EP1972871B1 - Heißwassersystem - Google Patents

Heißwassersystem Download PDF

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Publication number
EP1972871B1
EP1972871B1 EP07254438.0A EP07254438A EP1972871B1 EP 1972871 B1 EP1972871 B1 EP 1972871B1 EP 07254438 A EP07254438 A EP 07254438A EP 1972871 B1 EP1972871 B1 EP 1972871B1
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EP
European Patent Office
Prior art keywords
refrigerant
temperature
heat exchanger
pressure
detection means
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.)
Not-in-force
Application number
EP07254438.0A
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English (en)
French (fr)
Other versions
EP1972871A2 (de
EP1972871A3 (de
Inventor
Kazuki c/o Mitsubishi Electric Corp. Okada
Yoshikazu c/o Mitsubishi Electric Corp. Ono
Hirokuni c/o MITSUBISHI Electric Corp. SHIBA
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Publication of EP1972871A2 publication Critical patent/EP1972871A2/de
Publication of EP1972871A3 publication Critical patent/EP1972871A3/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
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F25B49/027—Condenser control arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D19/00—Details
    • F24D19/10—Arrangement or mounting of control or safety devices
    • F24D19/1006—Arrangement or mounting of control or safety devices for water heating systems
    • F24D19/1051—Arrangement or mounting of control or safety devices for water heating systems for domestic hot water
    • F24D19/1054—Arrangement or mounting of control or safety devices for water heating systems for domestic hot water the system uses a heat pump
    • 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
    • F24H15/00—Control of fluid heaters
    • F24H15/20—Control of fluid heaters characterised by control inputs
    • F24H15/227—Temperature of the refrigerant in heat pump cycles
    • 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
    • F24H15/00—Control of fluid heaters
    • F24H15/20—Control of fluid heaters characterised by control inputs
    • F24H15/242—Pressure
    • 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
    • F24H15/00—Control of fluid heaters
    • F24H15/30—Control of fluid heaters characterised by control outputs; characterised by the components to be controlled
    • F24H15/375—Control of heat pumps
    • F24H15/38—Control of compressors of heat pumps
    • 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
    • F24H15/00—Control of fluid heaters
    • F24H15/30—Control of fluid heaters characterised by control outputs; characterised by the components to be controlled
    • F24H15/375—Control of heat pumps
    • F24H15/385—Control of expansion valves of heat pumps
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/19—Calculation of parameters
    • 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
    • F25B2600/02—Compressor control
    • F25B2600/025—Compressor control by controlling speed
    • 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
    • F25B2600/19—Refrigerant outlet condenser 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
    • F25B2600/21—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
    • F25B2600/2513—Expansion 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
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1931—Discharge pressures
    • 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
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge side of the compressor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2116—Temperatures of a condenser
    • F25B2700/21163—Temperatures of a condenser of the refrigerant at the outlet of the condenser

Definitions

  • the present invention relates to a heat-pump hot water system equipped with a plate heat exchanger.
  • a general air conditioner controls a room temperature in such a manner as to calculate the difference between a temperature set by a remote control or the like and an actual room temperature, wherein when the difference is large, the speed of operation of a compressor is increased to enhance the performance of the air conditioner so that the actual room temperature reaches the set temperature as fast as possible.
  • the speed of operation of the compressor is decreased to reduce the performance of the air conditioner to save power and prevent the conditioner from being stopped because of overshooting of the room temperature relative to the set temperature.
  • a compressor In a hot water system, a compressor can be controlled by controlling a condensing temperature so as to reach a target condensing temperature in the same manner as the above because the condensing temperature depend on a target hot water temperature.
  • An example of the conventional air conditioner is disclosed in which the compressor is controlled according to the deviation between the condensing temperature of the refrigerant based on the pressure of the high-pressure refrigerant detected by a high-pressure sensor and a target condensing temperature (refer to Japanese Unexamined Patent Application Publication No. 2002-327949 (p. 4, Fig. 1 )).
  • the conventional air conditioner discloses a technique for controlling a compressor using a high-pressure sensor, it does not refer to application of this technique to a hot water system equipped with a plate heat exchanger.
  • the refrigerant flows in the plate heat exchanger acting as a condenser. Therefore, it is impossible to detect the condensing temperature by temperature detection means mounted on the surface, thus posing the problem that the compressor cannot be controlled according to the condensing temperature of the refrigerant.
  • UK Patent Application GB 2 414 289 discloses a heat pump installation containing an outdoor unit containing an evaporator.
  • the outdoor unit may also include a compressor and an electronically controlled expansion valve.
  • a first condenser is also disclosed.
  • European Patent Application EP 0 750 166 A2 discloses a refrigerant circulating system containing a four-way valve.
  • the present invention is made to solve the above problems. Accordingly, it is an object of the invention to provide a hot water system equipped with a plate heat exchanger capable of controlling a compressor so that the condensing temperature calculated from the pressure detected by pressure detection means reaches a target condensing temperature and performing subcooling control and superheat control using the calculated condensing temperature.
  • Fig. 1 is a refrigerant circuit diagram of a hot water system according to an example.
  • Fig. 2 is a graph showing the relationship between condensing pressure and condensing temperature of a refrigerating cycle.
  • the heat-pump hot water system includes a compressor 1, a four-way valve 2 for switching a refrigerant circuit, a plate heat exchanger 10 for exchanging heat between water and a refrigerant, a first electronic expansion valve 6 for controlling the flow rate of the refrigerant to decrease the pressure, a receiver 7 for holding an excess refrigerant, a second electronic expansion valve 8 for controlling the flow rate of the refrigerant to decrease the pressure, and a heat exchanger 9 for exchanging heat between air and the refrigerant, which are connected in order by a pipeline 3 and housed in a hot water system outdoor unit 40.
  • a pipe connecting the outlet of the compressor 1 and the four-way valve 2 for switching the refrigerating circuit has pressure detection means Pd for detecting the pressure of the discharged refrigerant.
  • the circuit has a structure in which the heat exchanger of the indoor unit of a so-called air conditioner is replaced with the plate heat exchanger 10 for exchanging heat between water and the refrigerant.
  • the plate heat exchanger 10 is, however, housed in the hot water system outdoor unit 40, as shown in Fig. 1 .
  • the pipeline for connection is therefore very short.
  • the refrigerant converted to high-pressure high-temperature gas in the compressor 1 is discharged from the compressor 1 and fed to the four-way valve 2 for switching the circuit.
  • the four-way valve 2 is fixed so as to feed the refrigerant discharged from the compressor 1 to the plate heat exchanger 10.
  • the refrigerant discharged from the four-way valve 2 is fed to the plate heat exchanger 10.
  • the refrigerant fed to the plate heat exchanger 10 exchanges heat with the water passing through a water pipe 50, and is condensed and in the plate heat exchanger 10 to radiate heat.
  • the refrigerant is condensed into a high-pressure normal-temperature liquid refrigerant in the plate heat exchanger 10.
  • the water obtains heat from the refrigerant to increase its temperature, and is discharged.
  • the condensed liquid refrigerant is decreased in pressure by the first electronic expansion valve 6.
  • the first electronic expansion valve 6 controls the refrigerant that is condensed by the plate heat exchanger 10 acting as a condenser according to the degree of subcooling.
  • the plate heat exchanger 10 has a structure in which the refrigerant and water flow between plates alternately to exchange heat. Therefore, it is impossible to dispose a temperature sensor for sensing the condensing temperature in the middle of the plate heat exchanger 10.
  • the pressure detection means Pd is used to detect the pressure of the refrigerant discharged from the compressor 1. That is, the pipe from the compressor 1 to the plate heat exchanger 10 is so short that pressure loss is low, so that the pressure detected by the pressure detection means Pd is substantially equal to the condensing pressure of the refrigerant in the plate heat exchanger 10.
  • the graph of Fig. 2 of the relationship between the condensing pressure and the condensing temperature of the refrigerating cycle there is a certain correlation between the condensing pressure and the condensing temperature (saturation temperature). Therefore, if the condensing pressure is known, the condensing temperature (saturation temperature) can be found. For example, in the case where the refrigerant is R410A, the condensing temperature (saturation temperature) at a condensing pressure of 2.7 MPa is 46°C, as shown in Fig. 2 .
  • the saturation temperature T10 of the refrigerant can be calculated from the condensing pressure of the refrigerant in the plate heat exchanger 10.
  • the degree of subcooling can be calculated as the difference between the saturation temperature T10 of the refrigerant and the actual condensing temperature of the liquid refrigerant detected by a temperature sensor Tix installed at the outlet of the plate heat exchanger 10.
  • the degree of opening of the first electronic expansion valve 6 When the degree of subcooling is low, the degree of opening of the first electronic expansion valve 6 is decreased so that the liquid of the refrigerant condensed by the plate heat exchanger 10 is increased to thereby increase the degree of subcooling. In contrast, when the degree of subcooling is high, the degree of opening of the first electronic expansion valve 6 is increased so that the liquid of the refrigerant condensed by the plate heat exchanger 10 is decreased to thereby decrease the degree of subcooling.
  • the degree of opening of the first electronic expansion valve 6 is controlled according to the calculated degree of subcooling to control the degree of subcooling.
  • the decompressed refrigerant becomes a low-presser low-temperature liquid refrigerant and enters the receiver 7 connected ahead thereof.
  • the receiver 7 holds an excess refrigerant.
  • the refrigerant discharged from the receiver 7 is again reduced in pressure by the second electronic expansion valve 8..
  • the decompressed refrigerant flows into the heat exchanger 9 that exchanges heat between air and the refrigerant.
  • the refrigerant flowing into the heat exchanger 9 Since the refrigerant flowing into the heat exchanger 9 is low in temperature, it receives heat from the air to evaporate into a low-pressure low-temperature gas refrigerant. In contrast, the air is cooled to low temperature and blows out.
  • the heat exchanger 9 thus acts as an evaporator of the refrigerating cycle.
  • the low-pressure low-temperature gas refrigerant discharged from the heat exchanger 9 again flows into the four-way valve 2 for switching the circuit, from which the gas refrigerant is fed to a pipe to the inlet of the compressor 1.
  • the low-pressure low-temperature gas refrigerant fed to the inlet of the compressor 1 is compressed in the compressor 1 into a high-pressure high-temperature gas refrigerant, and is discharged from the outlet.
  • the second electronic expansion valve 8 is located downstream of the receiver 12.
  • the second electronic expansion valve 8 controls the refrigerant to be evaporated in the heat exchanger 9 according to the degree of superheat (degree of discharge superheat).
  • the degree of discharge superheat for control is calculated from the difference between the temperature of the refrigerant discharged from the compressor 1 which is detected by temperature detection means Td and the saturation temperature T10 calculated from the condensing pressure of the refrigerant in the plate heat exchanger 10 detected by the pressure detection means Pd.
  • the degree of opening of the second electronic expansion valve 8 When the degree of discharge superheat is low, the degree of opening of the second electronic expansion valve 8 is decreased to thereby decrease the amount of the refrigerant evaporated by the heat exchanger 9 to increase the degree of dryness of the refrigerant due to evaporation, thereby increasing the degree of discharge superheat. In contrast, when the degree of discharge superheat is high, the degree of opening of the second electronic expansion valve. 8 is increased to thereby increase the amount of the refrigerant evaporated by the heat exchanger 9 to decrease the degree of dryness of the refrigerant due to evaporation, thereby decreasing the degree of discharge superheat.
  • the degree of discharge superheat can be controlled by adjusting the degree of opening of the second electronic expansion valve 8 according to the calculated degree of discharge superheat.
  • the foregoing cycle is repeated to thereby increase the temperature of the water by heat pump action of transferring the heat obtained from outside air to the water flowing in the water pipe 50.
  • a method for controlling the variable-capacity compressor 1 of the hot water system according to the example will be described.
  • the water flowing through the water pipe 50 gradually increases in temperature while circulating.
  • a target condensing temperature depends on a set water temperature because the condensing temperature depends on the temperature of the circulating water.
  • the target condensing temperature determined from the set water temperature corresponds to the set temperature of air conditioners.
  • the present condensing temperature corresponds to the temperature of the air flowing into the heat exchanger in the indoor unit of air conditioners.
  • the compressor 1 is controlled according to the difference between the present condensing temperature and the target condensing temperature determined from the set water temperature.
  • the present condensing temperature is calculated as the saturation temperature at the condensing pressure detected by the pressure detection means Pd.
  • the speed of operation of the compressor 1 is increased to increase the amount of the refrigerant circulating in the refrigerating cycle so that the actual condensing temperature reaches the target condensing temperature fast, thereby enhancing the performance.
  • the speed of operation of the compressor 1 is decreased to reduce the amount of the refrigerant circulating in the refrigerating cycle, thereby reducing the performance.
  • the hot water system of the example includes the pressure detection means Pd disposed between the outlet of the compressor 1 and the four-way valve 2, for detecting the pressure of the refrigerant discharged from the compressor 1, wherein the operation speed of the compressor 1 is controlled according to the difference between the condensing temperature calculated from the pressure detected by the pressure detection means Pd and a target condensing temperature.
  • the hot water system further includes the temperature sensor Tix disposed at the outlet of the plate heat exchanger 10 for detecting the temperature of the liquid refrigerant, wherein the degree of opening of the first electronic expansion valve 6 is adjusted according to the difference between the condensing temperature calculated from the pressure detected by the pressure detection means Pd and the temperature of the liquid refrigerant detected by the temperature sensor Tix.
  • the first electronic expansion valve 6 and the variable-capacity compressor 1 can be controlled by a control method similar to that for heating by an air conditioner, ensuring reliability similar to that established by the air conditioner.
  • the application of the control established for the air conditioner can reduce the period to develop a control program.
  • a refrigerant such as R410A used in the air conditioner allows a control constant for use in driving the actuators to be also applied, providing further reliability and reducing the period for development.
  • Fig. 3 is a refrigerant circuit diagram of a hot water system according to a first embodiment of the invention.
  • the heat-pump hot water system includes the compressor 1, the four-way valve 2 for switching the refrigerant circuit, the plate heat exchanger 10 for exchanging heat between water and the refrigerant, the first electronic expansion valve 6 for controlling the flow rate of the refrigerant to decrease the pressure, the receiver 7 for holding an excess refrigerant, the second electronic expansion valve 8 for controlling the flow rate of the refrigerant to decrease the pressure, and the heat exchanger 9 for exchanging heat between air and the refrigerant, which are connected in sequence by a pipeline and housed in the hot water system outdoor unit 40.
  • the first embodiment further includes pressure detection means Pc disposed at the pipe connecting the four-way valve 2 and the plate heat exchanger 10, for detecting the condensing pressure of the refrigerant.
  • the pressure detection means Pc for detecting the condensing pressure of the refrigerant is disposed at the pipe connecting the four-way valve 2 and the plate heat exchanger 10, the distance between the pressure detection means Pc and the plate heat exchanger 10 is short, so that the pressure loss of the pipe can be minimized. Accordingly, the condensing temperature can be measured more accurately than the previous example.

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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)

Claims (4)

  1. Warmwassersystem, umfassend:
    einen Kompressor (1) mit variabler Betriebskapazität;
    ein Vierwegeventil (2) zum Wechseln der Richtung des Kühlkreislaufs;
    eine Plattenwärmeaustauschvorrichtung (10) zum Austauschen von Wärme zwischen Wasser und dem Kältemittel;
    ein erstes Expansionsventil (6) zum Steuern der Flussrate des Kältemittels, um den Druck zu verringern; und
    eine Wärmeaustauschvorrichtung (9) zum Austauschen von Wärme zwischen der Luft und dem Kältemittel, die in dieser Reihenfolge durch eine Rohrleitung verbunden sind, um einen Kühlkreislauf zum Zirkulieren des Kältemittels zu bilden und dadurch Wasser zu erwärmen;
    gekennzeichnet durch ein Druckerfassungsmittel (Pc), das zwischen dem Vierwegeventil (2) und der Plattenwärmeaustauschvorrichtung (10) angeordnet ist, zum Erfassen des Kondensierungsdrucks des Kältemittels, wobei
    die Betriebsgeschwindigkeit des Kompressors (1) gemäß dem Unterschied zwischen der anhand des durch das Druckerfassungsmittel (Pc) erfassten Drucks berechneten Kondensiertemperatur und einer Zielkondensiertemperatur gesteuert wird.
  2. Warmwassersystem nach Anspruch 1, ferner umfassend:
    Temperaturerfassungsmittel (Tix) zum Erfassen der Temperatur eines flüssigen Kältemittels, das am Auslass der Plattenwärmeaustauschvorrichtung (10) angeordnet ist, wobei
    der Öffnungsgrad des ersten Expansionsventils (6) gemäß dem Unterschied zwischen der anhand des durch das Druckerfassungsmittel (Pc) erfassten Drucks berechneten Kondensiertemperatur und der durch das Temperaturerfassungsmittel (Tix) erkannten Temperatur des flüssigen Kältemittels gesteuert wird.
  3. Warmwassersystem nach Anspruch 1, ferner umfassend:
    eine Empfangsvorrichtung (7), die zwischen dem ersten Expansionsventil (6) und der Wärmeaustauschvorrichtung (9) angeordnet ist;
    ein zweites Expansionsventil (8), das zwischen der Empfangsvorrichtung (7) und der Wärmeaustauschvorrichtung (9) angeordnet ist; und
    Temperaturerfassungsmittel (Td) zum Erfassen der Temperatur des abgegebenen Kältemittels, das am Auslass des Kompressors (1) angeordnet ist, wobei
    der Öffnungsgrad des zweiten Expansionsventils (8) gemäß dem Unterschied zwischen der anhand des durch das Druckerfassungsmittel (Pc) erfassten Drucks berechneten Kondensiertemperatur und der durch das Temperaturerfassungsmittel (Td) erkannten Temperatur des flüssigen Kältemittels gesteuert wird.
  4. Warmwassersystem nach einem der Ansprüche 1 bis 3, wobei das im Kühlkreislauf benutzte Kältemittel R410A ist.
EP07254438.0A 2007-03-19 2007-11-13 Heißwassersystem Not-in-force EP1972871B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2007070995A JP2008232508A (ja) 2007-03-19 2007-03-19 給湯器

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Families Citing this family (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5711448B2 (ja) * 2009-02-24 2015-04-30 ダイキン工業株式会社 ヒートポンプシステム
WO2011014719A1 (en) * 2009-07-31 2011-02-03 Johnson Controls Technology Company Refrigerant control system and method
JP2011069570A (ja) * 2009-09-28 2011-04-07 Fujitsu General Ltd ヒートポンプサイクル装置
JP4854779B2 (ja) * 2009-12-09 2012-01-18 シャープ株式会社 空気調和機、膨張弁の開度制御方法およびプログラム
JP5228023B2 (ja) * 2010-10-29 2013-07-03 三菱電機株式会社 冷凍サイクル装置
WO2012081052A1 (ja) * 2010-12-15 2012-06-21 三菱電機株式会社 空調給湯複合システム
GB201102473D0 (en) 2011-02-11 2011-03-30 Esg Pool Ventilation Ltd Heating and cooling system and related methods
KR20120114576A (ko) * 2011-04-07 2012-10-17 엘지전자 주식회사 공기 조화기
WO2013093979A1 (ja) * 2011-12-22 2013-06-27 三菱電機株式会社 空気調和装置
JP2013185803A (ja) * 2012-03-12 2013-09-19 Panasonic Corp ヒートポンプ式温水暖房装置
CN103808012B (zh) * 2012-11-13 2016-06-08 珠海格力电器股份有限公司 变频热水器及其控制方法
JP5913402B2 (ja) * 2014-02-28 2016-04-27 ダイキン工業株式会社 ヒートポンプシステム
JP6387246B2 (ja) * 2014-05-19 2018-09-05 リンナイ株式会社 ヒートポンプ加熱装置
KR102181204B1 (ko) * 2014-06-09 2020-11-20 엘지전자 주식회사 냉매 시스템
WO2016046882A1 (ja) * 2014-09-22 2016-03-31 三菱電機株式会社 冷凍サイクル装置
EP3236174B1 (de) * 2014-11-27 2020-07-01 Mitsubishi Electric Corporation Kombination aus klimaanlage und heisswasserversorgungssystem
WO2016185689A1 (ja) * 2015-05-20 2016-11-24 パナソニックＩｐマネジメント株式会社 空調給湯システム
CN106766365A (zh) * 2016-11-28 2017-05-31 广东美的暖通设备有限公司 变频风冷热泵冷热水系统及其控制方法和空调
WO2018176283A1 (zh) * 2017-03-29 2018-10-04 广东美的制冷设备有限公司 空调器
CN107051963B (zh) * 2017-06-06 2022-08-12 扬州金威环保科技有限公司 一种基于分级循环加热原理的清洗液温控系统
CN107606834B (zh) * 2017-09-12 2020-09-04 广东美的暖通设备有限公司 多联机系统的控制方法及多联机系统
CN111578483B (zh) * 2020-04-21 2021-12-21 重庆海尔空调器有限公司 用于空调面板防凝露的方法及装置、空调
KR20230134730A (ko) * 2022-03-15 2023-09-22 삼성전자주식회사 히트 펌프 시스템 및 그 제어 방법

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE8119446U1 (de) * 1981-07-03 1981-11-05 Alcoa Deutschland Gmbh Verpackungswerke, 6520 Worms Bausatz fuer einen Kappenverschluss
JP3655681B2 (ja) * 1995-06-23 2005-06-02 三菱電機株式会社 冷媒循環システム
JP3632402B2 (ja) * 1997-10-22 2005-03-23 松下電器産業株式会社 ヒートポンプ給湯装置
JPH11270919A (ja) * 1998-03-25 1999-10-05 Mitsubishi Electric Corp 冷凍サイクル装置
JP2000104940A (ja) * 1998-09-28 2000-04-11 Kyushu Electric Power Co Inc ヒートポンプ式給湯システム
JP2000111213A (ja) * 1998-10-06 2000-04-18 Daikin Ind Ltd 冷凍装置
JP2001263831A (ja) * 2000-03-24 2001-09-26 Mitsubishi Electric Corp 冷凍サイクル装置
JP4169454B2 (ja) * 2000-04-12 2008-10-22 大阪瓦斯株式会社 貯湯式の給湯熱源装置
JP2001304703A (ja) * 2000-04-18 2001-10-31 Matsushita Electric Ind Co Ltd 冷凍サイクル装置
JP2002089958A (ja) * 2000-09-20 2002-03-27 Toshiba Kyaria Kk ヒートポンプ式給湯器
JP2002327949A (ja) 2001-04-27 2002-11-15 Daikin Ind Ltd 空気調和装置
JP4349851B2 (ja) * 2003-06-24 2009-10-21 日立アプライアンス株式会社 冷凍サイクル装置
JP3843978B2 (ja) * 2003-11-06 2006-11-08 松下電器産業株式会社 ヒートポンプ給湯装置
GB2414289A (en) * 2004-05-19 2005-11-23 Asker Barum Kuldeteknikk A S A heat pump installation
US7302811B2 (en) * 2004-11-23 2007-12-04 Parker Hannifin Corporation Fluid expansion-distribution assembly

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JP2008232508A (ja) 2008-10-02
EP1972871A3 (de) 2015-09-02

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