EP3594587A1 - Wärmepumpenvorrichtung zur warmwasserversorgung - Google Patents
Wärmepumpenvorrichtung zur warmwasserversorgung Download PDFInfo
- Publication number
- EP3594587A1 EP3594587A1 EP17899425.7A EP17899425A EP3594587A1 EP 3594587 A1 EP3594587 A1 EP 3594587A1 EP 17899425 A EP17899425 A EP 17899425A EP 3594587 A1 EP3594587 A1 EP 3594587A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- refrigerant
- temperature
- hot water
- inlet
- adjusting device
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
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- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 title claims abstract description 133
- 239000003507 refrigerant Substances 0.000 claims abstract description 202
- 239000007788 liquid Substances 0.000 claims abstract description 59
- 235000006506 Brasenia schreberi Nutrition 0.000 claims abstract description 24
- 238000001514 detection method Methods 0.000 claims description 32
- 238000009835 boiling Methods 0.000 abstract description 20
- 230000006835 compression Effects 0.000 abstract description 10
- 238000007906 compression Methods 0.000 abstract description 10
- 230000001629 suppression Effects 0.000 abstract description 9
- 239000012530 fluid Substances 0.000 abstract description 4
- 238000007562 laser obscuration time method Methods 0.000 abstract description 2
- 230000007423 decrease Effects 0.000 description 8
- 238000010586 diagram Methods 0.000 description 8
- 230000000694 effects Effects 0.000 description 8
- 230000007613 environmental effect Effects 0.000 description 6
- 230000007704 transition Effects 0.000 description 4
- CURLTUGMZLYLDI-UHFFFAOYSA-N Carbon dioxide Chemical compound O=C=O CURLTUGMZLYLDI-UHFFFAOYSA-N 0.000 description 3
- 238000010438 heat treatment Methods 0.000 description 3
- 239000010721 machine oil Substances 0.000 description 3
- 230000002159 abnormal effect Effects 0.000 description 2
- 238000004378 air conditioning Methods 0.000 description 2
- 229910002092 carbon dioxide Inorganic materials 0.000 description 2
- 239000001569 carbon dioxide Substances 0.000 description 2
- 230000003247 decreasing effect Effects 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 239000003921 oil Substances 0.000 description 2
- 230000007257 malfunction Effects 0.000 description 1
- 238000005057 refrigeration Methods 0.000 description 1
- 238000010079 rubber tapping Methods 0.000 description 1
- 239000004065 semiconductor Substances 0.000 description 1
Images
Classifications
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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
- F24H4/04—Storage heaters
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- 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
- F24D17/00—Domestic hot-water supply systems
- F24D17/02—Domestic hot-water supply systems using heat pumps
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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
- F25B30/00—Heat pumps
- F25B30/02—Heat pumps of the compression type
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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
- F25B40/00—Subcoolers, desuperheaters or superheaters
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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
- 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
- F25B2500/12—Sound
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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
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2513—Expansion valves
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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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2116—Temperatures of a condenser
- F25B2700/21161—Temperatures of a condenser of the fluid heated by the condenser
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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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2116—Temperatures of a condenser
- F25B2700/21162—Temperatures of a condenser of the refrigerant at the inlet of the condenser
Definitions
- the present invention relates to a heat pump hot water supply apparatus that includes a refrigerant amount adjusting device.
- a technique for changing the storage amount of liquid refrigerant in the refrigerant amount adjusting device to attain a predetermined capacity at optimal efficiency has been suggested (for example, Patent Literature 1).
- the capacity of the heat pump cycle is controlled by changing the amount of refrigerant in the condenser and adjusting pressure on a high-pressure side.
- the amount of refrigerant in the condenser increases by temporarily decreasing the opening degree of the expansion valve. With this increase, the storage amount of liquid refrigerant in the refrigerant amount adjusting device at an outlet of the evaporator decreases.
- Patent Literature 2 For a heat pump cycle including a compressor, a condenser, an expansion valve, an evaporator, and an internal heat exchanger, but not including a refrigerant amount adjusting device, a technique for reducing, using the internal heat exchanger, an increase in pressure on a high-pressure side at a time of inflow of water at high temperature while reducing cost by not including the refrigerant amount adjusting device, has been suggested (for example, Patent Literature 2).
- the concentration of refrigerant present in the condenser decreases, and the pressure increases abnormally.
- refrigerant present in a region from an outlet of the condenser to an inlet of the expansion valve is cooled down. Therefore, the concentration of refrigerant on the high-pressure side is increased, and the abnormal increase in the pressure on the high-pressure side is reduced.
- the refrigerant present in the region from the outlet of the condenser to the inlet of the expansion valve is cooled down by refrigerant present in a region from an outlet of the evaporator to the compressor.
- Patent Literature 1 efficiency can be improved by adjusting, using the refrigerant amount adjusting device, the amount of refrigerant and pressure on the high-pressure side.
- the refrigerant amount adjusting device needs to have a large capacity to store liquid refrigerant. Therefore, there is a problem that the size of equipment increases and cost is thus increased.
- no refrigerant amount adjusting device is provided. Therefore, an increase in the size of equipment can be avoided.
- the internal heat exchanger is used as means for reducing an increase in the pressure on the high-pressure side at the time of inflow of water at high temperature. In such a case, there are problems described below.
- refrigerant flows into the evaporator with a low heat capacity and is stored in the evaporator as liquid refrigerant. Then, when a certain period of time has passed, liquid refrigerant is stored in the compressor with a high heat capacity. However, if the apparatus is restarted immediately after the liquid refrigerant is stored in the evaporator, liquid back of the refrigerant to the compressor may occur because no refrigerant amount adjusting device is provided. If liquid compression of the liquid-back refrigerant is performed by the compressor, malfunction may occur.
- the present invention has been made to solve the above-mentioned problems, and an object thereof is to provide a heat pump hot water supply apparatus that guarantees the reliability of an apparatus by reducing high pressure at the time of inflow of water at high temperature and avoiding liquid compression caused by liquid back at the time of transition while reducing increases in the size and cost of equipment.
- a heat pump hot water supply apparatus of an embodiment of the present invention includes a refrigerant circuit in which a compressor, a condenser, an expansion valve, an evaporator, and a refrigerant amount adjusting device are connected sequentially; a hot water tank storing hot water heated by the condenser; a hot water circulating pump circulating hot water in a region between the condenser and the hot water tank; an inlet refrigerant temperature detection unit detecting an inlet refrigerant temperature of the condenser; an inlet water temperature detection unit detecting an inlet water temperature of the condenser; and a heat source unit control unit adjusting a valve opening degree of the expansion valve such that a difference between a hot water target temperature transmitted from a tank control unit provided at the hot water tank and the inlet refrigerant temperature is equal to a temperature difference set in advance.
- the heat source unit control unit changes the temperature difference to adjust the valve opening degree of the expansion valve in an opening
- a heat pump hot water supply apparatus of an embodiment of the present invention performs, in a case where the temperature of fluid sent from a hot water tank to a condenser by a hot water circulating pump is high (that is, at the time of inflow of water at high temperature), high-pressure suppression such that a valve opening degree of an expansion valve is adjusted in an opening direction so that concentration of refrigerant on a high-pressure side is reduced not to exceed a fixed pressure.
- concentration of refrigerant on a low-pressure side increases, and the refrigerant is thus stored in a refrigerant amount adjusting device as excess liquid refrigerant.
- the liquid-back refrigerant returned from the evaporator can be stored as liquid refrigerant in the refrigerant amount adjusting device.
- the refrigerant is stored in the refrigerant amount adjusting device so that liquid compression can be avoided, and the reliability of the compressor can thus be ensured.
- a suction muffler that includes a space in which liquid refrigerant can be stored is used as the refrigerant amount adjusting device, increases in the size and cost of equipment can also be reduced.
- a heat pump hot water supply apparatus of an embodiment of the present invention controls the valve opening degree of an expansion valve such that a difference between a hot water target temperature from a tank control unit provided at a hot water tank and a temperature detected by an inlet refrigerant detection unit of a condenser (hereinafter, referred to as an inlet refrigerant temperature) is equal to a temperature difference set in advance (hereinafter, referred to as a set temperature difference).
- the opening degree of the expansion valve may be controlled based only on a detection temperature obtained by a water inlet detection unit of the condenser and a target value for the inlet refrigerant detection unit of the condenser.
- the temperature difference is set in advance such that the relationship that a value obtained by subtracting the hot water target temperature from the inlet refrigerant temperature is more than 0 is obtained and the opening degree of the expansion valve is adjusted to achieve the set temperature difference. Therefore, water can be made to boil reliably irrespective of environmental conditions.
- Fig. 1 is a circuit diagram of a heat pump hot water supply apparatus 100 according to Embodiment 1 of the present invention.
- the heat pump hot water supply apparatus 100 includes a heat source unit 200 and a tank unit 300.
- the heat source unit 200 includes a refrigerant circuit in which a compressor 1 that compresses refrigerant and discharges the compressed refrigerant, a condenser 2 that exchanges heat between refrigerant and water, an expansion valve 3 of an electronic control type whose opening degree is variable to decompress high-pressure refrigerant into low-pressure refrigerant, an evaporator 4 that exchanges heat between air and refrigerant, and a refrigerant amount adjusting device 6 that is able to temporarily store liquid refrigerant are connected by a refrigerant pipe 19 in a ring shape.
- the heat source unit 200 also includes an inlet water temperature detection unit 9 that detects the temperature of water at the inlet of the condenser 2, an outlet water temperature detection unit 10 that detects the temperature of water at the outlet of the condenser 2, an outside air temperature detection unit 16 that detects the outside air temperature, an inlet refrigerant temperature detection unit 17 that detects the temperature of refrigerant at the inlet of the condenser 2, and an outlet refrigerant temperature detection unit 18 that detects the temperature of refrigerant at the outlet of the evaporator 4.
- Each of the above-mentioned detection units may include a temperature sensor.
- a fan 8 that promotes heat exchange between refrigerant and air in the evaporator 4 is installed in the vicinity of the evaporator 4.
- the fan 8 is rotated by driving of a fan motor 7, and air flow passing through the evaporator 4 is generated by the rotation.
- Carbon dioxide (CO 2 ) may be used as refrigerant.
- An operation of the heat source unit 200 is controlled by a heat source unit control unit 13.
- the tank unit 300 includes a hot water tank 14 that stores hot water heated by the condenser 2 and a hot water circulating pump 11 that is arranged between the condenser 2 and the hot water tank 14 and circulates hot water in a region between the condenser 2 and the hot water tank 14.
- the condenser 2 and the hot water tank 14 are connected by a hot water circulating pipe 15.
- An operation of the tank unit 300 is controlled by a tank control unit 12.
- the tank control unit 12 is able to transmit a hot water target temperature to the heat source unit control unit of the heat source unit 200.
- Fig. 2 is a block diagram of the heat source unit control unit 13.
- the heat source unit control unit 13 includes a compressor rotation speed control part 21 that controls the rotation speed of the compressor 1, a fan rotation speed control part 22 that controls the rotation speed of the fan motor 7, a pump rotation speed control part 23 that controls the rotation speed of the hot water circulating pump 11, a detection temperature reception part 24 that receives a detection temperature such as an inlet refrigerant temperature of the condenser 2, an expansion valve opening degree adjustment part 25 that adjusts the opening degree of the expansion valve 3, and a hot water target temperature reception part 26 that receives a hot water target temperature transmitted from the tank control unit 12.
- the expansion valve opening degree adjustment part 25 adjusts the valve opening degree of the of the expansion valve 3 such that a difference between the hot water target temperature and the inlet refrigerant temperature becomes equal to a set temperature difference.
- the expansion valve opening degree adjustment part 25 changes the set temperature difference and adjusts the valve opening degree of the expansion valve 3 in an opening direction.
- the set temperature difference is stored in advance in a memory unit 30 in the heat source unit 200.
- the heat source unit control unit 13 includes, for example, a microchip.
- the memory unit 30 includes, for example, a semiconductor memory.
- Fig. 3 is a cross-sectional view of the compressor 1 and the refrigerant amount adjusting device 6.
- refrigerant in a two-phase gas-liquid state flows from the evaporator 4 through a suction pipe 31 into the refrigerant amount adjusting device 6
- gas refrigerant flows through a relay pipe 32 into the compressor 1, and liquid refrigerant is stored as excess refrigerant in a liquid refrigerant storage part 33 of the refrigerant amount adjusting device 6.
- the compressor 1 compresses the gas refrigerant, causes the compressed gas refrigerant to be discharged through a discharge pipe 34, and sends the discharged gas refrigerant to the condenser 2.
- the liquid refrigerant storage part 33 is an internal space provided at a bottom part of the refrigerant amount adjusting device 6, which is a tube shape.
- a so-called suction muffler achieving a muffling effect may be used as the refrigerant amount adjusting device 6.
- the suction muffler serves as both muffling means and excess refrigerant storing means.
- Refrigerating machine oil, along with refrigerant flows through the suction pipe 31 into the refrigerant amount adjusting device 6.
- An oil return hole 35 through which refrigerating machine oil stored at the bottom of the liquid refrigerant storage part 33 returns to the compressor 1 is provided at the relay pipe 32. Refrigerant and refrigerating machine oil may be temporarily stored in a mixed or separate state at the bottom of the liquid refrigerant storage part 33.
- Fig. 4 is a flowchart of boiling operation control by the heat source unit control unit 13. Boiling operation control for the heat pump hot water supply apparatus 100 will be explained below with reference to Fig. 4 .
- the heat source unit control unit 13 provided in the heat source unit 200 starts a boiling operation (step S11).
- the heat source unit control unit 13 receives a hot water target temperature, along with the boiling operation instruction.
- the heat source unit control unit 13 receives an inlet water temperature of the condenser 2 (step S12). In the case where the inlet water temperature is equal to or higher than a predetermined temperature, the heat source unit control unit 13 ends the operation control, without performing the boiling operation (step S13).
- the heat source unit control unit 13 controls the rotation frequency of the compressor 1 in accordance with the inlet water temperature detected by the outside air temperature detection unit 16 and the inlet water temperature detection unit 9 (step S14).
- the heat source unit control unit 13 determines whether or not the inlet water temperature detected by the inlet water temperature detection unit 9 of the condenser 2 is equal to or more than a predetermined threshold value (step S15). In the case where the inlet water temperature is less than the predetermined threshold value, the heat source unit control unit 13 reads a first temperature difference stored in the memory unit 30, and defines the read first temperature difference as a set temperature difference (step S16). In the case where the inlet water temperature is equal to or more than the predetermined threshold value, the heat source unit control unit 13 reads a second temperature difference stored in the memory unit 30, and defines the read second temperature difference as a set temperature difference (step S17). The second temperature difference is smaller than the first temperature difference.
- the heat source unit control unit 13 After setting a temperature difference, the heat source unit control unit 13 performs processing described below. First, the heat source unit control unit 13 receives an inlet refrigerant temperature detected by the inlet refrigerant detection unit 17 of the condenser 2 (step S18). Next, the heat source unit control unit 13 calculates a difference between the hot water target temperature and the inlet refrigerant temperature (step S19). Hereinafter, this difference will be referred to as a calculated temperature difference. Next, the heat source unit control unit 13 adjusts the opening degree of the expansion valve 3 such that the calculated temperature difference becomes equal to the set temperature difference (step S20). When the inlet water temperature of the condenser 2 reaches the predetermined threshold value or more, the valve opening degree is adjusted based on the second temperature difference, which is smaller than the first temperature difference. Accordingly, the valve opening degree is adjusted in an opening direction.
- the first temperature difference may be set such that an optimal COP can be obtained under environmental conditions such as, for example, certain outside air temperature conditions and inlet water temperature conditions (winter standard heating conditions, mid-term standard heating conditions, or other conditions defined by JIS).
- the second temperature difference is set to a value smaller than the first temperature difference such that pressure on the high-pressure side at the time of inflow of water at high temperature does not exceed the designed upper limit.
- These temperature differences are fixed values under certain fixed conditions such as the above-mentioned outside air temperature or inlet water temperature. These temperature differences may be set to fixed values, for example, within a range from 15 degrees C to 30 degrees C.
- the opening degree of the expansion valve 3 may be controlled based only on the outside air temperature, the inlet water temperature detected by the inlet water temperature detection unit 9 of the condenser 2, a target value for the inlet refrigerant temperature detected by the inlet refrigerant detection unit 17 of the condenser 2, and the hot water target temperature from the tank control unit 12. However, depending on the environmental condition, there may be a relationship that the hot water target temperature is higher than the target value for the inlet refrigerant temperature, and water may not boil.
- the opening degree of the expansion valve 3 is adjusted such that the calculated temperature difference becomes equal to a set temperature difference by defining the first temperature difference as the set temperature difference in the case where the inlet water temperature is less than the predetermined threshold value and defining the second temperature difference, which is smaller than the first temperature difference, as the set temperature difference in the case where the inlet water temperature reaches the predetermined threshold value or more.
- Fig. 5 is a schematic diagram illustrating transition of the temperature of hot water stored in the hot water tank 14.
- the temperature of water supplied to the heat source unit 200 is low (for example, 5 degrees C).
- the inlet water temperature of the condenser 2 increases before boiling is completed (for example, 5 to 60 degrees C).
- the temperature of water in the hot water tank 14 before the boiling operation is about 5 degrees C
- the temperature of hot water in an upper part of the hot water tank 14 during the boiling operation is 90 degrees C
- the temperature of hot water in a lower part of the hot water tank 14 during the boiling operation is 5 degrees C.
- the temperature of hot water in the upper part of the hot water tank 14 before boiling is completed is 90 degrees C
- the temperature of hot water in the lower part of the hot water tank 14 before boiling is completed is 60 degrees C, which is medium temperature water.
- the second temperature difference which is smaller than the first temperature difference, is defined as the set temperature difference. The second temperature difference is smaller than the first temperature difference.
- the opening degree of the expansion valve 3 is set such that the difference between the hot water target temperature from the tank control unit 12 and the detection temperature obtained by the inlet refrigerant detection unit 17 of the condenser 2 becomes equal to the changed set temperature difference.
- Fig. 6 is a time chart illustrating an inlet water temperature 41 of the condenser 2, an inlet refrigerant temperature 42 of the condenser 2, a hot water target temperature 43 of the tank control unit 12, a stored refrigerant amount 44 in the refrigerant amount adjusting device 6, and the valve opening degree of the expansion valve.
- the pressure on the high-pressure side is reduced by adjustment of the opening degree of the expansion valve 3 mentioned above, whereas the concentration of refrigerant on the low-pressure side increases.
- the temperature difference between the inlet refrigerant temperature 42 and the hot water target temperature 43 during the period up to the time point T1 at which the inlet water temperature 41 reaches the predetermined threshold value 41a is 30 degrees C
- the temperature difference at or later than the time point T1 at which the inlet water temperature 41 reaches the predetermined threshold value 41a is 25 degrees C.
- the boiling operation ends (step S13).
- the amount of refrigerant filled in the entire refrigeration circuit may be, for example, about 1000 grams.
- a target value 44a for the stored refrigerant amount 44 in the refrigerant amount adjusting device 6 may be, for example, about 30 grams. In the case where a suction muffler is used as the refrigerant amount adjusting device 6, excess liquid refrigerant is stored at the bottom part of the suction muffler.
- the heat source unit control unit 13 may start a boiling operation. After the operation stops, the expansion valve 3 is fully opened, and the pressure on the high-pressure side and the pressure on the low-pressure side are balanced. At this time, by being affected by the outside air temperature, refrigerant flows into the evaporator 4 that has a low heat capacity (easily transfers heat), and is stored as liquid refrigerant. When a fixed time has passed, liquid refrigerant is stored in the compressor 1, which has a high heat capacity. If restarting is performed immediately after the entire liquid refrigerant is stored in the evaporator 4, the liquid refrigerant stored in the evaporator 4 flows into the compressor 1 at one time.
- liquid back of liquid refrigerant to the compressor 1 may occur, resulting in liquid compression by the compressor 1.
- liquid refrigerant from the evaporator 4 at the time of start of the apparatus is temporarily stored in the refrigerant amount adjusting device 6. Therefore, liquid compression of refrigerant by the compressor 1 can be avoided, and the reliability of the compressor 1 can thus be ensured.
- the heat pump hot water supply apparatus 100 in the case where the temperature of fluid sent from the bottom part of the hot water tank 14 to the condenser 2 by the hot water circulating pump 11 is high (that is, at the time of inflow of water at high temperature), concentration of refrigerant on the high-pressure side is reduced by adjusting the valve opening degree of the expansion valve 3 in the opening direction, and high-pressure suppression is thus performed such that a certain fixed pressure is not exceeded.
- concentration of refrigerant on the low-pressure side increases, and liquid storage of excess liquid refrigerant into the refrigerant amount adjusting device 6 is thus performed.
- the refrigerant amount adjusting device 6 is provided in the heat pump hot water supply apparatus 100 according to Embodiment 1, and liquid refrigerant is stored in the refrigerant amount adjusting device 6. Therefore, liquid compression by the compressor 1 can be avoided, and the reliability of the compressor 1 can thus be ensured.
- a suction muffler may be used as the refrigerant amount adjusting device 6. The suction muffler serves as both muffling means and the refrigerant amount adjusting device 6. Therefore, there is no need to provide a separate refrigerant amount adjusting device. Thus, effects such as reduction of cost and reduction of the increase of capacity of an outdoor unit can be achieved.
- Fig. 7 is a circuit diagram of the heat pump hot water supply apparatus 100 that includes an internal heat exchanger 5.
- the refrigerant amount adjusting device 6 with a certain size or more cannot be installed.
- the internal heat exchanger 5 which allows heat exchange between refrigerant in a region from the outlet of a condenser 2 to the inlet of an expansion valve 3 and refrigerant in a region from the outlet of an evaporator 4 to the inlet of a compressor 1, may be provided, as illustrated in Fig. 7 .
- the expansion valve 3 is provided at a refrigerant flow passage between the evaporator 4 and the internal heat exchanger 5.
- Fig. 8 is a pressure-enthalpy chart illustrating effects in high-pressure suppression.
- Fig. 9 is a pressure-enthalpy chart illustrating effects in COP improvement.
- the internal heat exchanger 5 has two roles. One of the roles is, as illustrated in Fig. 8 , to increase the concentration of refrigerant in the evaporator 4 and store the refrigerant in the evaporator when the inlet water temperature of the condenser 2 increases by heat exchange by the internal heat exchanger 5. In accordance with this, the concentration of refrigerant on the high-pressure side can be reduced, and high pressure can thus be suppressed.
- Signs 51 and 52 represent an enthalpy range on the low-pressure side and an enthalpy range on the high-pressure side, respectively, varied by heat exchange by the internal heat exchanger 5.
- the other role is, as illustrated in Fig. 9 , to be able to provide superheat at the outlet of the evaporator 4 and thus improve the COP.
- a sign 54 in Fig. 9 represents an enthalpy range increased when superheat is provided at the outlet of the evaporator 4 by the internal heat exchanger 5.
- a sign 55 represents transition of state of refrigerant in the case where the internal heat exchanger 5 is provided.
- a sign 56 represents transition of state of refrigerant in the case where the internal heat exchanger 5 is not provided.
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- 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)
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/JP2017/009418 WO2018163345A1 (ja) | 2017-03-09 | 2017-03-09 | ヒートポンプ給湯装置 |
Publications (3)
Publication Number | Publication Date |
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EP3594587A1 true EP3594587A1 (de) | 2020-01-15 |
EP3594587A4 EP3594587A4 (de) | 2020-02-26 |
EP3594587B1 EP3594587B1 (de) | 2021-04-21 |
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ID=63448305
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP17899425.7A Active EP3594587B1 (de) | 2017-03-09 | 2017-03-09 | Wärmepumpenvorrichtung zur warmwasserversorgung |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP3594587B1 (de) |
JP (1) | JP6704505B2 (de) |
WO (1) | WO2018163345A1 (de) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
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CN115095986B (zh) * | 2022-06-30 | 2023-03-14 | 九阳股份有限公司 | 一种即热出水机的控制方法 |
Family Cites Families (10)
Publication number | Priority date | Publication date | Assignee | Title |
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NO890076D0 (no) * | 1989-01-09 | 1989-01-09 | Sinvent As | Luftkondisjonering. |
JPH0718602A (ja) | 1993-06-29 | 1995-01-20 | Sekisui Chem Co Ltd | 埋込栓 |
JP3659197B2 (ja) * | 2000-06-21 | 2005-06-15 | 松下電器産業株式会社 | ヒートポンプ給湯機 |
JP4731806B2 (ja) | 2003-12-01 | 2011-07-27 | パナソニック株式会社 | 冷凍サイクル装置およびその制御方法 |
JP2007212103A (ja) * | 2006-02-13 | 2007-08-23 | Matsushita Electric Ind Co Ltd | ヒートポンプ式給湯機 |
JP4948374B2 (ja) * | 2007-11-30 | 2012-06-06 | 三菱電機株式会社 | 冷凍サイクル装置 |
JP5173469B2 (ja) * | 2008-02-15 | 2013-04-03 | 三菱電機株式会社 | ヒートポンプ給湯装置 |
JP5558937B2 (ja) * | 2010-06-30 | 2014-07-23 | 株式会社コロナ | ヒートポンプ式給湯装置 |
JP5776314B2 (ja) * | 2011-04-28 | 2015-09-09 | 株式会社ノーリツ | ヒートポンプ給湯機 |
JP5861577B2 (ja) * | 2012-07-05 | 2016-02-16 | 株式会社デンソー | 給湯装置 |
-
2017
- 2017-03-09 WO PCT/JP2017/009418 patent/WO2018163345A1/ja unknown
- 2017-03-09 EP EP17899425.7A patent/EP3594587B1/de active Active
- 2017-03-09 JP JP2019504216A patent/JP6704505B2/ja active Active
Also Published As
Publication number | Publication date |
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JP6704505B2 (ja) | 2020-06-03 |
JPWO2018163345A1 (ja) | 2019-07-18 |
WO2018163345A1 (ja) | 2018-09-13 |
EP3594587B1 (de) | 2021-04-21 |
EP3594587A4 (de) | 2020-02-26 |
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