WO2019171508A1 - Compresseur rotatif - Google Patents

Compresseur rotatif Download PDF

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Publication number
WO2019171508A1
WO2019171508A1 PCT/JP2018/008815 JP2018008815W WO2019171508A1 WO 2019171508 A1 WO2019171508 A1 WO 2019171508A1 JP 2018008815 W JP2018008815 W JP 2018008815W WO 2019171508 A1 WO2019171508 A1 WO 2019171508A1
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WO
WIPO (PCT)
Prior art keywords
flow path
compression chamber
refrigerant
injection flow
valve body
Prior art date
Application number
PCT/JP2018/008815
Other languages
English (en)
Japanese (ja)
Inventor
祐策 石部
Original Assignee
三菱電機株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to PCT/JP2018/008815 priority Critical patent/WO2019171508A1/fr
Priority to JP2020504564A priority patent/JP6910534B2/ja
Priority to CN201880090508.1A priority patent/CN111788391B/zh
Publication of WO2019171508A1 publication Critical patent/WO2019171508A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/04—Heating; Cooling; Heat insulation

Definitions

  • 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.
  • a rotary compressor in which a rotary type compression mechanism is accommodated in a sealed container is known.
  • 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.
  • coolant supplied to the injection flow path from the inside of a refrigerant circuit via injection piping is injected (inject
  • a compressor having a compression mechanism having two compression chambers is also known as a conventional rotary compressor.
  • a rotary compressor in which the compression mechanism unit has two compression chambers will be referred to as a twin rotary compressor.
  • an injection flow path is provided in a compression mechanism section.
  • 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.
  • 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).
  • 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.
  • 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. .
  • 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.
  • 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.
  • 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.
  • 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 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 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.
  • 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.
  • 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.
  • 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.
  • 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
  • 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.
  • 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.
  • 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.
  • a mechanical expansion valve or a capillary tube that employs a diaphragm for the pressure receiving portion can be applied.
  • 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 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
  • This gaseous refrigerant is sucked into the rotary compressor 1 from the suction muffler 7.
  • 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.
  • 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.
  • 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.
  • the lower bearing 13 is provided in the lower surface part of the lower cylinder 15, and obstruct
  • 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
  • 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.
  • the first piston 16a rotates in the first compression chamber 14a of the upper cylinder 14.
  • 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.
  • the second cylinder 24 is slidably provided in the lower cylinder 15.
  • the second piston 16b rotates in the second compression chamber 15a of the lower cylinder 15.
  • 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.
  • the discharge side end of the first discharge port 26a opens, for example, in the flange portion of the upper bearing 12.
  • 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.
  • noise amplified by resonance in the internal space of the sealed container 8 can be reduced.
  • 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.
  • 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.
  • the discharge side end of the second discharge port 26b opens, for example, in the flange portion of the lower bearing 13.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • the rotary compressor 1 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.
  • the oil separator 20 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.
  • the compression mechanism 11 of the rotary compressor 1 includes an injection flow path for injecting a refrigerant into the first compression chamber 14a and the second compression chamber 15a.
  • 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
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • the first valve body 44 opens and closes the first injection flow path 31.
  • 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.
  • 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
  • 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
  • the first The injection flow path 31 is easy to open.
  • 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.
  • the second pressure receiving portion 46 becomes an end portion on the end portion 43 side of the first valve body 44.
  • 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.
  • the configuration of the first check valve 40 is merely an example.
  • the diameter of the first through hole 44a of the first valve body 44 is smoothly reduced toward the first compression chamber 14a.
  • the first through hole 44a of the first valve body 44 may have a stepped diameter that decreases toward the first compression chamber 14a.
  • 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.
  • 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.
  • 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.
  • the first injection flow path 31 described above is merely an 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.
  • 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
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • the second valve body 54 opens and closes the second injection flow path 32.
  • 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.
  • the 2nd valve body 54 contacts the edge part 52, and the 2nd injection flow path 32 is closed.
  • 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.
  • 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
  • the second The injection flow path 32 is easy to open.
  • the diameter of the second through hole 54a of the second valve element 54 decreases toward the second compression chamber 15a.
  • the diameter of the second through hole 54a increases from the end 53 side toward the end 52 side.
  • the fourth pressure receiving portion 56 is an end portion on the end portion 53 side of the second valve body 54.
  • 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.
  • the configuration of the second check valve 50 is merely an example.
  • the diameter of the second through hole 54a of the second valve body 54 is smoothly reduced toward the second compression chamber 15a.
  • 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.
  • 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.
  • 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.
  • 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.
  • the above-described second injection flow path 32 is merely an 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.
  • 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
  • the operation of the rotary compressor 1 according to the present embodiment will be described.
  • 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
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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 of the conventional rotary compressor 201 shown in FIG. 8 is provided in the lower bearing 213.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • the second check valve 250 has a second injection flow path 232. Is configured to open.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • the second valve body 54 of the second check valve 50 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.
  • the first check valve 40 is opened. That is, the first injection flow path 31 is opened.
  • coolant supplied to the 1st injection flow path 31 from the injection piping 6 is injected into the 1st compression chamber 14a.
  • the first check valve 40 is closed.
  • the rotary compressor 1 can suppress the refrigerant being compressed in the first compression chamber 14 a from leaking into the first injection flow path 31.
  • the second check valve 50 is opened. That is, the second injection flow path 32 is opened. Thereby, the refrigerant
  • 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.
  • first check valve 40 and the second check valve 50 shown in the present embodiment are examples.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • the rotary compressor 1 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.
  • 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.
  • 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.
  • 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.
  • the rotary compressor 1 which concerns on this Embodiment which can suppress the refrigerant

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

L'invention concerne un compresseur rotatif comprenant une première voie d'écoulement d'injection, permettant d'injecter un réfrigérant dans une première chambre de compression, une seconde voie d'écoulement d'injection, permettant d'injecter un réfrigérant dans une seconde chambre de compression, un premier clapet de non-retour, disposé dans la première voie d'écoulement d'injection et un second clapet de non-retour, disposé dans la seconde voie d'écoulement d'injection. Dans le premier corps de soupape du premier clapet de non-retour, la pression du réfrigérant présent sur le côté plus éloigné de la première chambre de compression que le premier corps de soupape dans la première voie d'écoulement d'injection agit dans le sens d'ouverture de la première voie d'écoulement d'injection et la pression du réfrigérant dans la première chambre de compression agit dans le sens de fermeture du premier canal d'injection. Dans le second corps de soupape du second clapet de non-retour, la pression du réfrigérant présent sur le côté plus éloigné de la seconde chambre de compression que le second corps de soupape dans la seconde voie d'écoulement d'injection, agit dans le sens d'ouverture de la seconde voie d'écoulement d'injection et la pression du réfrigérant dans la seconde chambre de compression agit dans le sens de fermeture de la seconde voie d'écoulement d'injection.
PCT/JP2018/008815 2018-03-07 2018-03-07 Compresseur rotatif WO2019171508A1 (fr)

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PCT/JP2018/008815 WO2019171508A1 (fr) 2018-03-07 2018-03-07 Compresseur rotatif
JP2020504564A JP6910534B2 (ja) 2018-03-07 2018-03-07 ロータリ圧縮機
CN201880090508.1A CN111788391B (zh) 2018-03-07 2018-03-07 旋转式压缩机

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2023037972A1 (fr) * 2021-09-10 2023-03-16 ダイキン工業株式会社 Compresseur et dispositif de climatisation

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JPH05133368A (ja) * 1991-11-12 1993-05-28 Matsushita Electric Ind Co Ltd 逆止弁装置を備えた２段圧縮冷凍装置
JPH1113664A (ja) * 1997-06-27 1999-01-19 Daikin Ind Ltd ロータリ圧縮機
JPH11107950A (ja) * 1997-10-06 1999-04-20 Matsushita Electric Ind Co Ltd 圧縮機のインジェクション装置
JPH11304037A (ja) * 1998-04-22 1999-11-05 Aisin Seiki Co Ltd バルブ
WO2018003016A1 (fr) * 2016-06-28 2018-01-04 三菱電機株式会社 Compresseur à spirale

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CN202117924U (zh) * 2011-06-13 2012-01-18 广东美芝制冷设备有限公司 冷媒喷射式旋转压缩机
CN205101227U (zh) * 2015-10-26 2016-03-23 艾默生环境优化技术(苏州)有限公司 旋转式压缩机构及包括该旋转式压缩机构的压缩机和系统

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH05133368A (ja) * 1991-11-12 1993-05-28 Matsushita Electric Ind Co Ltd 逆止弁装置を備えた２段圧縮冷凍装置
JPH1113664A (ja) * 1997-06-27 1999-01-19 Daikin Ind Ltd ロータリ圧縮機
JPH11107950A (ja) * 1997-10-06 1999-04-20 Matsushita Electric Ind Co Ltd 圧縮機のインジェクション装置
JPH11304037A (ja) * 1998-04-22 1999-11-05 Aisin Seiki Co Ltd バルブ
WO2018003016A1 (fr) * 2016-06-28 2018-01-04 三菱電機株式会社 Compresseur à spirale

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2023037972A1 (fr) * 2021-09-10 2023-03-16 ダイキン工業株式会社 Compresseur et dispositif de climatisation
JP2023040761A (ja) * 2021-09-10 2023-03-23 ダイキン工業株式会社 圧縮機、および、空気調和装置

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CN111788391B (zh) 2022-10-04
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JPWO2019171508A1 (ja) 2020-12-10

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