EP2476973B9 - Dispositif à cycle de réfrigération - Google Patents

Dispositif à cycle de réfrigération Download PDF

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Publication number
EP2476973B9
EP2476973B9 EP09850230.5A EP09850230A EP2476973B9 EP 2476973 B9 EP2476973 B9 EP 2476973B9 EP 09850230 A EP09850230 A EP 09850230A EP 2476973 B9 EP2476973 B9 EP 2476973B9
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EP
European Patent Office
Prior art keywords
compressor
expander
refrigeration cycle
refrigerant
pressure
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Application number
EP09850230.5A
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German (de)
English (en)
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EP2476973B1 (fr
EP2476973A4 (fr
EP2476973A1 (fr
Inventor
Yusuke Shimazu
Keisuke Takayama
Masayuki Kakuda
Hideaki Nagata
Takeshi Hatomura
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Publication of EP2476973A1 publication Critical patent/EP2476973A1/fr
Publication of EP2476973A4 publication Critical patent/EP2476973A4/fr
Publication of EP2476973B1 publication Critical patent/EP2476973B1/fr
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Classifications

    • 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
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • 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
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/06—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point using expanders
    • 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
    • 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
    • F25B2400/0403—Refrigeration circuit bypassing means for the condenser
    • 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
    • F25B2400/14—Power generation using energy from the expansion of the refrigerant
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/26—Problems to be solved characterised by the startup of the refrigeration cycle
    • 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2501—Bypass valves

Definitions

  • the present invention relates to a refrigeration cycle apparatus recovering power by using an expander.
  • a refrigeration cycle apparatus as above is proposed, for example, that "has a structure in which a drive shaft of the other compressor is connected to an output shaft of an expansion mechanism.
  • a structure in which a bypass pipe is provided that connects a gas suction port and a gas discharge port and that bypasses the other compressor, the bypass pipe provided with a check valve that regulates the communication of a refrigerant from the gas discharge port to the gas suction port (refer to Patent Literature 1, for example).
  • a bypass pipe equalizes pressure between the discharge side pressure and the suction side pressure of the compressor. This facilitates the start up of the expander (expansion mechanism) and the compressor that is connected to this expander with a shaft.
  • FIG. 11 is an explanatory diagram of Patent Literature 1 illustrating a pressure change in the compression chamber of the compressor connected to the expander with a shaft.
  • the pressure in the compression chamber of the compressor changes during the process depicted by arrows in Fig. 11 .
  • the compressor is a positive displacement compressor, and, thus, the pressure increases in the inside. Therefore, in order to start up the compressor, a compression power amounting to the area C illustrated in Fig. 1 is needed. That is to say, even when the suction side and the discharge side of the compressor is bypassed, as illustrated in Patent Literature 1, a "negative power" will exist. Thus, in some cases, the "negative power" becomes larger than the "positive power” obtained in the expander, and a possibility of the expander not starting up arises.
  • the start up of expanders and compressors are influenced by the static friction acting on thrust bearings, radial bearings, and the like of the expanders and compressors.
  • This static friction is larger than the kinetic friction acting on the thrust bearings, radial bearings, and the like while the expanders and compressors are driven. Therefore, in order to start up expanders and compressors, a "positive power" overcoming the static friction acting on the thrust bearings, radial bearings, and the like of the expanders and compressors will also be required, and the start up of the expanders and the compressors become even more unstable.
  • refrigerant in a compression process is typically introduced into the back side of the oscillating scroll.
  • refrigerant in the expansion process is typically introduced into the back side of the oscillating scroll.
  • a driving source such as a motor will be needed to be rotated with a torque surpassing the jamming.
  • the driving source needs to be rotated slightly backwards. In any event, they are not reliable start up methods.
  • EP-A-1 411 309 discloses a refrigeration cycle apparatus according to he preamble of claim 1.
  • the present invention has been made to solve at least one of the above problems and an object of the invention is, in a refrigeration cycle apparatus recovering power with an expander, to obtain a refrigeration cycle apparatus that is capable of reliably starting up an expander compared to conventional refrigeration cycle apparatuses.
  • An refrigeration cycle apparatus includes a refrigerant circuit having the features of claim 1.
  • a refrigeration cycle apparatus is provided with a pressure regulating device that maintains the pressure on the discharge side of a second compressor lower than the pressure on the suction side of the second compressor at least until the second compressor is started up.
  • the refrigeration cycle apparatus is provided with an expander startup facilitating device that controls the density of the refrigerant flowing into the expander such that the pressure on the discharge side of the expander is lower than the pressure on the inlet side of the expander at least until the expander is started up. Accordingly, even when the expander is started up in a state in which a pressure difference is small between the inlet side and the outlet side of the expander, high-density refrigerant flowing into the expander can be prevented. Hence, the expander can be reliably started up compared to conventional refrigeration cycle apparatuses.
  • Fig. 1 is a refrigerant circuit diagram of a refrigeration cycle apparatus of Embodiment 1 of the invention.
  • a refrigeration cycle apparatus 1 uses carbon dioxide as a refrigerant and includes a first compressor 2, a second compressor 3, a radiator 4, an expander 5, and an evaporator 6 connected in order with a refrigerant piping. Further, a drive shaft of the second compressor 3 and a drive shaft of the expander 5 are connected with a shaft 7. Note that the radiator 4 and the evaporator 6 may be disposed in plural numbers.
  • the first compressor 2 is equipped with, for example, a motor that is driven with supply of electrical power, and is capable of driving independently.
  • the second compressor 3 is a positive displacement compressor and is driven by power recovered by the expander 5.
  • the expander 5 is a positive displacement expander and supplies the power recovered during the expansion of the refrigerant to the second compressor 3.
  • a fan 4a is provided that sends air (heat medium), which exchanges heat with the refrigerant flowing in the radiator 4, to the radiator 4.
  • a fan 6a is provided that sends air (heat medium), which exchanges heat with the refrigerant flowing in the evaporator 6, to the evaporator 6.
  • radiator 4 corresponds to a first heat exchanger in the invention.
  • evaporator 6 corresponds to a second heat exchanger in the invention.
  • Fan 4a corresponds to a heat medium sending device.
  • a check valve 10 and a bypass is also provided.
  • the check valve 10 is disposed between the radiator 5 and the expander 5, and regulates the refrigerant from flowing from the expander 5 to the radiator 4.
  • One end of the bypass 8 is connected between the first compressor 2 and the second compressor 3, and the other end is connected between the check valve 10 and the expander 5.
  • This bypass 8 is provided with an on-off valve 9 that closes and opens the bypass 8.
  • the refrigeration cycle apparatus 1 is disposed with a temperature sensor 21 on the discharge side of the second compressor 3, the temperature sensor 21 serving as a refrigerant temperature measuring device.
  • a controller 100 controls the rotation speed of the motor equipped in the first compressor 2, rotation speed of the fan 4a, rotation speed of the fan 6a, and the closing and opening of the on-off valve 9. This controller 100 also receives the detection value of the temperature sensor21.
  • Fig. 2 is a refrigerant circuit diagram showing the refrigerant flow during the steady state of the refrigeration cycle apparatus according to Embodiment 1 of the invention.
  • the on-off valve 9 is in a closed state. That is, in the steady state, the refrigerant is not allowed to flow in the bypass 8. Note that in Fig. 2 , piping in which the refrigerant flows is depicted with thick lines.
  • the refrigerant that has been compressed into a high-temperature middle-pressure refrigerant in the first compressor 2 is discharged from the first compressor 2.
  • This high-temperature middle-pressure refrigerant is compressed in the second compressor 3 into a high-temperature high-pressure state (supercritical state), and flows into the radiator 4.
  • the refrigerant that has flowed into the radiator 4 transfers heat to the air sent by the fan 4a and turns into a low-temperature high-pressure refrigerant.
  • This low-temperature high-pressure refrigerant passes through the first check valve 10 and flows into the expander 5.
  • the refrigerant that has flowed into the expander 5 is decompressed into a low-pressure refrigerant with low dryness.
  • the expander 5 recovers power. Then, the recovered power is supplied to the second compressor 3 through the shaft 7.
  • the low-pressure refrigerant with low dryness that has flowed out from the expander 5 flows into the evaporator 6.
  • the refrigerant that has flowed into the evaporator 6 receives heat from the air sent from the fan 6a and turns into a low-pressure refrigerant with high dryness or a low-pressure super-heated gas refrigerant.
  • the refrigerant that has flowed out of the evaporator 6 is sucked into the first compressor 2.
  • the refrigeration cycle apparatus 1 achieves energy saving.
  • Fig. 3 is a refrigerant circuit diagram showing the refrigerant flow during the start up of the refrigeration cycle apparatus of Embodiment 1 of the invention.
  • the on-off valve 9 is in an opened state. That is, in the start up, the refrigerant is allowed to flow in the bypass 8.
  • piping in which the refrigerant flows is depicted with thick lines.
  • the check valve 10 prevents the refrigerant flowing out of the bypass 8 to flow to the radiator 4 and the discharge side of the second compressor 3.
  • the pressure on the suction side of the second compressor 3 is the pressure of the refrigerant that has been discharged from the first compressor 2, which is higher than the pressure on the discharge side of the second compressor 3.
  • the pressure on the suction side of the second compressor 3 is higher than the pressure on the discharge side of the second compressor 3.
  • the time for the second compressor 3 to start up after the first compressor 2 has started up is a few seconds (with the refrigeration cycle apparatus 1 of Embodiment 1, about two to three seconds, for example). Accordingly, the refrigerant flowing in the discharge side of the second compressor 3 is stored in the radiator 4 (the radiator 4 serving as a buffer), and therefor the pressure rise on the discharge side of the second compressor 3 becomes slack.
  • the bypass 8 and the on-off valve 9 are the pressure regulating device of the invention.
  • the check valve 10 is provided in order to reliably obtain the pressure difference between the suction side of the second compressor 3 and the pressure of the discharge side thereof.
  • the refrigerant on the outlet side of the expander 5 is sucked into the first compressor 2 via the evaporator 6. Specifically, when the expander 5 is in a suspended state, the pressure on the discharge side of the expander 5 becomes smaller than the inlet side of the expander 5. Further, since the refrigerant flowing into the inlet side of the expander 5 is a refrigerant that has not passed through the radiator 4, the refrigerant is low in density. That is, the bypass 8 and the on-off valve 9 are the expander startup facilitating device of the invention.
  • the check valve 10 does not have to be a constitution of the expander startup facilitating device.
  • pressure difference of the expander 5 When the pressure difference between the pressure on the inlet side of the expander 5 and the pressure on the outlet side of the expander 5 (hereinafter referred to as "pressure difference of the expander 5") becomes large, the expander 5 is started up (the driving starts).
  • Fig. 4 is an explanatory diagram illustrating a pressure change in an expansion chamber of the expander during the start up of the expander according to Embodiment 1 of the invention.
  • the pressure in the expansion chamber of the expander 5 changes during the process depicted by arrows in Fig. 4 . Further, for reference purpose, the pressure change in the expansion chamber during start up of the expander according to Patent Literature 2 will be depicted with a broken line.
  • Fig. 5 is an explanatory diagram illustrating a pressure change in the compression chamber of the second compressor during the start up of the second compressor according to Embodiment 1 of the invention.
  • the pressure in the compression chamber of the second compressor 3 changes during the process depicted by arrows in Fig. 5 .
  • the compression power at this time is the power corresponding to the "area A - area B", and is smaller than that of the conventional refrigeration cycle apparatus that equalizes the pressure on the discharge side and the suction side of the compressor (Patent Literature 1, for example). Accordingly, it is easier to start up the second compressor 3 than the conventional refrigeration cycle apparatus. Further, depending on the extent of the inverse pressure, a power recovery corresponding to area B - area A can be obtained. The power in proportion to this will contribute to the stable start up of the second compressor 3.
  • the on-off valve 9 is in an opened state until the refrigeration cycle apparatus 1 is capable of operating in the steady state.
  • the controller 100 controls the on-off valve 9 as below.
  • the refrigerant temperature discharged from the second compressor 3 rises. Additionally, the pressure on the discharge side of the second compressor 3 becomes larger or equal to the pressure on the suction side. That is, it is possible to operate the refrigeration cycle apparatus 1 in the steady state.
  • the temperature of the refrigerant discharged from the second compressor 3 is detected with the temperature sensor 21.
  • the controller 100 determines that the refrigeration cycle apparatus 1 is capable of operating in the steady state when the detection temperature of the temperature sensor 21 is above or equal to a certain threshold value, and closes the on-off valve 9.
  • the pressure on the suction side of the second compressor 3 is made to be larger than the pressure on the discharge side thereof at least until the second compressor 3 is started up. Further, at least until the expander 5 starts up, the pressure on the outlet side of the expander 5 is made to be smaller than the pressure on the inlet side of the expander 5, and the refrigerant flowing to the inlet side of the expander 5 is made to be low in density. Accordingly, it is possible to start up the second compressor 3 and the expander 5 more reliably than the conventional refrigeration cycle apparatus.
  • the invention may be embodied by providing a four-way valve in the refrigeration cycle apparatus so that the flows of the refrigerant may be switched.
  • Fig. 6 is another refrigerant circuit diagram of the refrigeration cycle apparatus according to Embodiment 1 of the invention.
  • a four-way valve 14 is disposed on an outlet side of a second compressor 3. With this four-way valve 14, a passage of a refrigerant discharged from a second compressor 3 is switched between a passage flowing to a radiator 4 and a passage flowing to an evaporator 6. Further, the four-way valve 14 switches a refrigerant passage flowing into a first compressor 2 between the passage from the evaporator 6 and the passage from the radiator 4.
  • a four-way valve 15 is disposed on an inlet side of an expander 5.
  • the four-way valve 15 switches the refrigerant passage flowing into the expander 5 between a passage from the radiator 4 and a passage from the evaporator 6.
  • the air-conditioning apparatus When the above refrigeration cycle apparatus is used in an air-conditioning apparatus, the air-conditioning apparatus will be capable of carrying out both a cooling operation and a heating operation.
  • a check valve 10 may be provided in the vicinity of the inlet port of the expander 5, and a bypass 8 may be provided between the check valve 10 and the expander 5.
  • an intercooler 22 may be provided between the first compressor 2 and the second compressor 3. Note that in Fig. 7 , an exemplary case in which the intercooler 22 is disposed in the refrigeration cycle apparatus 1 is shown.
  • the inclination of the isentropic line of this refrigerant in the Mollier chart becomes steep. That is, the power required for the second compressor 3 to compress the refrigerant can be reduced.
  • the connecting portion of the bypass 8 between the first compressor 2 and the second compressor 3 may be on the upstream side of the intercooler 22 or the downstream side of the intercooler 22. In the former case, a sudden pressure rise of the discharge pressure of the first compressor 2 until the expander 5 starts up can be suppressed. This effect may be achieved by replacing an on-off valve 9 with a flow control valve and by controlling the opening degree of the flow control valve.
  • the heat medium that exchanges heat with the radiator 4 and the evaporator 6 is air, but other heat mediums may be used.
  • the heat medium exchanging heat with the radiator 4 may be water, and the refrigeration cycle apparatus according to Embodiment 1 may be used for supplying hot water.
  • the heat medium exchanging heat with the radiator 4 and the evaporator 6 may be water or brine, and this heat medium may be conveyed to the conditioned space to air-condition the conditioned space.
  • Embodiment 1 carbon dioxide, which has zero ozone depleting potential and has an outstandingly small global warming potential compared to chlorofluorocarbon, is used, but the type of the refrigerant is arbitrary.
  • the operating efficiency (COP) of the refrigeration cycle apparatus that employs carbon dioxide is lower compared to refrigeration cycle apparatuses that uses conventional refrigerants. Therefore, it is highly advantageous to employ the invention to a refrigeration cycle apparatus that uses carbon dioxide. Note that when using a refrigerant that is not compressed into a supercritical state, the radiator 4 functions as a condenser.
  • the expander 5 and the second compressor 3 may be connected electrically.
  • the expander 5 may be connected to a power generator, and the power recovered by the expander 5 may be converted into electric power that is supplied to the second compressor 3.
  • a pressure sensor may be used to determine whether steady operation is capable or not. More specifically, a pressure sensor may be disposed on both the discharge side and the suction side of the second compressor 3. Additionally, when the detection values of these pressure sensors are above or equal to a certain threshold value, the refrigeration cycle apparatus 1 (refrigeration cycle apparatus 51) may determine that steady operation is possible.
  • Embodiment 2 is the same as Embodiment 1.
  • Fig. 8 is a refrigerant circuit diagram of a refrigeration cycle apparatus of Embodiment 2 of the invention.
  • a refrigeration cycle apparatus 52 according to Embodiment 2 is different with the refrigeration cycle apparatus 1 according to Embodiment 1 in the following points.
  • Other configurations of the refrigeration cycle apparatus 52 is the same as that of the refrigeration cycle apparatus 1.
  • first compressor 2 and the second compressor 3 are opposite. Further, a check valve 13 is provided in place of the check valve 10. Furthermore, a bypass 11 and an on-off valve 12 are provided replacing the bypass 8 and the on-off valve 9.
  • the check valve 13 is disposed between an expander 5 and an evaporator 6, and regulates the refrigerant from flowing from the evaporator 5 to the expander 5.
  • bypass 11 One end of the bypass 11 is connected between the second compressor 3 and the first compressor 2, and the other end is connected between the expander 5 and the check valve 13.
  • This bypass 11 is provided with the on-off valve 12 that closes and opens the bypass 11.
  • Fig. 9 is a refrigerant circuit diagram showing a refrigerant flow during a steady state of the refrigeration cycle apparatus of Embodiment 2 of the invention.
  • the on-off valve 12 is in a closed state. That is, in the steady state, the refrigerant is not allowed to flow in the bypass 11.
  • piping in which the refrigerant flows is depicted with thick lines.
  • the refrigerant that has been compressed into a high-temperature middle-pressure refrigerant in the second compressor 3 is discharged from the second compressor 3.
  • This high-temperature middle-pressure refrigerant is compressed in the first compressor 2 into a high-temperature high-pressure state (supercritical state), and flows into a radiator 4.
  • the refrigerant that has flowed into the radiator 4 transfers heat to the air sent by a fan 4a and turns into a low-temperature high-pressure refrigerant.
  • This low-temperature high-pressure refrigerant flows into the expander 5.
  • the refrigerant that has flowed into the expander 5 is decompressed into a low-pressure refrigerant with low dryness. During this decompression process, the expander 5 recovers power.
  • the low-pressure refrigerant with low dryness that has flowed out from the expander 5 flows into the evaporator 6 through the check valve 13.
  • the refrigerant that has flowed into the evaporator 6 receives heat from the air sent from a fan 6a and turns into a low-pressure refrigerant with high dryness or a low-pressure super-heated gas refrigerant.
  • the refrigerant that has flowed out of the evaporator 6 is sucked into the second compressor 3.
  • the refrigeration cycle apparatus 52 achieves energy saving.
  • Fig. 10 is a refrigerant circuit diagram showing a refrigerant flow during the start up of the refrigeration cycle apparatus of Embodiment 2 of the invention.
  • the on-off valve 12 is in an opened state. That is, in the start up, the refrigerant is allowed to flow in the bypass 11. Further, the fan 4a that is sending air to the radiator is stopped or has a speed of rotation (rotation speed) lower than that of a steady state. Note that in Fig. 10 , piping in which the refrigerant flows is depicted with thick lines.
  • the refrigerant that has been condensed in the first compressor 2 passes through the radiator 4 and reaches the expander 5. Further, with the start up of the first compressor 2, the refrigerant on the outlet side of the expander 5 passes through the bypass 11 and is sucked into the first compressor 2.
  • the check valve 13 prevents the refrigerant in the suction side of the second compressor 3 to be sucked into the first compressor 2. That is, during the start up in which the second compressor 3 is suspended, the pressure on the suction side of the second compressor 3 becomes higher than the pressure on the discharge side of the second compressor 3.
  • the pressure on the suction side of the second compressor 3 is higher than the pressure on the discharge side of the second compressor 3.
  • the time for the second compressor 3 to start up after the first compressor 2 has started up is a few seconds (with the refrigeration cycle apparatus 52 of Embodiment 2, about two to three seconds, for example). Accordingly, most of the refrigerant that is sucked into the suction side of the second compressor 3 is the refrigerant stored in the evaporator 6 (the evaporator 6 serving as a buffer), and therefor the pressure rise on the suction side of the second compressor 3 becomes slack.
  • the bypass 11 and the on-off valve 12 are the pressure regulating device of the invention.
  • the check valve 13 is provided in order to reliably obtain the pressure difference between the suction side of the second compressor 3 and the pressure of the discharge side thereof.
  • the controller 100 that controls the bypass 11 and the on-off valve 12, and the rotation speed of the fan 4a is the expander startup facilitating device of the invention.
  • the check valve 13 does not have to be a constitution of the expander startup facilitating device.
  • the pressure of the compression chamber of the second compressor 3 that is connected to the expander 5 via the shaft 7 changes as shown in Fig. 5 (same as Embodiment 1). Since the pressure on the suction side of the second compressor 3 is larger than the pressure on the discharge side thereof (the pressure is inverse), it is supercompressed.
  • the compression power at this time is the power corresponding to the "area A - area B", and is smaller than that of the conventional refrigeration cycle apparatus that equalizes the pressure on the discharge side and the suction side of the compressor (Patent Literature 1, for example). Accordingly, it is easier to start up the second compressor 3 than the conventional refrigeration cycle apparatus. Further, depending on the extent of the inverse pressure, a power recovery corresponding to area B - area A can be obtained. The power in proportion to this will contribute to the stable start up of the second compressor 3.
  • the controller 100 controls the on-off valve 12 as below.
  • the refrigerant temperature discharged from the second compressor 3 rises. Additionally, the pressure on the discharge side of the second compressor 3 becomes larger or equal to the pressure on the suction side. That is, it is possible to operate the refrigeration cycle apparatus 52 in the steady state.
  • the temperature of the refrigerant discharged from the second compressor 3 is detected with a temperature sensor 21.
  • the controller 100 determines that the refrigeration cycle apparatus 1 is capable of operating in the steady state when the detection temperature of the temperature sensor 21 is above or equal to a certain threshold value, and closes the on-off valve 12.
  • the rotation speed of the fan 4a is changed to the rotation speed for the steady state.
  • a pressure sensor may be used to determine whether the refrigeration cycle apparatus 52 is capable of the steady operation or not.
  • the pressure on the suction side of the second compressor 3 is made to be larger than the pressure on the discharge side thereof at least until the second compressor 3 is started up. Further, at least until the expander 5 starts up, the pressure on the outlet side of the expander 5 is made to be smaller than the pressure on the inlet side of the expander 5, and the refrigerant flowing to the inlet side of the expander 5 is made to be low in density. Accordingly, it is possible to start up the second compressor 3 and the expander 5 more reliably than the conventional refrigeration cycle apparatus.
  • 1 refrigeration cycle apparatus 2 first compressor; 3 second compressor; 4 radiator; 4a fan; 5 expander; 6 evaporator; 6a fan; 7 shaft; 8 bypass; 9 on-off valve; 10 check valve; 11 bypass; 12 on-off valve; 13 check valve; 14 four-way valve; 15 four-way valve; 21 temperature sensor; 22 intercooler; 51 refrigeration cycle apparatus; 52 refrigeration cycle apparatus; 100 controller.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air Conditioning Control Device (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)

Claims (5)

  1. Appareil à cycle de réfrigération (1, 51, 52), comprenant :
    un circuit de fluide frigorigène reliant un premier compresseur (2), un premier échangeur de chaleur qui sert en tant que radiateur (4) ou condenseur, un détendeur (5), et un deuxième échangeur de chaleur qui sert en tant qu'évaporateur (6) en série avec une tuyauterie ;
    un deuxième compresseur (3) qui est commandé par la puissance récupérée par le détendeur (5),
    dans lequel le deuxième compresseur (3) est disposé
    (i) entre le premier compresseur (2) et le premier échangeur de chaleur dans le circuit de fluide frigorigène ; ou
    (ii) entre le premier compresseur (2) et le deuxième échangeur de chaleur dans le circuit de fluide frigorigène ;
    caractérisé en ce que
    le deuxième compresseur (3) est un compresseur volumétrique,
    l'appareil à cycle de réfrigération (1) comprenant en outre un dispositif de régulation de pression qui maintient une pression d'un côté de décharge du deuxième compresseur (3) à une valeur inférieure à une pression d'un côté d'aspiration du deuxième compresseur (3) au moins jusqu'à ce que le deuxième compresseur (3) ait été démarré,
    dans lequel le dispositif de régulation de pression comprend :
    une dérivation (8, 11) ayant une extrémité reliée entre le premier compresseur (2) et le deuxième compresseur (3) et l'autre extrémité reliée entre le premier échangeur de chaleur et le détendeur (5) ; et
    une vanne tout ou rien (9, 12) prévue dans la dérivation (8, 11), et
    dans lequel la vanne tout ou rien (9, 12) est maintenue dans un état ouvert au moins jusqu'à ce que le deuxième compresseur (3) ait été démarré.
  2. Appareil à cycle de réfrigération (1) de la variante (i) de la revendication 1, comprenant en outre un clapet anti-retour (10) prévu à une position, qui est plus proche du premier échangeur de chaleur que le point de liaison de la dérivation (8), sur un passage entre le premier échangeur de chaleur et le détendeur (5), le clapet anti-retour (10) régulant un écoulement du fluide frigorigène vers le premier échangeur de chaleur.
  3. Appareil à cycle de réfrigération (1) de la variante (ii) de la revendication 1, comprenant en outre un clapet anti-retour (13) prévu à une position, qui est plus proche du deuxième échangeur de chaleur que le point de liaison de la dérivation (11), sur un passage entre le deuxième échangeur de chaleur et le détendeur (5), le clapet anti-retour (13) régulant un écoulement du fluide frigorigène vers le détendeur (5).
  4. Appareil à cycle de réfrigération (1) de la variante (i) de la revendication 1, comprenant en outre un dispositif d'envoi de milieu de chaleur qui envoie un milieu de chaleur, qui échange de la chaleur avec le fluide frigorigène s'écoulant dans le premier échangeur de chaleur, au premier échangeur de chaleur, dans lequel
    au moins jusqu'à ce que le deuxième compresseur (3) ait été démarré, la vitesse de rotation du dispositif d'envoi de milieu de chaleur est réduite au-dessous de la vitesse de rotation cible ou le dispositif d'envoi de milieu de chaleur est arrêté.
  5. Appareil à cycle de réfrigération (1) selon l'une quelconque des revendications 1 à 4, dans lequel le fluide frigorigène s'écoulant dans le circuit de fluide frigorigène est du dioxyde de carbone.
EP09850230.5A 2009-10-07 2009-10-07 Dispositif à cycle de réfrigération Active EP2476973B9 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2009/067459 WO2011042959A1 (fr) 2009-10-07 2009-10-07 Dispositif à cycle de réfrigération

Publications (4)

Publication Number Publication Date
EP2476973A1 EP2476973A1 (fr) 2012-07-18
EP2476973A4 EP2476973A4 (fr) 2017-08-16
EP2476973B1 EP2476973B1 (fr) 2018-09-26
EP2476973B9 true EP2476973B9 (fr) 2019-02-13

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US (1) US20120167606A1 (fr)
EP (1) EP2476973B9 (fr)
JP (1) JP5389184B2 (fr)
CN (1) CN102575885B (fr)
ES (1) ES2693240T3 (fr)
WO (1) WO2011042959A1 (fr)

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US20110247358A1 (en) * 2008-12-22 2011-10-13 Panasonic Corporation Refrigeration cycle apparatus
CN103196187B (zh) * 2013-04-19 2015-07-01 东南大学 基于膨胀功回收的加压溶液除湿空调装置及调控方法
CN103512256A (zh) * 2013-09-22 2014-01-15 孙西峰 一种制冷系统及空调
FR3034464B1 (fr) * 2015-04-03 2017-03-24 Snecma Refroidissement du circuit d'huile d'une turbomachine
CN106352601B (zh) * 2016-03-14 2020-04-07 李华玉 第三类热驱动压缩式热泵
CN107621093A (zh) * 2017-10-19 2018-01-23 天津商业大学 基于余压回收的蒸发冷却器过冷的co2冷冻冷藏系统
CN107631511A (zh) * 2017-10-19 2018-01-26 天津商业大学 基于余压回收的辅助过冷的co2中低温冷冻冷藏系统
CN107631510A (zh) * 2017-10-19 2018-01-26 天津商业大学 基于余压回收的co2中低温冷冻冷藏系统
US11300339B2 (en) 2018-04-05 2022-04-12 Carrier Corporation Method for optimizing pressure equalization in refrigeration equipment
CN110715474A (zh) * 2019-11-28 2020-01-21 广东美的制冷设备有限公司 运行控制方法、压缩空气换热系统以及存储介质
CN115823759A (zh) * 2022-11-25 2023-03-21 珠海格力电器股份有限公司 压缩制冷系统及控制方法

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JP3462156B2 (ja) * 1999-11-30 2003-11-05 株式会社東芝 冷蔵庫
JP3953871B2 (ja) * 2002-04-15 2007-08-08 サンデン株式会社 冷凍空調装置
JP2004137979A (ja) * 2002-10-18 2004-05-13 Matsushita Electric Ind Co Ltd 膨張機
JP4321095B2 (ja) * 2003-04-09 2009-08-26 日立アプライアンス株式会社 冷凍サイクル装置
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Also Published As

Publication number Publication date
EP2476973B1 (fr) 2018-09-26
EP2476973A4 (fr) 2017-08-16
JP5389184B2 (ja) 2014-01-15
ES2693240T3 (es) 2018-12-10
WO2011042959A1 (fr) 2011-04-14
US20120167606A1 (en) 2012-07-05
CN102575885B (zh) 2014-09-10
JPWO2011042959A1 (ja) 2013-02-28
CN102575885A (zh) 2012-07-11
EP2476973A1 (fr) 2012-07-18

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