, during the design phase, the length of the outlet pipe 69 can be easily adjusted by simply moving the container 61 of the receiver 25 circumferentially along the sealed container 13, so that the outlet pipe 69 becomes an appropriate length for generating a pressurization effect. Therefore, the compressor 3 and refrigeration cycle device 1 can more easily obtain a pressurization effect among various compressors with different target operating states.

[0107] The compressor 3 and refrigeration cycle device 1 of this embodiment include a liquid receiver 25. When viewed from below, the liquid receiver 25 is positioned such that a straight line passing through the rotation center of the crankshaft 19 and the center of the container 61 of the liquid receiver 25 is designated as a first imaginary line VL1, and a 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 is designated as a second imaginary line VL2. The compressor 3 is positioned such that the angle θ between the first imaginary line VL1 and the second imaginary line VL2 is less than 90°. Therefore, when the compressor 3 and refrigeration cycle device 1 wish to shorten the length of the outlet pipe 69 to achieve a suitable length for generating a pressurization effect, by making the angle θ less than 90°, the length of at least one of the two curved pipes 81 and 83 can be shortened during the design phase, easily adjusting the length of the outlet pipe 69 to be shorter. Furthermore, by making the angle θ less than 90°, the compressor 3 and refrigeration cycle device 1 can reduce the installation volume required for the compressor 3 compared to the case where the angle θ is 90°.

[0108] In this embodiment, the compressor 3 and the refrigeration cycle device 1 have at least one outlet pipe 69 connected to the side of the container 61 of the liquid receiver 25, i.e., from the cylinder 61a of the container 61 to the inside of the container 61. Therefore, compared to the case where the compressor 3 and the refrigeration cycle device 1 are connected to the container 61 from the bottom surface of the container 61 of the liquid receiver 25, i.e., the lower end plate 61c, to the inside of the container 61, the length of at least one outlet pipe 69 can be adjusted without moving the container 61 upwards.

[0109] Furthermore, when the number of at least one outlet pipe 69 is small, it is not necessary to ensure a correspondingly large area separating the side of the container 61 from the refrigerant discharge chamber OR. That is, the volume of the refrigerant discharge chamber OR can be reduced. Therefore, when the number of at least one outlet pipe 69 is small, the compressor 3 and the refrigeration cycle device 1 can improve the gas-liquid separation capability by correspondingly increasing the volume of the refrigerant inlet chamber IR in the container 61.

[0110] Furthermore, the inlet openings 69i of each of the multiple outlet pipes 69 can be arranged substantially at the same radial position on the cylinder 61a, spaced apart in the direction along the centerline of the cylinder 61a. That is, compared with conventional compressors that have outlet pipes with complex structures within the liquid receiver, the compressor 3 can easily adjust the lengths of each of the multiple outlet pipes 69 to be the same. Therefore, the compressor 3 and the refrigeration cycle device 1 can make the resonant frequencies of the outlet pipes 69 consistent in each of the multiple outlet pipes 69, thereby maximizing the pressurization effect.

[0111] Furthermore, the compressor 3 and the receiver 25 of the refrigeration cycle device 1 in this embodiment are provided with a partition plate 63, which has a downwardly recessed recess 64. The recess 64 has a bottom 64a inside the container 61 of the receiver 25, which is located below the inlet opening 69i of the uppermost outlet pipe 69. The partition plate 63 increases the volume of the refrigerant inlet chamber IR of the container 61 of the receiver 25 by the amount of downward recess of the recess 64. Therefore, compared with the case where the partition plate 63 does not have a recess 64, the compressor 3 and the refrigeration cycle device 1 can further increase the volume of the refrigerant inlet chamber IR of the container 61, and further improve the gas-liquid separation capability of the receiver 25, that is, the gas-liquid separation capability of the compressor 3. In particular, as in this embodiment, even when the inlet opening 69i of the outlet pipe 69 is located on the side of the container 61, the compressor 3 and the refrigeration cycle device 1 can suppress the overall enlargement of the liquid receiver 25 and ensure sufficient gas-liquid separation capability.

[0112] Therefore, according to the compressor 3 and refrigeration cycle device 1 of this embodiment, the compressor 3 can simultaneously achieve excellent gas-liquid separation capability based on ensuring liquid storage capacity and improve maximum capacity based on pressurization effect.

[0113] Furthermore, in this embodiment, compressor 3 is a rotary compressor. However, it is not limited to this; compressor 3 could also be, for example, an oscillating compressor or a sliding vane compressor, achieving the same effect as a rotary compressor.

[0114] Several embodiments of the present invention have been described, but these embodiments are given by way of example and are not intended to limit the scope of the invention. These new embodiments can be implemented in various other ways, 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 or spirit of the invention, and are included within the scope of the invention as described in the claims and its equivalents.

[0115] 1…Refrigeration cycle device, 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…Cylinder, 13b…Upper end plate, 13c…Lower end plate, 15…Motor, 17…Compression mechanism, 19…Crankshaft, 19a…Intermediate section, 19b…Lower end section, 21…Main bearing, 23…Secondary bearing, 25…Liquid receiver, 27…Stator, 29…Rotor, 31…Eccentric part, 31a…First eccentric part, 31b…Second eccentric part, 32…Frame, 33…First cylinder block, 35…Second cylinder block, 37…Divider plate, 39…First cylinder block chamber, 41…Second cylinder block chamber, 43…First roller, 45…Second roller, 46…Blade, 47…First suction port, 48 …Second suction inlet, 49…First ejection silencer, 50…Second ejection silencer, 51…Bracket, 61…Container, 61a…Cylinder, 61b…Upper end plate, 61c…Lower end plate, 63…Divider plate, 63a…Flat surface, 64…Recess, 64a…Bottom, 65…Inlet pipe, 67…Connecting pipe, 67i…Inlet opening, 67o…Outlet opening, 67d…Refrigeration oil return hole, 69…Outlet pipe, 69i…Inlet opening, 69o…Outlet opening, 71…Filter, 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 connecting section, 87…Second connecting section.

Claims

1. A compressor, comprising: A cylindrical, sealed container; A compression mechanism, housed in the sealed container, is capable of compressing the refrigerant; An electric motor, housed in the sealed container, drives the compression mechanism; The crankshaft transmits the rotational driving force of the electric motor to the compression mechanism; and A liquid reservoir, disposed outside the sealed container, is connected to the suction side of the compression mechanism. The liquid reservoir includes: Containers; and At least one outlet pipe has an outlet opening connected to the suction side of the compression mechanism. The container of the reservoir is arranged circumferentially 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, The at least one outlet pipe includes two curved pipes.

3. The compressor according to claim 2, When viewed from below, with the straight line passing through the center of rotation of the crankshaft and the center of the container of the reservoir designated as the first imaginary line VL1, the two curved tubes each have portions extending in a direction parallel to the first imaginary line VL1.

4. The compressor according to claim 3, The two curved tubes each have a portion extending in a direction orthogonal to the first imaginary line VL1.

5. The compressor according to claim 1, When viewed from below, if a straight line passing through the center of rotation of the crankshaft and the center of the container of the reservoir is designated as a first imaginary line VL1, and a straight line passing through the center of rotation of the crankshaft and the center of the outlet opening of the at least one outlet pipe is designated as a second imaginary line VL2, the angle θ between the first imaginary line VL1 and the second imaginary line VL2 is less than 90°.

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

7. The compressor according to claim 6, The liquid receiver includes a partition plate disposed inside the container of the liquid receiver, dividing the internal space of the container into a refrigerant inlet chamber and a refrigerant outlet chamber, and has a downwardly recessed portion. The at least one outlet pipe has an inlet opening connected to the refrigerant discharge chamber. The recess has a bottom located below the inlet opening of the uppermost outlet pipe in the at least one outlet pipe.

8. A refrigeration cycle device, comprising: The compressor according to claim 1; heat sink; Expansion device; Heat absorber; and A refrigerant pipe connects the compressor, the radiator, the expansion device, and the heat absorber to allow refrigerant to flow.

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