WO2018100729A1 - Dispositif à cycle de réfrigération - Google Patents

Dispositif à cycle de réfrigération Download PDF

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Publication number
WO2018100729A1
WO2018100729A1 PCT/JP2016/085889 JP2016085889W WO2018100729A1 WO 2018100729 A1 WO2018100729 A1 WO 2018100729A1 JP 2016085889 W JP2016085889 W JP 2016085889W WO 2018100729 A1 WO2018100729 A1 WO 2018100729A1
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WO
WIPO (PCT)
Prior art keywords
compressor
water
discharge pressure
heat exchanger
heater
Prior art date
Application number
PCT/JP2016/085889
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English (en)
Japanese (ja)
Inventor
篤志 佐藤
Original Assignee
三菱電機株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to PCT/JP2016/085889 priority Critical patent/WO2018100729A1/fr
Priority to JP2018553616A priority patent/JP6689404B2/ja
Publication of WO2018100729A1 publication Critical patent/WO2018100729A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H4/00—Fluid heaters characterised by the use of heat pumps
    • F24H4/02—Water heaters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • 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
    • F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
    • 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
    • F25B30/00—Heat pumps
    • F25B30/02—Heat pumps of the compression type
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/12—Hot water central heating systems using heat pumps

Definitions

  • the present invention relates to a refrigeration cycle apparatus that performs an air conditioning operation including cooling and heating and a hot water supply operation.
  • a conventional air conditioning and hot water supply complex system includes, for example, one outdoor unit, a plurality of air conditioning indoor units, and a water heater.
  • the outdoor unit includes a compressor, a four-way valve, an outdoor heat exchanger, and a control device capable of inverter control.
  • Each indoor unit has an indoor heat exchanger
  • the water heater has a water heat exchanger.
  • An expansion valve is provided for each heat exchanger of the indoor heat exchanger and the water heat exchanger (see, for example, Patent Document 1).
  • this combined air-conditioning and hot-water supply system can operate only one indoor unit as a cooling operation or a heating operation, operate all indoor units as a cooling operation or heating operation, and operate only a water heater. In addition, the heating of the indoor unit and the simultaneous operation of the water heater can be performed.
  • the expansion valve is located downstream of the heat exchanger in any of the case where the water heater is operated, the indoor unit is heated, and the indoor unit is heated and the water heater is operated simultaneously. Therefore, the refrigerant flows into both the heat exchanger and the water heat exchanger of the indoor unit. For this reason, when one indoor unit is in a heating operation or a water heater is in operation, high-pressure and high-temperature refrigerant also flows through the stopped indoor unit or water heater.
  • the drain water adheres to the heat exchanger, and the drain water accumulates in the drain pan.
  • the cooling operation is stopped in this state and the water heater is operated, as described above, the high-pressure and high-temperature refrigerant also flows through the heat exchanger of the stopped indoor unit.
  • the drain water on the surface of the heat exchanger and the drain water accumulated in the drain pan evaporate, the interior of the indoor unit becomes hot and humid, and as a result, water droplets adhere to members such as the fan and the casing.
  • the size of the water droplet increases as the temperature of the heat exchanger increases, and the water droplet falls when the gravity of the water droplet becomes larger than the viscous resistance force against the inner wall of the housing of the water droplet.
  • the present invention has been made to solve the above problems, and provides a refrigeration cycle apparatus that prevents water droplets from falling from an indoor unit when a hot water supply operation is performed after the cooling operation of the indoor unit is stopped. To do.
  • the refrigeration cycle apparatus includes a heat source unit including a compressor, a refrigerant circulating through a branch pipe for air conditioning branched from a refrigerant pipe connected to the compressor, and air in an air-conditioning target space.
  • An indoor unit for exchanging heat in the water a hot water heater for exchanging heat between the refrigerant circulating in the hot water branch pipe branched from the refrigerant pipe and water, and a pressure sensor for detecting the discharge pressure of the compressor
  • a controller that controls the compressor according to the operating state of the indoor unit and the water heater, and the controller operates the water heater after stopping the cooling operation of the indoor unit.
  • an upper limit value is set to the target value of the discharge pressure of the compressor, and the compressor is controlled so that the discharge pressure detected by the pressure sensor follows the upper limit value.
  • FIG. 1 It is a conceptual diagram which shows the refrigerant circuit of the air conditioning hot-water supply complex system in Embodiment 1 of this invention. It is sectional drawing which shows the internal structure of the example of 1 structure of the indoor unit shown in FIG. It is a block diagram which shows the example of 1 structure of the control part shown in FIG. It is a flowchart which shows the procedure which determines the control flag regarding control of a compressor about the control method in Embodiment 1 of this invention. It is a flowchart which shows the procedure of the operation
  • FIG. 2 It is a conceptual diagram which shows the refrigerant circuit of the air-conditioning / hot-water supply complex system in Embodiment 2 of this invention. It is a graph which shows transition of the discharge pressure and operation frequency of a compressor, the temperature of the water in a tank, and the state of the power supply of a heater in the case where the water heater shown in FIG. 6 performs a boiling operation. It is a flowchart which shows the procedure of the operation
  • FIG. 1 is a conceptual diagram showing a refrigerant circuit of an air conditioning and hot water supply complex system in Embodiment 1 of the present invention.
  • FIG. 2 is a cross-sectional view showing an internal structure of a configuration example of the indoor unit shown in FIG.
  • FIG. 2 shows the case where the indoor units 302a and 302b shown in FIG. 1 are cassette type indoor units, the indoor units 302a and 302b are not limited to cassette type indoor units.
  • FIG. 2 shows a half cross-sectional structure of the indoor unit 302a.
  • the air conditioning and hot water supply combined system 100 includes a heat source unit 301, indoor units 302 a and 302 b that air-condition an air-conditioning target space, and a water heater 303.
  • a heating device 304 is connected to the water heater 303.
  • a branch unit 305 is provided between the indoor units 302 a and 302 b and the hot water heater 303 and the heat source unit 301.
  • FIG. 1 shows a case where there are two indoor units, the number of indoor units may be one or three or more.
  • the heat source unit 301 includes a compressor 11, a heat exchanger 12, a blower 13, a four-way valve 14, a control unit 15, a throttle unit 16, and an accumulator 10.
  • the compressor 11, the four-way valve 14 and the heat exchanger 12 are connected by a refrigerant pipe 17.
  • the refrigerant pipe 17 is provided with a pressure sensor 18 for detecting the refrigerant discharge pressure on the discharge port side of the compressor 11.
  • the compressor 11, the blower 13, the four-way valve 14, and the pressure sensor 18 are connected to the control unit 15 via signal lines.
  • Compressor 11 compresses and discharges refrigerant to be sucked.
  • the blower 13 supplies outside air to the heat exchanger 12.
  • the heat exchanger 12 performs heat exchange between the refrigerant and the outside air.
  • the four-way valve 14 switches the refrigerant flow path.
  • the pressure sensor 18 outputs the detected discharge pressure value to the control unit 15.
  • the branch unit 305 has expansion valves 51a to 51c.
  • the expansion valves 51a to 51c are provided in the air conditioning branch pipes 17a and 17b and the hot water supply branch pipe 17c branched from the refrigerant pipe 17 extending from the throttle portion 16 of the heat source unit 301.
  • the air conditioning branch pipes 17a and 17b return to the branch unit 305 through the indoor units 302a and 302b.
  • the hot water branch pipe 17 c returns to the branch unit 305 through the hot water heater 303.
  • the air conditioning branch pipes 17 a and 17 b extending from the indoor units 302 a and 302 b and the hot water supply branch pipe 17 c extending from the hot water heater 303 are joined to each other and connected to the four-way valve 14 side of the refrigerant pipe 17.
  • the expansion valves 51a to 51c are connected to the control unit 15 through signal lines.
  • the indoor unit 302a includes a heat exchanger 21a and a blower 22a.
  • the indoor unit 302b includes a heat exchanger 21b and a blower 22b.
  • the heat exchanger 21a is connected to the air conditioning branch pipe 17a.
  • the heat exchanger 21b is connected to the air conditioning branch pipe 17b.
  • the indoor unit 302a is provided with a drain pan 23a for collecting drain water condensed on the surface of the heat exchanger 21a in the direction of gravity of the heat exchanger 21a.
  • the indoor unit 302b is also provided with a drain pan (not shown) in the direction of gravity of the heat exchanger 21b.
  • FIG. 2 shows a state in which drain water 61 is attached to the surface of the heat exchanger 21a when the indoor unit 302a performs a cooling operation.
  • FIG. 2 shows a state in which drain water 61 adhering to the surface of the heat exchanger 21a is dropped and the drain water 62 is accumulated in the drain pan 23a.
  • the blower 22a shown in FIG. 1 sucks the air in the air-conditioning target space into the indoor unit 302a and supplies it to the heat exchanger 21a.
  • the blower 22b shown in FIG. 1 sucks the air in the air-conditioning target space into the indoor unit 302b and supplies it to the heat exchanger 21b.
  • the heat exchangers 21a and 21b exchange heat between the air in the air-conditioning target space and the refrigerant.
  • the blowers 22a and 22b are connected to the control unit 15 through signal lines.
  • the water heater 303 has a heat exchanger 31, a heat exchanger 33, a three-way valve 39, pumps 34 and 35, and a tank 36.
  • the heat exchanger 31, the heat exchanger 33, and the pump 34 are connected in order, and a primary water circuit 37 in which water circulates through these devices is configured.
  • the primary water circuit 37 is an example of a fluid circuit.
  • the heat exchanger 33, the pump 35, and the tank 36 are connected in order, and the secondary water circuit 38 which water circulates through these apparatuses is comprised.
  • the secondary water circuit 38 is an example of a water circuit.
  • the tank 36 is supplied with tap water from the outside.
  • the tank 36 is connected to a shower or the like in which hot water after heat exchange is used.
  • the heat exchanger 31 performs heat exchange between the water circulating in the primary water circuit 37 and the refrigerant passing through the hot water supply branch pipe 17c.
  • the heat exchanger 33 performs heat exchange between the water circulating in the primary water circuit 37 and the water in the tank 36.
  • a three-way valve 39 is provided between the heat exchanger 31 and the heat exchanger 33.
  • the primary water circuit 37 is branched from the three-way valve 39, and a heating device 304 is connected on the way, and a heating circuit 41 that joins the junction 40 between the heat exchanger 33 and the pump 34 is connected.
  • the three-way valve 39 and the pumps 34 and 35 are connected to the control unit 15 via signal lines.
  • FIG. 3 is a block diagram illustrating a configuration example of the control unit illustrated in FIG.
  • the control unit 15 includes a memory 151 that stores a program, a CPU (Central Processing Unit) 152 that executes processing according to the program, and a timer 153 that measures time.
  • the control unit 15 is, for example, a microcomputer.
  • the control unit 15 activates and stops the compressor 11 and the blowers 13, 22 a, and 22 b, the operation frequency, the operation frequency of the four-way valve 14 according to the operation instruction to the indoor units 302 a and 302 b and the operation state of the indoor units 302 a and 302 b.
  • the flow path switching and the opening degree of the throttle portion 16 and the expansion valves 51a and 51b are controlled.
  • control unit 15 switches the flow path of the three-way valve 39, starts and stops the pumps 34 and 35, the throttle unit 16 and the expansion valve according to the operation instruction to the water heater 303 and the operation state of the water heater 303.
  • the opening degree of 51c is controlled.
  • a temperature sensor (not shown) that detects the room temperature may be provided in the indoor units 302a and 302b.
  • the control unit 15 may control the compressor 11, the blowers 13, 22a, 22b, the throttle unit 16, and the expansion valves 51a, 51b so that the room temperature becomes the set temperature.
  • the heat source unit 301, the indoor units 302a, 302b, and the hot water heater 303 are connected, and the heat source unit 301, the indoor units 302a, 302b, the heat source unit 301, and the hot water heater 303 are refrigerated.
  • a cycle is constructed.
  • the solid line arrow shown in FIG. 1 shows the flow of the refrigerant when the water heater 303 is operating. Dashed arrows indicate the flow of water in the water heater 303.
  • FIG. 1 the case where hot water is circulated also in the heating apparatus 304 is shown.
  • FIG. 4 is a flowchart showing a procedure for determining a control flag related to control of the compressor in the control method according to Embodiment 1 of the present invention.
  • the control unit 15 is instructed to the indoor units 302a and 302b.
  • the operating state it is determined whether the compressor 11 is operated for cooling or heating.
  • the cooling use is a case where one or both of the indoor unit 302a and the indoor unit 302b is in the cooling operation.
  • the heating application includes the case where one of or both of the indoor unit 302a and the indoor unit 302b is in the heating operation, and the case where the water heater 303 is operated.
  • the memory 151 stores information of a control flag indicating whether or not to perform control for limiting the discharge pressure of the compressor 11. In the control flag, an invalid state in which the discharge pressure is not limited is set as an initial value.
  • step S1 shown in FIG. 4 the control unit 15 determines which application the compressor 11 is operating between heating and cooling.
  • the control unit 15 proceeds to step S3 and updates the control flag to the valid state.
  • the control unit 15 determines in step S1 that the compressor 11 is operating for heating, the process proceeds to step S2.
  • step S ⁇ b> 2 the control unit 15 starts the timer 153, and measures an operation time Tw that is an accumulated time during which the compressor 11 is operated for heating after the operation for cooling is stopped.
  • step S3 When the control flag is set to the valid state in step S3, the control unit 15 sets the value of the operation time Tw to 0 in step S4.
  • step S5 the control unit 15 compares the operation time Tw with the lower limit value Twlim of the operation time for heating use. If the operation time Tw is equal to or greater than the lower limit value Twlim, the control unit 15 proceeds to step S6 and updates the control flag to an invalid state.
  • step S5 when the operation time Tw is less than the lower limit value Twlim, the control unit 15 returns to step S1.
  • the control flag is set to the valid state or the invalid state according to the use of the compressor 11 and the operation time Tw. If the compressor 11 is in cooling operation, the control flag is set to the valid state. Further, when the compressor 11 is switched from the cooling use to the heating use operation, if the operation time for the heating use is less than a predetermined time, the control flag is maintained in an effective state, and the operation time for the heating use is set in advance. If a predetermined time or more elapses, the control flag is set to an invalid state. When the control flag is in the valid state, the control unit 15 sets an upper limit value for the target value of the discharge pressure of the compressor 11 and controls the compressor 11 so that the discharge pressure follows the upper limit value. When the control flag is invalid, the control unit 15 does not limit the discharge pressure of the compressor 11.
  • the inside of the housing of the indoor unit 302a is in a state where the drain water 61 adheres to the heat exchanger 21a and the drain water 62 accumulates in the drain pan 23a.
  • the inside of the housing of the indoor unit 302b is also in the same state as the indoor unit 302a.
  • FIG. 5 is a flowchart showing an operation procedure based on the control flag determined in FIG. 4 for the control method according to the first embodiment of the present invention.
  • the memory 151 stores a limit value Pdmlim of the target value of the discharge pressure of the compressor 11.
  • step S7 the control unit 15 determines the state of the control flag set by the procedure shown in FIG.
  • the control unit 15 proceeds to step S8 and compares the target discharge pressure Pdm with the limit value Pdmlim.
  • step S8 when the target discharge pressure Pdm is larger than the limit value Pdmlim, the control unit 15 proceeds to step S9 and updates the target discharge pressure Pdm to the limit value Pdmlim.
  • the control unit 15 proceeds to step S10 and does not correct the target discharge pressure Pdm.
  • steps S8 to S10 when the control flag is in the valid state, the target discharge pressure can be limited to a predetermined limit value or less.
  • step S7 when the control flag is invalid, the control unit 15 does not correct the target discharge pressure Pdm.
  • the target discharge pressure Pdm can be limited only when control relating to the limitation of the discharge pressure is required, that is, only when the control flag is in an effective state.
  • the control unit 15 determines the target discharge pressure Pdm in any of Step S9, Step S10, and Step S12, the discharge pressure Pd is determined using the values of the discharge pressure Pd and the target discharge pressure Pdm detected by the pressure sensor 18.
  • the operating frequency of the compressor 11 is controlled so as to follow the target discharge pressure Pdm (step S11).
  • the heat exchanger 21a functions as an evaporator, and as shown in FIG. 2, drain water 61 is formed on the surface of the heat exchanger 21a.
  • the drain water 62 accumulates in the drain pan 23a.
  • the control unit 15 fully closes the expansion valve 51a and switches the flow path of the four-way valve 14. Specifically, the control unit 15 controls the four-way valve 14 so that the refrigerant discharged from the compressor 11 flows into the hot water supply branch pipe 17 c via the four-way valve 14. As a result, the high-pressure and high-temperature refrigerant discharged from the compressor 11 flows from the refrigerant pipe 17 to the heat exchanger 31 via the hot water supply branch pipe 17c.
  • the control unit 15 controls the operation frequency of the compressor 11 so that the discharge pressure Pd of the compressor 11 follows the limit value Pdmlim lower than the normal target discharge pressure Pdm as necessary.
  • Pdmlim lower than the normal target discharge pressure Pdm as necessary.
  • the combined air conditioning and hot water supply system 100 circulates through a heat source unit 301 including the compressor 11 and air conditioning branch pipes 17a and 17b branched from the refrigerant pipe 17 connected to the compressor 11.
  • Hot water supply for exchanging heat between refrigerant and water circulating through the indoor units 302a and 302b for exchanging heat between the refrigerant and the air in the air-conditioning space, and the hot water branch pipe 17c branched from the refrigerant pipe 17
  • the control unit 15 stops the cooling operation of the indoor units 302a and 302b.
  • the upper limit value is set to the target value of the discharge pressure of the compressor 11 so that the discharge pressure detected by the pressure sensor 18 is lower than usual. And it controls the machine 11.
  • the control unit 15 stops the operation after performing the cooling operation of one or both of the indoor units 302a and 302b, and starts the operation of the water heater 303.
  • the discharge pressure of the machine 11 is suppressed to a pressure lower than usual. Therefore, the temperature of the refrigerant flowing into the water heater 303 is suppressed from becoming too high, and even if a part of the refrigerant flows into the air conditioning branch pipes 17a and 17b of the stopped indoor units 302a and 302b, the heat exchanger
  • the temperature of 21a, 21b is prevented from rising excessively, and excessive evaporation of the drain water 61, 62 is suppressed.
  • the inside of the housing is in a high temperature and high humidity state and water droplets are prevented from adhering to the inner wall of the housing, and the attached water droplets can be prevented from falling from the suction ports of the indoor units 302a and 302b.
  • the control unit 15 discharges the compressor 11 when the operation time Tw of the compressor 11 is equal to or less than a predetermined lower limit value Twlim after the cooling operation of the indoor units 302a and 320b is stopped.
  • An upper limit value of pressure may be set.
  • the operation time Tw is less than or equal to the lower limit value Twlim, water droplets may adhere to the inner walls of the casings of the indoor units 302a and 302b, but this can be prevented.
  • the operation time Tw is larger than the lower limit value Twlim, the discharge pressure of the compressor 11 is not limited, so the boiling time in the water heater 303 can be shortened.
  • the operation time Tw used for determining whether or not to set the upper limit value for the target value of the discharge pressure includes the case where the control unit 15 performs the heating operation of the indoor units 302a and 302b. It may be the time for operating the compressor 11 for the purpose. In this case, even when the indoor units 302a and 302b stop the cooling operation and are switched to the simultaneous operation of the heating operation and the hot water supply operation of the indoor units 302a and 302b, generation of water droplets in the casing of the indoor unit is suppressed. Can do.
  • Embodiment 2 As described in the first embodiment, when the upper limit value is set to the target value of the discharge pressure of the compressor 11, for example, when the water heater 303 performs a boiling operation for a shower application, the boiling time becomes longer. There is a case.
  • a heater is provided in the water heater 303 to suppress an increase in boiling time.
  • FIG. 6 is a conceptual diagram showing a refrigerant circuit of the air-conditioning and hot-water supply complex system in Embodiment 2 of the present invention.
  • the water heater 303 has a heater 32.
  • the heater 32 is provided between the three-way valve 39 and the heat exchanger 31.
  • a power source (not shown) that supplies power to the heater 32 is connected to the heater 32.
  • the control unit 15 is connected to the power source of the heater 32 via a signal line.
  • the control unit 15 controls the power on and off of the heater 32 when an instruction to start operation of the water heater 303 is input from the user in a state where the upper limit value is set to the target value of the discharge pressure of the compressor 11. To do.
  • FIG. 7 is a graph showing the transition of the discharge pressure and operating frequency of the compressor, the temperature of water in the tank, and the state of the power supply of the heater when the water heater shown in FIG. 6 performs a boiling operation. is there.
  • the horizontal axis of the four graphs shown in FIG. 7 is time.
  • the vertical axis of the uppermost graph indicates the change in the discharge pressure Pd of the compressor 11.
  • This graph is referred to as a discharge pressure graph.
  • the vertical axis of the second graph from the top indicates the change in the operating frequency F of the compressor 11.
  • This graph is referred to as a frequency graph.
  • the vertical axis of the second graph from the bottom indicates the change in the water temperature T tank of the tank 36.
  • This graph is referred to as a water temperature graph.
  • the vertical axis of the lowermost graph indicates the change in the state where the heater 32 is on and off. This graph is referred to as a heater state graph.
  • the target temperature of the water temperature in the tank 36 is expressed as Tref.
  • FIG. 8 is a flowchart showing an operation procedure based on the control flag determined in FIG. 4 for the control method according to the second embodiment of the present invention.
  • steps S7 to S12 are the same as the operations described with reference to FIG.
  • the memory 151 illustrated in FIG. 3 stores a lower limit frequency Fmin that is a lower limit value of the operating frequency F of the compressor 11.
  • step S11 immediately after the start of boiling, the control unit 15 increases the operating frequency F of the compressor 11 and controls the compressor 11 so that the discharge pressure Pd matches the target discharge pressure Pdm. Thereafter, the operating frequency F of the compressor 11 increases or decreases so that the discharge pressure Pd becomes stable at the target discharge pressure Pdm.
  • the operating frequency F of the compressor 11 gradually decreases and finally sticks to the lower limit frequency Fmin.
  • the state where the operating frequency F of the compressor 11 is stuck to the lower limit frequency Fmin indicates that the amount of heat supplied from the heat source unit 301 is insufficient, and operating for a long time in this state extends the boiling time. It leads to.
  • step S13 the control unit 15 determines whether or not the discharge pressure Pd is equal to or higher than the target discharge pressure Pdm. When the discharge pressure Pd is smaller than the target discharge pressure Pdm, the control unit 15 returns to step S7. In step S13, when the discharge pressure Pd is equal to or higher than the target discharge pressure Pdm, the control unit 15 proceeds to step S14 and determines whether or not the operation frequency F is equal to the lower limit frequency Fmin. When the operating frequency F is not equal to the lower limit frequency Fmin, the control unit 15 returns to step S7. In step S14, when the operating frequency F is equal to the lower limit frequency Fmin, the control unit 15 proceeds to step S15 and stops the compressor 11. Subsequently, the control unit 15 proceeds to step S ⁇ b> 16, turns on the heater 32, and starts supplying power to the heater 32.
  • step S ⁇ b> 16 the control unit 15 keeps the heater 32 powered on until the water temperature Ttank becomes equal to or higher than the target temperature Tref.
  • the control unit 15 proceeds to step S17, turns off the power supply of the heater 32, and stops the power supply to the heater 32.
  • the control unit 15 performs switching between operation and stop of the compressor 11 and switching between power supply to the heater 32 and power supply stop based on the discharge pressure Pd and the operation frequency F of the compressor 11. Is going. For example, in steps S13 to S16 shown in FIG. 8, the control unit 15 performs compression from a state in which the compressor 11 is operated but power is not supplied to the heater 32 based on the discharge pressure Pd and the operating frequency F of the compressor 11. This means that the operation of the machine 11 is stopped and the heater 32 is switched to a state where electric power is supplied. Moreover, when returning to step S7 by determination of step S13 and step S14, the control part 15 operates the compressor 11 without supplying electric power to the heater 32 based on the discharge pressure Pd or the operating frequency F of the compressor 11. That would be the choice.
  • step S15 of the flowchart shown in FIG. 8 the control unit 15 may proceed to step S16 and start supplying power to the heater 32 while the operation of the compressor 11 is continued.
  • the heat exchanger 31 can use both the heat obtained in the refrigeration cycle and the heat generated by the heater 32.
  • the control unit 15 stops the compressor 11 and supplies power to the heater 32. Also good.
  • Embodiment 2 when the hot water supply operation is started after the cooling operation of one or both of the indoor units 302a and 302b is stopped, the control unit 15 not only suppresses the discharge pressure of the compressor 11. Based on the discharge pressure Pd and the operating frequency F of the compressor 11, the operation and stop of the compressor 11 are switched and the power supply of the heater 32 is switched on and off. Therefore, not only the effect similar to Embodiment 1 is acquired but it can suppress that the boiling time in the water heater 303 becomes long. Since the control unit 15 switches the operation based on the discharge pressure Pd and the operation frequency F of the compressor 11, it is not necessary to provide a new sensor.
  • the control unit 15 determines whether to switch the operation and stop of the compressor 11 and to switch on and off the power of the heater 32 based on the discharge pressure Pd and the operation frequency of the compressor 11. Although it is performed based on F, it may be performed based on the amount of heat of the heat exchanger 31. In this case, since the control unit 15 switches the operation based on the amount of heat actually required, the effect of suppressing an increase in the boiling time is improved.
  • the amount of heat of the heat exchanger 31 can be calculated from, for example, the difference between the incoming water temperature to the heat exchanger 31 and the outgoing water temperature from the heat exchanger 31 and the water flow rate of the pump 34. An example is described below.
  • FIG. 9 is a block diagram illustrating an example of a configuration electrically connected to the control unit illustrated in FIG.
  • the control unit 15 is connected to the heater 32, the incoming water temperature sensor 42, the outgoing water temperature sensor 43, and the flow rate sensor 44 through signal lines in addition to the devices shown in FIG. 3.
  • the incoming water temperature sensor 42 and the flow rate sensor 44 are provided between the pump 34 and the heat exchanger 31.
  • the outlet temperature sensor 43 is provided between the heat exchanger 31 and the three-way valve 39.
  • the incoming water temperature sensor 42 detects the temperature of the water flowing into the heat exchanger 31 as the incoming water temperature.
  • the outlet water temperature sensor 43 detects the temperature of the water flowing out from the heat exchanger 31 as the outlet water temperature.
  • the flow sensor 44 detects the flow rate of water discharged from the pump 34 and flowing into the heat exchanger 31.
  • the amount of heat per unit time is Q [J / min], the density of water is ⁇ [g / cm 3 ], the flow rate per unit time is L [cm 3 / min], and the temperature difference between the incoming water temperature Tin and the outgoing water temperature Tout Is ⁇ T [K], and the specific heat of water is C [J / g ⁇ K].
  • the memory 151 stores the density ⁇ of water, the specific heat C, and the formula (1).
  • the memory 151 records a threshold value for determining the operation and stop of the compressor 11 and the supply and stop of power to the heater 32 with respect to the calculated heat quantity Q.
  • the memory 151 includes a first threshold value that determines whether or not to use both the compressor 11 and the heater 32, and a second threshold value that determines which of the compressor 11 and the heater 32 is used. I remember it.
  • the control part 15 may change the threshold value which the memory 151 memorize
  • the control unit 15 calculates a temperature difference ⁇ T from the incoming water temperature Tout received from the incoming water temperature sensor 43 and the incoming water temperature Tin received from the incoming water temperature sensor 42. Then, the controller 15 calculates the heat quantity Q by substituting the flow rate L received from the flow rate sensor 44 and the temperature difference ⁇ T into the equation (1). Further, the control unit 15 compares the calculated heat quantity Q with a threshold value stored in the memory 151. When the amount of heat Q is less than the first threshold value, the boiling time may be long, so the control unit 15 performs both the operation of the compressor 11 and the power supply to the heater 32.
  • the control unit 15 stops the compressor 11 and supplies power to the heater 32. I do.
  • the controller 15 does not supply power to the heater 32 and operates the compressor 11 because sufficient heat is obtained for boiling by the refrigeration cycle by the operation of the compressor 11. I do.
  • the criteria for switching between the operation and stop of the compressor 11 and the power supply to the heater 32 and switching between the stop are determined by the discharge pressure and operation frequency of the compressor 11 and the heat exchanger 31. It is not limited to the amount of heat exchanged and the coefficient of performance of the refrigeration cycle.
  • the control unit 15 may perform switching between operation and stop of the compressor 11 and switching between power supply to the heater 32 and power supply stop based on the state of the refrigeration cycle including these determination criteria.
  • Embodiments 1 and 2 have been described in the case where the refrigeration cycle apparatus is an air conditioning and hot water supply combined system as an embodiment of a refrigeration cycle apparatus that performs an air conditioning operation including cooling and heating and a hot water supply operation.
  • the present invention is not limited to those described in the first and second embodiments.
  • the control unit 15 measures the operation time Tw for heating use of the compressor 11 after the cooling operation is stopped.
  • the control unit 15 may adopt the minimum value among the plurality of operation times Tw as the operation time Tw that is a criterion for determining whether or not the upper limit value is set in the compressor 11. Accordingly, it is possible to determine whether or not the discharge pressure control of the compressor 11 is necessary from the operation state of each indoor unit, which cannot be obtained when the operation time focusing on one compressor 11 is used as a reference. it can. As a result, even if the plurality of indoor units stop the cooling operation at different times, the effect of preventing the drop of water droplets can be obtained more reliably.
  • the heating application of the compressor 11 is applied not only to the boiling operation in the water heater 303 but also to the heating operation of at least one of the indoor units 302a and 302b, or the heating operation by the water heater 303 using the heating device 304. be able to.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Air Conditioning Control Device (AREA)

Abstract

Ce dispositif à cycle de réfrigération comprend : une unité de source de chaleur comprenant un compresseur; une unité intérieure qui effectue un échange de chaleur entre l'air dans un espace à climatiser et un fluide frigorigène s'écoulant et circulant à travers un tuyau de dérivation de climatisation qui se ramifie à partir d'un tuyau de fluide frigorigène relié au compresseur; un chauffe-eau qui effectue un échange de chaleur entre l'eau et un fluide frigorigène s'écoulant et circulant à travers un tuyau de dérivation de chauffage d'eau qui se ramifie à partir du tuyau de fluide frigorigène; un capteur de pression qui détecte la pression de décharge du compresseur; et une unité de commande qui commande le compresseur en fonction des états de fonctionnement de l'unité intérieure et du chauffe-eau. Lorsque le chauffe-eau est actionné après que l'opération de refroidissement de l'unité intérieure soit arrêtée, l'unité de commande règle une valeur limite supérieure comme valeur cible pour la pression de décharge du compresseur et commande le compresseur de telle sorte que la pression de décharge détectée par le capteur de pression suit la valeur limite supérieure.
PCT/JP2016/085889 2016-12-02 2016-12-02 Dispositif à cycle de réfrigération WO2018100729A1 (fr)

Priority Applications (2)

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PCT/JP2016/085889 WO2018100729A1 (fr) 2016-12-02 2016-12-02 Dispositif à cycle de réfrigération
JP2018553616A JP6689404B2 (ja) 2016-12-02 2016-12-02 冷凍サイクル装置

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PCT/JP2016/085889 WO2018100729A1 (fr) 2016-12-02 2016-12-02 Dispositif à cycle de réfrigération

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WO2018100729A1 true WO2018100729A1 (fr) 2018-06-07

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109931687A (zh) * 2019-02-22 2019-06-25 珠海格力电器股份有限公司 换热器及具有其的温度调节系统

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JPH09264597A (ja) * 1996-03-28 1997-10-07 Mitsubishi Electric Corp 分離型空気調和機
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JPS611968A (ja) * 1984-06-13 1986-01-07 三菱電機株式会社 冷暖房・給湯ヒ−トポンプ装置
JPS61149760A (ja) * 1984-12-21 1986-07-08 Mitsubishi Electric Corp ヒ−トポンプ式給湯機
JPH09264597A (ja) * 1996-03-28 1997-10-07 Mitsubishi Electric Corp 分離型空気調和機
JP2006234296A (ja) * 2005-02-25 2006-09-07 Mitsubishi Heavy Ind Ltd マルチ型空気調和装置
WO2012085970A1 (fr) * 2010-12-22 2012-06-28 三菱電機株式会社 Dispositif composite de fourniture d'eau chaude et de climatisation
WO2012111063A1 (fr) * 2011-02-14 2012-08-23 三菱電機株式会社 Dispositif à cycle de réfrigération et procédé de commande de cycle de réfrigération
JP2013079769A (ja) * 2011-10-05 2013-05-02 Hitachi Appliances Inc ヒートポンプ給湯機及び冷凍サイクル
JP2013160485A (ja) * 2012-02-08 2013-08-19 Hitachi Appliances Inc ヒートポンプ式液体加熱装置
JP2015059691A (ja) * 2013-09-18 2015-03-30 三菱電機株式会社 空気調和機及び空気調和システム
JP2015098982A (ja) * 2013-11-19 2015-05-28 三菱電機株式会社 温冷水空調システム
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Publication number Priority date Publication date Assignee Title
CN109931687A (zh) * 2019-02-22 2019-06-25 珠海格力电器股份有限公司 换热器及具有其的温度调节系统

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