WO2023144889A1 - Chauffe-eau à stockage - Google Patents

Chauffe-eau à stockage Download PDF

Info

Publication number
WO2023144889A1
WO2023144889A1 PCT/JP2022/002680 JP2022002680W WO2023144889A1 WO 2023144889 A1 WO2023144889 A1 WO 2023144889A1 JP 2022002680 W JP2022002680 W JP 2022002680W WO 2023144889 A1 WO2023144889 A1 WO 2023144889A1
Authority
WO
WIPO (PCT)
Prior art keywords
condenser
hot water
refrigerant
refrigerant pipe
water storage
Prior art date
Application number
PCT/JP2022/002680
Other languages
English (en)
Japanese (ja)
Inventor
健太 村田
大樹 広崎
Original Assignee
三菱電機株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to JP2023576289A priority Critical patent/JPWO2023144889A1/ja
Priority to PCT/JP2022/002680 priority patent/WO2023144889A1/fr
Publication of WO2023144889A1 publication Critical patent/WO2023144889A1/fr

Links

Images

Classifications

    • 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
    • F24H1/00—Water heaters, e.g. boilers, continuous-flow heaters or water-storage heaters
    • F24H1/18—Water-storage heaters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H4/00—Fluid heaters characterised by the use of heat pumps
    • F24H4/02—Water heaters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/02—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being helically coiled

Definitions

  • This disclosure relates to a storage hot water heater.
  • Patent Document 1 describes a water tank having a wall made of a material having heat transfer properties, a pipe attached to the outer periphery of the wall of the water tank and carrying a refrigerant, and a pipe extending along the length of the pipe.
  • a water heater is also disclosed that includes a heat-conducting material in heat transfer contact with the tub wall and the tube, and at least one layer of material that is tightly wrapped around the tub wall and tube.
  • the present disclosure has been made to solve the problems described above, and aims to provide a hot water storage type water heater that is advantageous in increasing the amount of heat stored in the hot water storage tank.
  • a hot water storage type water heater includes a hot water storage tank, and a condenser disposed in the hot water storage tank and having a spiral refrigerant pipe centered on a vertical line. and the vertical length of the vertical cross-sectional shape of the refrigerant tube in the lower part of the condenser is shorter than the vertical length of the vertical cross-sectional shape of the refrigerant tube in the upper part of the condenser.
  • FIG. 1 is a diagram showing a storage hot water heater according to Embodiment 1.
  • FIG. 4 is a graph showing the temperature distribution along the vertical direction in the hot water storage tank during the hot water storage operation.
  • FIG. 4 is a schematic cross-sectional side view for explaining the water temperature distribution in the hot water storage tank;
  • FIG. 2 is a cross-sectional view showing an example of a vertical cross-sectional shape of a refrigerant pipe of a condenser in the hot water storage type water heater according to Embodiment 1;
  • 4 is a cross-sectional view showing another example of the vertical cross-sectional shape of the refrigerant pipe of the condenser in the hot water storage type water heater according to Embodiment 1.
  • FIG. 1 is a diagram showing a storage hot water heater according to Embodiment 1.
  • FIG. 4 is a graph showing the temperature distribution along the vertical direction in the hot water storage tank during the hot water storage operation.
  • FIG. 4 is a schematic cross-sectional side view for
  • FIG. 4 is a cross-sectional view showing another example of the vertical cross-sectional shape of the refrigerant pipe of the condenser in the hot water storage type water heater according to Embodiment 1.
  • FIG. 10 is a schematic cross-sectional side view for explaining a hot water storage type water heater according to Embodiment 2;
  • FIG. 1 is a diagram showing a hot water storage type hot water heater 1 according to Embodiment 1.
  • a storage hot water heater 1 according to Embodiment 1 includes a heat source device 2 and a tank unit 3 .
  • the heat source machine 2 is arranged outdoors.
  • the tank unit 3 may be arranged outdoors or may be arranged indoors.
  • the heat source device 2 and the tank unit 3 are connected via extension pipes 4 and 5 and electric cables (not shown).
  • the hot water storage type water heater 1 may be for domestic use or may be for business use.
  • Hot water storage tank 6 is provided inside the housing of the tank unit 3 .
  • Hot water storage tank 6 in the present embodiment has a cylindrical outer shape.
  • the central axis of the hot water storage tank 6 is substantially parallel to the vertical line.
  • the hot water tank 6 may be made of metal, for example stainless steel.
  • a heat insulating material (not shown) is provided inside the housing of the tank unit 3 to cover the condenser 17 and the hot water storage tank 6, which will be described later.
  • a water supply port 7 is arranged at the bottom of the hot water storage tank 6 .
  • a hot water supply port 8 is arranged above the hot water storage tank 6 .
  • a water supply pipe 9 is connected to the water supply port 7 .
  • a hot water supply pipe 10 is connected to the hot water supply port 8 .
  • the downstream of the hot water supply pipe 10 is connected to a hot water supply terminal (not shown) inside the building.
  • the hot water supply terminal may include, for example, at least one of a faucet, a shower, and a bathtub.
  • water supplied from a water source such as tap water flows into the lower part of the hot water storage tank 6 through the water supply pipe 9, so that the inside of the hot water storage tank 6 is always kept full.
  • the water pressure from the water supply pipe 9 causes the hot water in the hot water storage tank 6 to flow out from the hot water supply port 8 to the hot water supply pipe 10 .
  • the same amount of water flows from the water supply pipe 9 through the water supply port 7 into the lower part of the hot water storage tank 6 .
  • the hot water supply operation is such that hot water in the hot water storage tank 6 flows out from the hot water supply port 8 and water flows into the hot water storage tank 6 from the water supply port 7 .
  • the heat source device 2 is provided with an evaporator 11 that evaporates the refrigerant, a compressor 12 that compresses the refrigerant flowing out of the evaporator 11, an expansion valve 13, and a control circuit 14.
  • Evaporator 11 in the present embodiment evaporates the refrigerant by exchanging heat between the outdoor air and the refrigerant.
  • the heat source device 2 further includes a blower 15 that blows outdoor air to the evaporator 11 .
  • the hot water storage type water heater 1 further includes a condenser 17 arranged in the hot water storage tank 6 .
  • the condenser 17 exchanges heat between the refrigerant compressed by the compressor 12 and the water in the hot water storage tank 6 to condense the refrigerant.
  • the condenser 17 has a helical or coiled refrigerant pipe 18 centered on a vertical line.
  • a refrigerant pipe 18 is spirally or coiledly wound between a heat insulating material (not shown) covering the outer periphery of the hot water storage tank 6 and the surface of the hot water storage tank 6 .
  • the refrigerant pipe 18 is in contact with the outer wall of the hot water storage tank 6 so as to be able to conduct heat.
  • the heat of the refrigerant flowing through the refrigerant pipe 18 is transferred to the peripheral wall of the hot water storage tank 6 .
  • the heat transmitted to the peripheral wall of the hot water storage tank 6 is transmitted to the water in the hot water storage tank 6, thereby heating the water in the hot water storage tank 6.
  • - ⁇ Refrigerant pipe 18 is arranged such that its position gradually lowers while going around the outer periphery of hot water storage tank 6 from upstream to downstream.
  • the central axis of the spiral or coil formed by the refrigerant pipe 18 coincides with the central axis of the hot water storage tank 6 .
  • the refrigerant pipe 18 may be made of metal.
  • a material forming the refrigerant pipe 18 may be, for example, copper, a copper alloy, aluminum, an aluminum alloy, or the like.
  • the condenser 17 has an upper portion 17A and a lower portion 17B.
  • the lower portion 17B is positioned lower than the upper portion 17A.
  • the refrigerant is configured to flow from the refrigerant pipe 18 in the upper portion 17A of the condenser 17 to the refrigerant pipe 18 in the lower portion 17B of the condenser 17 .
  • the vertical dimension LA of the upper portion 17A of the condenser 17 is the vertical distance from the upper end of the upper portion 17A to the lower end of the upper portion 17A.
  • the vertical dimension LB of the lower portion 17B of the condenser 17 is the vertical distance from the upper end of the lower portion 17B to the lower end of the lower portion 17B.
  • Vertical dimension LA of upper portion 17A of condenser 17 is greater than vertical dimension LB of lower portion 17B of condenser 17 .
  • the extension pipe 4 forms a refrigerant passage that connects the outlet of the compressor 12 to the inlet of the upper portion 17A of the condenser 17.
  • the extension pipe 5 forms a refrigerant passage that connects the outlet of the lower portion 17B of the condenser 17 to the inlet of the expansion valve 13 .
  • the refrigerant compressed by the compressor 12 moves from the heat source device 2 through the extension pipe 4 to the tank unit 3 and flows into the inlet of the upper portion 17A of the condenser 17 .
  • the refrigerant that has passed through the refrigerant pipe 18 in the upper portion 17A of the condenser 17 flows into the refrigerant pipe 18 in the lower portion 17B of the condenser 17 .
  • the refrigerant that has flowed out from the outlet of the lower portion 17B of the condenser 17 returns from the tank unit 3 through the extension pipe 5 to the heat source device 2 and flows into the expansion valve 13 .
  • the expansion valve 13 expands the refrigerant flowing out of the condenser 17 .
  • the refrigerant is decompressed when passing through the expansion valve 13 .
  • the expansion valve 13 may be a linear expansion valve whose degree of opening can be continuously adjusted.
  • the refrigerant that has passed through the expansion valve 13 flows into the evaporator 11 .
  • the refrigerant evaporated in the evaporator 11 flows into the compressor 12 and is compressed.
  • the control circuit 14 controls the hot water storage operation.
  • the hot water storage operation is an operation in which high-temperature, high-pressure refrigerant is supplied from the compressor 12 to the condenser 17 and the water in the hot-water storage tank 6 is heated by the high-temperature, high-pressure refrigerant flowing through the refrigerant pipe 18 of the condenser 17 .
  • Control circuitry 14 may include at least one processor and at least one memory. At least one processor may accomplish each function of control circuit 14 by reading and executing a program stored in at least one memory. Control circuitry 14 may comprise at least one piece of dedicated hardware.
  • the control circuit 14 may be, for example, a single circuit, a composite circuit, a programmed processor, a parallel programmed processor, an Application Specific Integrated Circuit (ASIC), a Field-Programmable Gate Array (FPGA), or a combination thereof. .
  • ASIC Application Specific Integrated Circuit
  • FPGA Field-Programmable Gate Array
  • control circuit 14 is arranged in the heat source machine 2, but as a modification, the control circuit 14 may be arranged in the tank unit 3. Further, the function of the control circuit 14 may be achieved by the controller arranged in the heat source device 2 and the controller arranged in the tank unit 3 communicating and cooperating with each other. At least part of the functions of the control circuit 14 may be achieved by a cloud server connected via a network such as the Internet.
  • the control circuit 14 controls the operation of the compressor 12 and the opening of the expansion valve 13 .
  • the operating speed of compressor 12 may be variable.
  • the control circuit 14 may vary the operating speed of the compressor 12 by varying the operating frequency of the electric motor provided in the compressor 12 through inverter control. The higher the operating frequency of the compressor 12, the higher the operating speed of the compressor 12. The higher the operating speed of the compressor 12, the greater the refrigerant circulation amount and the higher the heating capacity.
  • the heating capacity is the amount of heat given from the refrigerant to the water in the hot water storage tank 6 per unit time, and its unit is watt.
  • the control circuit 14 may communicate with the user interface 19 by wired communication or wireless communication.
  • the user interface 19 may be, for example, a remote control device installed on the wall of the room.
  • user interface 19 may be a mobile device such as a smart phone, for example.
  • FIG. 2 is a graph showing the temperature distribution along the vertical direction in the hot water storage tank 6 during the hot water storage operation.
  • the vertical axis in FIG. 2 corresponds to the vertical position in the hot water storage tank 6 represented by the volume of water from the bottom of the hot water storage tank 6 .
  • Water temperature distribution in FIG. 2 indicates the distribution of tank water temperature.
  • Tank wall surface temperature in FIG. 2 indicates the temperature distribution of the wall surface of the hot water tank 6 .
  • “Refrigerant temperature” in FIG. 2 indicates the temperature distribution of the refrigerant in the condenser 17 .
  • the refrigerant temperature in the vertical region where the refrigerant temperature is substantially constant along the vertical direction corresponds to the condensing temperature.
  • the refrigerant has two phases of gas and liquid.
  • the refrigerant at the inlet of the condenser 17 is in a superheated gas with a temperature above the condensation temperature. The difference between the temperature of the superheated refrigerant and the condensing temperature is called the degree of superheat.
  • the refrigerant is a superheated gas in a part of the region near the inlet, and the refrigerant is a gas-liquid two-phase in other regions.
  • the vertical region SC where the refrigerant temperature is lower than the condensation temperature corresponds to the lower portion 17B of the condenser 17.
  • the refrigerant is condensed into a liquid phase. That is, the vertical area SC corresponding to the lower portion 17B of the condenser 17 is filled with liquid refrigerant, which is a liquid-phase refrigerant.
  • the temperature of the liquid refrigerant is lower than the condensation temperature.
  • the difference between the condensing temperature and the temperature of the liquid refrigerant is called the degree of subcooling.
  • the degree of supercooling is also commonly referred to as subcooling.
  • a liquid refrigerant having a temperature lower than the condensation temperature flows out from the condenser 17 .
  • the liquid refrigerant flows into the expansion valve 13 through the extension pipe 5 .
  • the tank wall temperature in the vertical region where the refrigerant temperature is equal to the condensing temperature is slightly lower than the condensing temperature and is almost constant along the vertical direction.
  • the tank wall temperature in the vertical region where the refrigerant is in a superheated gas state is higher than the tank wall temperature in the vertical region where the refrigerant temperature is equal to the condensing temperature.
  • the tank wall surface temperature in the upper vertical region gradually decreases upward and becomes equal to the tank water temperature. This is because the walls of the hot water storage tank 6 are not heated in the vertical region above the upper end of the condenser 17 .
  • the heat of the refrigerant passing through the refrigerant pipe 18 of the condenser 17 is transmitted to the wall of the hot water storage tank 6 and further to the water in contact with the inner wall of the hot water storage tank 6 .
  • the density of the water decreases, and the water subjected to buoyancy moves upward within the hot water storage tank 6 .
  • natural convection heat transfer occurs between the inner wall of the hot water storage tank 6 and the water. Also, natural convection occurs in the hot water storage tank 6 .
  • the tank water temperature from the vertical region where the refrigerant temperature is equal to the condensing temperature to the top of the hot water storage tank 6 is , distributed almost uniformly along the vertical direction. That is, the tank water temperature from the boundary between the upper portion 17A and the lower portion 17B of the condenser 17 to the uppermost portion of the hot water storage tank 6 is distributed substantially uniformly along the vertical direction.
  • the tank water temperature is also lowered.
  • the tank water temperature from the boundary between the upper portion 17A and the lower portion 17B of the condenser 17 to the bottom of the hot water storage tank 6 is higher than the tank water temperature in the vertical area above it. lower.
  • FIG. 3 is a schematic cross-sectional side view for explaining the water temperature distribution in the hot water storage tank 6.
  • FIG. The diagram on the right side in FIG. 3 corresponds to the hot water storage type hot water heater 1 according to the first embodiment.
  • the diagram on the left side of FIG. 3 corresponds to a comparative example. As shown in the diagram on the right side of FIG. It is shorter than the vertical length V of the vertical cross-sectional shape.
  • the vertical length V of the vertical cross-sectional shape of the refrigerant pipe 18 is constant throughout the condenser 17 .
  • the vertical cross-sectional shape of the refrigerant pipe 18 is the shape of a cross section obtained by cutting the refrigerant pipe 18 along a plane including the vertical line that is the center of the spiral formed by the refrigerant pipe 18 .
  • the vertical cross-sectional shape of the refrigerant pipe 18 is the cross-sectional shape obtained by cutting the refrigerant pipe 18 along a plane including the central axis of the hot water storage tank 6 .
  • the vertical length V corresponds to the vertical distance from the top to the bottom of the vertical cross-sectional shape.
  • the control circuit 14 fills the refrigerant pipe 18 in the lower portion 17B of the condenser 17 with liquid refrigerant, and the refrigerant pipe 18 in the upper portion 17A of the condenser 17 fills with superheated gas refrigerant or gas-liquid two-phase refrigerant.
  • the operation of the compressor 12 and the operation of the expansion valve 13 are controlled so that When the refrigerant pipe 18 in the lower portion 17B of the condenser 17 is filled with liquid refrigerant, the refrigerant at the inlet of the expansion valve 13 can be reliably prevented from becoming two phases of gas and liquid, so controllability of the heat source device 2 is improved. .
  • the tank water temperature is low in the vertical region SC corresponding to the lower portion 17B of the condenser 17 filled with liquid refrigerant. Therefore, in order to increase the amount of heat stored in the hot water storage tank 6, it is advantageous for the vertical area SC corresponding to the lower portion 17B of the condenser 17 to be narrow.
  • the vertical length V of the vertical cross-sectional shape of the refrigerant pipe 18 in the lower portion 17B of the condenser 17 is longer than the vertical length V of the vertical cross-sectional shape of the refrigerant pipe 18 in the upper portion 17A of the condenser 17.
  • the shortness is advantageous in shortening the vertical dimension LB of the lower portion 17B of the condenser 17 .
  • the vertical area where the tank water temperature is low is narrowed, so that the amount of heat stored in the hot water storage tank 6 can be increased.
  • the vertical dimension LC of the lower portion of the condenser 17 filled with liquid refrigerant is longer than in the present embodiment. Therefore, in the hot water storage tank 6, the vertical region where the tank water temperature is low is wider than in the present embodiment, so the amount of heat stored in the hot water storage tank 6 is smaller than in the present embodiment.
  • FIG. 3 is a schematic diagram and is simplified.
  • the size of the vertical cross-sectional shape of the refrigerant pipe 18 is exaggerated compared to the size of the hot water storage tank 6 .
  • the number of turns of the spiral formed by the refrigerant pipe 18 in the upper portion 17A of the condenser 17 is two, but in reality, the number of turns of the spiral formed by the refrigerant pipe 18 in the upper portion 17A of the condenser 17 is three. It can be more than that.
  • the number of turns of the spiral formed by the refrigerant pipe 18 in the lower portion 17B of the condenser 17 is 2, but in reality, the number of turns of the spiral formed by the refrigerant pipe 18 in the lower portion 17B of the condenser 17 is 2. may be 3 or more.
  • the vertical length V of the vertical cross-sectional shape of the refrigerant pipe 18 in the upper portion 17A of the condenser 17 is 1.1. It is preferably 1 time or more, more preferably 1.3 times or more.
  • the vertical length V of the vertical cross-sectional shape of the refrigerant pipe 18 in the upper portion 17A of the condenser 17 is three times or less the vertical length V of the vertical cross-sectional shape of the refrigerant pipe 18 in the lower portion 17B of the condenser 17. is preferable, and 2.5 times or less is more preferable. If the above relationship is satisfied, it is more advantageous for increasing the amount of heat stored in the hot water storage tank 6 .
  • the vertical dimension LA of the upper portion 17A of the condenser 17 is preferably 1.2 times or more, and preferably 1.5 times or more, the vertical dimension LB of the lower portion 17B of the condenser 17. more preferred. Also, the vertical dimension LA of the upper portion 17A of the condenser 17 is preferably 20 times or less, more preferably 15 times or less, the vertical dimension LB of the lower portion 17B of the condenser 17 . If the above relationship is satisfied, it is more advantageous for increasing the amount of heat stored in the hot water storage tank 6 .
  • FIG. 4 is a cross-sectional view showing an example of the vertical cross-sectional shape of the refrigerant pipe 18 of the condenser 17 in the hot water storage type water heater 1 according to Embodiment 1.
  • the vertical cross-sectional shape of the refrigerant pipe 18 shown in FIG. 4 is cocoon-shaped.
  • the vertical length V of the vertical cross-sectional shape of the refrigerant pipe 18 shown in FIG. 4 is longer than the horizontal length H of the vertical cross-sectional shape.
  • the horizontal length H corresponds to the horizontal distance from the left end to the right end of the vertical cross-sectional shape.
  • the refrigerant pipe 18 may have a flat portion 18b at a portion that is joined to the wall surface of the hot water storage tank 6. As shown in FIG. The flat portion 18b is a portion where the pipe wall of the refrigerant pipe 18 forms a flat region. Since the refrigerant pipe 18 has the flat portion 18b, the contact area between the wall surface of the hot water storage tank 6 and the refrigerant pipe 18 is increased, the contact heat resistance is reduced, and the amount of heat exchange can be increased.
  • a heat transfer material 20 may be provided between the wall surface of the hot water storage tank 6 and the refrigerant pipe 18 .
  • the heat transfer material 20 may be, for example, solder, brazing material, or weld metal.
  • refrigerant pipe 18 having the cocoon-shaped vertical cross-sectional shape shown in FIG. 4
  • a refrigerant pipe 18 having an elliptical vertical cross-sectional shape without the recess 18a may be used.
  • FIG. 5 is a cross-sectional view showing another example of the vertical cross-sectional shape of the refrigerant pipe 18 of the condenser 17 in the hot water storage type water heater 1 according to Embodiment 1. As shown in FIG. The difference between the example of FIG. 5 and the example of FIG. 4 will be described.
  • the vertical cross-sectional shape of the refrigerant pipe 18 shown in FIG. 5 is D-shaped.
  • the refrigerant pipe 18 having this D-shaped vertical cross section has one bulge on the opposite side of the flat portion 18b.
  • the value of V/H obtained by dividing the vertical length V of the vertical cross-sectional shape of the refrigerant pipe 18 by the horizontal length H of the vertical cross-sectional shape is hereinafter referred to as the "aspect ratio".
  • the aspect ratio V/H of the refrigerant pipe 18 having a D-shaped vertical cross-section as shown in FIG. is also small.
  • FIG. 6 is a cross-sectional view showing another example of the vertical cross-sectional shape of the refrigerant pipe 18 of the condenser 17 in the hot water storage type water heater 1 according to Embodiment 1. As shown in FIG. The difference between the example in FIG. 6 and the example in FIG. 4 will be described.
  • the vertical cross-sectional shape of the refrigerant pipe 18 shown in FIG. 6 is C-shaped.
  • the refrigerant pipe 18 having a C-shaped vertical cross section has an upper projecting portion 18c projecting radially outward from the hot water storage tank 6 and an upper projecting portion 18c projecting radially outward from the hot water storage tank 6 on the opposite side of the flat portion 18b.
  • the vertical cross-sectional shape of the refrigerant pipe 18 of the condenser 17 in the hot water storage type hot water heater 1 according to Embodiment 1 may be circular.
  • the aspect ratio V/H of the refrigerant pipes 18 at the lower portion 17B of the condenser 17 is smaller than the aspect ratio V/H of the refrigerant pipes 18 at the upper portion 17A of the condenser 17 .
  • the vertical length V of the vertical cross-sectional shape of the refrigerant pipe 18 in the lower portion 17B of the condenser 17 is shorter than the vertical length V of the vertical cross-sectional shape of the refrigerant pipe 18 in the upper portion 17A of the condenser 17.
  • the vertical cross-sectional shape of the refrigerant pipe 18 in the upper portion 17A of the condenser 17 may be, for example, the above-described cocoon shape or an elliptical shape. If the vertical cross-sectional shape of the refrigerant pipe 18 in the upper portion 17A of the condenser 17 is cocoon-shaped or elliptical, the contact area between the wall surface of the hot water storage tank 6 and the refrigerant pipe 18 increases, and the heat exchange amount of the condenser 17 increases. improves. In addition, since the cocoon-shaped or elliptical vertical cross-sectional shape has a relatively small cross-sectional area, the internal volume of the upper portion 17A of the condenser 17 is relatively small. As a result, the amount of refrigerant required for the entire refrigerant circuit can be reduced.
  • the vertical cross-sectional shape of the refrigerant pipe 18 in the lower portion 17B of the condenser 17 may be, for example, the above-described D-shape, circle, or C-shape. If the vertical cross-sectional shape of the refrigerant pipe 18 in the lower portion 17B of the condenser 17 is D-shaped, circular, or C-shaped, the aspect ratio V/H is relatively small. can be made smaller.
  • the vertical cross-sectional shape of the refrigerant pipe 18 in the lower portion 17B of the condenser 17 is D-shaped or C-shaped, the cross-sectional area is smaller than the circular cross-section, so the internal volume of the lower portion 17B of the condenser 17 is compared. becomes less meaningful. As a result, the amount of refrigerant required for the entire refrigerant circuit can be reduced.
  • the vertical cross-sectional shape of the refrigerant pipes 18 in the upper portion 17A of the condenser 17 and the vertical cross-sectional shape of the refrigerant pipes 18 in the lower portion 17B of the condenser 17 may be of different types.
  • the vertical cross-sectional shape of the refrigerant pipe 18 in the upper portion 17A of the condenser 17 is cocoon-shaped or elliptical
  • the vertical cross-sectional shape of the refrigerant pipe 18 in the lower portion 17B of the condenser 17 is D-shaped, circular, or It may be C-shaped.
  • the vertical cross-sectional shape of the refrigerant pipes 18 in the upper portion 17A of the condenser 17 and the vertical cross-sectional shape of the refrigerant pipes 18 in the lower portion 17B of the condenser 17 are of the same type, and the aspect ratio V/H is different from each other.
  • both the vertical cross-sectional shape of the refrigerant pipe 18 in the upper portion 17A of the condenser 17 and the vertical cross-sectional shape of the refrigerant pipe 18 in the lower portion 17B of the condenser 17 are D-shaped, and the upper portion 17A of the condenser 17
  • the aspect ratio V/H of the refrigerant pipe 18 at the lower portion 17B of the condenser 17 may be smaller than the aspect ratio V/H of the refrigerant pipe 18 at .
  • the number of turns of the spiral formed by the refrigerant pipe 18 in the upper portion 17A of the condenser 17 is greater than the number of turns of the spiral formed by the refrigerant pipe 18 in the lower portion 17B of the condenser 17. If the number of turns of the spiral of the refrigerant pipe 18 of the upper portion 17A where the refrigerant reaches a relatively high temperature is relatively large and the number of turns of the spiral of the refrigerant pipe 18 of the lower portion 17B where the temperature of the refrigerant becomes relatively low is relatively small, the hot water storage tank It is more advantageous in increasing the heat storage amount of 6.
  • Embodiment 2 Next, Embodiment 2 will be described with reference to FIG. 7. The description will focus on differences from Embodiment 1 described above, and common descriptions will be simplified or omitted. Moreover, the same code
  • FIG. 7 is a schematic cross-sectional side view for explaining the hot water storage type hot water heater 1 according to Embodiment 2.
  • FIG. The diagram on the right side in FIG. 7 corresponds to the hot water storage type hot water heater 1 according to the second embodiment. As the diagram on the right side of FIG. It is smaller than the pitch P of the helix that the tube 18 forms.
  • the pitch P of the spiral formed by the refrigerant pipes 18 corresponds to the center-to-center distance between two adjacent refrigerant pipes 18 in a cross section cut along a plane including the central axis of the hot water storage tank 6 .
  • the pitch P of the spiral formed by the refrigerant pipes 18 in the lower portion 17B of the condenser 17 is equal to the spiral pitch P formed by the refrigerant pipes 18 in the upper portion 17A of the condenser 17.
  • the pitch P of the spiral formed by the refrigerant pipes 18 in the lower portion 17B of the condenser 17 is the pitch P of the spiral formed by the refrigerant pipes 18 in the upper portion 17A of the condenser 17.
  • the vertical dimension LB of the lower portion 17B of the condenser 17 can be made shorter. As a result, in the hot water storage tank 6, the vertical region where the tank water temperature is low becomes narrower, so that the amount of heat stored in the hot water storage tank 6 can be increased.
  • the example in which the refrigerant pipe 18 of the condenser 17 is wound around the hot water tank 6 has been described.
  • the spiral or coiled refrigerant pipe 18 may be arranged so as to be inscribed in the inner wall surface of the hot water storage tank 6 .
  • the spiral or coiled refrigerant pipe 18 may be arranged so as to be submerged inside the hot water tank 6 without contacting the inner wall surface of the hot water tank 6 .

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)

Abstract

Un chauffe-eau à stockage selon la présente divulgation comprend un réservoir de stockage d'eau chaude et un condenseur disposé dans le réservoir de stockage d'eau chaude et présentant un tuyau de réfrigérant sous la forme d'une hélice autour d'une ligne verticale. Le condenseur présente une partie supérieure et une partie inférieure qui est inférieure à la partie supérieure. La longueur verticale de la forme de section transversale verticale du tuyau de réfrigérant au niveau de la partie inférieure du condenseur est plus courte que la longueur verticale de la forme de section transversale verticale du tuyau de réfrigérant au niveau de la partie supérieure du condenseur. Le pas hélicoïdal formé par le tuyau de réfrigérant au niveau de la partie inférieure du condenseur peut être inférieur au pas hélicoïdal formé par le tuyau de réfrigérant au niveau de la partie supérieure du condenseur.
PCT/JP2022/002680 2022-01-25 2022-01-25 Chauffe-eau à stockage WO2023144889A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
JP2023576289A JPWO2023144889A1 (fr) 2022-01-25 2022-01-25
PCT/JP2022/002680 WO2023144889A1 (fr) 2022-01-25 2022-01-25 Chauffe-eau à stockage

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2022/002680 WO2023144889A1 (fr) 2022-01-25 2022-01-25 Chauffe-eau à stockage

Publications (1)

Publication Number Publication Date
WO2023144889A1 true WO2023144889A1 (fr) 2023-08-03

Family

ID=87471165

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2022/002680 WO2023144889A1 (fr) 2022-01-25 2022-01-25 Chauffe-eau à stockage

Country Status (2)

Country Link
JP (1) JPWO2023144889A1 (fr)
WO (1) WO2023144889A1 (fr)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2006521528A (ja) * 2003-03-28 2006-09-21 シドンズ・スティーブンス・ディベロップメンツ・ピーティーワイ・リミテッド 給湯器／冷水器
JP2007071426A (ja) * 2005-09-06 2007-03-22 Hitachi Ltd ヒートポンプ式給湯機及びそれに用いられる熱交換器
JP2008267790A (ja) * 2007-03-27 2008-11-06 Daikin Ind Ltd ヒートポンプ式給湯装置および暖房給湯装置
FR3077622A1 (fr) * 2018-02-07 2019-08-09 Atlantic Industrie Appareil de chauffage thermodynamique d'une cuve

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2006521528A (ja) * 2003-03-28 2006-09-21 シドンズ・スティーブンス・ディベロップメンツ・ピーティーワイ・リミテッド 給湯器／冷水器
JP2007071426A (ja) * 2005-09-06 2007-03-22 Hitachi Ltd ヒートポンプ式給湯機及びそれに用いられる熱交換器
JP2008267790A (ja) * 2007-03-27 2008-11-06 Daikin Ind Ltd ヒートポンプ式給湯装置および暖房給湯装置
FR3077622A1 (fr) * 2018-02-07 2019-08-09 Atlantic Industrie Appareil de chauffage thermodynamique d'une cuve

Also Published As

Publication number Publication date
JPWO2023144889A1 (fr) 2023-08-03

Similar Documents

Publication Publication Date Title
JP5506929B2 (ja) タンクレス温水システム用のコイル管熱交換器
EP2154443A1 (fr) Installation d'alimentation en eau chaude pour le chauffage
JP6482641B2 (ja) 熱交換セルのセットを製造する方法及びそのようにして得られる熱交換セルのセット
JP2008267792A (ja) ヒートポンプ式給湯装置
JP2006336894A (ja) ヒートポンプ給湯機
JP2008267790A (ja) ヒートポンプ式給湯装置および暖房給湯装置
JP4200329B2 (ja) 熱交換装置及びそれを用いたヒートポンプ給湯装置
EP2770277B1 (fr) Chauffe-eau
JP2005133999A (ja) ヒートポンプ式給湯機
EP2770278A1 (fr) Chauffe-eau
JP6573210B2 (ja) 二重管式熱交換器及びこれを備えたヒートポンプ式熱源機
JP2013024543A (ja) 熱交換器及びそれを用いたヒートポンプ式加熱装置
JP3812389B2 (ja) 冷凍サイクル装置
US4621592A (en) Boiler having improved heat absorption
JP6277713B2 (ja) ２重管式熱交換器
WO2023144889A1 (fr) Chauffe-eau à stockage
US4371036A (en) Heat exchanger, particularly for heat pumps
JP4572662B2 (ja) 熱交換器
JP4063237B2 (ja) 熱交換装置及びそれを用いたヒートポンプ給湯装置
JP4455869B2 (ja) 空気調和機及びその運転制御方法
JP5929012B2 (ja) 熱交換器及びヒートポンプ給湯装置
JP2009133530A (ja) 熱交換器及びそれを用いてなるヒートポンプ給湯機
JP4207895B2 (ja) 加熱器
JP3922214B2 (ja) 熱交換器およびそれを用いたヒートポンプ給湯機
JP2013024536A (ja) 液冷媒熱交換器及びヒートポンプ給湯機

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 22923758

Country of ref document: EP

Kind code of ref document: A1

ENP Entry into the national phase

Ref document number: 2023576289

Country of ref document: JP

Kind code of ref document: A

ENP Entry into the national phase

Ref document number: 2022923758

Country of ref document: EP

Effective date: 20240826