EP3594587A1 - Heat pump hot water supply device - Google Patents
Heat pump hot water supply device 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
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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
- 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.
Abstract
Description
- The present invention relates to a heat pump hot water supply apparatus that includes a refrigerant amount adjusting device.
- For a heat pump cycle including a compressor, a condenser, an expansion valve, an evaporator, and 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. As the amount of refrigerant on the high-pressure side increases, the pressure increases and the capacity increases. In contrast, by opening the expansion valve, the storage amount of liquid refrigerant in the refrigerant amount adjusting device at the outlet of the evaporator increases, and the amount of refrigerant on the high-pressure side decreases. When the pressure on the high-pressure side decreases, the capacity decreases. As described above, operation at the optimal efficiency can be achieved by adjusting the storage amount of liquid refrigerant in the refrigerant amount adjusting device as a cycle.
- Furthermore, 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). In the case where the temperature of fluid sent to the condenser by a hot water circulating pump from a bottom part of a hot water tank is high (that is, at the time of inflow of water at high temperature), the concentration of refrigerant present in the condenser decreases, and the pressure increases abnormally. To reduce the abnormal increase in the pressure, 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. As described above, by reducing the pressure on the high-pressure side by the internal heat exchanger without using the refrigerant amount adjusting device, cost reduction can be achieved.
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- Patent Literature 1: Japanese Unexamined Patent Application Publication No.
7-18602 - Patent Literature 2: Japanese Unexamined Patent Application Publication No.
2005-164103 - In
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. However, 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. InPatent Literature 2, no refrigerant amount adjusting device is provided. Therefore, an increase in the size of equipment can be avoided. However, in place of the refrigerant amount adjusting device, 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. Immediately after an operation of an apparatus stops, 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. When the inlet water temperature reaches a threshold value or more, the heat source unit control unit changes the temperature difference to adjust the valve opening degree of the expansion valve in an opening direction.
- 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. In contrast, since 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. Even if an apparatus is restarted immediately after liquid refrigerant is stored in an evaporator, the liquid-back refrigerant returned from the evaporator can be stored as liquid refrigerant in the refrigerant amount adjusting device. With this configuration, 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. Furthermore, in the case where 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.
- Furthermore, 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. However, depending on the operation environmental condition, there may be a relationship that the hot water target temperature is higher than the target value, and water may not boil. In contrast, according to an embodiment of the present invention, 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.
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- [
Fig. 1] Fig. 1 is a circuit diagram of a heat pump hot water supply apparatus according to the present invention. - [
Fig. 2] Fig. 2 is a block diagram of a heat source unit control unit and a memory unit. - [
Fig. 3] Fig. 3 is a cross-sectional view of a compressor and a refrigerant amount adjusting device. - [
Fig. 4] Fig. 4 is a flowchart illustrating boiling operation control by the heat source unit control unit. - [
Fig. 5] Fig. 5 is a schematic diagram illustrating transition of the temperature of hot water stored in a hot water tank. - [
Fig. 6] Fig. 6 is a time chart of an inlet water temperature and an inlet refrigerant temperature of a condenser, the amount of refrigerant stored in the refrigerant amount adjusting device, a hot water target temperature of a tank control unit, and the valve opening degree of an expansion valve. - [
Fig. 7] Fig. 7 is a circuit diagram of a heat pump hot water supply apparatus according to the present invention that includes an internal heat exchanger. - [
Fig. 8] Fig. 8 is a pressure-enthalpy chart illustrating effects in high pressure suppression. - [
Fig. 9] Fig. 9 is a pressure-enthalpy chart illustrating effects in improvement of a coefficient of performance (hereinafter, referred to as a COP). - Hereinafter, an
outdoor unit 100 of an air-conditioning apparatus according toEmbodiment 1 of the present invention will be explained with reference to drawings. -
Fig. 1 is a circuit diagram of a heat pump hotwater supply apparatus 100 according toEmbodiment 1 of the present invention. The heat pump hotwater supply apparatus 100 includes aheat source unit 200 and atank unit 300. - The
heat source unit 200 includes a refrigerant circuit in which acompressor 1 that compresses refrigerant and discharges the compressed refrigerant, acondenser 2 that exchanges heat between refrigerant and water, anexpansion valve 3 of an electronic control type whose opening degree is variable to decompress high-pressure refrigerant into low-pressure refrigerant, anevaporator 4 that exchanges heat between air and refrigerant, and a refrigerantamount adjusting device 6 that is able to temporarily store liquid refrigerant are connected by arefrigerant pipe 19 in a ring shape. Furthermore, theheat source unit 200 also includes an inlet water temperature detection unit 9 that detects the temperature of water at the inlet of thecondenser 2, an outlet watertemperature detection unit 10 that detects the temperature of water at the outlet of thecondenser 2, an outside airtemperature detection unit 16 that detects the outside air temperature, an inlet refrigeranttemperature detection unit 17 that detects the temperature of refrigerant at the inlet of thecondenser 2, and an outlet refrigeranttemperature detection unit 18 that detects the temperature of refrigerant at the outlet of theevaporator 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 theevaporator 4 is installed in the vicinity of theevaporator 4. The fan 8 is rotated by driving of afan motor 7, and air flow passing through theevaporator 4 is generated by the rotation. Carbon dioxide (CO2) may be used as refrigerant. An operation of theheat source unit 200 is controlled by a heat sourceunit control unit 13. - The
tank unit 300 includes ahot water tank 14 that stores hot water heated by thecondenser 2 and a hotwater circulating pump 11 that is arranged between thecondenser 2 and thehot water tank 14 and circulates hot water in a region between thecondenser 2 and thehot water tank 14. Thecondenser 2 and thehot water tank 14 are connected by a hotwater circulating pipe 15. An operation of thetank unit 300 is controlled by atank control unit 12. Thetank control unit 12 is able to transmit a hot water target temperature to the heat source unit control unit of theheat source unit 200. -
Fig. 2 is a block diagram of the heat sourceunit control unit 13. The heat sourceunit control unit 13 includes a compressor rotationspeed control part 21 that controls the rotation speed of thecompressor 1, a fan rotationspeed control part 22 that controls the rotation speed of thefan motor 7, a pump rotationspeed control part 23 that controls the rotation speed of the hotwater circulating pump 11, a detectiontemperature reception part 24 that receives a detection temperature such as an inlet refrigerant temperature of thecondenser 2, an expansion valve openingdegree adjustment part 25 that adjusts the opening degree of theexpansion valve 3, and a hot water targettemperature reception part 26 that receives a hot water target temperature transmitted from thetank control unit 12. The expansion valve openingdegree adjustment part 25 adjusts the valve opening degree of the of theexpansion valve 3 such that a difference between the hot water target temperature and the inlet refrigerant temperature becomes equal to a set temperature difference. When the inlet water temperature reaches a predetermined threshold value or more, the expansion valve openingdegree adjustment part 25 changes the set temperature difference and adjusts the valve opening degree of theexpansion valve 3 in an opening direction. The set temperature difference is stored in advance in amemory unit 30 in theheat source unit 200. The heat sourceunit control unit 13 includes, for example, a microchip. Thememory unit 30 includes, for example, a semiconductor memory. -
Fig. 3 is a cross-sectional view of thecompressor 1 and the refrigerantamount adjusting device 6. In the case where refrigerant in a two-phase gas-liquid state flows from theevaporator 4 through asuction pipe 31 into the refrigerantamount adjusting device 6, gas refrigerant flows through arelay pipe 32 into thecompressor 1, and liquid refrigerant is stored as excess refrigerant in a liquidrefrigerant storage part 33 of the refrigerantamount adjusting device 6. Thecompressor 1 compresses the gas refrigerant, causes the compressed gas refrigerant to be discharged through adischarge pipe 34, and sends the discharged gas refrigerant to thecondenser 2. The liquidrefrigerant storage part 33 is an internal space provided at a bottom part of the refrigerantamount adjusting device 6, which is a tube shape. A so-called suction muffler achieving a muffling effect may be used as the refrigerantamount adjusting device 6. In this case, the suction muffler serves as both muffling means and excess refrigerant storing means. Refrigerating machine oil, along with refrigerant, flows through thesuction pipe 31 into the refrigerantamount adjusting device 6. An oil return hole 35 through which refrigerating machine oil stored at the bottom of the liquidrefrigerant storage part 33 returns to thecompressor 1 is provided at therelay pipe 32. Refrigerant and refrigerating machine oil may be temporarily stored in a mixed or separate state at the bottom of the liquidrefrigerant storage part 33. -
Fig. 4 is a flowchart of boiling operation control by the heat sourceunit control unit 13. Boiling operation control for the heat pump hotwater supply apparatus 100 will be explained below with reference toFig. 4 . - First, when receiving a boiling operation instruction from the
tank control unit 12 provided in thetank unit 300, the heat sourceunit control unit 13 provided in theheat source unit 200 starts a boiling operation (step S11). The heat sourceunit control unit 13 receives a hot water target temperature, along with the boiling operation instruction. Next, the heat sourceunit 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 sourceunit control unit 13 ends the operation control, without performing the boiling operation (step S13). In the case where the inlet water temperature is lower than the predetermined temperature, the heat sourceunit control unit 13 controls the rotation frequency of thecompressor 1 in accordance with the inlet water temperature detected by the outside airtemperature detection unit 16 and the inlet water temperature detection unit 9 (step S14). - Next, 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 thecondenser 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 sourceunit control unit 13 reads a first temperature difference stored in thememory 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 sourceunit control unit 13 reads a second temperature difference stored in thememory 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. - After setting a temperature difference, the heat source
unit control unit 13 performs processing described below. First, the heat sourceunit control unit 13 receives an inlet refrigerant temperature detected by the inletrefrigerant detection unit 17 of the condenser 2 (step S18). Next, the heat sourceunit 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 sourceunit control unit 13 adjusts the opening degree of theexpansion valve 3 such that the calculated temperature difference becomes equal to the set temperature difference (step S20). When the inlet water temperature of thecondenser 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 thecondenser 2, a target value for the inlet refrigerant temperature detected by the inletrefrigerant detection unit 17 of thecondenser 2, and the hot water target temperature from thetank 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. For example, in the case where, at the time of inflow of water at high temperature, to suppress the pressure on the high-pressure side, processing for uniformly decreasing the target value for the inlet refrigerant temperature is performed, regardless of the hot water target temperature, the relationship that the hot water target temperature is higher than the target value for the inlet refrigerant temperature may be obtained. In contrast, in the heat pump hotwater supply apparatus 100 according toEmbodiment 1, temperature differences satisfying the relationship that a value obtained by subtracting the hot water target temperature from the inlet refrigerant temperature is more than 0 are stored in advance as first and second temperature differences in thememory unit 30. Then, the opening degree of theexpansion 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. With the above processing, a failure in which water does not boil can be avoided while performing adjustment such that the pressure on the high-pressure side does not exceed the designed upper limit pressure at the time of inflow of water at high temperature. -
Fig. 5 is a schematic diagram illustrating transition of the temperature of hot water stored in thehot water tank 14. During a period of a boiling operation from the start of boiling, the temperature of water supplied to theheat source unit 200 is low (for example, 5 degrees C). However, the inlet water temperature of thecondenser 2 increases before boiling is completed (for example, 5 to 60 degrees C). For example, in the case where the city water minimum temperature is 5 degrees C and the hot water tapping maximum temperature is 90 degrees C, the temperature of water in thehot water tank 14 before the boiling operation is about 5 degrees C, the temperature of hot water in an upper part of thehot water tank 14 during the boiling operation is 90 degrees C, and the temperature of hot water in a lower part of thehot water tank 14 during the boiling operation is 5 degrees C. The temperature of hot water in the upper part of thehot water tank 14 before boiling is completed is 90 degrees C, and the temperature of hot water in the lower part of thehot water tank 14 before boiling is completed is 60 degrees C, which is medium temperature water. - When the inlet water temperature increases, concentration of refrigerant present in the
condenser 2 decreases. At this time, if the first temperature difference set in advance to achieve the optimal COP under certain environmental conditions is maintained, the pressure abnormally increases. Thus, under certain environmental conditions that may cause the pressure on the high-pressure side to exceed a designed pressure (for example, under conditions where, at a low outside air temperature, the maximum boiling temperature and the maximum heating capacity are required, the inlet refrigerant temperature of thecondenser 2 is high, and the rotation speed of thecompressor 1 reaches the maximum), 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. Therefore, when the inlet water temperature reaches the predetermined temperature or more, the set temperature difference decreases. Then, the opening degree of theexpansion valve 3 is set such that the difference between the hot water target temperature from thetank control unit 12 and the detection temperature obtained by the inletrefrigerant detection unit 17 of thecondenser 2 becomes equal to the changed set temperature difference. With such control, high-pressure suppression can be performed such that the concentration of refrigerant on the high-pressure side can be reduced and the pressure on the high-pressure side does not exceed the designed pressure. -
Fig. 6 is a time chart illustrating aninlet water temperature 41 of thecondenser 2, an inletrefrigerant temperature 42 of thecondenser 2, a hotwater target temperature 43 of thetank control unit 12, a storedrefrigerant amount 44 in the refrigerantamount 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 theexpansion valve 3 mentioned above, whereas the concentration of refrigerant on the low-pressure side increases. During a period up to a time point T1 at which theinlet water temperature 41 detected by the inlet water temperature detection unit 9 of thecondenser 2 reaches a predetermined threshold value 41 (for example, 50 degrees C), refrigerant is used up under the designed pressure or below, and there is no excess liquid refrigerant. Therefore, no liquid refrigerant is stored in the refrigerantamount adjusting device 6. During this period, the inletrefrigerant temperature 42 and the hotwater target temperature 43 are constant. After theinlet water temperature 41 detected by the inlet water temperature detection unit 9 of thecondenser 2 exceeds thepredetermined threshold value 41a, to achieve an operation at the designed pressure or below, liquid storage of excess liquid refrigerant into the refrigerantamount adjusting device 6 is performed, and high-pressure suppression is thus performed. That is, at the time point T1 at which the inlet water temperature exceeds thepredetermined threshold value 41, adjustment of the valve opening degree in steps S17 to S20 starts. At this time, avalve opening degree 45 is adjusted such that the difference between the inletrefrigerant temperature 42 and the hotwater target temperature 43 becomes equal to a fixed set temperature difference (second temperature difference). Thevalve opening degree 45 starts increasing at the time point T1. Accordingly, the actual temperature difference decreases. For example, the temperature difference between the inletrefrigerant temperature 42 and the hotwater target temperature 43 during the period up to the time point T1 at which theinlet water temperature 41 reaches thepredetermined threshold value 41a is 30 degrees C, and the temperature difference at or later than the time point T1 at which theinlet water temperature 41 reaches thepredetermined threshold value 41a is 25 degrees C. At a time point T2 at which theinlet water temperature 41 reaches apredetermined temperature 41b, the boiling operation ends (step S13). The amount of refrigerant filled in the entire refrigeration circuit may be, for example, about 1000 grams. Atarget value 44a for the storedrefrigerant amount 44 in the refrigerantamount adjusting device 6 may be, for example, about 30 grams. In the case where a suction muffler is used as the refrigerantamount adjusting device 6, excess liquid refrigerant is stored at the bottom part of the suction muffler. - Soon after the boiling operation stops, the heat source
unit control unit 13 may start a boiling operation. After the operation stops, theexpansion 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 theevaporator 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 thecompressor 1, which has a high heat capacity. If restarting is performed immediately after the entire liquid refrigerant is stored in theevaporator 4, the liquid refrigerant stored in theevaporator 4 flows into thecompressor 1 at one time. In the case where the refrigerantamount adjusting device 6 is not provided unlikeEmbodiment 1, liquid back of liquid refrigerant to thecompressor 1 may occur, resulting in liquid compression by thecompressor 1. In contrast, in the heat pump hotwater supply apparatus 100 according toEmbodiment 1, liquid refrigerant from theevaporator 4 at the time of start of the apparatus is temporarily stored in the refrigerantamount adjusting device 6. Therefore, liquid compression of refrigerant by thecompressor 1 can be avoided, and the reliability of thecompressor 1 can thus be ensured. - As described above, in the heat pump hot
water supply apparatus 100 according toEmbodiment 1, in the case where the temperature of fluid sent from the bottom part of thehot water tank 14 to thecondenser 2 by the hotwater 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 theexpansion valve 3 in the opening direction, and high-pressure suppression is thus performed such that a certain fixed pressure is not exceeded. In contrast, the concentration of refrigerant on the low-pressure side increases, and liquid storage of excess liquid refrigerant into the refrigerantamount adjusting device 6 is thus performed. Due to storage of excess liquid refrigerant in the refrigerantamount adjusting device 6, there is no need to provide an internal heat exchanger that allows heat exchange between high-pressure-side refrigerant and low-pressure-side refrigerant. Thus, cost can be reduced. After the operation stops, refrigerant flows into theevaporator 4 with a low heat capacity and is stored as liquid refrigerant in theevaporator 4. After that, when the fixed time has passed, liquid refrigerant is stored in thecompressor 1 with a high heat capacity. In the case where the apparatus is restarted immediately after liquid refrigerant is stored in theevaporator 4, if no refrigerantamount adjusting device 6 is provided, liquid back to thecompressor 1 may cause liquid compression. Thus, the refrigerantamount adjusting device 6 is provided in the heat pump hotwater supply apparatus 100 according toEmbodiment 1, and liquid refrigerant is stored in the refrigerantamount adjusting device 6. Therefore, liquid compression by thecompressor 1 can be avoided, and the reliability of thecompressor 1 can thus be ensured. A suction muffler may be used as the refrigerantamount adjusting device 6. The suction muffler serves as both muffling means and the refrigerantamount 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. - Hereinafter, an
outdoor unit 100 of an air-conditioning apparatus according toEmbodiment 2 of the present invention will be explained with reference to drawings. -
Fig. 7 is a circuit diagram of the heat pump hotwater supply apparatus 100 that includes an internal heat exchanger 5. For example, due to constraints on structure, the refrigerantamount adjusting device 6 with a certain size or more cannot be installed. In such a case, if a designed pressure on a high-pressure side may be exceeded, the internal heat exchanger 5, which allows heat exchange between refrigerant in a region from the outlet of acondenser 2 to the inlet of anexpansion valve 3 and refrigerant in a region from the outlet of anevaporator 4 to the inlet of acompressor 1, may be provided, as illustrated inFig. 7 . In this case, theexpansion valve 3 is provided at a refrigerant flow passage between theevaporator 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 inFig. 8 , to increase the concentration of refrigerant in theevaporator 4 and store the refrigerant in the evaporator when the inlet water temperature of thecondenser 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 Fig. 9 , to be able to provide superheat at the outlet of theevaporator 4 and thus improve the COP. Asign 54 inFig. 9 represents an enthalpy range increased when superheat is provided at the outlet of theevaporator 4 by the internal heat exchanger 5. Asign 55 represents transition of state of refrigerant in the case where the internal heat exchanger 5 is provided. Asign 56 represents transition of state of refrigerant in the case where the internal heat exchanger 5 is not provided. - In the case where both the internal heat exchanger 5 and the refrigerant
amount adjusting device 6 are used as inEmbodiment 2, effects of high-pressure suppression and COP improvement mentioned above can be achieved. If the amount of liquid storage in the refrigerantamount adjusting device 6 can be increased to an extent not causing overflow, the internal heat exchanger 5 can be made compact, which leads to reduction in cost. Furthermore, by performing control such that the entire amount of excess liquid refrigerant can be stored only in the refrigerantamount adjusting device 6, the internal heat exchanger 5 can be removed as inEmbodiment 1. Therefore, a further reduction in cost can be achieved. - 1 compressor, 2 condenser, 3 expansion valve, 4 evaporator, 5 internal heat exchanger, 6 refrigerant amount adjusting device, 7 fan motor, 8 fan, 9 inlet water temperature detection unit, 10 outlet water temperature detection unit, 11 hot water circulating pump, 12 tank control unit, 13 heat source unit control unit, 14 hot water tank, 15 hot water circulating pipe, 16 outside air temperature detection unit, 17 inlet refrigerant temperature detection unit, 18 outlet refrigerant temperature detection unit, 19 refrigerant pipe, 21 compressor rotation speed control part, 22 fan rotation speed control part, 23 pump rotation speed control part, 24 detection temperature reception part, 25 expansion valve opening degree adjustment part, 26 temperature reception part, 30 memory unit, 31 suction pipe, 32 relay pipe, 33 liquid refrigerant storage part, 34 discharge pipe, 35 oil return hole, 100 heat pump hot water supply apparatus, 200 heat source unit, 300 tank unit
Claims (6)
- A heat pump hot water supply apparatus comprising: 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, wherein when the inlet water temperature reaches a threshold value or more, the heat source unit control unit changes the temperature difference to adjust the valve opening degree of the expansion valve in an opening direction.
- The heat pump hot water supply apparatus of claim 1, wherein refrigerant is stored in the refrigerant amount adjusting device when the inlet water temperature reaches the threshold value or more.
- The heat pump hot water supply apparatus of claim 1 or 2, wherein the refrigerant amount adjusting device is provided at an inlet of the compressor.
- The heat pump hot water supply apparatus of any one of claims 1 to 3, wherein the refrigerant amount adjusting device is a suction muffler that includes a space in which liquid refrigerant is able to be stored.
- The heat pump hot water supply apparatus of any one of claims 1 to 4, further comprising an internal heat exchanger allowing heat exchange between refrigerant in a region from an outlet of the condenser to an inlet of the expansion valve and refrigerant in a region from an outlet of the evaporator to an inlet of the compressor.
- The heat pump hot water supply apparatus of any one of claims 1 to 5, further comprising a memory unit storing the temperature difference set in advance,
wherein the temperature difference set in advance is equal to a temperature difference represented by a relationship that a value obtained by subtracting the hot water target temperature from the inlet refrigerant temperature is more than 0.
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PCT/JP2017/009418 WO2018163345A1 (en) | 2017-03-09 | 2017-03-09 | Heat pump hot water supply device |
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NO890076D0 (en) * | 1989-01-09 | 1989-01-09 | Sinvent As | AIR CONDITIONING. |
JPH0718602A (en) | 1993-06-29 | 1995-01-20 | Sekisui Chem Co Ltd | Tie plug |
JP3659197B2 (en) * | 2000-06-21 | 2005-06-15 | 松下電器産業株式会社 | Heat pump water heater |
JP4731806B2 (en) | 2003-12-01 | 2011-07-27 | パナソニック株式会社 | Refrigeration cycle apparatus and control method thereof |
JP2007212103A (en) * | 2006-02-13 | 2007-08-23 | Matsushita Electric Ind Co Ltd | Heat pump type hot water supply apparatus |
JP4948374B2 (en) * | 2007-11-30 | 2012-06-06 | 三菱電機株式会社 | Refrigeration cycle equipment |
JP5173469B2 (en) * | 2008-02-15 | 2013-04-03 | 三菱電機株式会社 | Heat pump water heater |
JP5558937B2 (en) * | 2010-06-30 | 2014-07-23 | 株式会社コロナ | Heat pump type water heater |
JP5776314B2 (en) * | 2011-04-28 | 2015-09-09 | 株式会社ノーリツ | Heat pump water heater |
JP5861577B2 (en) * | 2012-07-05 | 2016-02-16 | 株式会社デンソー | Water heater |
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