WO2019171508A1

WO2019171508A1 - Rotary compressor

Info

Publication number: WO2019171508A1
Application number: PCT/JP2018/008815
Authority: WO
Inventors: 祐策石部
Original assignee: 三菱電機株式会社
Priority date: 2018-03-07
Filing date: 2018-03-07
Publication date: 2019-09-12
Also published as: CN111788391A; JP6910534B2; JPWO2019171508A1; CN111788391B

Abstract

Provided is a rotary compressor according to the present invention comprising a first injection flow path for injecting a refrigerant into a first compression chamber, a second injection flow path for injecting a refrigerant into a second compression chamber, a first check valve provided in the first injection flow path, and a second check valve provided in the second injection flow path. In the first valve body of the first check valve, the pressure of the refrigerant present on the side farther from the first compression chamber than the first valve body in the first injection flow path acts in the direction to open the first injection flow path, and the pressure of the refrigerant in the first compression chamber acts in the direction to close the first injection channel. In the second valve body of the second check valve, the pressure of the refrigerant present on the side farther from the second compression chamber than the second valve body in the second injection flow path acts in the direction to open the second injection flow path, and the pressure of the refrigerant in the second compression chamber acts in the direction to close the second injection flow path.

Description

Rotary compressor

The present invention relates to a rotary compressor having a function of injecting (injecting) a refrigerant into a compression chamber.

Compressor compresses refrigerant sucked into the compression chamber from the suction port. As one of such compressors, a rotary compressor in which a rotary type compression mechanism is accommodated in a sealed container is known. In addition, for the purpose of improving the efficiency of the refrigeration cycle apparatus, a conventional rotary compressor includes a compressor in which an injection flow path communicating with the compression chamber at a position different from the suction port is provided in the compression mechanism section. . The injection flow path is connected to an injection pipe provided outside the rotary compressor. And the refrigerant | coolant supplied to the injection flow path from the inside of a refrigerant circuit via injection piping is injected (inject | pouring) into a compression chamber.

Further, a compressor having a compression mechanism having two compression chambers is also known as a conventional rotary compressor. Hereinafter, a rotary compressor in which the compression mechanism unit has two compression chambers will be referred to as a twin rotary compressor. Even in a conventional twin rotary compressor, there is a compressor in which an injection flow path is provided in a compression mechanism section. In the case of a twin rotary compressor, the injection flow path communicates with each of the two compression chambers. That is, the refrigerant supplied from the refrigerant circuit to the injection flow path via the injection pipe is injected into each of the two compression chambers.

Here, since the dead volume is in the injection pipe and the injection flow path, the compression efficiency of the compressor is lowered. The dead volume is a space where the refrigerant communicates with the compression chamber in the middle of compression, and is a space where the refrigerant flowing out of the compression chamber is re-expanded. Therefore, a conventional twin rotary compressor having an injection flow path in the compression mechanism section also includes a compressor having a check valve for restricting the flow of refrigerant flowing out of the compression chamber into the injection flow path. It has been proposed (see Patent Document 1). In other words, the twin rotary compressor described in Patent Document 1 includes a check valve that regulates the flow of the refrigerant flowing out of the compression chamber into the injection flow path inside the sealed container. That is, in the twin rotary compressor described in Patent Document 1, the injection flow path is closed by the check valve in a state where the refrigerant is not injected from the injection flow path into the compression chamber. Therefore, by providing the check valve in this manner, the space upstream of the check valve in the injection pipe and the injection flow path does not become dead volume, and thus it is possible to suppress a decrease in the compression efficiency of the compressor. . In addition, the upstream side of the check valve in the injection pipe and the injection flow path is a portion on the upstream side of the check valve in the refrigerant flow during the refrigerant injection in the injection pipe and the injection flow path. That is, the upstream side of the check pipe in the injection pipe and the injection flow path indicates a portion of the injection pipe and the injection flow path that is on the side farther from the compression chamber than the check valve.

JP 2013-36442 A

In the twin rotary compressor described in Patent Document 1, the check valve opens the injection flow path when the pressure of the refrigerant existing in the injection flow path portion on the upstream side of the check valve becomes equal to or higher than the specified pressure. The injection flow path and the compression chamber both communicate with each other. At this time, the check valve of the twin rotary compressor described in Patent Document 1 is configured such that when the pressure of the refrigerant existing in the injection flow path portion on the upstream side of the check valve becomes equal to or higher than the specified pressure, Open regardless of the refrigerant pressure. For this reason, in the twin rotary compressor described in Patent Document 1, when there is a compression chamber in which the pressure of the internal refrigerant is higher than that of the refrigerant upstream of the check valve among the two compression chambers, The refrigerant that is being compressed from the compression chamber leaks into the injection flow path. And the compression performance of a twin rotary compressor will fall by this refrigerant | coolant leak. That is, the conventional twin rotary compressor provided with an injection flow path in the compression mechanism section and a check valve in the injection flow path has a problem that the compression performance deteriorates due to refrigerant leakage from the compression chamber. .

The present invention has been made in order to solve the above-described problem, and is a twin rotary compressor having an injection flow path in a compression mechanism and a check valve in the injection flow path, and a refrigerant from a compression chamber It aims at proposing the twin rotary compressor which can suppress leakage more than before.

A rotary compressor according to the present invention includes a hermetic container and a rotary-type compression mechanism portion accommodated in the hermetic container, and the compression mechanism part sucks from the first suction port and the first suction port. A first compression chamber for compressing the refrigerant, a second suction port, a second compression chamber for compressing the refrigerant sucked from the second suction port, and the first compression chamber at a position different from the first suction port. A first injection flow path for injecting refrigerant into the first compression chamber, and the second compression chamber at a position different from the second suction port, and injecting the refrigerant into the second compression chamber. A second injection flow path; a first check valve provided in the first injection flow path for regulating the flow of refrigerant flowing from the first compression chamber to the first injection flow path; and the second injection flow On the road And a second check valve that regulates a flow of the refrigerant flowing out from the second compression chamber to the second injection flow path, the first check valve being provided in a reciprocating manner, A first valve body that opens and closes one injection flow path, and the first valve body includes a refrigerant that is present on a side farther from the first compression chamber than the first valve body in the first injection flow path. The pressure of the refrigerant acts in the direction to open the first injection flow path, and the pressure of the refrigerant in the first compression chamber acts in the direction to close the first injection flow path, and the second check valve Has a second valve body that is reciprocally movable and opens and closes the second injection flow path, and the second valve body includes the second valve body in the second injection flow path than the second valve body. 2 The pressure of the refrigerant existing on the side away from the compression chamber The second acts in the direction of opening the injection flow passage, the pressure of refrigerant in the second compression chamber, has a structure which acts in a direction to close the second injection channel.

The rotary compressor according to the present invention is a twin rotary compressor provided with an injection flow path in the compression mechanism and a check valve in the injection flow path. In the rotary compressor according to the present invention, the pressure of the refrigerant in the first compression chamber is higher than the pressure of the refrigerant existing on the side farther from the first compression chamber than the first valve body in the first injection flow path. Then, the first injection flow path and the first compression chamber are not communicated. In the rotary compressor according to the present invention, the pressure of the refrigerant in the second compression chamber is higher than the pressure of the refrigerant existing on the side farther from the second compression chamber than the second valve body in the second injection flow path. When the state is reached, the second injection flow path and the second compression chamber are not in communication with each other. Therefore, the rotary compressor which concerns on this invention can suppress the refrigerant | coolant leakage from a compression chamber rather than before.

It is a refrigerant circuit figure showing an example of the refrigerating cycle device provided with the rotary compressor concerning an embodiment of the invention. It is a longitudinal section showing a rotary compressor concerning an embodiment of the invention. FIG. 3 is a cross-sectional view taken along line AA in FIG. 2. FIG. 3 is a sectional view taken along line BB in FIG. It is a principal part enlarged view which shows the 1st injection flow path and 2nd injection flow path periphery of the rotary compressor which concerns on embodiment of this invention. It is a principal part enlarged view which shows the 1st injection flow path and 2nd injection flow path periphery of the rotary compressor which concerns on embodiment of this invention. It is a principal part enlarged view which shows the 1st injection flow path and 2nd injection flow path periphery of an example of the conventional rotary compressor. It is a principal part enlarged view which shows the 1st injection flow path and 2nd injection flow path periphery of another example of the conventional rotary compressor. It is a figure for demonstrating operation | movement of the 1st check valve and the 2nd check valve in the rotary compressor which concerns on embodiment of this invention. It is a principal part enlarged view which shows the 1st injection flow path and 2nd injection flow path periphery in another example of the rotary compressor which concerns on embodiment of this invention. It is a principal part enlarged view which shows the 1st injection flow path and 2nd injection flow path periphery in another example of the rotary compressor which concerns on embodiment of this invention.

Embodiment.
FIG. 1 is a refrigerant circuit diagram illustrating an example of a refrigeration cycle apparatus including a rotary compressor according to an embodiment of the present invention.
A refrigeration cycle apparatus 100 according to the present embodiment includes a rotary compressor 1, an evaporator 2, an expansion device 4, and a condenser 3.

The rotary compressor 1 compresses the sucked refrigerant into a high-temperature and high-pressure gaseous refrigerant. Details of the rotary compressor 1 will be described later. The evaporator 2 is, for example, a fin and tube heat exchanger, a microchannel heat exchanger, a shell and tube heat exchanger, a heat pipe heat exchanger, a double pipe heat exchanger, a plate heat exchanger, or the like. Can be configured. The evaporator 2 is connected to the discharge pipe 21 of the rotary compressor 1 and the expansion device 4 by a refrigerant pipe. When the high-temperature and high-pressure gaseous refrigerant discharged from the rotary compressor 1 flows through the refrigerant flow path of the evaporator 2, it dissipates heat to the heat exchange target such as air supplied to the evaporator 2 to condense, and the high-pressure liquid refrigerant Becomes a refrigerant.

The expansion device 4 can be constituted by, for example, an electric expansion valve capable of adjusting the flow rate of the refrigerant. The expansion device 4 is connected to the evaporator 2 and the condenser 3 by refrigerant piping. The expansion device 4 expands the high-pressure liquid refrigerant that has flowed out of the evaporator 2 into a low-temperature and low-pressure gas-liquid two-phase refrigerant. As the expansion device 4, a mechanical expansion valve or a capillary tube that employs a diaphragm for the pressure receiving portion can be applied.

Further, an injection pipe 5 is connected between the evaporator 2 and the expansion device 4. The injection pipe 5 is also connected to a first injection flow path 31 and a second injection flow path 32 described later of the rotary compressor 1. The rotary compressor 1 according to the present embodiment includes an injection pipe 6 connected to the first injection flow path 31 and the second injection flow path 32 outside the sealed container 8 described later. The injection pipe 5 is connected to the injection pipe 6. That is, the injection pipe 5 is connected to the first injection flow path 31 and the second injection flow path 32 via the injection pipe 6.

The condenser 3 is, for example, a fin and tube heat exchanger, a microchannel heat exchanger, a shell and tube heat exchanger, a heat pipe heat exchanger, a double pipe heat exchanger, a plate heat exchanger, or the like. Can be configured. The condenser 3 is connected to the expansion device 4 and the suction muffler 7 of the rotary compressor 1 by refrigerant piping. The low-temperature and low-pressure gas-liquid two-phase refrigerant that has flowed out of the expansion device 4 evaporates by being heated by a heat exchange target such as air supplied to the condenser 3 when flowing through the refrigerant flow path of the condenser 3. A refrigerant. This gaseous refrigerant is sucked into the rotary compressor 1 from the suction muffler 7. In addition, when the gas-liquid two-phase refrigerant flows out of the condenser 3, the suction muffler 7 separates into a gaseous refrigerant and a liquid refrigerant inside and performs a function of supplying the gaseous refrigerant to a compression mechanism unit 11 described later. Is.

FIG. 2 is a longitudinal sectional view showing a rotary compressor according to the embodiment of the present invention. 3 is a cross-sectional view taken along the line AA in FIG. 4 is a cross-sectional view taken along the line BB of FIG. 5 and 6 are enlarged views of the main part showing the vicinity of the first injection channel and the second injection channel of the rotary compressor according to the embodiment of the present invention.
In FIG. 5, the flow path in the first check valve 40 provided in the first injection flow path 31 is closed, and the flow path in the second check valve 50 provided in the second injection flow path 32. Indicates a closed state. FIG. 6 shows a flow path in the first check valve 40 provided in the first injection flow path 31 and a flow path in the second check valve 50 provided in the second injection flow path 32. Indicates the opened state. 3 and 4 are different from FIG. 2 in the positions of some components. This is to facilitate recognition of these configurations.

The rotary compressor 1 includes a first compression chamber 14a and a second compression chamber 15a as described later. That is, the rotary compressor 1 is a twin rotary compressor. The rotary compressor 1 includes a sealed container 8. Inside the sealed container 8 are housed a compression mechanism 11, a motor 9 that is a drive source of the compression mechanism 11, and a crankshaft 10 that transmits the driving force of the motor 9 to the compression mechanism 11.

The motor 9 includes a stator 9a and a rotor 9b. The stator 9 a is fixed to the inner peripheral surface of the sealed container 8. The rotor 9b is installed inside the stator 9a with a specified gap. A crankshaft 10 is fixed to the rotor 9b. That is, when the rotor 9b rotates, the crankshaft 10 also rotates together with the rotor 9b.

The compression mechanism 11 includes an upper bearing 12, a lower bearing 13, an upper cylinder 14, a lower cylinder 15, an intermediate plate 17, and the like. Specifically, the upper cylinder 14 has a substantially cylindrical first compression chamber 14a. The lower cylinder 15 has a substantially cylindrical second compression chamber 15a. An intermediate plate 17 is disposed between the upper cylinder 14 and the lower cylinder 15.

The upper bearing 12 is provided on the upper surface of the upper cylinder 14 and closes the upper opening of the first compression chamber 14a. That is, the first compression chamber 14 a of the upper cylinder 14 is secured by the upper bearing 12 and the intermediate plate 17. Moreover, the lower bearing 13 is provided in the lower surface part of the lower cylinder 15, and obstruct | occludes the lower opening of the 2nd compression chamber 15a. That is, the second compression chamber 15 a of the lower cylinder 15 is secured by the lower bearing 13 and the intermediate plate 17.

The crankshaft 10 passes through the upper bearing 12, the upper cylinder 14, the intermediate plate 17, the lower cylinder 15 and the lower bearing 13 that are sequentially stacked. The crankshaft 10 is rotatably supported by an upper bearing 12 and a lower bearing 13. Further, the crankshaft 10 is formed with a first eccentric portion 10a at a position corresponding to the first compression chamber 14a of the upper cylinder 14, and at a position corresponding to the second compression chamber 15a of the lower cylinder 15, the second eccentric portion 10b. Is formed. The first eccentric portion 10a is provided with a substantially cylindrical first piston 16a, and the second eccentric portion 10b is provided with a substantially cylindrical second piston 16b.

A first vane 24a is slidably provided on the upper cylinder 14. When the crankshaft 10 is rotated by the motor 9, the first piston 16a rotates in the first compression chamber 14a of the upper cylinder 14. At this time, the first vane 24a is urged toward the first piston 16a by a spring (not shown) so that the first vane 24a follows the outer peripheral portion of the first piston 16a. Similarly, the second cylinder 24 is slidably provided in the lower cylinder 15. When the crankshaft 10 is rotated by the motor 9, the second piston 16b rotates in the second compression chamber 15a of the lower cylinder 15. At this time, the second vane 24b is urged toward the second piston 16b by a spring (not shown) so that the second vane 24b follows the outer peripheral portion of the second piston 16b.

A first suction port 25a communicates with the first compression chamber 14a of the upper cylinder 14. The suction muffler 7 is connected to the first suction port 25a via the first suction pipe 27a. A first discharge port 26 a communicates with the first compression chamber 14 a of the upper cylinder 14. That is, when the first piston 16a rotates in the first compression chamber 14a of the upper cylinder 14, the refrigerant flowing into the suction muffler 7 is sucked into the first compression chamber 14a from the first suction port 25a. At this time, when the first piston 16a rotates in the first compression chamber 14a of the upper cylinder 14, the space surrounded by the first vane 24a and the outer peripheral surface of the first piston 16a in the first compression chamber 14a is The volume gradually decreases. Thereby, the refrigerant in the first compression chamber 14a is compressed. Then, the refrigerant compressed in the first compression chamber 14a is discharged from the first discharge port 26a.

It should be noted that the discharge side end of the first discharge port 26a opens, for example, in the flange portion of the upper bearing 12. In the present embodiment, the upper discharge muffler 18 is provided so as to cover the discharge side end of the first discharge port 26a. That is, the refrigerant discharged from the first discharge port 26 a once enters the upper discharge muffler 18 and is then discharged from the upper discharge muffler 18 into the internal space of the sealed container 8. By providing the upper discharge muffler 18, noise amplified by resonance in the internal space of the sealed container 8 can be reduced.

Similarly, the second suction port 25b communicates with the second compression chamber 15a of the lower cylinder 15. The suction muffler 7 is connected to the second suction port 25b via the second suction pipe 27b. Further, the second discharge port 26 b communicates with the second compression chamber 15 a of the lower cylinder 15. That is, when the second piston 16b rotates in the second compression chamber 15a of the lower cylinder 15, the refrigerant flowing into the suction muffler 7 is sucked into the second compression chamber 15a from the second suction port 25b. At this time, when the second piston 16b rotates in the second compression chamber 15a of the lower cylinder 15, the space surrounded by the second vane 24b and the outer peripheral surface of the second piston 16b in the second compression chamber 15a is The volume gradually decreases. Thereby, the refrigerant in the second compression chamber 15a is compressed. Then, the refrigerant compressed in the second compression chamber 15a is discharged from the second discharge port 26b.

It should be noted that the discharge side end of the second discharge port 26b opens, for example, in the flange portion of the lower bearing 13. In the present embodiment, the lower discharge muffler 19 is provided so as to cover the discharge side end of the second discharge port 26b. That is, the refrigerant discharged from the second discharge port 26 b once enters the lower discharge muffler 19, and then is discharged from the lower discharge muffler 19 to the internal space of the sealed container 8. By providing the lower discharge muffler 19, it is possible to reduce noise amplified by resonance of the internal space of the sealed container 8.

The refrigerant released into the internal space of the sealed container 8 passes between the stator 9a and the rotor 9b of the motor 9 and flows out from the discharge pipe 21 to the outside of the sealed container 8.

Incidentally, refrigeration oil is stored at the bottom of the sealed container 8. This refrigerating machine oil is supplied to each sliding part of the compression mechanism part 11. Each sliding portion of the compression mechanism 11 is, for example, between the crankshaft 10 and the first piston 16a, between the first piston 16a and the upper cylinder 14, between the first piston 16a and the intermediate plate 17, These are between the crankshaft 10 and the second piston 16 b, between the second piston 16 b and the lower cylinder 15, and between the second piston 16 b and the intermediate plate 17. By supplying refrigerating machine oil to each sliding part of the compression mechanism part 11, it can prevent that the components of the compression mechanism part 11 contact directly, and it can prevent that a component is damaged. Moreover, since the refrigerating machine oil seals the sliding part by supplying the refrigerating machine oil to each sliding part of the compression mechanism part 11, it is also possible to prevent refrigerant leakage from the sliding part. In the rotary compressor 1 according to the present embodiment, a passage (not shown) is formed in the crankshaft 10. Due to the rotation of the crankshaft 10, the refrigerating machine oil stored at the bottom of the hermetic container 8 is sucked into the flow path in the crankshaft 10 in the manner of a centrifugal pump, and the refrigerating machine oil flows to each sliding part of the compression mechanism 11. Supplied.

A part of the refrigerating machine oil supplied to each sliding portion of the compression mechanism unit 11 is discharged from the first compression chamber 14a and the second compression chamber 15a together with the compressed refrigerant. For this reason, the rotary compressor 1 according to the present embodiment includes an oil separator 20 in order to prevent the refrigeration oil from going out of the rotary compressor 1 from the discharge pipe 21. The oil separator 20 is fixed to the crankshaft 10 so that the refrigerant discharged from the first compression chamber 14a and the second compression chamber 15a blocks the flow path toward the discharge pipe 21. By providing the oil separator 20, the mixed fluid of the refrigerant and the refrigerating machine oil collides with the oil separator 20, the refrigerant and the refrigerating machine oil are separated, and the refrigerating machine oil can be returned to the bottom of the sealed container 8. For this reason, by providing the oil separator 20, it can suppress that refrigeration oil goes out of the rotary compressor 1 from the discharge piping 21. FIG.

Here, the compression mechanism 11 of the rotary compressor 1 according to the present embodiment includes an injection flow path for injecting a refrigerant into the first compression chamber 14a and the second compression chamber 15a. Specifically, the compression mechanism unit 11 includes a first injection flow path 31 and a second injection flow path 32.

The first injection flow path 31 is connected to the injection pipe 5 via the injection pipe 6 as described above. The first injection flow path 31 communicates with the first compression chamber 14a at a position different from the first suction port 25a. That is, the 1st injection flow path 31 is a flow path which injects the refrigerant | coolant supplied from the injection piping 5 to the 1st compression chamber 14a. In the present embodiment, the first injection flow path 31 is connected to the injection pipe 6, and a check valve installation portion 31a in which the first check valve 40 is provided, a recess 31b communicating with the check valve installation portion 31a, and In addition, a communication hole 31c that communicates the recess 31b and the first compression chamber 14a is provided. In the present embodiment, the first injection flow path 31 is formed in the upper bearing 12.

The first check valve 40 is provided in the check valve installation portion 31 a of the first injection flow path 31. That is, the first check valve 40 is provided in the sealed container 8. The first check valve 40 regulates the flow of the refrigerant flowing out from the first compression chamber 14a to the first injection flow path 31. The first check valve 40 includes a casing 41 and a first valve body 44 provided in the casing 41 so as to reciprocate. The first valve body 44 has, for example, a substantially cylindrical shape whose central axis is in the reciprocating direction. The first valve body 44 is formed with a first through hole 44a penetrating in the reciprocating direction. The casing 41 has, for example, a substantially cylindrical shape, and has an end portion 42 and an end portion 43 in the reciprocating direction of the first valve body 44.

The end portion 42 is an end portion disposed on the side farther from the first compression chamber 14 a than the first valve body 44 in the first injection flow path 31. In other words, in the refrigerant flow when the refrigerant is injected from the first injection flow path 31 to the first compression chamber 14 a, the end 42 is on the upstream side of the first valve body 44. The end portion 42 is formed with a through hole 42a. Therefore, the refrigerant in the injection pipe 5 flows into the casing 41 from the through hole 42a. The pressure of the refrigerant supplied from the injection pipe 5 to the first check valve 40 acts on the end of the first valve body 44 on the end 42 side. The through hole 42 a is disposed at a position that does not face the first through hole 44 a of the first valve body 44. For this reason, when the first valve body 44 comes into contact with the end portion 42, the through hole 42 a is closed by the first valve body 44. That is, when the first valve body 44 comes into contact with the end portion 42, the flow path in the first check valve 40 is closed. In other words, when the first valve body 44 comes into contact with the end portion 42, the first injection flow path 31 is closed.

The end portion 43 is an end portion that is disposed closer to the first compression chamber 14 a than the first valve body 44 in the first injection flow path 31. In other words, in the refrigerant flow when the refrigerant is injected from the first injection flow path 31 to the first compression chamber 14 a, the end 43 is on the downstream side of the first valve body 44. A through hole 43 a is formed in the end portion 43. Therefore, the pressure of the refrigerant in the first compression chamber 14a acts on the end portion on the end portion 42 side of the first valve body 44 through the communication hole 31c and the recess 31b. The through hole 43 a is disposed at a position facing the first through hole 44 a of the first valve body 44. For this reason, even if the first valve body 44 contacts the end portion 43, the through hole 43 a is not blocked by the first valve body 44. That is, even if the first valve body 44 contacts the end portion 43, the flow path in the first check valve 40 is not closed. In other words, even if the first valve body 44 contacts the end portion 43, the first injection flow path 31 is in an open state.

That is, the first valve body 44 opens and closes the first injection flow path 31. In the first valve body 44, the pressure of the refrigerant existing in the first injection flow path 31 on the side farther from the first compression chamber 14 a than the first valve body 44 opens the first injection flow path 31. Acts on direction. Further, the pressure of the refrigerant in the first compression chamber 14 a acts on the first valve body 44 in the direction in which the first injection flow path 31 is closed. Therefore, when the pressure of the refrigerant in the first compression chamber 14a is higher than the pressure of the refrigerant existing on the side farther from the first compression chamber 14a than the first valve body 44 in the first injection flow path 31, the first valve body 44 moves to the end 42 side of the casing 41. And the 1st valve body 44 contacts the edge part 42, and the 1st injection flow path 31 is closed. Further, when the pressure of the refrigerant in the first compression chamber 14a is lower than the pressure of the refrigerant existing on the side farther from the first compression chamber 14a than the first valve body 44 in the first injection flow path 31, the first valve body 44 moves to the end 43 side of the casing 41. That is, the 1st valve body 44 will be in the state which left | separated from the edge part 42, and will be in the state in which the 1st injection flow path 31 was opened.

Here, in the first valve body 44 according to the present embodiment, the first valve body 44 receives the pressure of the refrigerant existing on the side farther from the first compression chamber 14a than the first valve body 44 in the first injection flow path 31. The area of the 1 pressure receiving part 45 is larger than the area of the 2nd pressure receiving part 46 which receives the pressure of the refrigerant | coolant of the 1st compression chamber 14a. By configuring the first valve body 44 in this way, the movement of the first valve body 44 toward the end 43 is facilitated. That is, when the pressure of the refrigerant existing on the side farther from the first compression chamber 14a than the first valve body 44 in the first injection flow path 31 becomes higher than the pressure of the refrigerant in the first compression chamber 14a, the first The injection flow path 31 is easy to open.

Specifically, in the present embodiment, the first through hole 44a of the first valve body 44 has a diameter that decreases toward the first compression chamber 14a. In other words, the diameter of the first through hole 44a increases from the end 43 side toward the end 42 side. When the first through hole 44 a is formed in this manner, the second pressure receiving portion 46 becomes an end portion on the end portion 43 side of the first valve body 44. Further, the first pressure receiving portion 45 becomes an end portion on the end portion 42 side of the first valve body 44 and an inner peripheral surface of the first through hole 44a. Therefore, the area of the first pressure receiving part 45 can be made larger than the area of the second pressure receiving part 46.

Note that the configuration of the first check valve 40 is merely an example. For example, in the present embodiment, the diameter of the first through hole 44a of the first valve body 44 is smoothly reduced toward the first compression chamber 14a. Not limited to this, the first through hole 44a of the first valve body 44 may have a stepped diameter that decreases toward the first compression chamber 14a. Further, for example, the area of the first pressure receiving part 45 may be made larger than the area of the second pressure receiving part 46 by forming a convex part at the end of the first valve body 44 on the end part 42 side. Further, the configuration in which the area of the first pressure receiving portion 45 is larger than the area of the second pressure receiving portion 46 is not an essential configuration in the first check valve 40. In the first injection flow path 31, the pressure of the refrigerant existing on the side farther from the first compression chamber 14a than the first valve body 44 acts in the direction to open the first injection flow path 31, and the refrigerant in the first compression chamber 14a. If the pressure acts in the direction in which the first injection flow path 31 is closed, the configuration of the first check valve 40 may be changed as appropriate.

Also, the first injection flow path 31 described above is merely an example. For example, at least a part of the first injection flow path 31 may be formed in a component part of the compression mechanism unit 11 other than the upper bearing 12. Further, the arrangement position of the first check valve 40 is not limited to the above position. If the second injection flow path 32 is not joined between the end of the first injection flow path 31 on the first compression chamber 14a side and the first check valve 40, an arbitrary position of the first injection flow path 31 The first check valve 40 can be disposed at the end.

The second injection flow path 32 is connected to the injection pipe 5 via the injection pipe 6 as described above. The second injection flow path 32 communicates with the second compression chamber 15a at a position different from the second suction port 25b. That is, the 2nd injection flow path 32 is a flow path which injects the refrigerant | coolant supplied from the injection piping 5 to the 2nd compression chamber 15a. In the present embodiment, the second injection flow path 32 is connected to the injection pipe 6 and has a check valve installation portion 32a provided with the second check valve 50, a recess 32b communicating with the check valve installation portion 32a, and In addition, a communication hole 32c that communicates the recess 32b and the second compression chamber 15a is provided. In the present embodiment, the second injection flow path 32 is formed in the lower bearing 13.

The second check valve 50 is provided in the check valve installation portion 32 a of the second injection flow path 32. That is, the second check valve 50 is provided in the sealed container 8. The second check valve 50 regulates the flow of the refrigerant flowing out from the second compression chamber 15a to the second injection flow path 32. The second check valve 50 includes a casing 51 and a second valve body 54 provided in the casing 51 so as to freely reciprocate. The second valve body 54 has, for example, a substantially cylindrical shape whose central axis is in the reciprocating direction. The second valve body 54 is formed with a second through hole 54a penetrating in the reciprocating direction. The casing 51 has, for example, a substantially cylindrical shape, and has an end 52 and an end 53 in the reciprocating direction of the second valve body 54.

The end 52 is an end disposed on the side farther from the second compression chamber 15 a than the second valve body 54 in the second injection flow path 32. In other words, in the refrigerant flow when the refrigerant is injected from the second injection flow path 32 to the second compression chamber 15 a, the end 52 is upstream of the second valve body 54. The end 52 is formed with a through hole 52a. Therefore, the refrigerant in the injection pipe 5 flows into the casing 51 from the through hole 52a. The pressure of the refrigerant supplied from the injection pipe 5 to the second check valve 50 acts on the end of the second valve body 54 on the end 52 side. The through hole 52a is disposed at a position that does not face the second through hole 54a of the second valve body 54. For this reason, when the 2nd valve body 54 contacts the edge part 52, the through-hole 52a is obstruct | occluded by the 2nd valve body 54. FIG. That is, when the second valve body 54 comes into contact with the end 52, the flow path in the second check valve 50 is closed. In other words, the second injection flow path 32 is closed when the second valve body 54 comes into contact with the end portion 52.

The end portion 53 is an end portion that is disposed closer to the second compression chamber 15 a than the second valve body 54 in the second injection flow path 32. In other words, in the refrigerant flow when the refrigerant is injected from the second injection flow path 32 to the second compression chamber 15 a, the end portion 53 is on the downstream side of the second valve body 54. A through hole 53 a is formed in the end portion 53. Therefore, the pressure of the refrigerant in the second compression chamber 15a acts on the end of the second valve body 54 on the end 52 side via the communication hole 32c and the recess 32b. The through hole 53a is disposed at a position facing the second through hole 54a of the second valve body 54. For this reason, even if the second valve body 54 contacts the end portion 53, the through hole 53 a is not blocked by the second valve body 54. That is, even if the second valve body 54 contacts the end portion 53, the flow path in the second check valve 50 is not closed. In other words, even if the second valve body 54 contacts the end portion 53, the second injection flow path 32 is in an open state.

That is, the second valve body 54 opens and closes the second injection flow path 32. In the second valve body 54, the pressure of the refrigerant existing in the second injection flow path 32 on the side farther from the second compression chamber 15 a than the second valve body 54 opens the second injection flow path 32. Acts on direction. Further, the pressure of the refrigerant in the second compression chamber 15a acts on the second valve body 54 in the direction in which the second injection flow path 32 is closed. Therefore, when the pressure of the refrigerant in the second compression chamber 15a is higher than the pressure of the refrigerant existing on the side farther from the second compression chamber 15a than the second valve body 54 in the second injection flow path 32, the second valve body. 54 moves to the end 52 side of the casing 51. And the 2nd valve body 54 contacts the edge part 52, and the 2nd injection flow path 32 is closed. When the pressure of the refrigerant in the second compression chamber 15a is lower than the pressure of the refrigerant existing on the side farther from the second compression chamber 15a than the second valve body 54 in the second injection flow path 32, the second valve body 54 moves to the end 53 side of the casing 51. That is, the second valve body 54 is separated from the end 52, and the second injection flow path 32 is opened.

Here, in the second valve body 54 according to the present embodiment, the second valve body 54 receives the pressure of the refrigerant existing on the side farther from the second compression chamber 15a than the second valve body 54 in the second injection flow path 32. The area of the 3 pressure receiving part 55 is larger than the area of the 4th pressure receiving part 56 which receives the pressure of the refrigerant | coolant of the 2nd compression chamber 15a. By configuring the second valve body 54 in this manner, the movement of the second valve body 54 toward the end 53 is facilitated. That is, when the pressure of the refrigerant existing on the side farther from the second compression chamber 15a than the second valve body 54 in the second injection flow path 32 becomes higher than the pressure of the refrigerant in the second compression chamber 15a, the second The injection flow path 32 is easy to open.

Specifically, in the present embodiment, the diameter of the second through hole 54a of the second valve element 54 decreases toward the second compression chamber 15a. In other words, the diameter of the second through hole 54a increases from the end 53 side toward the end 52 side. When the second through hole 54 a is formed in this manner, the fourth pressure receiving portion 56 is an end portion on the end portion 53 side of the second valve body 54. Moreover, the 3rd pressure receiving part 55 becomes the edge part by the side of the edge part 52 of the 2nd valve body 54, and the internal peripheral surface of the 2nd through-hole 54a. Therefore, the area of the third pressure receiving part 55 can be made larger than the area of the fourth pressure receiving part 56.

Note that the configuration of the second check valve 50 is merely an example. For example, in the present embodiment, the diameter of the second through hole 54a of the second valve body 54 is smoothly reduced toward the second compression chamber 15a. Not only this but the 2nd through-hole 54a of the 2nd valve body 54 may become small in step shape as it goes to the 2nd compression chamber 15a. Further, for example, the area of the third pressure receiving part 55 may be made larger than the area of the fourth pressure receiving part 56 by forming a convex part at the end of the second valve body 54 on the end 52 side. Further, the configuration in which the area of the third pressure receiving portion 55 is larger than the area of the fourth pressure receiving portion 56 is not an essential configuration in the second check valve 50. In the second injection flow path 32, the pressure of the refrigerant existing on the side farther from the second compression chamber 15a than the second valve body 54 acts in the direction of opening the second injection flow path 32, and the refrigerant in the second compression chamber 15a. If the pressure acts in the direction in which the second injection flow path 32 is closed, the configuration of the second check valve 50 may be changed as appropriate.

Further, the above-described second injection flow path 32 is merely an example. For example, at least a part of the second injection flow path 32 may be formed in a component part of the compression mechanism unit 11 other than the lower bearing 13. Further, the arrangement position of the second check valve 50 is not limited to the above-described position. If the first injection flow path 31 is not joined between the end of the second injection flow path 32 on the second compression chamber 15a side and the second check valve 50, an arbitrary position of the second injection flow path 32 The second check valve 50 can be arranged in

Subsequently, the operation of the rotary compressor 1 according to the present embodiment will be described. Here, below, operation of the conventional twin rotary compressor in which the injection flow path is provided in the compression mechanism section will be described so that the effect of the rotary compressor 1 according to the present embodiment can be easily understood. And after that, operation | movement of the rotary compressor 1 which concerns on this Embodiment is demonstrated. Hereinafter, the conventional twin rotary compressor in which the injection flow path is provided in the compression mechanism section will be referred to as a conventional rotary compressor. Further, in the following description, when describing a conventional rotary compressor, each component of the conventional rotary compressor is denoted by reference numerals of the components of the rotary compressor 1 according to the present embodiment corresponding to these components. A reference numeral added with “200” is attached. For example, a reference numeral “217” is attached to an intermediate plate of a conventional rotary compressor.

FIG. 7 is an enlarged view of a main part showing the vicinity of a first injection flow path and a second injection flow path of an example of a conventional rotary compressor.
The first injection flow path 231 and the second injection flow path 232 of the conventional rotary compressor 201 shown in FIG. 7 are provided in the intermediate plate 217.

Specifically, the first injection flow path 231 includes a recess 231b and a communication hole 231c. The recess 231b is a place connected to the injection pipe 206. The communication hole 231c is a place where the recess 231b communicates with the first compression chamber 214a of the upper cylinder 214. The second injection flow path 232 includes a recess 231b and a communication hole 232c. The communication hole 232c is a place where the recess 231b communicates with the second compression chamber 215a of the lower cylinder 215. That is, the concave portion 231 b functions as a part of the first injection flow path 231 and also functions as a part of the second injection flow path 232. In other words, the first injection flow path 231 and the second injection flow path 232 merge at the recess 231b and branch off at the communication hole 231c and the communication hole 232c.

In the conventional rotary compressor 201 shown in FIG. 7 configured as above, the first compression chamber 214a is always in communication with the first injection flow path 231 and the injection pipe 206. For this reason, the refrigerant in the middle of compression in the first compression chamber 214a leaks into the first injection flow path 231 and the injection pipe 206. In the conventional rotary compressor 201 shown in FIG. 7, the second compression chamber 215a is always in communication with the second injection flow path 232 and the injection pipe 206. For this reason, the refrigerant being compressed in the second compression chamber 215a leaks into the second injection flow path 232 and the injection pipe 206.

Here, the inside of the first injection channel 231, the second injection channel 232, and the injection pipe 206 becomes dead volume. For this reason, the conventional rotary compressor 201 shown in FIG.

In the conventional rotary compressor 201 shown in FIG. 7, the first compression chamber 214a and the second compression chamber 215a are always in communication. For this reason, the refrigerant in the middle of compression leaks from the compression chamber having the higher refrigerant pressure to the compression chamber having the lower refrigerant pressure. For example, when the pressure of the refrigerant in the first compression chamber 214a is higher than the pressure of the refrigerant in the second compression chamber 215a, the first compression chamber 214a is moved from the first compression chamber 214a to the second compression chamber 215a as shown by an arrow in FIG. The refrigerant in the middle of compression leaks out in the compression chamber 214a. Also in this respect, the conventional rotary compressor 201 shown in FIG. 7 has a reduced refrigerant compression performance.

FIG. 8 is an enlarged view of a main part showing the vicinity of a first injection flow path and a second injection flow path of another example of a conventional rotary compressor.
A first injection flow path 231 of the conventional rotary compressor 201 shown in FIG. 8 is provided in the upper bearing 212. Specifically, the first injection flow path 231 includes a recess 231b and a communication hole 231c. The recess 231b is a place connected to the injection pipe 206. The communication hole 231c is a place where the recess 231b communicates with the first compression chamber 214a of the upper cylinder 214. Further, the second injection flow path 232 of the conventional rotary compressor 201 shown in FIG. 8 is provided in the lower bearing 213. Specifically, the second injection flow path 232 includes a recess 232b and a communication hole 231c. The recess 232b is a portion connected to the injection pipe 206. The communication hole 232c is a place where the recess 232b communicates with the second compression chamber 215a of the lower cylinder 215.

Further, in the first injection flow path 231 of the conventional rotary compressor 201 shown in FIG. 8, a first check valve 240 for regulating the flow of the refrigerant flowing out from the first compression chamber 214a to the first injection flow path 231 is provided. Is provided. Further, in the second injection flow path 232 of the conventional rotary compressor 201 shown in FIG. 8, a second check valve 250 for regulating the flow of the refrigerant flowing out from the second compression chamber 215a to the second injection flow path 232 is provided. Is provided. In the conventional rotary compressor 201 shown in FIG. 8, the first injection flow path 231 is closed by the first check valve 240 in a state where the refrigerant is not injected from the first injection flow path 231 into the first compression chamber 214 a. It is done. Further, in the conventional rotary compressor 201 shown in FIG. 8, the second injection flow path 232 has the second check valve 250 in the state where the refrigerant is not injected from the second injection flow path 232 into the second compression chamber 215a. It is closed with. For this reason, the conventional rotary compressor 201 shown in FIG. 8 can reduce dead volume.

However, as shown in FIG. 8, when the pressure of the refrigerant existing on the side farther from the first compression chamber 214a than the first check valve 240 becomes equal to or higher than the first check valve 240, The first injection flow path 231 is opened. In other words, the first check valve 240 is configured to open the first injection flow path 231 when the pressure of the refrigerant supplied from the injection pipe 206 becomes equal to or higher than the specified pressure. At this time, the first check valve 240 opens regardless of the refrigerant pressure in the first compression chamber 214a when the pressure of the refrigerant supplied from the injection pipe 206 becomes equal to or higher than the specified pressure. That is, when the pressure of the refrigerant supplied from the injection pipe 206 becomes equal to or higher than the specified pressure, even if the pressure of the refrigerant in the first compression chamber 214a is higher than the pressure of the refrigerant supplied from the injection pipe 206, the first reverse The stop valve 240 opens. In such a state, in the rotary compressor 201 shown in FIG. 8, the refrigerant being compressed in the first compression chamber 214a leaks from the first compression chamber 214a to the first injection flow path 231.

Similarly, when the pressure of the refrigerant existing on the side farther from the second compression chamber 215a than the second check valve 250 becomes equal to or higher than the specified pressure, the second check valve 250 has a second injection flow path 232. Is configured to open. In other words, the second check valve 250 is configured to open the second injection flow path 232 when the pressure of the refrigerant supplied from the injection pipe 206 becomes equal to or higher than the specified pressure. At this time, the second check valve 250 opens regardless of the refrigerant pressure in the second compression chamber 215a when the pressure of the refrigerant supplied from the injection pipe 206 becomes equal to or higher than the specified pressure. That is, when the pressure of the refrigerant supplied from the injection pipe 206 becomes equal to or higher than the specified pressure, even if the pressure of the refrigerant in the second compression chamber 215a is higher than the pressure of the refrigerant supplied from the injection pipe 206, the second reverse The stop valve 250 opens. In such a state, in the rotary compressor 201 shown in FIG. 8, the refrigerant being compressed in the second compression chamber 215a leaks from the second compression chamber 215a to the second injection flow path 232.

For this reason, the compression performance of the rotary compressor 201 shown in FIG. 8 also deteriorates due to refrigerant leakage from the compression chamber.

On the other hand, the first valve body 44 of the first check valve 40 according to the present embodiment is more first than the first valve body 44 in the pressure of the refrigerant in the first compression chamber 14a and the first injection flow path 31. It operates by the difference with the pressure of the refrigerant existing on the side away from the compression chamber 14a. That is, the first valve body 44 of the first check valve 40 according to the present embodiment operates by the difference between the refrigerant pressure in the first compression chamber 14 a and the refrigerant pressure supplied from the injection pipe 6. In addition, the second valve body 54 of the second check valve 50 according to the present embodiment has a second pressure higher than the second valve body 54 in the second compression passage 15 and the pressure of the refrigerant in the second compression chamber 15a. It operates by the difference with the pressure of the refrigerant existing on the side away from the compression chamber 15a. That is, the second valve body 54 of the second check valve 50 according to the present embodiment operates by the difference between the refrigerant pressure in the second compression chamber 15 a and the refrigerant pressure supplied from the injection pipe 6. Therefore, the first check valve 40 and the second check valve 50 have the pressure of the refrigerant in the first compression chamber 14a, the pressure of the refrigerant in the second compression chamber 15a, and the pressure of the refrigerant supplied from the injection pipe 6. The operation is as shown in FIG.

FIG. 9 is a diagram for explaining the operation of the first check valve and the second check valve in the rotary compressor according to the embodiment of the present invention.
As shown in FIG. 9, when the pressure of the refrigerant supplied from the injection pipe 6 is larger than the pressure of the refrigerant in the first compression chamber 14a, the first check valve 40 is opened. That is, the first injection flow path 31 is opened. Thereby, the refrigerant | coolant supplied to the 1st injection flow path 31 from the injection piping 6 is injected into the 1st compression chamber 14a. On the other hand, when the pressure of the refrigerant in the first compression chamber 14a is larger than the pressure of the refrigerant supplied from the injection pipe 6, the first check valve 40 is closed. That is, when the refrigerant in the middle of compression in the first compression chamber 14a is in a condition of leaking into the first injection flow path 31, the first injection flow path 31 is closed. For this reason, the rotary compressor 1 according to the present embodiment can suppress the refrigerant being compressed in the first compression chamber 14 a from leaking into the first injection flow path 31.

Further, as shown in FIG. 9, when the pressure of the refrigerant supplied from the injection pipe 6 is larger than the pressure of the refrigerant in the second compression chamber 15a, the second check valve 50 is opened. That is, the second injection flow path 32 is opened. Thereby, the refrigerant | coolant supplied to the 2nd injection flow path 32 from the injection piping 6 is injected into the 2nd compression chamber 15a. On the other hand, when the pressure of the refrigerant in the second compression chamber 15a is larger than the pressure of the refrigerant supplied from the injection pipe 6, the second check valve 50 is closed. That is, when the refrigerant that is being compressed in the second compression chamber 15a leaks into the second injection flow path 32, the second injection flow path 32 is closed. For this reason, the rotary compressor 1 according to the present embodiment can suppress the refrigerant being compressed in the second compression chamber 15a from leaking into the second injection flow path 32.

Note that, as described above, the first check valve 40 and the second check valve 50 shown in the present embodiment are examples. Finally, another example of the first check valve 40 and another example of the second check valve 50 are introduced in FIGS. 10 and 11.

FIGS. 10 and 11 are enlarged views of the main part showing the vicinity of the first injection flow path and the second injection flow path in another example of the rotary compressor according to the embodiment of the present invention.
In FIG. 10, the flow path in the first check valve 40 provided in the first injection flow path 31 is closed, and the flow path in the second check valve 50 provided in the second injection flow path 32. Indicates a closed state. FIG. 11 shows a flow path in the first check valve 40 provided in the first injection flow path 31 and a flow path in the second check valve 50 provided in the second injection flow path 32. Indicates the opened state.

The first check valve 40 shown in FIGS. 10 and 11 includes a spring 47 in addition to the configuration described in FIGS. 5 and 6. The spring 47 biases the first valve body 44 in a direction in which the flow path in the first check valve 40 is closed, in other words, in a direction in which the first injection flow path 31 is closed. That is, the spring 47 urges the first valve body 44 in a direction in which the pressure of the refrigerant in the first compression chamber 14 a acts on the first valve body 44. For this reason, in the first check valve 40 shown in FIGS. 10 and 11, the pressure of the refrigerant supplied from the injection pipe 6 corresponds to the urging force of the spring 47 with respect to the pressure of the refrigerant in the first compression chamber 14a. When it becomes only high, the 1st injection flow path 31 will be opened.

Similarly, the second check valve 50 shown in FIGS. 10 and 11 includes a spring 57 in addition to the configuration described in FIGS. 5 and 6. The spring 57 urges the second valve body 54 in a direction in which the flow path in the second check valve 50 is closed, in other words, in a direction in which the second injection flow path 32 is closed. That is, the spring 57 urges the second valve body 54 in a direction in which the pressure of the refrigerant in the second compression chamber 15 a acts on the second valve body 54. For this reason, in the second check valve 50 shown in FIGS. 10 and 11, the pressure of the refrigerant supplied from the injection pipe 6 corresponds to the urging force of the spring 57 with respect to the pressure of the refrigerant in the second compression chamber 15a. When it becomes only high, the 2nd injection flow path 32 will be opened.

As described above, the rotary compressor 1 according to the present embodiment includes the sealed container 8 and the rotary-type compression mechanism unit 11 accommodated in the sealed container 8. The compression mechanism unit 11 includes a first suction port 25a, a first compression chamber 14a, a second suction port 25b, a second compression chamber 15a, a first injection flow channel 31, a second injection flow channel 32, A first check valve 40 and a second check valve 50 are provided. The first compression chamber 14a is a compression chamber that compresses the refrigerant sucked from the first suction port 25a. The second compression chamber 15a is a compression chamber that compresses the refrigerant sucked from the second suction port 25b. The first injection flow path 31 is a flow path that communicates with the first compression chamber 14a at a position different from the first suction port 25a and injects refrigerant into the first compression chamber 14a. The second injection flow path 32 is a flow path that communicates with the second compression chamber 15a at a position different from the second suction port 25b and injects refrigerant into the second compression chamber 15a. The first check valve 40 is a check valve that is provided in the first injection flow path 31 and regulates the flow of the refrigerant that flows out from the first compression chamber 14 a to the first injection flow path 31. The second check valve 50 is a check valve that is provided in the second injection flow path 32 and restricts the flow of the refrigerant flowing out from the second compression chamber 15a to the second injection flow path 32. The first check valve 40 is provided so as to freely reciprocate and has a first valve body 44 that opens and closes the first injection flow path 31. In the first valve body 44, the pressure of the refrigerant existing on the side farther from the first compression chamber 14 a than the first valve body 44 in the first injection flow path 31 opens the first injection flow path 31. Act on. Further, the pressure of the refrigerant in the first compression chamber 14 a acts on the first valve body 44 in the direction in which the first injection flow path 31 is closed. The second check valve 50 is provided so as to freely reciprocate, and has a second valve body 54 that opens and closes the second injection flow path 32. In the second valve body 54, the pressure of the refrigerant existing on the side farther from the second compression chamber 15 a than the second valve body 54 in the second injection flow path 32 opens the second injection flow path 32. Act on. Further, the pressure of the refrigerant in the second compression chamber 15a acts on the second valve body 54 in the direction in which the second injection flow path 32 is closed.

The rotary compressor 1 configured as described above is a refrigerant in which the pressure of the refrigerant in the first compression chamber 14a exists on the side farther from the first compression chamber 14a than the first valve body 44 in the first injection flow path 31. When the pressure is higher than the first pressure, the first injection flow path 31 and the first compression chamber 14a are not in communication with each other. Further, in the rotary compressor 1 configured in this way, the pressure of the refrigerant in the second compression chamber 15a is on the side farther from the second compression chamber 15a than the second valve body 54 in the second injection flow path 32. When the pressure is higher than the pressure of the existing refrigerant, the second injection flow path 32 and the second compression chamber 15a are not communicated with each other. Therefore, the rotary compressor 1 according to the present embodiment can suppress refrigerant leakage from the first compression chamber 14a and the second compression chamber 15a as compared with the conventional case.
Moreover, since the rotary compressor 1 which concerns on this Embodiment is equipped with the 1st check valve 40 and the 2nd check valve 50 in the compression mechanism part 11, it can also reduce dead volume.
Therefore, the rotary compressor 1 according to the present embodiment has improved compression performance than before.

Here, when the refrigerant leaks from the first compression chamber 14a and the second compression chamber 15a, the refrigerating machine oil in the first compression chamber 14a and the second compression chamber 15a is also caused by the leaked refrigerant. 14a and the second compression chamber 15a leak out. For this reason, the rotary compressor 1 which concerns on this Embodiment which can suppress the refrigerant | coolant leakage from the 1st compression chamber 14a and the 2nd compression chamber 15a than before is freezing machine oil from the 1st compression chamber 14a and the 2nd compression chamber 15a. Can also be prevented from leaking out. Therefore, the rotary compressor 1 according to the present embodiment can also suppress a shortage of refrigerating machine oil in each sliding portion of the compression mechanism unit 11, and can also suppress a failure of the compression mechanism unit 11 from the prior art.

1 Rotary compressor, 2 evaporator, 3 condenser, 4 expansion device, 5 injection piping, 6 injection piping, 7 suction muffler, 8 sealed container, 9 motor, 9a stator, 9b rotor, 10 crankshaft, 10a second 1 eccentric part, 10b second eccentric part, 11 compression mechanism part, 12 upper bearing, 13 lower bearing, 14 upper cylinder, 14a first compression chamber, 15 lower cylinder, 15a second compression chamber, 16a first piston, 16b first 2 pistons, 17 intermediate plate, 18 upper discharge muffler, 19 lower discharge muffler, 20 oil separator, 21 discharge pipe, 24a first vane, 24b second vane, 25a first suction port, 25b second suction port, 26a second 1 discharge port, 26b 2nd discharge port, 27a 1st suction piping, 27b 2nd suction piping, 31 First injection flow path, 31a check valve installation part, 31b recess, 31c communication hole, 32 second injection flow path, 32a check valve installation part, 32b recess, 32c communication hole, 40 first check valve, 41 casing 42 end portion, 42a through hole, 43 end portion, 43a through hole, 44 first valve body, 44a first through hole, 45 first pressure receiving portion, 46 second pressure receiving portion, 47 spring, 50 second check valve , 51 casing, 52 end, 52a through hole, 53 end, 53a through hole, 54 second valve body, 54a second through hole, 55 third pressure receiving part, 56 fourth pressure receiving part, 57 spring, 100 refrigeration cycle Equipment, 201 Rotary compressor (conventional), 206 Injection piping (conventional), 212 Upper bearing (conventional), 213 Lower bearing (subordinate) ), 214 Upper cylinder (conventional), 214a First compression chamber (conventional), 215 Lower cylinder (conventional), 215a Second compression chamber (conventional), 217 Intermediate plate (conventional), 231 First injection flow path (conventional) 231b recess (conventional), 231c communication hole (conventional), 232 second injection flow path (conventional), 232b recess (conventional), 232c communication hole (conventional), 240 first check valve (conventional), 250 second Check valve (conventional).

Claims

A sealed container;
A rotary compression mechanism housed in the sealed container;
With
The compression mechanism is
A first inlet,
A first compression chamber for compressing refrigerant sucked from the first suction port;
A second inlet,
A second compression chamber for compressing the refrigerant sucked from the second suction port;
A first injection flow path communicating with the first compression chamber at a position different from the first suction port, and injecting a refrigerant into the first compression chamber;
A second injection flow path communicating with the second compression chamber at a position different from the second suction port and injecting a refrigerant into the second compression chamber;
A first check valve which is provided in the first injection flow path and regulates the flow of the refrigerant flowing out from the first compression chamber to the first injection flow path;
A second check valve which is provided in the second injection flow path and regulates the flow of the refrigerant flowing out from the second compression chamber to the second injection flow path;
With
The first check valve has a first valve body that is reciprocally movable and opens and closes the first injection flow path.
In the first valve body,
In the first injection flow path, the pressure of the refrigerant present on the side farther from the first compression chamber than the first valve body acts in the direction of opening the first injection flow path,
The refrigerant pressure in the first compression chamber is configured to act in the direction of closing the first injection flow path,
The second check valve has a second valve body that is reciprocally movable and opens and closes the second injection flow path.
In the second valve body,
In the second injection flow path, the pressure of the refrigerant existing on the side farther from the second compression chamber than the second valve body acts in the direction of opening the second injection flow path,
The rotary compressor which is the structure which the pressure of the refrigerant | coolant of a said 2nd compression chamber acts in the direction which closes the said 2nd injection flow path.
The first valve body is
The area of the first pressure receiving portion that receives the pressure of the refrigerant that exists on the side farther from the first compression chamber than the first valve body in the first injection flow path receives the pressure of the refrigerant in the first compression chamber. The rotary compressor according to claim 1, wherein the rotary compressor is larger than an area of the second pressure receiving portion.
The first valve body has a first through hole penetrating in a reciprocating direction of the first valve body,
The rotary compressor according to claim 2, wherein the first through hole has a diameter that decreases toward the first compression chamber.
The second valve body is
The area of the third pressure receiving portion that receives the pressure of the refrigerant that is present on the side farther from the second compression chamber than the second valve body in the second injection flow path receives the pressure of the refrigerant in the second compression chamber. The rotary compressor according to any one of claims 1 to 3, wherein the rotary compressor is larger than an area of the fourth pressure receiving portion.
The second valve body is formed with a second through hole penetrating in the reciprocating direction of the second valve body,
The rotary compressor according to claim 4, wherein the second through hole has a diameter that decreases toward the second compression chamber.