EP2320165A2 - Kühlzyklusvorrichtung und Heißwassererhitzer - Google Patents

Kühlzyklusvorrichtung und Heißwassererhitzer Download PDF

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Publication number
EP2320165A2
EP2320165A2 EP10186452A EP10186452A EP2320165A2 EP 2320165 A2 EP2320165 A2 EP 2320165A2 EP 10186452 A EP10186452 A EP 10186452A EP 10186452 A EP10186452 A EP 10186452A EP 2320165 A2 EP2320165 A2 EP 2320165A2
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EP
European Patent Office
Prior art keywords
refrigerant
temperature
compressor
heat exchanger
refrigeration cycle
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP10186452A
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English (en)
French (fr)
Other versions
EP2320165B1 (de
EP2320165A3 (de
Inventor
Shunji Moriwaki
Shigeo Aoyama
Noriho Okaza
Yasuhiko Isayama
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Panasonic Corp
Original Assignee
Panasonic Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
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Publication of EP2320165A2 publication Critical patent/EP2320165A2/de
Publication of EP2320165A3 publication Critical patent/EP2320165A3/de
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Publication of EP2320165B1 publication Critical patent/EP2320165B1/de
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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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/02—Subcoolers
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/047—Water-cooled condensers
    • 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—Component parts or details not otherwise provided for in this subclass
    • F25B2400/13—Economisers
    • 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
    • F25B2500/08—Exceeding a certain temperature value in a refrigeration component or 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
    • F25B2500/00—Problems to be solved
    • F25B2500/31—Low ambient temperatures
    • 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
    • F25B2600/2509—Economiser valves
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2101—Temperatures in a bypass
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2103—Temperatures near a heat exchanger

Definitions

  • the present invention relates to a refrigeration cycle apparatus for subcooling a refrigerant that has flowed out of a condenser, and a hot water heater including the refrigeration cycle apparatus.
  • JP 10(1998)-68553 A discloses a refrigeration cycle apparatus 100 as shown in FIG. 6 .
  • the refrigeration cycle apparatus 100 includes a refrigerant circuit 110 in which a refrigerant circulates, and a bypass passage 120.
  • the refrigerant circuit 110 includes a compressor 111, a condenser 112, a subcooling heat exchanger 113, a main expansion valve 114, and an evaporator 115 that are connected circularly.
  • the bypass passage 120 is branched from the refrigerant circuit 110 between the condenser 112 and the subcooling heat exchanger 113, and extends through the subcooling heat exchanger 113 to join to the refrigerant circuit 110 between the evaporator 115 and the compressor 111.
  • Abypass expansion valve 121 is provided in the bypass passage 120 upstream of the subcooling heat exchanger 113.
  • the refrigeration cycle apparatus 100 further includes: a pressure sensor 131 for detecting a pressure of the refrigerant to be drawn into the compressor 111; a temperature sensor 141 for detecting a temperature (an evaporator outlet temperature) Teo of the refrigerant that has flowed out of the evaporator 115; and a temperature sensor 142 for detecting a temperature (a bypass side outlet temperature) Tbo of the refrigerant that has flowed out of the subcooling heat exchanger 113 in the bypass passage 120.
  • JP 10(1998)-68553 A also describes that: with the pressure detected by the pressure sensor 131, a saturation temperature Ts at this pressure is calculated; the main expansion valve 114 is controlled so that a degree of superheat (Teo - Ts) at an outlet of the evaporator 115 conforms to a target degree of superheat; and the bypass expansion valve 121 is controlled so that a degree of superheat (Tbo - Ts) at an outlet of the subcooling heat exchanger 113 conforms to a target degree of superheat.
  • the subcooling heat exchanger 113 cannot operate to its maximum capability because a larger amount of the refrigerant could be evaporated in the subcooling heat exchanger 113. More specifically, it is not possible to maximize the effect of increasing an enthalpy in the evaporator 115 owing to the heat exchange between the main flow refrigerant and the bypass flow refrigerant and the effect of reducing the pressure loss in a low pressure side refrigerant passage by bypassing the refrigerant.
  • the refrigerant bypassing the evaporator 115 is superheated, not only the specific volume of the refrigerant to be drawn into the compressor 111 increases and the circulating amount of the refrigerant reduces, but also the discharge temperature of the compressor increases.
  • the heating capacity may be insufficient.
  • the present invention is intended to provide a refrigeration cycle apparatus that is capable of maximizing the effect of increasing an enthalpy in an evaporator and the effect of reducing a pressure loss in a low pressure side refrigerant passage, and is capable of obtaining a sufficient heating capacity when an outside air temperature is low.
  • the present invention is also intended to provide a hot water heater including the refrigeration cycle apparatus.
  • the present invention provides a refrigeration cycle apparatus including: a refrigerant circuit including a compressor, a condenser, a subcooling heat exchanger, a main expansion means, and an evaporator that are connected circularly; a bypass passage that is branched from the refrigerant circuit between the condenser and the subcooling heat exchanger or between the subcooling heat exchanger and the main expansion means, and extends through the subcooling heat exchanger to join to the refrigerant circuit between the evaporator and the compressor; a bypass expansion means provided in the bypass passage upstream of the subcooling heat exchanger; a first temperature sensor for detecting a temperature of a refrigerant that has flowed out of the subcooling heat exchanger in the bypass passage; a second temperature sensor for detecting a temperature of the refrigerant that has flowed out of the evaporator in the refrigerant circuit; and a controller for controlling the bypass expansion means so that the temperature detected
  • the present invention also provides a hot water heater that performs heating by utilizing hot water produced by a heating means.
  • the hot water heater includes the refrigeration cycle apparatus as the heating means.
  • the refrigerant that has flowed out of the subcooling heat exchanger in the bypass passage can be maintained in a wet state or a saturated gaseous state.
  • the degree of superheat at the outlet of the evaporator is suppressed to be equal to or lower than the predetermined degree of superheat, it is possible to prevent a situation in which the flow rate of the refrigerant flowing through the bypass passage increases excessively and thus a dryness fraction of the refrigerant to be drawn into the compressor (the refrigerant resulting from the merge of the refrigerant that has flowed through the bypass passage and the refrigerant that has passed through the evaporator) lowers excessively. Accordingly, the dryness fraction of the refrigerant to be drawn into the compressor can fall in a desired range (at least 0.8 but less than 1.0, for example).
  • FIG. 1 is a schematic configuration diagram of a refrigeration cycle apparatus according to Embodiment 1 of the present invention.
  • FIG. 2 is a Mollier diagram of the refrigeration cycle apparatus shown in FIG. 1 .
  • FIG. 3 is a flow chart illustrating a control performed by a controller in Embodiment 1.
  • FIG. 4 is a schematic configuration diagram of a refrigeration cycle apparatus according to Embodiment 2 of the present invention.
  • FIG. 5 is a flow chart illustrating a control performed by a controller in Embodiment 2.
  • FIG. 6 is a schematic configuration diagram of a conventional refrigeration cycle apparatus.
  • FIG. 1 shows a refrigeration cycle apparatus 1A according to Embodiment 1 of the present invention.
  • the refrigeration cycle apparatus 1A includes: a refrigerant circuit 2 in which a refrigerant circulates; a bypass passage 3; and a controller 4.
  • the refrigerant include a zeotropic refrigerant mixture such as R407C, a nearly-azeotropic refrigerant mixture such as R410A, and a single refrigerant.
  • the refrigerant circuit 2 includes a compressor 21, a condenser 22, a subcooling heat exchanger 23, a main expansion valve (a main expansion means) 24, and an evaporator 25 that are connected circularly with a pipe.
  • a sub accumulator 26 and a main accumulator 27 for performing gas-liquid separation are provided between the evaporator 25 and the compressor 21.
  • the refrigerant circuit 2 is also provided with a four-way valve 28 for switching between a normal operation and a defrosting operation.
  • the refrigeration cycle apparatus 1A constitutes the heating means in the hot water heater that performs heating by utilizing hot water produced by the heating means
  • the condenser 22 is a heat exchanger that heats water by exchanging heat between the water and the refrigerant.
  • a supply pipe 71 and a recovery pipe 72 are connected to the condenser 22, so that water is supplied to the condenser 22 through the supply pipe 71 and the water (hot water) heated in the condenser 22 is recovered through the recovery pipe 72.
  • the hot water recovered through the recovery pipe 72 is sent to, for example, a heater such as a radiator, directly or through a hot water reservoir tank, and thereby heating is performed.
  • the bypass passage 3 is branched from the refrigerant circuit 2 between the subcooling heat exchanger 23 and the main expansion valves 24, and extends through the subcooling heat exchanger 23 to join to the refrigerant circuit 2 between the evaporator 25 and the compressor 21.
  • the bypass passage 3 joins to the refrigerant circuit 2 between the sub accumulator 26 and the main accumulator 27.
  • a bypass expansion valve (a bypass expansion means) 31 is provided in the bypass passage 3 upstream of the subcooling heat exchanger 23.
  • the refrigerant discharged from the compressor 21 is sent to the condenser 22 through the four-way valve 28.
  • the refrigerant discharged from the compressor 21 is sent to the evaporator 25 through the four-way valve 28.
  • FIG. 1 the flowing directions of the refrigerant in the normal operation are indicated by arrows.
  • the state change of the refrigerant in the normal operation will be described.
  • the high pressure refrigerant discharged from the compressor 21 flows into the condenser 22 and radiates heat to the water passing through the condenser 22.
  • the high pressure refrigerant that has flowed out of the condenser 22 flows into the subcooling heat exchanger 23 and is subcooled with the low pressure refrigerant decompressed by the bypass expansion valve 31.
  • the high pressure refrigerant that has flowed out of the subcooling heat exchanger 23 is divided to flow separately to the main expansion valve 24 and the bypass expansion valve 31.
  • the high pressure refrigerant divided to flow to the main expansion valve 24 is decompressed and expanded by the main expansion valve 24, and then flows into the evaporator 25.
  • the low pressure refrigerant that has flowed into the evaporator 25 absorbs heat from the air therein.
  • the high pressure refrigerant divided to flow to the bypass expansion valve 31 is decompressed and expanded by the bypass expansion valve 31, and then flows into the subcooling heat exchanger 23.
  • the low pressure refrigerant that has flowed into the subcooling heat exchanger 23 is heated with the high pressure refrigerant that has flowed out of the condenser 22.
  • the low pressure refrigerant that has flowed out of the subcooling heat exchanger 23 is merged with the low pressure refrigerant that has flowed out of the evaporator 25 and the resulted refrigerant is drawn into the compressor 21 once again.
  • the refrigeration cycle apparatus 1A of the present embodiment is configured so as to prevent the situation in which when the outside air temperature is low, the pressure of the refrigerant to be drawn into the compressor 21 is lowered and the circulating amount of the refrigerant is reduced, and thus the heating capacity of the condenser 22 is lowered.
  • it is important to increase an enthalpy difference in the evaporator 25 by subcooling the refrigerant, and to suppress the amount of the gaseous phase refrigerant having a low effect of absorbing heat flowing through a low pressure side of the refrigerant circuit 2 by bypassing the refrigerant with the bypass passage 3, and thereby reducing the pressure loss in the low pressure side of the refrigerant circuit 2.
  • the pressure loss in the low pressure side of the refrigerant circuit 2 is reduced, the pressure of the refrigerant to be drawn into the compressor 21 increases by the amount of the reduced pressure loss, reducing the specific volume of the refrigerant. Accordingly, the circulating amount of the refrigerant increases. Moreover, by increasing the enthalpy difference in the evaporator 25, it is possible to ensure the amount of heat absorption in the evaporator 25 even when the mass flow rate of the refrigerant passing through the evaporator 25 lowers due to the bypassing.
  • the bypass expansion valve 31 is controlled so as to prevent the refrigerant flowing through the bypass passage 3 from being superheated in the subcooling heat exchanger 23, which will be described in detail later. Accordingly, the refrigerant that has flowed out of the subcooling heat exchanger 23 in the bypass passage 3 is in a saturated state of Point a shown in FIG. 2 . In contrast, since the refrigerant is superheated in the evaporator 25, the refrigerant that has flowed out of the evaporator 25 is in the state of Point b shown in FIG. 2 . The refrigerant to be drawn into the compressor 21 is in the state of Point c, which is between Point a and Point b, because it is the result of the merge of these refrigerants.
  • the bypass passage 3 is provided with a first temperature sensor 61 for detecting a temperature (a bypass side outlet temperature) Tbo of the refrigerant that has flowed out of the subcooling heat exchanger 23.
  • the refrigerant circuit 2 is provided with: a pressure sensor 51 for detecting a pressure (a suction pressure) Ps of the refrigerant to be drawn into the compressor 21; a discharge temperature sensor 65 for detecting a temperature (a discharge temperature) Td of the refrigerant that has been discharged from the compressor 21; and a second temperature sensor 62 for detecting a temperature (an evaporator outlet temperature) Teo of the refrigerant that has flowed out of the evaporator 25.
  • the controller 4 controls the rotation speed of the compressor 21, the switching of the four-way valve 28, and openings of the main expansion valve 24 and the bypass expansion valve 31, based on the detected values detected by the sensors 51, 61, 62, and 65, etc.
  • the controller 4 controls the bypass expansion means 31 so that, in the normal operation, the bypass side outlet temperature Tbo detected by the first temperature sensor 61 conforms to a saturation temperature STs at the pressure of the refrigerant to be drawn into the compressor 21, and a degree of superheat SHe at an outlet of the evaporator 25 calculated based on the evaporator outlet temperature Teo detected by the second temperature sensor 62 is equal to or lower than a predetermined degree of superheat.
  • the controller 4 detects the discharge temperature Td with the discharge temperature sensor 65 (Step S1), and adjusts the opening of the main expansion valve 24 so that the discharge temperature Td conforms to a target value (Step S2).
  • the controller 4 detects the suction pressure Ps with the pressure sensor 51 and detects the bypass side outlet temperature Tbo with the first temperature sensor 61 (Step S3). Further, the controller 4 calculates, from the detected suction pressure Ps, the saturation temperature STs at the pressure of the refrigerant to be drawn into the compressor 21 (Step S4). The calculation of the saturation temperature STs is made using a refrigerant property formula. Thereafter, the controller 4 judges whether the bypass side outlet temperature Tbo is equal to the saturation temperature STs (Step S5).
  • Step S6 the controller 4 increases the opening of the bypass expansion valve 31 by a specified amount (Step S6) and returns to Step S1, under the assumption that a larger amount of refrigerant could have been evaporated in the subcooling heat exchanger 23.
  • the controller 4 proceeds to a control for correcting the opening of the bypass expansion valve 31, under the assumption that the subcooling heat exchanger 23 operates to its maximum capability to evaporate the refrigerant.
  • the controller 4 detects the evaporator outlet temperature Teo with the second temperature sensor 62 (Step S7), and calculates the degree of superheat SHe at the outlet of the evaporator 25 using a formula below (Step S8).
  • SHe Teo - STs
  • Step S9 the controller 4 judges whether the calculated degree of superheat SHe at the outlet of the evaporator 25 is equal to or lower than the predetermined degree of superheat. If NO in Step S9, the controller 4 reduces the opening of the bypass expansion valve 31 by a specified amount (Step S 10) and returns to Step S1, under the assumption that Point c shown in FIG. 2 is too far on the right (the degree of superheat is excessively high because the flow rate of the refrigerant is insufficient), that is, Point a is too far on the left (the refrigerant is excessively wet because the flow rate is excessively high). In contrast, if YES in Step S9, the controller 4 returns to Step S1 without changing the opening of the bypass expansion valve 31, under the assumption that the opening is appropriate.
  • the bypass side outlet temperature Tbo is maintained at the saturation temperature STs at the pressure of the refrigerant to be drawn into the compressor 21 as described above, the refrigerant that has flowed out of the subcooling heat exchanger 23 can be maintained in a wet state or in a saturated gaseous state.
  • the degree of superheat SHe at the outlet of the evaporator is suppressed to be equal to or lower than the predetermined degree of superheat, it is possible to prevent a situation in which the flow rate of the refrigerant flowing through the bypass passage 3 increases excessively and thus a dryness fraction of the refrigerant to be drawn into the compressor 21 (the refrigerant resulted from the merge of the refrigerant that has flowed through the bypass passage 3 and the refrigerant that has passed through the evaporator 25) lowers excessively. Accordingly, the dryness fraction of the refrigerant to be drawn into the compressor 21 can fall in a desired range (at least 0.8 but less than 1.0, for example).
  • the "predetermined degree of superheat" used in Step S9 preferably is a degree of superheat that allows the refrigerant to be drawn into the compressor 21 to have a dryness fraction of at least 0.8 but less than 1.0.
  • X is the dryness fraction of the refrigerant to be drawn into the compressor 21; ha is an enthalpy of the refrigerant to be drawn into the compressor 21; hl is an enthalpy of the saturated gaseous refrigerant at the pressure of the refrigerant to be drawn into the compressor 21; and hv is an enthalpy of the saturated liquid refrigerant at the pressure of the refrigerant to be drawn into the compressor 21.
  • the "predetermined degree of superheat" preferably is defined in accordance with an outside air temperature so that the dryness fraction of the refrigerant to be drawn into the compressor 21 reduces as the outside air temperature lowers.
  • an outside air temperature so that the dryness fraction of the refrigerant to be drawn into the compressor 21 reduces as the outside air temperature lowers.
  • the "predetermined degree of superheat" preferably is defined in accordance with a compression ratio of the refrigerant by the compressor 21 so that the dryness fraction of the refrigerant to be drawn into the compressor 21 reduces as the compression ratio increases.
  • a compression ratio of the refrigerant by the compressor 21 so that the dryness fraction of the refrigerant to be drawn into the compressor 21 reduces as the compression ratio increases.
  • the "predetermined degree of superheat” preferably is defined in accordance with the rotation speed of the compressor 21 so that the dryness fraction of the refrigerant to be drawn into the compressor 21 reduces as the rotation speed of the compressor 21 increases.
  • the pressure sensor 51 is provided in the refrigerant circuit 2, between the main accumulator 27 and a position at which the bypass passage 3 joins to the refrigerant circuit 2.
  • the pressure sensor 51 may be provided anywhere in the refrigerant circuit 2 as long as it is between the evaporator 25 and the compressor 21.
  • the pressure sensor 51 may be provided in the bypass passage 3 downstream of the subcooling heat exchanger 23.
  • FIG. 4 shows a refrigeration cycle apparatus 1B according to Embodiment 2 of the present invention.
  • the same components as those in Embodiment 1 are designated by the same reference numerals, and the descriptions thereof are omitted.
  • the controller 4 controls the bypass expansion means 31 so that, in the normal operation, the bypass side outlet temperature Tbo detected by the first temperature sensor 61 conforms to the saturation temperature STs at the pressure of the refrigerant to be drawn into the compressor 21, and the degree of superheat SHe at the outlet of the evaporator 25 calculated based on the evaporator outlet temperature Teo detected by the second temperature sensor 62 is equal to or lower than a predetermined degree of superheat, as in Embodiment 1.
  • Embodiment 1 is different from Embodiment 1 in that the controller 4 recognizes that the bypass side outlet temperature Tbo detected by the first temperature sensor 61 conforms to the saturation temperature STs at the pressure of the refrigerant to be drawn into the compressor 21 from the fact that the bypass side outlet temperature Tbo detected by the first temperature sensor 61 is approximately equal to a temperature detected by a third temperature sensor 63.
  • the pressure sensor 51 (see FIG. 1 ) is not provided in the refrigerant circuit 2 in the present embodiment. Instead, the third temperature sensor 63 for detecting a temperature (a bypass side inlet temperature) Tbi of the refrigerant to flow into the subcooling heat exchanger 23 is provided in the bypass passage 3.
  • the controller 4 detects the discharge temperature Td with the discharge temperature sensor 65 (Step S21), and adjusts the opening of the main expansion valve 24 so that the discharge temperature Td conforms to a target value (Step S22), as in Embodiment 1.
  • the controller 4 detects the bypass side outlet temperature Tbo with the first temperature sensor 61 and detects the bypass side inlet temperature Tbi with the third temperature sensor 63 (Step S23). Thereafter, the controller 4 judges whether the bypass side outlet temperature Tbo is approximately equal to the bypass side inlet temperature Tbi (Step S24). In reality, the bypass side outlet temperature Tbo is not completely equal to the bypass side inlet temperature Tbi because of the influence of the pressure loss. Thus, the term "approximately equal” is a concept taking this phenomenon into consideration. For example, in the case where the difference between the bypass side outlet temperature Tbo and the bypass side inlet temperature Tbi is 3K or less, it can be regarded as being approximately equal.
  • Step S24 If the bypass side outlet temperature Tbo is not approximately equal to the bypass side inlet temperature Tbi (NO in Step S24), the controller 4 increases the opening of the bypass expansion valve 31 by a specified amount (Step S25) and returns to Step S21, under the assumption that a larger amount of refrigerant could have been evaporated in the subcooling heat exchanger 23.
  • the controller 4 proceeds to the control for correcting the opening of the bypass expansion valve 31, under the assumption that the subcooling heat exchanger 23 operates to its maximum capability to evaporate the refrigerant.
  • the controller 4 detects the evaporator outlet temperature Teo with the second temperature sensor 62 (Step S26), and calculates the degree of superheat SHe at the outlet of the evaporator 25 using a formula below (Step S27).
  • SHe Teo - Tbi
  • Step S28 judges whether the calculated degree of superheat SHe at the outlet of the evaporator 25 is equal to or lower than the predetermined degree of superheat. If NO in Step S28, the controller 4 decreases the opening of the bypass expansion valve 31 by a specified amount (Step S29) and returns to Step S21, under the assumption that Point c shown in FIG. 2 is too far on the right, that is, Point a shown is too far on the left. In contrast, if YES in Step S28, the controller 4 returns to Step S21 without changing the opening of the bypass expansion valve 31, under the assumption that the opening is appropriate.
  • the third temperature sensor 63 for detecting the bypass side inlet temperature Tbi may be a temperature sensor for detecting a temperature (an evaporator inlet temperature) Tei of the refrigerant to flow into the evaporator 25 in the refrigerant circuit 2.
  • the flow chart in this case is given by replacing the bypass side inlet temperature Tbi in the flow chart shown in FIG. 5 with the evaporator inlet temperature Tei.
  • the main expansion valve 24 is controlled so that the discharge temperature Td conforms to a target value.
  • the method of controlling the main control valve 24 is not limited to this.
  • the main expansion valve 24 may be controlled so that the pressure of the refrigerant discharged from the compressor 21 conforms to a target value.
  • the main expansion valve 24 can be controlled based on a degree of superheat at an outlet of the compressor 21 or a degree of subcooling at an outlet of the condenser 22.
  • the bypass passage 3 does not necessarily have to be branched from the refrigerant circuit 2 between the subcooling heat exchanger 23 and the main expansion valves 24. It may be branched from the refrigerant circuit 2 between the condenser 22 and the subcooling heat exchanger 23.
  • main expansion means and the bypass expansion means of the present invention do not necessarily have to be expansion valves.
  • Each of them may be an expander that recovers power from the refrigerant expanding.
  • the rotation speed of the expander may be controlled by, for example, changing the load by using a power generator connected to the expander.
  • the present invention is particularly useful for hot water heaters that produce hot water with a refrigeration cycle apparatus and perform heating by utilizing the hot water.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)
  • Air Conditioning Control Device (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
EP10186452.8A 2009-10-05 2010-10-04 Kühlzyklusvorrichtung und Heißwassererhitzer Active EP2320165B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2009231659A JP5421717B2 (ja) 2009-10-05 2009-10-05 冷凍サイクル装置および温水暖房装置

Publications (3)

Publication Number Publication Date
EP2320165A2 true EP2320165A2 (de) 2011-05-11
EP2320165A3 EP2320165A3 (de) 2015-02-25
EP2320165B1 EP2320165B1 (de) 2018-04-11

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EP10186452.8A Active EP2320165B1 (de) 2009-10-05 2010-10-04 Kühlzyklusvorrichtung und Heißwassererhitzer

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EP (1) EP2320165B1 (de)
JP (1) JP5421717B2 (de)
CN (1) CN102032698B (de)
DK (1) DK2320165T3 (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2765370A1 (de) * 2013-02-08 2014-08-13 Panasonic Corporation Kühlgerät und Warmwassererzeuger
EP2535674A3 (de) * 2011-06-17 2015-05-20 Panasonic Corporation Kältekreislaufvorrichtung und hydronisches Heizgerät mit Kältekreislaufvorrichtung

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CN102032698B (zh) 2014-12-17
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