EP2497955B1 - Wärmepumpe, zweistufiger verdichter und verfahren für den betrieb einer wärmepumpe - Google Patents

Wärmepumpe, zweistufiger verdichter und verfahren für den betrieb einer wärmepumpe Download PDF

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Publication number
EP2497955B1
EP2497955B1 EP09851096.9A EP09851096A EP2497955B1 EP 2497955 B1 EP2497955 B1 EP 2497955B1 EP 09851096 A EP09851096 A EP 09851096A EP 2497955 B1 EP2497955 B1 EP 2497955B1
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EP
European Patent Office
Prior art keywords
low
stage compressor
stage
refrigerant
compressor portion
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EP09851096.9A
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English (en)
French (fr)
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EP2497955A4 (de
EP2497955A1 (de
Inventor
Masao Tani
Atsuyoshi Fukaya
Hiroyuki Nakagawa
Taro Kato
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Publication of EP2497955A4 publication Critical patent/EP2497955A4/de
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/06—Control using electricity
    • 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
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B25/00—Multi-stage pumps
    • 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
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
    • 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
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps
    • 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
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/02—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids specially adapted for several pumps connected in series or in parallel
    • 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
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/06—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids specially adapted for stopping, starting, idling or no-load operation
    • F04C28/065—Capacity control using a multiplicity of units or pumping capacities, e.g. multiple chambers, individually switchable or controllable
    • 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
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/28—Safety arrangements; Monitoring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • 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
    • F04C2240/00—Components
    • F04C2240/80—Other components
    • F04C2240/806—Pipes for fluids; Fittings therefor
    • 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
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/24—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • F04C28/26—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0401—Refrigeration circuit bypassing means for the compressor

Definitions

  • the present invention relates to a two-stage compressor including two compressor portions connected in series, and a heat pump apparatus employing a two-stage compressor.
  • the low-stage compressor portion compresses a refrigerant sucked from a heat pump cycle to a predetermined pressure (pressure to be reached).
  • the pressure to be reached is determined by setting the compressor chamber capacity of the low-stage compressor portion and the compressor chamber capacity of the high-stage compressor portion.
  • the high-stage compressor portion further compresses the refrigerant compressed by the low-stage compressor portion.
  • the refrigerant compressed by the high-stage compressor portion is discharged from the high-stage compressor portion to the internal space of the hermetically sealed container, and discharged from the hermetically sealed container to the heat pump cycle.
  • the compressor chamber capacity of the low-stage compressor portion and the compressor chamber capacity of the high-stage compressor portion determine the pressure to be reached in the low-stage compressor portion.
  • an over-compression state may undesirably occur where the refrigerant is compressed by compression of only the low-stage compressor portion to the discharge pressure at which the refrigerant is to be discharged to the heat pump cycle.
  • the compression of the high-stage compressor portion is a waste, and efficiency suffers.
  • the over-compression state tends to occur in a small-load state, e.g., heating operation is performed while the outer temperature is high. In other words, the over-compression state lowers the efficiency in a small-load state.
  • Patent Document 1 describes a two-stage compressor provided with a bypass route which connects a communication channel, where a refrigerant flows from a low-stage compressor portion to a high-stage compressor portion, to the discharge side space of the high-stage compressor portion.
  • a refrigerant in the communication channel bypasses the high-stage compressor portion and flows to the discharge side space of the high-stage compressor portion. This improves the efficiency in the over-compression state.
  • Patent Document 2 describes a heat pump apparatus provided with a release mechanism which returns part of a refrigerant compressed by a low-stage compressor portion to the suction side of the low-stage compressor portion.
  • the release mechanism is actuated, thus improving the efficiency of the compressor in a low-load state.
  • the refrigerant discharged from the low-stage compressor portion passes through a long, narrow communication channel and is discharged to the discharge side space of the high-stage compressor portion via the bypass route. While the refrigerant passes through the long, narrow communication path, a pressure loss is caused.
  • this two-stage compressor may be effective in avoiding a temporary over-compression state, it does not provide much effect in reducing the over-compression loss in a steady operation.
  • the discharge pressure is low, and accordingly the refrigerant gas has a large specific volume and a large volumetric quantity of flow. This causes a large pressure loss due to the insufficient flow channel area.
  • a heat pump apparatus comprises a main refrigerant circuit formed by connecting a compressor, a first heat exchanger, a first expansion mechanism, and a second heat exchanger sequentially with piping, the compressor including a low-stage compressor portion which compresses a refrigerant flowed therein, a high-stage compressor portion which further compresses the refrigerant compressed by the low-stage compressor portion, and a bypass mechanism which discharges the refrigerant compressed by the low-stage compressor portion and the high-stage compressor portion to the main refrigerant circuit when a necessary load as a quantity of heat needed to set a fluid which is to be heat-exchanged with the refrigerant flowing in the main refrigerant circuit in the first heat exchanger to have a predetermined temperature is higher than a first load predetermined, and discharges the refrigerant compressed by the low-stage compressor portion to the main refrigerant circuit while bypassing the high-stage compressor portion so that the refrigerant is not compressed by the high-stage compressor portion when the
  • the refrigerant compressed by the low-stage compressor portion when the load is low, the refrigerant compressed by the low-stage compressor portion is discharged to the main refrigerant circuit while bypassing the high-stage compressor portion so the refrigerant is not compressed by the high-stage compressor portion. This can decrease the over-compression loss which may occur in a low-load state.
  • a two-stage compressor 100 having a bypass port for bypassing a high-stage compressor portion will be described.
  • Fig. 1 is a plan view of the two-stage compressor 100 according to the first embodiment.
  • Fig. 2 is a sectional view taken along the line A - A' of Fig. 1 .
  • an intermediate connection pipe 51 portion is illustrated as a section taken along the line a -a'.
  • Fig. 5 is a sectional view taken along the line C - C' of Fig. 2 .
  • Fig. 6 is a sectional view taken along the line D - D' of Fig. 2 .
  • the two-stage compressor 100 includes, in a hermetically sealed container 1, an electric motor 2 having a stator 2a and a rotor 2b, the compressor mechanism portion 3 provided with two compressor portions, i.e., a low-stage compressor portion 10 and high-stage compressor portion 30, and a crank shaft 4.
  • a discharge pipe 5 is fitted in the upper portion of the hermetically sealed container 1.
  • the lower portion of the hermetically sealed container 1 forms a lubricating oil storage 6 where a lubricating oil is sealed.
  • the low-stage compressor portion 10 of the compressor mechanism portion 3 has a low-stage compression chamber 15 formed by a low-stage cylinder 11, a low-stage frame 14 which closes the upper side of the low-stage cylinder 11, and an intermediate partition 50 which closes the lower side of the low-stage cylinder 11.
  • the low-stage compressor portion 10 includes a low-stage rolling piston 12 which eccentrically rotates in the low-stage compression chamber 15, and a low-stage vane 13 (see Fig. 7 ) which partitions the low-stage compression chamber 15 into a suction side space and a discharge side space.
  • the suction pipe 8 is connected to a low-stage suction port 21 of the low-stage compression chamber 15.
  • the high-stage compressor portion 30 has a high-stage compression chamber 35, having a capacity smaller than that of the low-stage compression chamber 15, formed by a high-stage cylinder 31, a high-stage frame 34 which closes the lower side of the high-stage cylinder 31, and the intermediate partition 50 which closes the upper side of the high-stage cylinder 31.
  • the high-stage compressor portion 30 includes a high-stage rolling piston 32 which eccentrically rotates in the high-stage compression chamber 35, and a high-stage vane 33 (see Fig. 8 ) which partitions the high-stage compression chamber 35 into a suction side space and a discharge side space.
  • a low-stage discharge port 16 through which the low-stage compression chamber 15 communicates with the low-stage discharge space 20 is formed in the low-stage frame 14.
  • the low-stage discharge port 16 has a low-stage discharge valve 17 and low-stage valve stopper 18 attached using a rivet 28, thus forming a reed valve (see Fig. 6 ).
  • a high-stage discharge port 36 through which the high-stage compression chamber 35 communicates with the high-stage discharge space 40 is formed in the high-stage frame 34.
  • the high-stage discharge port 36 has a high-stage discharge valve 37 and high-stage valve stopper 38 attached using a rivet, thus forming a reed valve.
  • the low-stage cover 19 has a bypass port 23 through which the low-stage discharge space 20 communicates with a discharge pressure space 53 as the internal space of the hermetically sealed container 1.
  • the bypass port 23 has a bypass valve 24 and bypass valve stopper 25 attached using a rivet 29, thus forming a reed valve (see Fig. 5 ). This structure constitutes a bypass mechanism.
  • a discharge flow channel 52 is formed to extend through the high-stage frame 34, high-stage cylinder 31, intermediate partition 50, low-stage cylinder 11, low-stage frame 14, and low-stage cover 19 and allows the high-stage discharge space 40 and discharge pressure space 53 to communicate with each other.
  • the low-stage cover 19 is provided with an injector 60.
  • the injector 60 is connected to an injection pipe 61.
  • the electric motor 2 When electric power is supplied, the electric motor 2 operates.
  • the electric motor 2 and compressor mechanism portion 3 are connected to each other by the crank shaft 4, so power generated by the electric motor 2 is transmitted to the compressor mechanism portion 3 via the crank shaft 4.
  • the rotor 2b of the electric motor 2 rotates.
  • the crank shaft 4 inserted in the rotor 2b also rotates.
  • the crank shaft 4 rotates, the low-stage rolling piston 12 and high-stage rolling piston 32 in which the crank shaft 4 is inserted eccentrically rotate in the low-stage compression chamber 15 and high-stage compression chamber 35, respectively.
  • the eccentric rotation of the low-stage rolling piston 12 and high-stage rolling piston 32 compresses the refrigerant in the low-stage compressor portion 10 and high-stage compressor portion 30.
  • a low-pressure refrigerant flows into the suction muffler 7 from the outside.
  • the low-pressure refrigerant flowing in the suction muffler 7 is sucked into the low-stage compression chamber 15 through the suction pipe 8.
  • the sucked low-pressure refrigerant is compressed in the low-stage compression chamber 15 until its pressure reaches an intermediate pressure.
  • the pressure difference between the refrigerant in the low-stage compression chamber 15 and that in the low-stage discharge space 20 opens the low-stage discharge valve 17 to discharge the refrigerant in the low-stage compression chamber 15 through the low-stage discharge port 16 to the low-stage discharge space 20.
  • the intermediate pressure is a pressure determined by the ratio of the capacity of the suction chamber of the low-stage compression chamber 15 to the capacity of the suction chamber of the high-stage compression chamber 35.
  • the intermediate-pressure refrigerant discharged to the low-stage discharge space 20 is sucked into the high-stage compression chamber 35 through the intermediate connection pipe 51.
  • the sucked intermediate-pressure refrigerant is compressed in the high-stage compression chamber 35 until its pressure reaches a discharge pressure.
  • the pressure difference between the refrigerant in the high-stage compression chamber 35 and that in the high-stage discharge space 40 opens the high-stage discharge valve 37 to discharge the refrigerant in the high-stage compression chamber 35 through the high-stage discharge port 36 to the high-stage discharge space 40.
  • an injection refrigerant from the injection pipe 61 shown in Fig. 4 is injected into the low-stage discharge space 20 through the injector 60.
  • the injection refrigerant mixes with the intermediate-pressure refrigerant discharged from the low-stage compression chamber 15, and the mixture is compressed in the high-stage compressor portion 30.
  • an over-compression state may occur where the refrigerant is compressed by compression of only the low-stage compressor portion 10 to the discharge pressure.
  • the intermediate pressure of the refrigerant described above may undesirably become higher than the necessary discharge pressure.
  • the pressure difference between the refrigerant in the low-stage discharge space 20 and that in the discharge pressure space 53 opens the bypass valve 24, and the refrigerant in the low-stage discharge space 20 is discharged through the bypass port 23 to the discharge pressure space 53.
  • the refrigerant discharged from the low-stage compressor portion 10 to the low-stage discharge space 20 is not compressed by the high-stage compressor portion 30 but bypasses the high-stage compressor portion 30 and is discharged to the discharge pressure space 53.
  • the discharge pressure is obtained by compression of only the low-stage compressor portion 10. Compression by the high-stage compressor portion 30 is a waste. If the high-stage compressor portion 30 performs compression, the efficiency suffers. In the two-stage compressor 100, however, when the over-compression state occurs, the refrigerant compressed in the low-stage compressor portion 10 bypasses the high-stage compressor portion 30 and is discharged. This can suppress a loss (over-compression loss) accompanying an over-compression state.
  • the bypass port 23 is formed in the low-stage cover 19.
  • the refrigerant is discharged to the discharge pressure space 53 in the hermetically sealed container 1 through the bypass port 23 without passing through the intermediate connection pipe 51.
  • the refrigerant discharged to the discharge pressure space 53 through the bypass port 23 does not flow in the long, narrow intermediate connection pipe 51, it is free from compression loss. Consequently, over-compression loss can be suppressed effectively in normal operation.
  • the lower portion of the hermetically sealed container 1 forms the lubricating oil storage 6 where the lubricating oil is sealed.
  • the lubricating oil is supplied to the mechanical portion of the compressor mechanism portion 3.
  • an amount of lubricating oil sufficient to immerse at least the compressor portion (the low-stage compressor portion 10 in Fig. 2 ) positioned on the upper side is sealed.
  • the low-stage compressor portion is under the high-stage compressor portion, and accordingly the low-stage discharge space is under the low-stage compressor portion.
  • the low-stage cover is formed under the low-stage compressor portion.
  • the bypass port 23 is dipped in the lubricating oil.
  • the lubricating oil may enter the low-stage discharge space through the bypass port 23.
  • the bypass port cannot be formed in the low-stage cover.
  • the bypass port can be formed only in the narrow flow channel that connects the low-stage discharge space and the high-stage compressor portion, as in Patent Literature 1.
  • the low-stage compressor portion 10 is above the high-stage compressor portion 30, which is opposite to the conventional arrangement. Accordingly, the low-stage discharge space 20 is above the low-stage compressor portion 10, so that the low-stage cover 19 can be located at such a height that it will not be dipped in the lubricating oil. Consequently, the bypass port 23 can be formed in the low-stage cover 19.
  • the bypass port 23 is formed not in the intermediate connection pipe 51 but in the low-stage cover 19. This allows the bypass valve 24 to form a reed valve having a simple structure.
  • the bypass valve 24 can be a component of the same type as the low-stage discharge valve 17, and the bypass valve stopper 25 can be a component of the same type as the low-stage valve stopper 18. Since the number of types of the components is decreased, the cost can be suppressed. Since the structure of the bypass valve 24 is simplified, the assembly cost can also be suppressed.
  • the heat pump apparatus 101 equipped with the two-stage compressor 100 will be described.
  • Fig. 9 shows an example of a circuit configuration of a heat pump apparatus equipped with an injection circuit.
  • Fig. 10 is a Mollier diagram illustrating a state of a refrigerant in the heat pump apparatus 101 of Fig. 9 .
  • the horizontal axis indicates specific enthalpy and the vertical axis indicates refrigerant pressure.
  • the heat pump apparatus 101 includes a main refrigerant circuit formed by connecting the two-stage compressor 100, a heat exchanger 71 (second heat exchanger), a first expansion valve 72, a receiver 78, a third expansion valve 74, and a heat exchanger 76 (first heat exchanger) sequentially with piping.
  • the heat pump apparatus 101 also includes an injection circuit formed by connecting with piping a portion between the receiver 78 and third expansion valve 74 to the injection pipe 61 of the two-stage compressor 100.
  • the injection circuit is equipped with a second expansion valve 75 midway along the piping.
  • the heat pump apparatus 101 includes an internal heat exchanger 73 which exchanges the heat of the refrigerant in the main refrigerant circuit with the heat of the refrigerant in the injection circuit.
  • the heat pump apparatus 101 also includes a four-way valve 77 which changes the direction in which the refrigerant flows.
  • Heating operation in the description, indicates not only air heating in air conditioning but also water heating in hot water supply to provide hot water.
  • the high-temperature high-pressure gas refrigerant (a point 1 in Fig. 10 ) at the two-stage compressor 100 is discharged through the discharge pipe 5 of the two-stage compressor 100.
  • the high-temperature high-pressure gas refrigerant is then sent through the heat exchanger 71, as a condenser or a radiator, where the gas liquefies (a point 2 in Fig. 10 ).
  • the heat of the refrigerant increases the temperature of air or water to be used for air conditioning or hot water supply.
  • the liquid refrigerant from the heat exchanger 71 is sent through the first expansion valve 72 (a decompression mechanism) where the pressure of the liquid refrigerant is reduced, thereby turning into a two-phase gas-liquid refrigerant (a point 3 in Fig. 10 ).
  • the two-phase gas-liquid refrigerant from the first expansion valve 72 is sent through the receiver 78 where its heat is exchanged with the heat of a refrigerant to be sucked in the two-stage compressor 100, thereby cooled and liquefied (a point 4 in Fig. 10 ).
  • the flow of the liquid refrigerant in the receiver 78 is divided to the main refrigerant circuit on the side of the internal heat exchanger 73 and third expansion valve 74 and to the injection circuit on the side of the second expansion valve 75.
  • the liquid refrigerant in the main refrigerant circuit is sent through the internal heat exchanger 73 where its heat is exchanged with the heat of a two-phase gas-liquid refrigerant from the second expansion valve 75, where the pressure of the refrigerant in the injection circuit is reduced, and thereby the liquid refrigerant is further cooled (a point 5 in Fig. 10 ).
  • the liquid refrigerant cooled at the internal heat exchanger 73 is sent through the third expansion valve 74 (a decompression mechanism) where the pressure is reduced, and thereby the liquid turns into two-phase gas-liquid (a point 6 in Fig. 10 ).
  • the two-phase gas-liquid refrigerant from the third expansion valve 74 is sent through the heat exchanger 76 as an evaporator, where the gas-liquid refrigerant is heated (a point 7 in Fig. 10 ).
  • the heated refrigerant from the heat exchanger 76 is then sent through the receiver 78 where it is further heated (a point 8 in Fig. 10 ). Then, the heated refrigerant is sucked into the two-stage compressor 100 through the suction pipe 8.
  • the refrigerant flowing in the injection circuit is sent through the second expansion valve 75 (a decompression mechanism) where its pressure is reduced (a point 9 in Fig. 10 ), and then through the internal heat exchanger 73 for heat exchange (a point 10 in Fig. 10 ), as described earlier.
  • the two-phase gas-liquid refrigerant (an injection refrigerant) after heat exchange at the internal heat exchanger 73 flows without changing its phase in the low-stage discharge space 20 via the injection pipe 61 of the two-stage compressor 100.
  • the refrigerant flowing in the main refrigerant circuit and sucked in through the suction pipe 8 (the point 8 in Fig. 10 ) is compressed by the low-stage compressor portion 10 to have the intermediate pressure and heated (a point 11 in Fig. 10 ).
  • the heated and compressed refrigerant having the intermediate pressure and discharged to the low-stage discharge space 20 joins the injection refrigerant (the point 8 in Fig. 10 ) and cools (a point 12 in Fig. 10 ).
  • the cooled refrigerant (the point 12 in Fig. 10 ) is then compressed and heated by the high-stage compressor portion 30 to increase its temperature and pressure, and discharged to the discharge pressure space 53 via the discharge flow channel 52 (point 1 in Fig. 10 ).
  • the opening of the second expansion valve 75 is totally closed when the injection operation is not performed. More specifically, during injection operation, the second expansion valve 75 is set so that the size of its opening is larger than a predetermined size of opening. When the injection operation is not performed, the size of the opening of the second expansion valve 75 is set so that it is smaller than a predetermined size of opening. This may prevent the refrigerant from flowing into the injection pipe 61 of the two-stage compressor 100. In other words, all the amount of refrigerant passing through the heat exchanger 71, the first expansion valve 72, and the receiver 78 is sucked in the two-stage compressor 100 via the suction pipe 8.
  • the size of the opening of the second expansion valve 75 may be electronically controlled by a controller.
  • the controller is a microcomputer, for example.
  • the four-way valve 77 is set in a course indicated by broken lines during cooling operation.
  • the high-temperature high-pressure gas refrigerant (the point 1 in Fig. 10 ) at the two-stage compressor 100 is discharged through the discharge pipe 5 of the two-stage compressor 100.
  • the high-temperature high-pressure gas refrigerant is then sent through the heat exchanger 76, as a condenser or a radiator, where the gas liquefies by heat exchange (the point 2 in Fig. 10 ).
  • the liquid refrigerant from the heat exchanger 76 is then sent through the third expansion valve 74 where its pressure is reduced, and thereby turns into two-phase gas-liquid (the point 3 in Fig. 10 ).
  • the two-phase gas-liquid refrigerant from the third expansion valve 74 is then sent through the internal heat exchanger 73 where the gas-liquid refrigerant cools by heat exchange and thereby liquefies (the point 4 in Fig. 10 ).
  • the heat of the two-phase gas-liquid refrigerant from the third expansion valve 74 is exchanged with the heat of the two-phase gas-liquid refrigerant from the second expansion valve 75 (the point 9 in Fig. 10 ) where the pressure of the liquid refrigerant from the internal heat exchanger 73 is reduced.
  • the flow of the liquid refrigerant passed through the internal heat exchanger 73 (the point 4 in Fig. 10 ) is divided to the main refrigerant circuit on the receiver 78 side and the injection circuit on the internal heat exchanger 73 side.
  • the liquid refrigerant flowing in the main refrigerant circuit is sent through the receiver 78 where its heat is exchanged with the heat of the refrigerant to be sucked in the two-stage compressor 100, thereby further cooled (the point 5 in Fig. 10 ).
  • the cooled liquid refrigerant from the receiver 78 is then sent through the first expansion valve 72 where the pressure is reduced, and turns into two-phase gas-liquid (the point 6 in Fig. 10 ).
  • the two-phase gas-liquid refrigerant from the first expansion valve 72 is sent through the heat exchanger 71 as an evaporator to be heated by heat exchange (the point 7 in Fig. 10 ).
  • the refrigerant absorbs heat, thereby cooling air or water. This allows room air to be cooled, or water to be chilled or iced. This may also be used for refrigeration.
  • the heated refrigerant from the heat exchanger 71 is sent through the receiver 78 where it is further heated (the point 8 in Fig. 10 ), and then sucked in the two-stage compressor 100 via the suction pipe 8.
  • the refrigerant flowing in the injection circuit is sent through the second expansion valve 75 where the pressure is reduced (the point 9 in Fig. 10 ), and then heat-exchanged through the internal heat exchanger 73 (the point 10 in Fig. 10 ), as described earlier.
  • the two-phase gas-liquid refrigerant (the injection refrigerant) from the internal heat exchanger 73 flows without changing its phase into the low-stage discharge space 20 via the injection pipe 61 of the two-stage compressor 100.
  • the second expansion valve 75 is totally closed to stop the refrigerant from flowing into the injection pipe 61 of the two-stage compressor 100, like during heating operation.
  • the load refers to the necessary load as a quantity of heat needed to set the temperature of the fluid, the heat of which is be exchanged with the heat of the refrigerant flowing in the main refrigerant circuit in the heat exchanger 71, to a predetermined temperature.
  • the necessary load can be measured by referring to the outside temperature, the rotation frequency of the compressor, or the like as an index. Assume that a necessary load detector (not shown in the figure) detects the necessary load by detecting the outside temperature, the rotation frequency of the compressor, or the like.
  • the injection operation is performed during heating operation when the outside temperature is the same or below a predetermined temperature (e.g., 2°C) or when the rotation frequency of the compressor is the same or above a predetermined frequency (e.g., 60 Hz). Then, heating capacity may be enhanced when the outside temperature is low. This may result in achieving a heat pump apparatus having excellent performance in heating room air or water. In other cases where the injection operation is not needed, the second expansion valve 75 is totally closed, so the injection operation is not performed even during heating operation.
  • a predetermined temperature e.g., 2°C
  • a predetermined frequency e.g. 60 Hz
  • the bypass mechanism is actuated when the load decreases to reach an over-compression state. Then, the refrigerant compressed in the low-stage compressor portion 10 bypasses the high-stage compressor portion 30 so the refrigerant is not compressed by the high-stage compressor portion 30, and is discharged to the discharge pressure space 53, and then to the refrigerant circuit via the discharge pipe 5.
  • the heat pump apparatus 101 selectively performs the following control operations (1) to (3) in accordance with the intensity of the load.
  • a two-stage compressor 100 which has a mechanism in which a refrigerant in a suction muffler 7 is sucked into a high-stage compressor portion 30 by bypassing a low-stage compressor portion 10.
  • the two-stage compressor 100 is provided with a four-way valve 54 (selector portion) at a portion corresponding to a midway portion along a suction pipe 8 which connects the suction muffler 7 to a low-stage suction port 21 of the low-stage compressor portion 10 and a midway portion along an intermediate connection pipe 51 which connects an intermediate outflow port 22 of a low-stage cover 19 to a high-stage suction port 41 of the high-stage compressor portion 30.
  • a four-way valve 54 switch portion
  • the four-way valve 54 performs switching operation between a state (flow channels indicated by solid lines) in which the suction muffler 7 is connected to the low-stage suction port 21 and the intermediate outflow port 22 is connected to the high-stage suction port 41 and a state (flow channels indicated by broken lines) in which the suction muffler 7 is connected to the high-stage suction port 41 and the low-stage suction port 21 is connected to the intermediate outflow port 22.
  • the four-way valve 54 connects the suction muffler 7 to the low-stage suction port 21 and the intermediate outflow port 22 to the high-stage suction port 41 (the flow channels indicated by the solid lines) during normal operation.
  • the two-stage compressor 100 according to the second embodiment can compress the refrigerant with only the high-stage compressor portion 30 when the load is low and compression by both the low-stage compressor portion 10 and high-stage compressor portion 30 is not necessary.
  • the two-stage compressor 100 can have an improved compressor efficiency when the load is low.
  • the refrigerant flowing into the suction muffler 7 can be sucked by the high-stage compressor portion 30 directly without passing through the low-stage compressor portion 10. This eliminates preheat loss by the low-stage compressor portion 10.
  • the circulation amount of the refrigerant is adjusted by changing the rotation frequency of the electric motor in accordance with the load fluctuations of the heat pump apparatus. More specifically, when the load is low and the circulation amount of the refrigerant must be decreased, it is done so by decreasing the rotation frequency of the electric motor. When the load is large and the circulation amount of the refrigerant must be increased, it is done so by increasing the rotation frequency of the electric motor.
  • the compressor chamber capacity of the high-stage compressor portion 30 (the capacity of the high-stage compression chamber 35) is smaller than the compressor chamber capacity of the low-stage compressor portion 10 (the capacity of the low-stage compression chamber 15), as described in the first embodiment.
  • the electric motor of the compressor having the large compressor chamber capacity must have a lower rotation frequency than the rotation frequency of the electric motor of the compressor having the small compressor chamber capacity.
  • the electric motor of the two-stage compressor 100 when the refrigerant is to be compressed using mainly only the low-stage compressor portion 10, to obtain the same refrigerant circulation amount as that obtained when the refrigerant is to be compressed using only the high-stage compressor portion 30, the electric motor of the two-stage compressor 100 must have a lower rotation frequency because the compressor chamber capacity of the low-stage compressor portion 10 is larger.
  • the two-stage compressor 100 is switched between operation of compressing the refrigerant using mainly only the low-stage compressor portion 10 and operation of compressing the refrigerant using only the high-stage compressor portion 30 in accordance with how low the load is. More specifically, when the load is not very low, the four-way valve 54 is not switched but the bypass mechanism is actuated, so that the refrigerant is compressed using mainly only the low-stage compressor portion 10. When the load is very low, the four-way valve 54 is switched, and the refrigerant is compressed using only the high-stage compressor portion 30.
  • the rotation frequency must be lower than the rated rotation frequency.
  • the four-way valve 54 is switched so the refrigerant is compressed using only the high-stage compressor portion 30. Then, the rotation frequency of the electric motor can be increased to become close to the rated rotation frequency. Consequently, a higher efficiency can be obtained.
  • a two-stage compressor 100 will be described in which a refrigerant sucked in a high-stage compressor portion 30 is supplied to a low-stage back pressure chamber 26 of a low-stage vane 13 of a low-stage compressor portion 10.
  • Fig. 12 is a sectional view of a portion of a compressor mechanism portion 3 of the two-stage compressor 100 according to the third embodiment.
  • Fig. 13 is a view explaining the forces acting on the low-stage vane 13.
  • a pushing force "x" (vane centrifugal force) generated upon eccentric rotation of a low-stage rolling piston 12 acts on the low-stage vane 13 from the low-stage compression chamber 15 side toward the low-stage back pressure chamber 26 side.
  • a force "(Ps ⁇ a) + (Pc ⁇ b) + x" acts on the low-stage vane 13 from the low-stage compression chamber 15 side toward the low-stage back pressure chamber 26 side.
  • the refrigerant compressed by the low-stage compressor portion 10 and discharged to a low-stage discharge space 20 is sucked in the high-stage compression chamber 35 of the high-stage compressor portion 30 via an intermediate connection pipe 51 and the high-stage suction flow channel 42.
  • the refrigerant passes in the high-stage suction flow channel 42, it partly flows into the low-stage back pressure chamber 26 via the pressure inlet channel 55.
  • an intermediate-pressure refrigerant compressed in the low-stage compressor portion 10 flows into the low-stage back pressure chamber 26.
  • the pressure "Pv" of the refrigerant in the low-stage back pressure chamber 26 is not the intermediate pressure of the refrigerant discharged from the low-stage compressor portion 10, but the pressure obtained by enhancing the intermediate pressure by a value corresponding to the resistance of the intermediate connection pipe 51 which is generated as the refrigerant passes in the intermediate connection pipe 51.
  • the pressure "Pv" of the refrigerant in the low-stage back pressure chamber 26 is slightly higher than the intermediate pressure.
  • the low-stage compressor portion 10 compresses a low-pressure refrigerant to an intermediate pressure.
  • the pressure "Ps" of the suction refrigerant is the low pressure
  • the pressure "Pc” of the discharge refrigerant is the intermediate pressure.
  • the pressure "Pv" (the pressure slightly higher than the intermediate pressure) in the low-stage back pressure chamber 26 is higher than the pressure "Ps" (low pressure) or the pressure “Pc” (intermediate pressure) in the low-stage compression chamber 15.
  • the refrigerant flowing in a suction muffler 7 bypasses the low-stage compressor portion 10 and is sucked into the high-stage compression chamber 35 via the intermediate connection pipe 51 and high-stage suction flow channel 42. While the refrigerant passes in the high-stage suction flow channel 42, it partly flows into the low-stage back pressure chamber 26 via the pressure inlet channel 55. Accordingly, a low-pressure refrigerant flowing in the suction muffler 7 flows into the low-stage back pressure chamber 26. In other words, the pressure "Pv" in the low-stage back pressure chamber 26 is a low pressure.
  • the low-stage compressor portion 10 When the low-stage compressor portion 10 is bypassed, the low-stage compressor portion 10 does not suck the refrigerant through the suction muffler 7, and the refrigerant in the low-stage compressor portion 10 is the refrigerant circulating between the low-stage compression chamber 15 and low-stage discharge space 20. Thus, the same refrigerant is repeatedly compressed in the low-stage compressor portion 10. When, however, the refrigerant reaches a pressure higher than the discharge pressure, it is discharged to a discharge pressure space 53 via a bypass port 23. The pressure in the low-stage compression chamber 15 hence varies between the low pressure and the discharge pressure.
  • the pressure "Pv” (low pressure) in the low-stage back pressure chamber 26 is equal to or lower than the pressure "Ps" or “Pc” in the low-stage compression chamber 15.
  • the pressure "Pv” in the low-stage back pressure chamber 26 may occasionally become equal to the pressure in the low-stage compression chamber 15, it soon becomes lower than the pressure in the low-stage compression chamber 15.
  • the force “Fv” acting on the low-stage vane 13 becomes larger than 0 during normal operation.
  • the force “Fv” acting on the low-stage vane 13 can be decreased to be smaller than 0. More specifically, during normal operation, the force acting on the low-stage vane 13 from the low-stage back pressure chamber 26 side toward the low-stage compression chamber 15 side is set to be larger than the force acting from the low-stage compression chamber 15 side toward the low-stage back pressure chamber 26 side.
  • the low-stage vane 13 is pressed against the low-stage rolling piston 12 during normal operation. This means that the low-stage vane 13 follows the revolution of the low-stage rolling piston 12 well.
  • the low-stage vane 13 is hardly pressed against the low-stage rolling piston 12. Namely, the friction loss between the low-stage vane 13 and low-stage rolling piston 12 decreases.
  • a heat pump apparatus 101 equipped with the two-stage compressor 100 according to the third embodiment has a much better efficiency when the load is very low.
  • a two-stage compressor 100 which controls a torque to be generated in accordance with a necessary torque.
  • Fig. 14 is a graph showing torque fluctuations in an ordinary twin rotary compressor.
  • the twin rotary compressor is a compressor in which two compressor portions operate in parallel.
  • Fig. 15 is a graph showing torque fluctuations occurring when the two-stage compressor 100 according to the first embodiment performs normal operation.
  • the normal operation refers to an operation of sucking the refrigerant into the low-stage compressor portion 10 from the suction muffler 7. In this operation, the bypass valve 24 is closed and the refrigerant is not discharged via the bypass port 23.
  • Fig. 17 is a graph showing torque fluctuations occurring when the two-stage compressor 100 according to the second embodiment performs a high-stage direct suction operation.
  • the high-stage direct suction operation refers to an operation of switching the four-way valve 54 to the flow channels indicated by the broken lines in Fig. 11 so the refrigerant is sucked from the suction muffler 7 into the high-stage compressor portion 30.
  • the rotation torque fluctuations accompanying a change in crank angle of the crank shaft 4 in the two-stage compressor are larger than those in a twin rotary compressor. If the rotation torque accompanying the change in crank angle fluctuates greatly, the efficiency of the electric motor decreases and the vibration increases. In particular, a decrease in efficiency of the electric motor due to the large rotation torque fluctuations accompanying the change in crank angle affects the efficiency greatly adversely when the electric motor is operated at a low rotation frequency, that is, when the load is small. If the vibration increases, it produces noise and leads to a low reliability of the piping of the heat pump apparatus.
  • twin rotary compressor As the two compressor portions having the same compressor chamber capacities are arranged such that the phases of eccentricity of their rolling pistons are shifted from each other by 180°, their torques cancel each other. Therefore, in the twin rotary compressor, the torque fluctuations accompanying a change in crank angle are small, as shown in Fig. 14 .
  • the compression chamber capacity of the high-stage compressor portion 30 is smaller than that of the low-stage compressor portion 10, as described in the first embodiment.
  • the compression differs between the low-stage compressor portion 10 and the high-stage compressor portion 30. Consequently, the rotation torque fluctuations accompanying the change in crank angle in the two-stage compressor 100 are larger than those in the twin rotary compressor, as shown in Fig. 15 .
  • the rotation torque fluctuates greatly at a timing at which the refrigerant is discharged from the low-stage compression chamber 15 to the low-stage discharge space 20 and a timing at which the refrigerant is discharged from the high-stage compression chamber 35 to the high-stage discharge space 40.
  • the two-stage compressor 100 controls an electric motor 2 by a controller so that a torque (output torque) is generated in accordance with the necessary torque as the torque (load torque) needed for the operation.
  • This control operation suppresses the torque fluctuations.
  • the necessary torque can be determined from, e.g., the rotation frequency, a change in current, a change in vibration, and the crank angle of the compressor.
  • the controller determines the necessary torque from the rotation frequency and crank angle of the compressor.
  • the controller stores a table that records torques necessary for the respective rotation frequencies and crank angles of the compressor in advance in the memory.
  • the controller detects the rotation frequency and crank angle of the compressor and reads from the memory the necessary torque corresponding to the detected rotation frequency and crank angle of the compressor.
  • the controller then controls the electric motor 2 so that the readout necessary torque is generated.
  • the controller may perform learning control operation of learning necessary torques respectively corresponding to various indices such as the rotation frequency and crank angle of the compressor during operation, and control the torque based on the learned result.
  • the efficiency of the compressor can be further enhanced, and the vibration can be reduced.
  • the two-stage compressor 100 is a rotary two-stage compressor having the low-stage compressor portion 10 on the upper side and the high-stage compressor portion 30 on the lower side.
  • the bypass port 23 which communicates with the discharge pressure space 53, and the bypass valve 24 are formed in the low-stage cover 19 that forms the low-stage discharge space 20 of the low-stage compressor portion 10.
  • the suction pipe connected to the suction muffler 7, the suction pipe of the low-stage compressor portion 10, the discharge pipe of the low-stage compressor portion 10, and the suction pipe of the high-stage compressor portion 30 are connected to each other via the four-way valve 54, and the suction pipe connected to the suction muffler 7 communicates with the suction pipe of the high-stage compressor portion 30, so that the sucked refrigerant gas is sucked in the high-stage compressor portion 30 directly without flowing in the low-stage compressor portion 10.
  • the suction pressure of the high-stage compressor portion 30 is communicated to the low-stage back pressure chamber 26 of the low-stage compressor portion 10.
  • 1 hermetically sealed container; 2: electric motor; 2a: stator; 2b: rotor; 3: compressor mechanism portion; 4: crank shaft; 5: discharge pipe; 6: lubricating oil storage; 7: suction muffler; 8: suction pipe; 10: low-stage compressor portion; 11: low-stage cylinder; 12: low-stage rolling piston; 13: low-stage vane; 14: low-stage frame; 15: low-stage compression chamber; 16: low-stage discharge port; 17: low-stage discharge valve; 18: low-stage valve stopper; 19: low-stage cover; 20: low-stage discharge space; 21: low-stage suction port; 22: intermediate outflow port; 23: bypass port; 24: bypass valve; 25: bypass valve stopper; 26: low-stage back pressure chamber; 27: spring; 28, 29: rivet; 30: high-stage compressor portion; 31: high-stage cylinder; 32: high-stage rolling piston; 33: high-stage vane; 34: high-stage frame; 35: high-stage compression chamber; 36: high-

Claims (14)

  1. Zweistufen-Verdichter (100) für ein Kältemittel, umfassend:
    einen Niedrigstufe-Verdichterabschnitt (10), der ein über einen Ansauganschluss (21) in eine Verdichtungskammer (15) eingesaugtes Kältemittel verdichtet und das verdichtete Kältemittel über einen Ablassanschluss (16) ablässt;
    einen Niedrigstufe-Ablassabschnitt (19), der über dem Niedrigstufe-Verdichterabschnitt (10) ausgebildet ist und einen Ablassraum (20) bildet, in den das durch den Niedrigstufe-Verdichterabschnitt (10) verdichtete Kältemittel über den Ablassanschluss (16) abgelassen wird;
    eine Zwischenverbindungsleitung (51), aufweisend ein Ende, das mit dem Ablassraum (20) verbunden ist, der durch den Niedrigstufe-Ablassabschnitt gebildet ist;
    einen Hochstufe-Verdichterabschnitt (30), der mit dem anderen Ende der Zwischenverbindungsleitung (51) verbunden ist, und das in den Ablassraum (20) abgelassene Kältemittel über die Zwischenleitung in eine Verdichtungskammer (35) einsaugt und das Kältemittel verdichtet; und
    einen hermetisch abgedichteten Behälter (1) zum Bilden eines Innenraumes (53), der den Niedrigstufe-Verdichterabschnitt (10), den Hochstufe-Verdichterabschnitt (30) und den Niedrigstufe-Ablassabschnitt lagert und in den das durch den Hochstufe-Verdichterabschnitt (30) verdichtete Kältemittel abgegeben wird,
    der Niedrigstufe-Ablassabschnitt einen Bypassanschluss (23) aufweist, der den Ablassraum (20) mit dem Innenraum des hermetisch abgedichteten Behälters (1) verbindet, wobei der Bypassanschluss (23) mit einem Auf/Zu-Ventil (24) versehen ist, das sich öffnet, wenn das Kältemittel im Ablassraum (20) einen höheren Druck aufweist als ein Druck des Kältemittels im Innenraum,
    wobei der Hochstufe-Verdichterabschnitt (30) unter dem Niedrigstufe-Verdichterabschnitt (10) ausgebildet ist.
  2. Zweistufen-Verdichter (100) nach Anspruch 1, wobei
    der Ablassanschluss (16) des Niedrigstufe-Verdichterabschnitt s (10) mit einem Ein-/Aus-Ventil (17) versehen ist, das sich öffnet, wenn das Kältemittel in der Verdichtungskammer (15) des Niedrigstufe-Verdichterabschnitt s (10) einen höheren Druck aufweist als der Druck des Kältemittels im Ablassraum (20), und
    das Auf/Zu-Ventil (24), das an dem Bypassanschluss (23) des Niedrigstufe-Ablassabschnitts vorgesehen ist, eine Struktur aufweist, die mit der des Auf/Zu-Ventils (17), das an dem Ablassanschluss (16) des Niedrigstufe-Verdichterabschnitt s (10) vorgesehen ist, identisch ist.
  3. Zweistufen-Verdichter (100) nach Anspruch 2, wobei
    jedes von dem Auf/Zu-Ventil (17), das an dem Bypassanschluss (16) des Niedrigstufe-Verdichterabschnitt s (10) vorgesehen ist, und dem Auf/Zu-Ventil (24), das an dem Bypassanschluss (23) des Niedrigstufe-Ablassabschnitts vorgesehen ist, ein Membranventil umfasst.
  4. Zweistufen-Verdichter (100) nach Anspruch 1, ferner umfassend:
    einen Ansaugschalldämpfer (7), in den das Kältemittel von einer Außenseite strömt;
    eine Ansaugleitung (8), die den Ansaugschalldämpfer (7) mit dem Ansauganschluss (21) des Niedrigstufe-Verdichterabschnitt s (10) verbindet; und
    einen Schaltabschnitt (54), der einen selektiven Schaltvorgang durchführt zwischen einem Strömungskanal (42), entlang dem das in den Ansaugschalldämpfer (7) strömende Kältemittel in den Niedrigstufe-Verdichterabschnitt (10) von dem Ansauganschluss (21) über die Ansaugleitung (8) eingesaugt wird, und einem Strömungskanal (52), der einen mittleren Abschnitt der Ansaugleitung (8) mit einem mittleren Abschnitt der Zwischenverbindungsleitung (51) verbindet und veranlasst, dass das in den Ansaugschalldämpfer (7) strömende Kältemittel den Niedrigstufe-Verdichterabschnitt (10) umgeht, so dass das Kältemittel ohne Verdichtung durch den Niedrigstufe-Verdichterabschnitt (10) in den Hochstufe-Verdichterabschnitt (30) eingesaugt wird.
  5. Zweistufen-Verdichter (100) nach Anspruch 4, wobei
    der Schaltabschnitt einen selektiven Schaltvorgang durchführt zwischen einem Strömungskanal (42), der den Ansaugschalldämpfer (7) an dem Ansauganschluss (21) des Niedrigstufe-Verdichterabschnitt s (10) mit der Ansaugleitung (8) verbindet und den Niedrigstufe-Ablassabschnitt an dem Ansauganschluss (21) des Hochstufe-Verdichterabschnitts (30) mit der Zwischenverbindungsleitung (51) verbindet, und einem Strömungskanal (52), der einen mittleren Abschnitt der Ansaugleitung (8) mit einem mittleren Abschnitt der Zwischenverbindungsleitung (51) verbindet, um den Ansaugschalldämpfer (7) mit dem Ansauganschluss (21) des Hochstufe-Verdichterabschnitts (30) zu verbinden, und den Niedrigstufe-Ablassabschnitt mit dem Ansauganschluss (21) des Niedrigstufe-Verdichterabschnitt s (10) verbindet.
  6. Zweistufen-Verdichter (100) nach Anspruch 4, wobei die Verdichtungskammer (35) des Hochstufe-Verdichterabschnitts (30) eine Kapazität aufweist, die kleiner ist als eine Kapazität der Verdichtungskammer (15) des Niedrigstufe-Verdichterabschnitt s (10).
  7. Zweistufen-Verdichter (100) nach Anspruch 1, wobei
    der Niedrigstufe-Verdichterabschnitt (10) umfasst:
    eine Gegendruckkammer (26) und
    ein Leitblech (13), das auf Druckausübung durch einen Druck in der Gegendruckkammer (26) in Richtung der Verdichtungskammer (15) ragt und die Verdichtungskammer (15) in einen Raum auf einer Seite dem Ansauganschluss (21) und einen Raum auf einer Seite dem Ablassanschluss (16) unterteilt, und
    der Zweistufen-Verdichter (100) ferner einen Einströmkanal (42) umfasst, entlang dem ein Teil des in die Verdichtungskammer (35) des Hochstufe-Verdichterabschnitts (30) einzusaugenden Kältemittels in die am Niedrigstufe-Verdichterabschnitt (10) vorgesehene Gegendruckkammer (26) einströmt.
  8. Zweistufen-Verdichter (100) nach Anspruch 1, ferner umfassend:
    einen Elektromotor (2), der den Niedrigstufe-Verdichterabschnitt (10) und den Hochstufe-Verdichterabschnitt (30) antreibt; und
    eine Steuereinheit, die Betrieb des Elektromotors (2) steuert, um ein erforderliches Drehmoment zu erzeugen gemäß einem Drehmoment, das benötigt wird, um den Niedrigstufe-Verdichterabschnitt (10) und den Hochstufe-Verdichterabschnitt (30) anzutreiben.
  9. Zweistufen-Verdichter (100) nach Anspruch 1, ferner umfassend:
    eine Einspritzleitung (61), die mit einem Zwischenströmungskanal verbunden ist, der den Niedrigstufe-Verdichterabschnitt (10) und den Hochstufe-Verdichterabschnitt (30) verbindet und der durch den Niedrigstufe-Ablassabschnitt und die Zwischenverbindungsleitung (51) gebildet ist.
  10. Wärmepumpenvorrichtung (101), umfassend:
    einen Zweistufen-Verdichter (100) nach Anspruch 1, und
    einen Hauptkältemittelkreislauf, der durch Verbinden des Zweistufen-Verdichters (100), eines ersten Wärmetauschers (76), eines ersten Expansionsmechanismus (72) und eines zweiten Wärmetauschers (71) nacheinander mittels einer Leitung, gebildet ist.
  11. Wärmepumpenvorrichtung (101) nach Anspruch 10, ferner umfassend:
    einen Einspritzkreislauf, der gebildet ist durch Verbinden mittels einer Leitung eines Abschnitts zwischen dem ersten Wärmetauscher (76) und dem ersten Expansionsmechanismus im Hauptkältemittelkreislauf mit einer Einspritzleitung (61), die mit einem Zwischenströmungskanal verbunden ist, der den Niedrigstufe-Verdichterabschnitt (10) und den Hochstufe-Verdichterabschnitt (30) im Verdichter verbindet und der durch den Niedrigstufe-Ablassabschnitt und die Zwischenverbindungsleitung (51) gebildet ist, wobei der Einspritzkreislauf mit einem zweiten Expansionsmechanismus (75) in der Mitte entlang der Leitung ausgestattet ist; und
    eine Steuereinheit, die einen Steuerungsvorgang des Vergrößerns einer Öffnung des zweiten Expansionsmechanismus, der im Einspritzkreislauf vorgesehen ist, auf nicht weniger als eine vorherbestimmte Größe, wenn die erforderliche Last höher ist als eine zweite Last, die vorherbestimmt ist, höher zu sein als die erste Last, so dass ein Teil des Kältemittels, das im Hauptkältemittelkreislauf vom ersten Wärmetauscher (76) zum Expansionsmechanismus strömt, aus der Einspritzleitung (61) in den Zwischenströmungskanal des Verdichters über den Einspritzkreislauf eingespritzt wird.
  12. Wärmepumpenvorrichtung (101) nach Anspruch 10, ferner umfassend:
    einen Schaltabschnitt (54), der veranlasst, dass das aus dem Hauptkältemittelkreislauf strömende Kältemittel den Niedrigstufe-Verdichterabschnitt (10) umgeht, wenn die erforderliche Last geringer ist als eine dritte Last, die vorherbestimmt ist, geringer zu sein als die erste Last, so dass das Kältemittel ohne Kompression durch den Niedrigstufe-Verdichterabschnitt (10) in den Hochstufe-Verdichterabschnitt (30) eingesaugt wird.
  13. Verfahren des Betreibens einer Wärmepumpenvorrichtung (101) nach Anspruch 10,
    wobei das Verfahren umfasst:
    Ablassen eines durch den Niedrigstufe-Verdichterabschnitt (10) und den Hochstufe-Verdichterabschnitt (30) verdichteten Kältemittels in den Hauptkältemittelkreislauf, wenn eine erforderliche Last als eine Wärmemenge, die benötigt wird, um ein Fluid, das mit einem Kältemittel, das im Hauptkältemittelkreislauf im ersten Wärmetauscher (76) strömt, Wärme austauschen soll, einzustellen, um eine vorherbestimmte Temperatur aufzuweisen, höher ist als eine vorherbestimmte erste Last;
    Ablassen des durch den Niedrigstufe-Verdichterabschnitt (10) verdichteten Kältemittels in den Hauptkältemittelkreislauf durch Umgehen des Hochstufe-Verdichterabschnitts (30), so dass das Kältemittel durch den Hochstufe-Verdichterabschnitt (30) nicht verdichtet wird, wenn die erforderliche Last geringer ist als die erste Last; und
    Veranlassen des aus dem Hauptkältemittelkreislauf strömenden Kältemittels, den Niedrigstufe-Verdichterabschnitt (10) zu umgehen, wenn die erforderliche Last geringer ist als eine dritte Last, die vorherbestimmt ist, geringer zu sein als die erste Last, so dass das Kältemittel in den Hochstufe-Verdichterabschnitt (30), der eine Verdichtungskammer (35) mit einer Kapazität aufweist, die kleiner ist als eine Kapazität der Verdichtungskammer (15) des Niedrigstufe-Verdichterabschnitts (10), ohne Verdichtung durch den Niedrigstufe-Verdichterabschnitt (10) eingesaugt wird.
  14. Verfahren des Betreibens einer Wärmepumpenvorrichtung (101) nach Anspruch 13, wobei die Wärmepumpenvorrichtung (101) ferner einen Einspritzkreislauf umfasst, der gebildet ist durch Verbinden eines Abschnitts zwischen dem ersten Wärmetauscher (76) und dem ersten Expansionsmechanismus im Hauptkältemittelkreislauf mit einer Einspritzleitung (61), die mit einem Zwischenströmungskanal verbunden ist, der den Niedrigstufe-Verdichterabschnitt (10) und den Hochstufe-Verdichterabschnitt (30) im Verdichter verbindet,
    wobei das Verfahren des Betreibens einer Wärmepumpenvorrichtung (101) ferner umfasst:
    Einspritzen eines Teils des Kältemittels, das im Hauptkältemittelkreislauf vom ersten Wärmetauscher (76) zum Expansionsmechanismus strömt, vom Einspritzkreislauf zum Zwischenströmungskanal, wenn die erforderliche Last höher ist als eine zweite Last, die vorherbestimmt ist, höher zu sein als die erste Last.
EP09851096.9A 2009-11-06 2009-11-06 Wärmepumpe, zweistufiger verdichter und verfahren für den betrieb einer wärmepumpe Active EP2497955B1 (de)

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Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2601289B1 (de) * 2010-08-04 2017-07-12 Cellular Dynamics International, Inc. Neuprogrammierung immortalisierter b-zellen
JP2013001268A (ja) * 2011-06-17 2013-01-07 Nippon Soken Inc 車両用空調装置
JP5586537B2 (ja) * 2011-07-28 2014-09-10 三菱電機株式会社 ロータリ二段圧縮機
CN103375405A (zh) * 2012-04-26 2013-10-30 珠海格力电器股份有限公司 压缩机及具有其的空调系统和热泵热水器
JP2013245594A (ja) * 2012-05-24 2013-12-09 Mitsubishi Electric Corp 密閉形回転式冷媒圧縮機
CN104075493B (zh) * 2013-03-27 2016-08-03 特灵空调系统(中国)有限公司 排气温度可控制的压缩系统及其排气温度控制方法
US10267539B2 (en) 2014-02-17 2019-04-23 Carrier Corporation Hot gas bypass for two-stage compressor
CN106286573A (zh) * 2016-09-28 2017-01-04 珠海格力节能环保制冷技术研究中心有限公司 双级压缩机曲轴及双级压缩机
CN109595165A (zh) * 2017-09-30 2019-04-09 广东美芝制冷设备有限公司 高低压分割的多级压缩机
CN109595164A (zh) * 2017-09-30 2019-04-09 广东美芝制冷设备有限公司 压缩机
JP6943345B2 (ja) * 2018-09-18 2021-09-29 富士電機株式会社 多段圧縮機
CA3137384C (en) * 2019-08-23 2024-04-16 Guangdong Meizhi Compressor Co., Ltd. Rotary compressor and refrigeration cycle device
CN112197453B (zh) * 2020-10-26 2023-08-08 珠海格力节能环保制冷技术研究中心有限公司 压缩机、双压缩机串联热泵机组及其控制方法
CN113340031B (zh) * 2021-05-27 2023-04-07 广东芬尼克兹节能设备有限公司 一种co2热泵系统的控制方法及其控制系统、存储介质

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH01277695A (ja) * 1988-04-28 1989-11-08 Toshiba Corp ２シリンダ形ロータリコンプレッサ
JPH0211886A (ja) * 1988-06-29 1990-01-16 Toshiba Corp 冷凍サイクル装置
JP2812022B2 (ja) * 1991-11-12 1998-10-15 松下電器産業株式会社 バイパス弁装置を備えた多段気体圧縮機
JP3370026B2 (ja) * 1999-09-09 2003-01-27 三洋電機株式会社 ２段圧縮式ロータリコンプレッサ
JP2003021089A (ja) * 2001-07-03 2003-01-24 Kobe Steel Ltd ２段圧縮冷凍機およびその運転方法
JP4300726B2 (ja) * 2001-09-21 2009-07-22 パナソニック株式会社 回転式気体圧縮機
JP2004309012A (ja) * 2003-04-07 2004-11-04 Sanyo Electric Co Ltd 冷媒サイクル装置
JP2006161659A (ja) * 2004-12-07 2006-06-22 Hitachi Ltd 冷凍サイクル装置
EP2088388B1 (de) * 2008-02-06 2019-10-02 STIEBEL ELTRON GmbH & Co. KG Wärmepumpensystem

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

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WO2011055444A1 (ja) 2011-05-12
EP2497955A4 (de) 2018-01-24
EP2497955A1 (de) 2012-09-12
KR101280155B1 (ko) 2013-06-28
KR20120048039A (ko) 2012-05-14

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