JP2023124224A - Compressor and heat pump type water heater system - Google Patents

Abstract

To provide a compressor that can separate a lubricant from a refrigerant with a small number of components, and to provide a heat pump type water heater system including the compressor.SOLUTION: A compression mechanism part 1 includes a cylinder chamber 11 for compressing a refrigerant. A case 2 accommodates the compression mechanism part 1. A compressor 101 is configured to cause compressed refrigerant, which is discharged from the cylinder chamber 11 of the compression mechanism part 1, to pass through a circumference passage CP between an outer peripheral part 13OS of the compression mechanism part 1 and an inner wall 21IS of the case 2.SELECTED DRAWING: Figure 3

Description

The present invention relates to a compressor and a heat pump hot water supply system.

2. Description of the Related Art Conventionally, a compressor used in, for example, a heat pump hot water supply system is filled with lubricating oil to lubricate and slide movable parts such as a compression mechanism. A part of the lubricating oil is mixed with the refrigerant gas and sealed in the compressor.

Lubricating oil is essential for the operation of the compressor that controls the compression process in the heat pump cycle, but it is not important for the condensation process, expansion process, and evaporation process. Rather, the lubricating oil also becomes a factor that lowers the thermal efficiency due to the oil film in the circuit. Therefore, it is important to have a means and a mechanism to prevent lubricating oil from being taken out of the compressor as much as possible.

Techniques for separating the refrigerant and lubricating oil before being discharged from the compressor to the refrigerant circuit are disclosed, for example, in Japanese Patent Application Laid-Open No. 2005-139974 (Patent Document 1), Japanese Patent No. 4469094 (Patent Document 2), and Japanese Patent Application Laid-Open No. 6. -101678 (Patent Document 3).

Patent Literatures 1 and 2 describe separating refrigerant and lubricating oil using a disk-shaped member attached to a shaft. Patent Literature 3 describes separating the refrigerant and the lubricating oil by providing a partition plate to form a constricted portion.

JP 2005-139974 A Japanese Patent No. 4469094 JP-A-6-101678

However, the configurations and mechanisms described in Patent Documents 1 to 3 require a disk-shaped member or a partition plate for separating the lubricating oil and the refrigerant, which increases the number of parts and increases the cost of the compressor. , there is a problem that the size of the compressor itself becomes large.

A main object of the present invention is to provide a compressor capable of separating lubricating oil and refrigerant with a small number of parts, and a heat pump hot water supply system having the compressor.

A compressor according to the present invention includes a compression mechanism and a case. The compression mechanism has a cylinder chamber for compressing refrigerant. The case accommodates the compression mechanism. The compressor is configured to allow compressed refrigerant discharged from a cylinder chamber of the compression mechanism to pass through a circumferential passage between the outer peripheral portion of the compression mechanism and the inner wall of the case.

In the compressor described above, the compression mechanism section has a cylinder. A concave portion forming a circumferential passage is provided on the outer circumference of the cylinder.

In the compressor described above, the cylinder is provided with an oil return path.

The compressor is a horizontal compressor, and in this compressor, the cylinder is provided with an exhaust port for exhausting the compressed refrigerant from the circumferential passage. The oil return path is located below the height position of the center of the cylinder chamber, and the exhaust port is located above the height position of the center of the cylinder chamber.

In the compressor described above, the circumferential passage has an arc portion that forms an arc of 180° or more.

In the compressor described above, the case includes a shell case. The shell case has a portion forming a circumferential passage and is made of a material containing aluminum.

In the compressor described above, the inner wall of the case forming the circumferential passage has an uneven shape.

In the compressor described above, the compressor further includes an electric motor section and a fan. The electric motor section has a stator fixed to the case and a rotor rotating with respect to the stator. The fan is attached to the rotor of the electric motor section and is sprayed with the compressed refrigerant discharged from the compression mechanism section.

The heat pump hot water supply system according to the present invention includes the compressor, a condenser provided so that the compressed refrigerant discharged from the compressor exchanges heat with a heat medium, and the condenser exchanges heat with the compressed refrigerant. and a tank in which the heat medium is stored.

ADVANTAGE OF THE INVENTION According to this invention, the compressor which can separate a lubricating oil and a refrigerant|coolant with few components, and the heat pump hot-water supply system which has this compressor can be provided.

1 is a block diagram for explaining a heat pump hot water supply system according to an embodiment; FIG. It is a sectional view for explaining a compressor concerning this embodiment. FIG. 3 is a schematic cross-sectional view along line III-III of FIG. 2; FIG. 4 is a perspective view for explaining an oil return path and an exhaust port provided in a cylinder; FIG. 4 is a perspective view showing a state in which dimples are formed as an example of uneven shapes on the inner peripheral surface of the shell case that forms the circumferential passage. FIG. 4 is a perspective view showing a configuration in which a fan is attached to a rotor of a motor;

Hereinafter, embodiments of the present disclosure will be described in detail with reference to the drawings. In the specification and drawings, the same components or corresponding components are denoted by the same reference numerals, and redundant description will not be repeated. Also, in the drawings, the configuration may be omitted or simplified for convenience of explanation. At least part of the embodiment and each modification may be combined arbitrarily with each other.

<Configuration of heat pump hot water supply system>
As shown in FIG. 1 , heat pump hot water supply system 300 according to the present embodiment has heat pump unit (also referred to as HP unit) 100 and hot water storage unit 200 .

HP unit 100 includes a refrigerant circuit in which refrigerant circulates. The refrigerant circuit of HP unit 100 includes compressor 101 , water heat exchanger 102 , expansion valve 103 and air heat exchanger 104 . The compressor 101 sucks low-pressure gas refrigerant, compresses the gas refrigerant, and discharges it as high-pressure gas refrigerant (compressed refrigerant). A detailed configuration of the compressor 101 will be described later.

Water heat exchanger 102 acts as a condenser in HP unit 100 . The high-pressure gas refrigerant discharged from the compressor 101 is condensed by exchanging heat with water flowing through the hot water storage unit 200 in the water heat exchanger 102 . The expansion valve 103 decompresses and expands the high-pressure liquid refrigerant condensed in the water heat exchanger 102 . Air heat exchanger 104 acts as an evaporator in HP unit 100 . The low-pressure gas-liquid two-phase refrigerant decompressed by the expansion valve 103 evaporates by exchanging heat with the outside air sent from the blower 105 in the air heat exchanger 104 . The low-pressure gas refrigerant evaporated in air heat exchanger 104 is sucked into compressor 101 .

The hot water storage unit 200 includes a pump 201 and a hot water storage tank 202 . Pump 201 and hot water tank 202 are connected to water heat exchanger 102 in HP unit 100 . In other words, heat pump hot water supply system 300 includes a refrigerant circuit and a water circuit through which water circulates. A part of the water circuit is formed inside the water heat exchanger 102 of the HP unit 100 and another part of the water circuit is formed inside the pump 201 and the hot water tank 202 of the hot water storage unit 200 .

Pump 201 sends low-temperature water in hot water storage tank 202 to water heat exchanger 102 . Water heat exchanger 102 heats water in hot water storage unit 200 . The water sent from the hot water storage tank 202 to the water heat exchanger 102 is heated by exchanging heat with the high pressure gas refrigerant discharged from the compressor 101 . The water (hot water) heated by the water heat exchanger 102 is returned to the hot water storage tank 202 and stored in the hot water storage tank 202 .

Hot water storage unit 200 further includes a water supply pipe 203 , a hot water outlet pipe 204 and a water heater 205 . The water supply pipe 203 is connected to the hot water storage tank 202 and supplies water to the hot water storage tank 202 . Hot water outlet pipe 204 is connected to hot water storage tank 202 via water heater 205 . The heated water (hot water) in the hot water storage tank 202 is further heated by the water heater 205 as necessary and then output to the hot water outlet pipe 204 .

<Configuration of Compressor>
Next, the configuration of compressor 101 will be described with reference to FIGS. 2 to 4. FIG.

As shown in FIG. 2, the compressor 101 is, for example, a horizontal rotary compressor. In a horizontal rotary compressor, a central axis C of a rotating shaft 12, which will be described later, extends laterally (for example, horizontally). The compressor 101 has a compression mechanism section 1 , a case 2 and an electric motor section 3 .

Case 2 includes shell case 21 , first shell cover 22 , and second shell cover 23 . Shell case 21 has a cylindrical shape. The shell case 21 extends along the axial direction, and the internal space of the shell case 21 is open on one side and the other side in the axial direction. The first shell cover 22 closes one open end of the shell case 21 in the axial direction. The second shell cover 23 closes the other open end of the shell case 21 in the axial direction.

Case 2 has an internal space surrounded by shell case 21 , first shell cover 22 and second shell cover 23 . Specifically, the internal space of the case 2 is a space surrounded by the inner peripheral surface of the shell case 21 in the radial direction and sandwiched between the first shell cover 22 and the second shell cover 23 . be. The internal space of the case 2 accommodates the compression mechanism section 1 and the electric motor section 3 .

The compression mechanism portion 1 is configured to compress low-pressure gas refrigerant. The compression mechanism 1 is lubricated with lubricating oil. Compression mechanism portion 1 includes cylinder 13 , eccentric portion 12</b>B of rotating shaft 12 , first cylinder cover 14 , second cylinder cover 15 , and piston 16 .

The cylinder 13 has a cylindrical shape with a first through hole 13A. The first through hole 13A penetrates through the cylinder 13 . A cylinder chamber 11 is formed inside the first through hole 13A.

The rotating shaft 12 passes through the cylinder chamber 11 . The eccentric portion 12B of the rotary shaft 12 is arranged inside the first through hole 13A. The eccentric portion 12B protrudes from the outer circumference of the shaft portion 12A of the rotating shaft 12 . The central axis of the eccentric portion 12B is parallel to the central axis C of the shaft portion 12A and is eccentric with respect to the central axis C. The outer diameter of the eccentric portion 12B is larger than the outer diameter of the shaft portion 12A. A cylindrical piston 16 is fitted to the outer periphery of the eccentric portion 12B.

The rotary shaft 12 is provided so as to rotate around the central axis C. As shown in FIG. The piston 16 eccentrically rotates around the central axis C together with the eccentric portion 12B as the rotating shaft 12 rotates.

Hereinafter, the direction in which the central axis C of the rotating shaft 12 extends is simply referred to as the axial direction, the radial direction with respect to the central axis C is simply referred to as the radial direction, and the circumferential direction with respect to the central axis C is simply referred to as the circumferential direction. Compressor 101 is intended to be used with its axial direction aligned with the horizontal direction.

Each of the first cylinder cover 14 and the second cylinder cover 15 is arranged so as to sandwich the cylinder chamber 11 in the axial direction. The first cylinder cover 14 is in contact with one side surface of the cylinder 13 in the axial direction. The first cylinder cover 14 closes one open end of the first through hole 13A of the cylinder 13 . The second cylinder cover 15 is in contact with the other side surface of the cylinder 13 in the axial direction. The second cylinder cover 15 closes the other open end of the first through hole 13A of the cylinder 13 .

The first cylinder cover 14 and the second cylinder cover 15 sandwich the eccentric portion 12B and the piston 16, respectively, in the axial direction. The first cylinder cover 14 has a second through hole 14A through which the shaft portion 12A of the rotating shaft 12 is passed. The second cylinder cover 15 has a third through hole 15A through which the shaft portion 12A of the rotary shaft 12 is passed.

The cylinder chamber 11 is defined by a cylinder 13 , a first cylinder cover 14 , a second cylinder cover 15 and a piston 16 .

The cylinder 13 is fixed to a shell case 21 of the case 2 which will be described later. The first cylinder cover 14 and the second cylinder cover 15 are fixed to the cylinder 13 . The first cylinder cover 14 and the second cylinder cover 15 are not directly connected to the case 2 .

The electric motor unit 3 is, for example, a motor. The electric motor section 3 has a rotor 31 and a stator 32 . A stator 32 is fixed to the case 2 . The stator 32 has a main body made of, for example, a plurality of laminated electromagnetic steel sheets, and a coil wound around the main body. Rotor 31 is rotatable with respect to stator 32 . The rotor 31 has a main body made of, for example, laminated electromagnetic steel sheets, and magnets embedded in the main body. A shaft portion 12A of the rotating shaft 12 is fixed to the rotor 31 . The rotor 31 rotates around the central axis C of the rotating shaft 12 .

When the compressor 101 is driven, the electric motor section 3 causes current to flow through the coils to generate electromagnetic force. drives the piston 16 of

One end of the rotating shaft 12 is inserted into the recess 22B of the first shell cover 22 . The other end of rotating shaft 12 is inserted into recess 23B of second shell cover 23 . The recessed portion 22B is a recessed portion with respect to the inner surface 22A of the first shell cover 22 and does not penetrate the first shell cover 22. As shown in FIG. The recessed portion 23B is a recessed portion with respect to the inner surface 23A of the second shell cover 23 and does not penetrate the second shell cover 23. As shown in FIG. The rotating shaft 12 penetrates neither the first shell cover 22 nor the second shell cover 23 .

The inner peripheral surface of each of recesses 22B and 23B is in contact with the outer peripheral surface of rotating shaft 12 . The inner peripheral surface of each of the recesses 22B and 23B serves as a sliding surface that slides on the outer peripheral surface of the rotating shaft 12 while the rotating shaft 12 is rotating around the central axis C, and constitutes a slide bearing. Thereby, the rotary shaft 12 is supported by the first shell cover 22 and the second shell cover 23 so as to be rotatable around the central axis C. As shown in FIG.

The shell case 21 is formed with a path 21</b>A that connects the suction port 24 of the compressor 101 and the suction hole 13</b>B of the cylinder 13 . Path 21A is arranged above each of rotating shaft 12 and cylinder chamber 11 . One end of the path 21A is connected to the suction port 24 . The other end of the path 21A opens to the inner peripheral surface of the shell case 21 and is connected to the suction hole 13B that opens to the outer peripheral surface of the cylinder 13 . Low-pressure gas refrigerant sucked from the suction port 24 of the compressor 101 is guided to the cylinder chamber 11 through the path 21A and the suction hole 13B.

The internal space of the case 2 has a first space S1 and a second space S2. The first space portion S<b>1 is a space arranged between the compression mechanism portion 1 and the first shell cover 22 . The second space S<b>2 is a space arranged between the compression mechanism 1 and the second shell cover 23 . A part of each of the first space S1 and the second space S2 is provided so as to store lubricating oil.

As shown in FIG. 3 , the compression mechanism 1 further includes a discharge valve 17 and vanes (partition plates) 18 . The discharge valve 17 can open and close the discharge hole 13C. The discharge valve 17 closes the discharge hole 13C when the pressure in the cylinder chamber 11 is lower than a predetermined pressure. The discharge valve 17 opens the discharge hole 13C when the pressure in the cylinder chamber 11 reaches a predetermined pressure or higher.

The vane 18 divides the internal space of the cylinder chamber 11 into a suction chamber connected to the suction hole 13B and a compression chamber 11A connected to the discharge hole 13C. The vanes 18 are arranged to extend radially. A radially inner peripheral end of the vane 18 is pressed against the outer peripheral surface of the piston 16 . As a result, the vanes 18 move radially forward and backward with respect to the inner peripheral surface of the cylinder chamber 11 as the piston 16 rotates.

The cylinder chamber 11 is connected to the circumferential passage CP through the discharge hole 13C. The circumferential passage CP is arranged between the outer peripheral portion 13OS of the compression mechanism portion 1 and the inner wall 21IS of the case 2 . An exhaust port 13E is connected to the circumferential passage CP. The exhaust port 13E is a portion that exhausts the compressed refrigerant in the circumferential passage CP to the outside of the circumferential passage CP. Thus, the circumferential passage CP constitutes a path through which the compressed refrigerant discharged from the cylinder chamber 11 through the discharge hole 13C flows to the exhaust port 13E.

The circumferential passage CP has an arc portion that forms an arc when viewed from the axial direction of the rotating shaft 12 . The arc portion forms an arc around the central axis C, for example. The arc portion may form an arc with a point other than the central axis C as the center. Also, as the circular arc portion, a circular arc portion composed of one circular arc will be described, but the circular arc portion may be composed of a combination of a plurality of circular arcs.

The arc portion of the circumferential passage CP forms an arc of 180° or more around the central axis C, for example. Here, 180° or more means that the arc portion from the circumferential end of the discharge port 13C indicated by the dashed line L1 in FIG. is the angle θ formed with the center.

Further, the exhaust port 13E is located above the height position of the horizontal line L3 passing through the central axis C when viewed from the axial direction of the rotating shaft 12. As shown in FIG. Similarly, the discharge hole 13C is also positioned above the height position of the horizontal line L3.

Note that FIG. 3 shows a state in which the vane 18 is most retracted (moved to the outer peripheral side) with respect to the inner peripheral surface of the cylinder chamber 11 and the volume of the compression chamber 11A is the largest during the compression process.

As shown in FIG. 4, a recess 13D is arranged on the outer periphery of the cylinder 13. As shown in FIG. The recess 13</b>D forms a circumferential passage CP together with the inner wall of the case 2 . A recess may be arranged in the inner wall of the case 2 , and the recess may form the circumferential passage CP together with the outer peripheral surface of the cylinder 13 .

The exhaust port 13E includes an exhaust port 13EA arranged on one axial side of the recess 13D and an exhaust port 13EB arranged on the other axial side of the recess 13D. 2, the compressed refrigerant is discharged from the circumferential passage CP of the cylinder 13 toward the first shell cover 22, and the compressed refrigerant is discharged from the circumferential passage CP of the cylinder 13 toward the second shell cover 23. be.

As shown in FIG. 4, the cylinder 13 is provided with an oil return path 13F. The oil return path 13F penetrates the cylinder 13 from the end face 13S1 of the cylinder 13 on the first shell cover 22 side to the end face 13S2 on the second shell cover 23 side.

As shown in FIG. 2 , the oil return path 13F connects the first space S1 and the second space S2 inside the case 2 . As a result, lubricating oil can flow between the first space S1 and the second space S2 through the oil return path 13F.

As shown in FIG. 3, the cylinder chamber 11 has a circular shape when viewed from the axial direction of the rotating shaft 12 . When viewed from the axial direction, the central axis C of the shaft portion 12A of the rotary shaft 12 coincides with the center of the circular cylinder chamber 11, and the shaft portion 12A and the cylinder chamber 11 are concentric with each other.

The exhaust port 13E and the oil return path 13F are arranged on opposite sides of each other with respect to a horizontal line L3 passing through the center (center axis C) of the cylinder chamber 11 when viewed from the axial direction. Specifically, the exhaust port 13E is positioned above the horizontal line L3, and the oil return path 13F is positioned below the horizontal line L3.

In addition, when viewed from the axial direction, the oil return path 13F is located below the height position of the center of the cylinder chamber 11 (center axis C). Further, the exhaust port 13E is located above the center height position of the cylinder chamber 11 .

The lubricating oil that lubricates the compression mechanism 1 is not particularly limited, but includes, for example, at least one selected from the group consisting of ester oil, ether oil, alkylbenzene oil, and polyalkylene glycol oil.

Any material may be used for each of the first cylinder cover 14 and the second cylinder cover 15 as long as it can receive the compressive load. The material forming each of the first cylinder cover 14 and the second cylinder cover 15 may be a metal material, or may be a material having a lower strength than the metal material, such as a resin material. This is because each of the first cylinder cover 14 and the second cylinder cover 15 does not act as a bearing that receives a load perpendicular to the axial direction of the rotating shaft 12 .

Preferably, the material forming each of the first cylinder cover 14 and the second cylinder cover 15 includes synthetic resin having self-lubricating properties, such as polytetrafluoroethylene (PTFE) resin, polyphenylene sulfide (PPS) resin, poly At least one selected from the group consisting of ether sulfone (PES) resin and polyether ether ketone (PEEK) resin is included.

Preferably, the material forming the shell case 21 of the case 2 is a material with high thermal conductivity. A material forming the shell case 21 of the case 2 includes, for example, aluminum (Al). The material forming the shell case 21 of the case 2 is, for example, pure aluminum, an aluminum alloy, or the like.

<Operation in Compressor 101>
Next, operation of compressor 101 in the present embodiment will be described with reference to FIGS. 2 and 3. FIG.

As shown in FIG. 2, electromagnetic force is generated by supplying current to the coils of the stator 32 in the electric motor section 3 . This electromagnetic force causes the rotor 31 to rotate about the central axis C together with the rotating shaft 12 . As a result, the piston 16 rotates within the cylinder chamber 11 of the compression mechanism 1 via the eccentric portion 12B of the rotating shaft 12 .

On the other hand, the low-pressure gas refrigerant sucked from the suction port 24 of the compressor 101 is guided to the cylinder chamber 11 through the path 21A and the suction hole 13B.

As shown in FIG. 3 , the low-pressure gas refrigerant supplied into the cylinder chamber 11 is compressed by the swivel drive of the piston 16 . When the gas refrigerant is compressed and the pressure of the gas refrigerant in the compression chamber 11A reaches or exceeds a predetermined pressure, the discharge valve 17 opens the discharge hole 13C. When the discharge hole 13C is opened, compressed gas refrigerant (compressed refrigerant) is discharged from the compression chamber 11A through the discharge hole 13C to the circumferential passage CP.

The compressed refrigerant discharged to the circumferential passage CP moves circumferentially along the circumferential passage CP as indicated by the white arrows in FIG. 3 when viewed from the axial direction. The compressed refrigerant that has moved in the circumferential direction reaches the exhaust port 13E and is exhausted from the circumferential passage CP through the exhaust port 13E.

As the compressed refrigerant moves circumferentially along the circumferential passage CP, centrifugal force separates the lubricating oil from the compressed refrigerant. Therefore, the compressed refrigerant from which the lubricating oil has been separated is discharged from the exhaust port 13E. The lubricating oil separated from the compressed refrigerant may be discharged from the circumferential passage CP through holes provided in the cylinder 13 to at least one of the first space S1 and the second space S2.

<Modification>
Next, a modified example of the above embodiment will be described with reference to FIGS. 5 and 6. FIG.

As shown in FIG. 5, in the compressor of Modification 1, the inner wall of the case 2 forming the circumferential passage CP has an uneven shape. For example, recesses such as a plurality of dimples DP are arranged on an inner wall 21IS of the case 2 forming a circumferential passage CP of the shell case 21 . Each of the multiple dimples DP is, for example, a circular depression in the inner wall 21IS. The uneven shape of the inner wall of the case 2 forming the circumferential passage CP is not limited to the dimples DP, and may be recesses or protrusions of other shapes.

As shown in FIG. 6 , in the compressor of Modification 2, a fan 41 is attached to the rotor 31 of the electric motor section 3 . The fan 41 has a plurality of blades 41a and support plates 41b and 41c.

Each of the plurality of blades 41a extends from the central axis C side to the outer peripheral side centering on the central axis C. As shown in FIG. One axial end of each of the blades 41a is connected to the support plate 41b. The other axial end of each of the blades 41a is connected to the support plate 41c.

Each of the support plates 41b and 41c has an annular shape and a through hole in the center. The shaft portion 12A of the rotating shaft 12 is inserted through each through hole of the support plates 41b and 41c. Thereby, each of the support plates 41b and 41c is arranged concentrically with the shaft portion 12A.

The compressed refrigerant discharged from the compression mechanism section 1 is sprayed onto the blades 41 a of the fan 41 . For example, the compressed refrigerant discharged from the compression mechanism section 1 is guided to the blades 41a of the fan 41 through the copper pipe 42 and then sprayed onto the blades 41a of the fan 41 . The copper pipe 42 may be connected to the exhaust port 13E of the cylinder 13, for example. In this case, the copper pipe 42 is connected to the exhaust port 13EB on the side of the electric motor section 3 of the compression mechanism section 1, as shown in FIG.

Since the configuration of the compressors in Modifications 1 and 2 other than the above is substantially the same as the configuration of the compressor 101 in the embodiment shown in FIGS. and do not repeat the description.

<effect>
Next, effects of the present embodiment and modified examples 1 and 2 will be described.

As shown in FIG. 3, in the compressor 101 according to the above embodiment, the compressed refrigerant discharged from the cylinder chamber 11 of the compression mechanism portion 1 is discharged from the outer peripheral portion 13OS (bottom portion of the recessed portion 13D) of the compression mechanism portion 1. It is configured so as to pass through a circumferential passage CP between the inner wall 21IS of the case 2 and the inner wall 21IS. As the compressed refrigerant moves circumferentially along the circumferential passage CP, centrifugal force separates the lubricating oil from the compressed refrigerant. Therefore, it is possible to separate the lubricating oil and the compressed refrigerant with a small number of parts without adding parts.

In the compressor 101, as shown in FIG. 4, the outer periphery of the cylinder 13 is provided with a recess 13D forming a circumferential passage. By providing the recessed portion 13D in this manner, the circumferential passage CP can be configured between the outer peripheral portion 13OS of the compression mechanism portion 1 and the inner wall 21IS of the case 2 without adding any parts. Therefore, it is possible to separate the lubricating oil and the compressed refrigerant with a small number of parts.

In the compressor 101, as shown in FIGS. 2 to 4, the cylinder 13 is provided with an oil return path 13F. As a result, the lubricating oil can move between the first space S1 and the second space S2 inside the case 2 , so that the lubricating oil can be uniformly collected in the case 2 .

In the compressor 101 described above, as shown in FIG. located above the height of As a result, the height position of the exhaust port 13E can be separated from the oil surface of the lubricating oil in the case 2, thereby suppressing the lubricating oil from entering the circumferential passage CP through the exhaust port 13E.

In the compressor 101 described above, as shown in FIG. 3, the circumferential passage has an arc portion that forms an arc of 180° or more. This prevents lubricating oil from entering the circumferential passage CP from the oil pool in the case 2 through the exhaust port 13E.

In the compressor 101, the shell case 21 shown in FIG. 2 has a portion forming the circumferential passage CP, and at least the portion forming the circumferential passage CP is made of a material containing aluminum. Aluminum is a material with high thermal conductivity. This makes it easier for the case 2 to receive heat from the high-temperature compressed refrigerant, thereby improving the heat exchange efficiency between the case 2 and the compressed refrigerant. Therefore, the COP (Coefficient Of Performance) of the heat pump is improved.

In the compressor of Modification 1, as shown in FIG. 5, the inner wall 21IS of the case 2 forming the circumferential passage CP has an uneven shape. This unevenness (for example, dimples DP) increases the contact area between the compressed refrigerant and the inner wall of the case 2 in the circumferential passage CP. As a result, the case 2 more easily receives heat from the high-temperature compressed refrigerant, further improving the COP of the heat pump.

In the compressor of Modified Example 2, as shown in FIG. 6, the fan 41 is attached to the rotor 31 and is blown with the compressed refrigerant discharged from the compression mechanism section 1 . The blowing of the compressed refrigerant causes the fan 41 to rotate and apply rotational force to the rotating shaft 12 . As a result, the driving force of the rotating shaft 12 is improved, and the electric power supplied to the electric motor section 3 can be reduced, so that the COP of the heat pump is further improved.

Heat pump hot water supply system 300 shown in FIG. 1 has compressor 101 shown in FIGS. 2 to 6, so that lubricating oil and refrigerant can be separated with a small number of parts.

In the above description, a horizontal rotary compressor has been described as a compressor, but the compressor is not limited to a horizontal type and may be a vertical type. good.

It should be considered that the embodiments disclosed this time are illustrative in all respects and not restrictive. The scope of the present invention is indicated by the scope of the claims rather than the above description, and is intended to include all modifications within the scope and meaning equivalent to the scope of the claims.

Reference Signs List 1 compression mechanism portion 2 case 3 electric motor portion 11 cylinder chamber 11A compression chamber 12 rotating shaft 12A shaft portion 12B eccentric portion 13 cylinder 13A first through hole 13B suction hole 13C discharge hole 13D , 22B, 23B recessed portion 13E, 13EA, 13EB exhaust port 13F, 21A path 13S1, 13S2 end face 14 first cylinder cover 14A second through hole 15 second cylinder cover 15A third through hole 16 piston , 17 discharge valve, 18 vane, 21 shell case, 21IS inner wall, 22 first shell cover, 22A, 23A inner surface, 23 second shell cover, 24 suction port, 31 rotor, 32 stator, 41 fan, 41a blade , 41b, 41c support plate 42 copper pipe 100 unit 101 compressor 102 water heat exchanger 103 expansion valve 104 air heat exchanger 105 blower 200 hot water storage unit 201 pump 202 hot water storage tank 203 water supply pipe, 204 hot water outlet pipe, 205 water heater, 300 heat pump hot water supply system, C central axis, CP circumferential passage, DP dimple, L3 horizontal line, S1 first space, S2 second space.

Claims (9)

a compression mechanism having a cylinder chamber for compressing the refrigerant;
and a case housing the compression mechanism,
A compressor configured to allow compressed refrigerant discharged from the cylinder chamber of the compression mechanism portion to pass through a circumferential passage between an outer peripheral portion of the compression mechanism portion and an inner wall of the case. The compression mechanism section has a cylinder,
2. The compressor according to claim 1, wherein an outer circumference of said cylinder is provided with a recess forming said circumferential passage. The compressor according to claim 2, wherein said cylinder is provided with an oil return path. The compressor is a horizontal compressor,
The cylinder is provided with an exhaust port for exhausting the compressed refrigerant from the circumferential passage,
4. The compressor according to claim 3, wherein said oil return path is positioned below a height position of the center of said cylinder chamber, and said exhaust port is positioned above a height position of the center of said cylinder chamber. . The compressor according to any one of claims 1 to 4, wherein the circumferential passage has an arc portion that forms an arc of 180° or more. the case includes a shell case,
The compressor according to any one of claims 1 to 5, wherein said shell case has a portion forming said circumferential passage and is made of a material containing aluminum. The compressor according to any one of claims 1 to 6, wherein said inner wall of said case forming said circumferential passage has an uneven shape. an electric motor section having a stator fixed to the case and a rotor rotating with respect to the stator;
8. The compressor according to any one of claims 1 to 7, further comprising a fan attached to the rotor of the electric motor section and capable of blowing compressed refrigerant discharged from the compression mechanism section. A compressor according to any one of claims 1 to 8;
a condenser provided so that the compressed refrigerant discharged from the compressor exchanges heat with a heat medium;
A heat pump hot water supply system, comprising: a tank in which the heat medium heat-exchanged with the compressed refrigerant in the condenser is stored.

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