EP2434233B1 - Appareil à cycle de réfrigération et appareil de chauffage d'eau chaude - Google Patents

Appareil à cycle de réfrigération et appareil de chauffage d'eau chaude Download PDF

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Publication number
EP2434233B1
EP2434233B1 EP11182247.4A EP11182247A EP2434233B1 EP 2434233 B1 EP2434233 B1 EP 2434233B1 EP 11182247 A EP11182247 A EP 11182247A EP 2434233 B1 EP2434233 B1 EP 2434233B1
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EP
European Patent Office
Prior art keywords
temperature
refrigerant
evaporator
superheat degree
bypass
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EP11182247.4A
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German (de)
English (en)
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EP2434233A3 (fr
EP2434233A2 (fr
Inventor
Shunji Moriwaki
Shigeo Aoyama
Michiyoshi Kusaka
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Panasonic Corp
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Panasonic Corp
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Publication of EP2434233A3 publication Critical patent/EP2434233A3/fr
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    • 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
    • F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
    • F25B29/003—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously of the compression type system
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
    • 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—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
    • F25B2400/13—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
    • F25B2600/00—Control issues
    • F25B2600/21—Refrigerant outlet evaporator temperature
    • 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
    • F25B6/00—Compression machines, plants or systems, with several condenser circuits
    • F25B6/04—Compression machines, plants or systems, with several condenser circuits arranged in series

Definitions

  • the present invention relates to a refrigeration cycle apparatus and a hot-water heating apparatus which bypass a portion of refrigerant flowing out from a condenser, which exchange heat between refrigerant flowing through a refrigeration cycle and refrigerant flowing through a bypass passage, and which supercool the refrigerant flowing through the refrigeration cycle.
  • a supercooling heat exchanger is provided at a location downstream of a condenser of a refrigeration cycle, expanded refrigerant is made to flow into the supercooling heat exchanger, thereby supercooling refrigerant which flows out from the condenser (see patent document 1 for example).
  • Fig. 4 shows a conventional refrigeration cycle apparatus described in the patent document 1.
  • a refrigeration cycle apparatus 100 includes a refrigerant circuit 110 through which refrigerant circulates, and a bypass passage 120.
  • the refrigerant circuit 110 is formed circularly by connecting a compressor 111, a condenser 112, a supercooling heat exchanger 113, a main expansion valve 114 and an evaporator 115 to one another through pipes.
  • the bypass passage 120 branches off from the refrigerant circuit 110 between the supercooling heat exchanger 113 and the main expansion valve 114, and is connected to the refrigerant circuit 110 between the evaporator 115 and the compressor 111 through the supercooling heat exchanger 113.
  • the bypass passage 120 is provided with a bypass expansion valve 121 at a location upstream of the supercooling heat exchanger 113.
  • the refrigeration cycle apparatus 100 includes a temperature sensor 141 which detects temperature (discharge temperature) Td of refrigerant discharged from the compressor 111, a temperature sensor 142 which detects temperature (evaporator inlet temperature) Te of refrigerant flowing into the evaporator 115, a temperature sensor 143 which detects temperature (bypass inlet temperature) Tbi of refrigerant flowing into the supercooling heat exchanger 113 in the bypass passage 120, a temperature sensor 144 which detects temperature (bypass outlet temperature) Tbo of refrigerant flowing out from the supercooling heat exchanger 113 in the bypass passage 120, a main expansion valve controller in which target temperature Td (target) of a discharge pipe of the compressor 111 is set from evaporator inlet temperature Te detected by the temperature sensor 142 and which controls the main expansion valve 114 such that discharge temperature Td detected by the temperature sensor 141 becomes equal to the target temperature Td (target), and a bypass expansion valve controller which controls the bypass expansion valve 121 such that a difference (Tb
  • Patent document 2 forming the closest prior art from which the present invention starts, discloses, amongst others, a forth liquid pipe and a second expansion valve as well as a discharged temperature sensor.
  • the discharged temperature sensor is used for adjusting the amount of the liquid injection by controlling the opening degree of a third expansion valve.
  • Discharge temperature Td is substantially determined by suction refrigerant of the compressor 111 which is a mixture of refrigerant flowing through the refrigerant circuit 110 and refrigerant flowing through the bypass passage 120.
  • the present invention is achieved for solving the conventional problem, and it is an object of the invention to provide a refrigeration cycle apparatus and a hot-water heating apparatus capable of enhancing the heating ability by swiftly controlling a refrigeration cycle state into an appropriate state.
  • the present invention provides a refrigeration cycle apparatus comprising: a refrigeration circuit to which a compressor, a condenser, a supercooling heat exchanger, main expansion means and an evaporator are circularly connected to one another; a bypass passage which branches off from the refrigeration circuit between the supercooling heat exchanger and the main expansion means, and which is connected to the refrigeration circuit between the evaporator and the compressor through the supercooling heat exchanger; bypass expansion means provided at a location upstream of the supercooling heat exchanger of the bypass passage; a first temperature sensor which detects discharge temperature of refrigerant discharged from the compressor; a second temperature sensor which detects evaporator outlet temperature of refrigerant flowing out from the evaporator in the refrigeration circuit; and a control apparatus, wherein the control apparatus adjusts an opening degree of the bypass expansion means based on the discharge temperature and based on an evaporator outlet superheat degree calculated from the evaporator outlet temperature.
  • the refrigeration cycle apparatus and the hot-water heating apparatus of the present invention determine an improper distribution between a flow rate of refrigerant flowing through the refrigeration circuit and a flow rate of refrigerant flowing through the bypass passage, and always control the flow rate distribution into an appropriate distribution swiftly. Therefore, it is possible to sufficiently secure a heat absorption amount in the evaporator, and it is possible to maximize the enthalpy difference increasing effect in the evaporator obtained by the heat exchange between refrigerant flowing through the refrigeration circuit and refrigerant flowing through the bypass passage in the supercooling heat exchanger, and the pressure loss reducing effect of the low pressure refrigerant path obtained by bypassing of refrigerant. It is possible to provide a refrigeration cycle apparatus and a hot-water heating apparatus capable of obtaining higher operation efficiency and sufficient heating ability even when outside temperature is low.
  • the invention provides a refrigeration cycle apparatus comprising: a refrigeration circuit to which a compressor, a condenser, a supercooling heat exchanger, main expansion means and an evaporator are circularly connected to one another; a bypass passage which branches off from the refrigeration circuit between the supercooling heat exchanger and the main expansion means, and which is connected to the refrigeration circuit between the evaporator and the compressor through the supercooling heat exchanger; bypass expansion means provided at a location upstream of the supercooling heat exchanger of the bypass passage; a first temperature sensor which detects discharge temperature of refrigerant discharged from the compressor; a second temperature sensor which detects evaporator outlet temperature of refrigerant flowing out from the evaporator in the refrigeration circuit; and a control apparatus, wherein the control apparatus adjusts an amount of refrigerant flowing through the bypass expansion means based on the discharge temperature and based on an evaporator outlet superheat degree calculated from the evaporator outlet temperature.
  • the refrigeration circuit is in the poor-efficient refrigeration cycle state caused by the improper refrigerant distribution in which the circulation amount of the refrigerant flowing through the bypass passage is excessively large and the circulation amount of the refrigerant flowing through the refrigeration circuit is excessively small.
  • the bypass expansion means is forcibly closed by a predetermined operation amount, since the circulation amount of the refrigerant flowing through the bypass passage is reduced, the circulation amount of the refrigerant flowing through the refrigeration circuit is increased, and the refrigerant distribution is improved. Therefore, it is possible to secure sufficient heat absorption amount in the evaporator.
  • the control apparatus reduces the amount of refrigerant flowing through the bypass expansion means when the discharge temperature is lower than a predetermined temperature and the evaporator outlet superheat degree is higher than a predetermined superheat degree. According to this, when the temperature of the refrigerant discharged from the compressor is lower than the target temperature and a superheat degree at the outlet of the evaporator becomes excessively high, it is possible to more precisely determine that the refrigeration circuit is in the poor-efficient refrigeration cycle state caused by the improper refrigerant distribution in which the circulation amount of the refrigerant flowing through the bypass passage is excessively large and the circulation amount of the refrigerant flowing through the refrigeration circuit is excessively small. Therefore, efficiency is not deteriorated by mistaken decision.
  • the refrigeration cycle apparatus further includes a pressure sensor which detects a suction pressure of refrigerant sucked into the compressor, the control apparatus calculates saturation temperature under the suction pressure from the suction pressure, and the control apparatus calculates a bypass passage outlet superheat degree from the saturation temperature and the evaporator outlet temperature. According to this, the saturation temperature under a pressure of refrigerant sucked by the compressor is calculated from a pressure detected by the pressure sensor, thereby precisely calculating a superheat degree at the outlet of the bypass passage.
  • the control apparatus more increases the changing opening of the bypass expansion means. According to this, it is possible to determine whether a proper degree of the refrigerant flow rate distribution is high or low from the superheat degree in the outlet of the evaporator, and the bypass expansion means can be closed by an operation amount corresponding to the proper degree. Therefore, the control response is enhanced. Hence, the effect of the invention can swiftly be obtained and comfort can also be enhanced.
  • the control apparatus increases an amount of refrigerant flowing through the main expansion means when the discharge temperature is lower than predetermined temperature and the evaporator outlet superheat degree is higher than a predetermined superheat degree. According to this, even if the bypass expansion means is closed, the main expansion means is opened. Therefore, it is possible to avoid a case where a suction pressure is abnormally reduced by excessively narrowing the main expansion means, and the reliability of the compressor in addition to the effect of the invention can be enhanced.
  • the control apparatus increases an amount of refrigerant flowing through the main expansion means when the discharge temperature is lower than predetermined temperature, the evaporator outlet superheat degree is higher than a predetermined superheat degree and the suction pressure is lower than a predetermined pressure value. According to this, since it is determined that the suction pressure is lowered from the detection value of the pressure sensor, it is possible to open the main expansion means while determining that the main expansion means is excessively narrowed. Therefore, it is possible to reliably prevent the suction pressure from being abnormally lowered, to improve the flow rate distribution more swiftly, and to further enhance the effect of the invention.
  • the control apparatus more increases the changing opening of the main expansion means. According to this, since the opening amount is adjusted to a value corresponding to a reduction state of the suction pressure when the bypass expansion means is closed. Therefore, it is possible to swiftly handle abrupt variation of the suction pressure caused by variation in an operation state and a load state, and it is possible to especially enhance the reliability of the compressor in the effect of the invention.
  • Fig. 1 is a schematic block diagram in the embodiment of the invention.
  • a refrigeration cycle apparatus 1A includes a refrigerant circuit 2 through which refrigerant is circulated, a bypass passage 3 and a control apparatus 4.
  • the refrigerant it is possible to use zeotropic refrigerant mixture zeotropic refrigerant mixture such as R407C, pseudo azerotropic refrigerant mixture such as R410A and a single refrigerant.
  • the refrigerant circuit 2 is formed circularly by connecting a compressor 21, a condenser 22, a supercooling heat exchanger 23, a main expansion valve (main expansion means) 24 and an evaporator 25 to one another through pipes.
  • a sub-accumulator 26 and a main accumulator 27 which separate gas and liquid from each other are provided between the evaporator 25 and the compressor 21.
  • the refrigerant circuit 2 is provided with a four-way valve 28 which switches between a normal operation and a defrosting operation.
  • the refrigeration cycle apparatus 1A configures heading means of the hot-water heating apparatus which utilizes hot water produced by the heating means for a heating operation.
  • the condenser 22 is a heat exchanger which exchanges heat between the refrigerant and water, thereby heating water.
  • a supply pipe 71 and a recovering pipe 72 are connected to the condenser 22, water is supplied to the condenser 22 through the supply pipe 71, and water (hot water) heated by the condenser 22 is recovered through the recovering pipe 72.
  • Hot water recovered by the recovering pipe 72 is directly sent to a heater such as a radiator or sent to the heater through a hot water tank, thereby carrying out the heating operation.
  • the bypass passage 3 branches off from the refrigerant circuit 2 between the supercooling heat exchanger 23 and the main expansion valve 24, and is connected to the refrigerant circuit 2 between the evaporator 25 and the compressor 21 through the supercooling heat exchanger 23.
  • the bypass passage 3 is connected to the refrigerant circuit 2 between the sub-accumulator 26 and the main accumulator 27.
  • the bypass passage 3 is provided with the bypass expansion valve (bypass expansion means) 31 at a location upstream of the supercooling heat exchanger 23.
  • refrigerant discharged from the compressor 21 is sent to the condenser 22 through the four-way valve 28.
  • refrigerant discharged from the compressor 21 is sent to the evaporator 25 through the four-way valve 28.
  • Fig. 1 a flowing direction of refrigerant at the time of the normal operation is shown with solid lines.
  • High pressure refrigerant discharged from the compressor 21 flows into the condenser 22, and dissipates heat to water passing through the condenser 22.
  • the high pressure refrigerant which flows out from the condenser 22 flows into the supercooling heat exchanger 23, and is supercooled by low pressure refrigerant which is decompressed by the bypass expansion valve 31.
  • High pressure refrigerant which flows out from the supercooling heat exchanger 23 is distributed to a pipe connected to the main expansion valve 24 and a pipe connected to the bypass expansion valve 31.
  • the high pressure refrigerant distributed to the pipe connected to the main expansion valve 24 is decompressed and expanded by the main expansion valve 24 and then, the high pressure refrigerant flows into the evaporator 25.
  • the low pressure refrigerant which flows into the evaporator 25 absorbs heat from air.
  • the high pressure refrigerant distributed to the pipe connected to the bypass expansion valve 31 is decompressed and expanded by the bypass expansion valve 31 and then, flows into the supercooling heat exchanger 23.
  • the low pressure refrigerant which flows into the supercooling heat exchanger 23 is heated by the high pressure refrigerant which flows out from the condenser 22. Thereafter, the low pressure refrigerant flowing out from the supercooling heat exchanger 23 merges with the low pressure refrigerant flowing out from the evaporator 25 and is again sucked into the compressor 21.
  • the refrigeration cycle apparatus 1A of the embodiment is configured such that a pressure of refrigerant sucked into the compressor 21 is lowered when outside air temperature is low, the refrigeration circulation amount is reduced, and this prevents the heating ability of the condenser 22 from being deteriorated.
  • the bypass passage 3 makes refrigerant bypass, thereby suppressing gas phase refrigerant having a small endothermic effect flowing through a low pressure pipe of the refrigerant circuit 2 and this reduces a pressure loss in the low pressure pipe of the refrigerant circuit 2.
  • the refrigeration circulation amount is increased. If the enthalpy difference at the evaporator 25 is increased, even if a mass flow rate of refrigerant which passes through the evaporator 25 is lowered by the bypass, it is possible to secure the heat absorption amount at the evaporator 25. That is, the supercooling degree of refrigerant and the bypass amount are maximized, it is possible to obtain the maximum heating ability enhancing effect of the condenser 22 and the maximum coefficient of performance enhancing effect of the refrigeration cycle apparatus 1A.
  • a refrigerant flow rate distribution becomes improper i.e., when a circulation amount of refrigerant flowing through the bypass passage 3 becomes excessively large and a circulation amount of refrigerant flowing through the refrigerant, circuit 2 becomes excessively small
  • control is performed such that the bypass expansion valve 31 is closed by a predetermined opening degree and the main expansion valve 24 is opened by a predetermined opening degree. Therefore, in the bypass passage 3, a circulation amount of refrigerant flowing through the bypass passage 3 is reduced and a state of refrigerant flowing out from the supercooling heat exchanger 23 approaches a saturation state as shown with a dot a' in Fig. 2 from a state where a drying degree is small as shown with a dot a in Fig. 2 .
  • the state of refrigerant flowing out from the evaporator 25 approaches a saturation state as shown with a dot b' in Fig. 2 from the supercooled state as shown with a dot b in Fig. 2 . That is, the heat absorption amount in the evaporator 25 is increased and the discharge refrigerant temperature of the compressor 21 is appropriately secured in a state where the supercooling heat exchanger 23 sufficiently acts and the enthalpy difference increasing effect in the evaporator 25 and the pressure loss reducing effect caused by the bypass are sufficiently obtained.
  • the refrigerant circuit 2 includes a pressure sensor 51 which detects a pressure (suction pressure) Ps of refrigerant sucked into the compressor 21, a first temperature sensor 61 which detects temperature (discharge temperature) Td of refrigerant discharged from the compressor 21, and a second temperature sensor 62 which detects temperature (evaporator outlet temperature) Teo of refrigerant flowing out from the evaporator 25.
  • the bypass passage 3 includes a third temperature sensor 63 which detects temperature (bypass passage cutlet temperature) Tbo of refrigerant flowing out from the supercooling heat exchanger 23.
  • the control apparatus 4 includes a first control apparatus 4A and a second control apparatus 48.
  • the control apparatus 4 controls, based on detection values detected by the various sensors such as the pressure sensor 51, the first temperature sensor 61, the second temperature sensor 62 and the third temperature sensor 63, the number of rotations of the compressor 21 and the four-way valve 28, the opening degrees of the main expansion valve 24 and the bypass expansion valve 31.
  • the first control apparatus 4A controls the bypass expansion valve 31 such that a superheat degree SHb at the outlet of the bypass passage 3 calculated based on bypass outlet temperature Tbo detected by the third temperature sensor 63 and based on a suction pressure Ps detected by the pressure sensor 51 becomes equal to a predetermined superheat degree (bypass superheat degree control target value), and controls such that the bypass expansion valve 31 is closed by a predetermined first operation amount when temperature detected by the first temperature sensor 61 is lower than predetermined temperature and when a superheat degree SHe at the outlet of the evaporator 25 calculated based on evaporator outlet temperature Teo detected by the second temperature sensor 62 and suction pressure Ps detected by the pressure sensor 51 becomes higher than a predetermined superheat degree (evaporator superheat degree control target value).
  • the second control apparatus 4B controls the main expansion valve 24 such that discharge temperature Td detected by the first temperature sensor 61 becomes equal to predetermined temperature (discharge temperature control target value), and controls such that the main expansion valve 24 opens by a predetermined second operation amount when temperature detected by the first temperature sensor 61 is lower than predetermined temperature, and when a superheat degree SHe at the outlet of the evaporator 25 calculated based on the evaporator outlet temperature Teo detected by the second temperature sensor 62 and based on the suction pressure Ps detected by the pressure sensor 51 becomes higher than the predetermined superheat degree, and when the suction pressure Ps detected by the pressure sensor 51 becomes lower than a predetermined pressure.
  • predetermined temperature discharge temperature control target value
  • control apparatus 4 detects discharge temperature Td by the first temperature sensor 61, evaporator outlet temperature Teo by the second temperature sensor 62 and bypass outlet temperature Tbo by the third temperature sensor 63 (step 3).
  • control apparatus 4 detects a suction pressure Ps by the pressure sensor 51 (step 2), and calculates saturat ion temperature STs under a pressure of refrigerant sucked into compressor 21 from the detected suction pressure Ps (step 3) .
  • the saturation temperature STs is calculated using a refrigerant physical property equation.
  • control apparatus 4 determines whether the discharge temperature Td is lower than the predetermined discharge temperature (step 5).
  • the control apparatus 4 adjusts an opening degree of the bypass expansion valve 31 such that the superheat degree SHb becomes equal to the superheat degree control target value (step 6). Then, the control apparatus 4 adjusts an opening degree of the main expansion valve 24 such that the discharge temperature Td becomes equal to the discharge temperature control target value (step 7) and returns to step 1.
  • the control apparatus 4 determines whether the superheat degree SHe at the outlet of the evaporator 25 is higher than a predetermined superheat degree (step 8).
  • the control apparatus 4 adjusts the opening degree of the bypass expansion valve 31 such that the superheat degree SHb becomes equal to the bypass superheat degree control target value (step 6), adjusts the opening degree of the main expansion valve 24 such that the discharge temperature Td becomes equal to the discharge temperature control target value (step 7), and the procedure returns to step 1.
  • control apparatus 4 closes the opening degree of the bypass expansion valve 31 by a predetermined first operation amount (step 9).
  • control apparatus 4 determines whether the suction pressure Ps is lower than a predetermined pressure (step 10). If the suction pressure Ps is higher than the predetermined pressure in step 10, it can be considered that the opening degree of the main expansion valve 24 is appropriate and thus, the procedure is returned to step 1 as it is.
  • the control apparatus 4 opens the opening degree of the bypass expansion valve 31 by a predetermined second operation amount (step 11), and the procedure returns to step 1.
  • a bypass passage outlet temperature Tbo is detected by the first temperature sensor 61 which detects temperature of refrigerant discharged from the compressor 21 in the refrigerant circuit 2, the second temperature sensor 62 which detects temperature of refrigerant flowing out from the evaporator 25, the pressure sensor 51 which detects a pressure of refrigerant sucked into the compressor 21, and the third temperature sensor 63 which detects temperature of refrigerant flowing out from the supercooling heat exchanger 23 in the bypass passage 3.
  • the first control apparatus 4A controls the bypass expansion valve 31 such that the superheat degree SHb at the outlet of the bypass passage 3 calculated based on the bypass passage outlet temperature Tbo detected by the third temperature sensor 63 and the suction pressure Ps detected by the pressure sensor 51 becomes equal to the predetermined superheat degree. Further, when temperature detected by the first temperature sensor 61 is lower than predetermined temperature and when the superheat degree SHe at the outlet of the evaporator 25 is higher than a predetermined superheat degree, the first control apparatus 4A controls the bypass expansion valve 31 such that it closes by the predetermined first operation amount.
  • the refrigeration circuit is in a poor-efficient refrigeration cycle state caused by an improper refrigerant flow rate distribution (the circulation amount of refrigerant flowing through the bypass passage 3 is excessively large and the circulation amount of refrigerant flowing through the refrigerant circuit 2 is excessively small).
  • the bypass expansion valve 31 is forcibly closed by the predetermined operation amount, the circulation amount of refrigerant flowing through the bypass passage 3 is reduced, the circulation amount of refrigerant flowing through the refrigerant circuit 2 is increased, and the circulation amount of refrigerant can swiftly be distributed appropriately.
  • the heat absorption amount in the evaporator 25 can sufficiently be secured. It is possible to make full use of the enthalpy difference increasing effect in the evaporator 25 by heat exchange between refrigerant flowing through the refrigerant circuit 2 and refrigerant flowing through the bypass passage 3 in the supercooling heat exchanger 23, and the pressure loss reducing effect of the low pressure refrigerant path by the bypass of refrigerant. High operation efficiency and sufficient heating ability can be obtained even when outside air temperature is low.
  • the second control apparatus 4B controls the main expansion valve 24 such that the discharge temperature Td detected by the first temperature sensor 61 becomes equal to the predetermined temperature.
  • the second control apparatus 4B controls the main expansion valve 24 such that it opens by the second operation amount when temperature detected by the first temperature sensor 61 is lower than the predetermined temperature, when the superheat degree SHe at the outlet of the evaporator 25 calculated based on the evaporator outlet temperature Teo detected by the second temperature sensor 62 and the suction pressure Ps detected by the pressure sensor 51 is higher than the predetermined superheat degree, and when the suction pressure Ps detected by the pressure sensor 51 becomes lower than the predetermined pressure.
  • the main expansion valve 24 can be opened while limiting the current state to a state where the main expansion valve 24 is excessively narrowed. Therefore, abnormal reduction in the suction pressure Ps is reliably prevented, the flow rate distribution can more swiftly be improved, and the reliability of the compressor in addition to the effect of the invention can be enhanced.
  • the predetermined first operation amount of the embodiment is determined in accordance with the superheat degree SHe at the outlet of the evaporator 25 such that the larger the superheat degree SHe at the outlet of the evaporator 25 becomes, the larger the operation amount becomes. According to this configuration, it is possible to determine from the superheat degree SHe at the outlet of the evaporator 25 whether the proper degree of the refrigerant distribution is high or low and since the bypass expansion valve 31 is closed by the operation amount in accordance with the proper degree, the control response is enhanced. Therefore, the effect of the invention can swiftly be obtained and comfort can be enhanced.
  • the predetermined second operation amount of the embodiment is determined in accordance with a pressure such that as a pressure detected by the pressure sensor 51 becomes lower than the predetermined pressure value, the operation amount is more increased. According to this, since the opening operation amount is secured in accordance with a pressure reduction state, it is possible to swiftly handle abrupt variation in the suction pressure Ps caused by variation in the operation state and the load state, and it is possible to especially enhance the reliability of the compressor 21 in the effect of the invention.
  • the pressure sensor 51 is provided between the main accumulator 27 and the position where the bypass passage 3 is connected to the refrigerant circuit 2, but the pressure sensor 51 may be provided at any position of the refrigerant circuit 2 only if the pressure sensor 51 is located between the evaporator 25 and the compressor 21. Alternatively, the pressure sensor 51 may be provided at a location downstream of the supercooling heat exchanger 23 of the bypass passage 3.
  • bypass expansion valve 31 is controlled such that the superheat degree SHb at the outlet of the bypass passage 3 becomes equal to the target value in the embodiment, the controlling method of the bypass expansion valve 31 is not limited to this.
  • the bypass expansion valve 31 may be controlled such that temperature of supercooling degree of the outlet of the supercooling heat exchanger 23 becomes equal to the target value.
  • bypass expansion valve 31 may be controlled based on the supercooling degree of refrigerant at the outlet of the condenser 22.
  • bypass passage 3 branches off from the refrigerant circuit 2 between the supercooling heat exchanger 23 and the main expansion valve 24, and the bypass passage 3 may branch off from the refrigerant circuit 2 between the condenser 22 and the supercooling heat exchanger 23.
  • the main expansion valve 24 and the bypass expansion valve 31 of the invention are expansion valves, and may be expansion devices which recover power from expanding refrigerant.
  • the number of rotations of the expansion device may be controlled by changing a load by a power generator connected to the expansion device.
  • the superheat degree SHe at the outlet of the evaporator 25 is calculated based on the evaporator outlet temperature Teo detected by the second temperature sensor 62 and the suction pressure Ps detected by the pressure sensor 51.
  • steam temperature of the evaporator 25 can be used instead of using the suction pressure Ps detected by the pressure sensor 51. That is, the second temperature sensor 62 is disposed at a position where the steam temperature of the evaporator 25 can be measured (substantially at a central portion of the evaporator 25 where refrigerant flows in a two-phase state under most operation conditions for example), and the steam temperature is detected. If the evaporating temperature is subtracted from temperature detected by the second temperature sensor 62, the superheat degree SHe of the outlet of the evaporator 25 can be calculated.
  • the present invention is especially useful for a hot-water heating apparatus which produces hot water by a refrigeration cycle apparatus and which utilizes the hot water for a heating operation.

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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)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Air Conditioning Control Device (AREA)

Claims (7)

  1. Appareil à cycle de réfrigération (1A) comprenant: un circuit de réfrigération (2) auquel un compresseur (21), un condenseur (22), un échangeur de chaleur de sous-refroidissement (23), un moyen d'expansion principal (24) et un évaporateur (25) sont reliés de manière circulaire les uns aux autres; un passage de dérivation (3) qui se ramifie à partir du circuit de réfrigération (2) entre l'échangeur de chaleur de sous-refroidissement (23) et le moyen d'expansion principal (24), et qui est relié au circuit de réfrigération (2) entre l'évaporateur (25) et le compresseur (21) par l'intermédiaire de l'échangeur de chaleur de sous-refroidissement (23); un moyen d'expansion de dérivation (31) disposé à un emplacement en amont de l'échangeur de chaleur de sous-refroidissement (23) du passage de dérivation (3); un premier capteur de température (61) qui détecte la température d'évacuation du réfrigérant évacué par le compresseur (21); un second capteur de température (62) qui détecte la température de sortie d'évaporateur du réfrigérant s'écoulant hors de l'évaporateur (25) dans le circuit de réfrigération (2); et un appareil de commande (4),
    caractérisé en ce que l'appareil de commande (4) commande le moyen d'expansion de dérivation (31) de telle sorte qu'une quantité de réfrigérant s'écoulant à travers le moyen d'expansion de dérivation (31) diminue lorsque la température d'évacuation qui est détectée par le premier capteur de température (61) est inférieure à la température d'évacuation prédéterminée et le degré de surchauffe de sortie d'évaporateur calculé à partir de la température de sortie d'évaporateur qui est détectée par le second capteur de température (62) est supérieur au degré de surchauffe prédéterminé sur la base de la température d'évacuation et sur la base d'un degré de surchauffe de sortie d'évaporateur calculé à partir de la température de sortie d'évaporateur.
  2. Appareil à cycle de réfrigération (1A) selon la revendication 1, comprenant en outre un capteur de pression (51) qui détecte une pression d'aspiration du réfrigérant aspiré dans le compresseur (21), dans lequel
    l'appareil de commande (4) calcule la température de saturation sous la pression d'aspiration à partir de la pression d'aspiration, et
    l'appareil de commande (4) calcule un degré de surchauffe de sortie de passage de dérivation à partir de la température de saturation et de la température de sortie d'évaporateur.
  3. Appareil à cycle de réfrigération (1A) selon la revendication 1, dans lequel
    à mesure que le degré de surchauffe de sortie d'évaporateur devient plus important, l'appareil de commande (4) augmente davantage l'ouverture variable du moyen d'expansion de dérivation (31).
  4. Appareil à cycle de réfrigération (1A) selon la revendication 2 ou 3, dans lequel
    l'appareil de commande (4) augmente une quantité de réfrigérant s'écoulant à travers le moyen d'expansion principal (24) lorsque la température d'évacuation est inférieure à une température prédéterminée et le degré de surchauffe de sortie d'évaporateur est supérieur à un degré de surchauffe prédéterminé.
  5. Appareil à cycle de réfrigération (1A) selon la revendication 2 ou 3, dans lequel
    l'appareil de commande (4) augmente une quantité de réfrigérant s'écoulant à travers le moyen d'expansion principal (24) lorsque la température d'évacuation est inférieure à une température prédéterminée, le degré de surchauffe de sortie d'évaporateur est supérieur à un degré de surchauffe prédéterminé et la pression d'aspiration est inférieure à une valeur de pression prédéterminée.
  6. Appareil à cycle de réfrigération (1A) selon la revendication 4 ou 5, dans lequel
    à mesure que la pression d'aspiration devient inférieure à la valeur de pression prédéterminée, l'appareil de commande (4) augmente davantage l'ouverture variable du moyen d'expansion principal (24).
  7. Appareil de chauffage à eau chaude comprenant l'appareil à cycle de réfrigération (1A) selon l'une quelconque des revendications 1 à 6.
EP11182247.4A 2010-09-24 2011-09-21 Appareil à cycle de réfrigération et appareil de chauffage d'eau chaude Active EP2434233B1 (fr)

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JP2010213491A JP5533491B2 (ja) 2010-09-24 2010-09-24 冷凍サイクル装置及び温水暖房装置

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EP2434233A3 EP2434233A3 (fr) 2015-03-04
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JP2017088137A (ja) * 2015-11-17 2017-05-25 株式会社ヴァレオジャパン 車両用空調装置の冷凍サイクル及びこれを搭載した車両
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Publication number Publication date
CN102419024B (zh) 2015-02-25
EP2434233A3 (fr) 2015-03-04
DK2434233T3 (da) 2019-08-26
CN102419024A (zh) 2012-04-18
EP2434233A2 (fr) 2012-03-28
JP5533491B2 (ja) 2014-06-25
JP2012067967A (ja) 2012-04-05

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