WO2021187937A1 - 히트펌프 시스템 및 이를 이용한 냉난방 시스템 - Google Patents
히트펌프 시스템 및 이를 이용한 냉난방 시스템 Download PDFInfo
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- WO2021187937A1 WO2021187937A1 PCT/KR2021/003412 KR2021003412W WO2021187937A1 WO 2021187937 A1 WO2021187937 A1 WO 2021187937A1 KR 2021003412 W KR2021003412 W KR 2021003412W WO 2021187937 A1 WO2021187937 A1 WO 2021187937A1
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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
- F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
- F25B25/005—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00 using primary and secondary systems
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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
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- 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
- F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D9/0031—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other
- F28D9/0043—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
- F28D9/005—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another the plates having openings therein for both heat-exchange media
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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
- F24D3/00—Hot-water central heating systems
- F24D3/18—Hot-water central heating systems using heat pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
- F24F5/0007—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater cooling apparatus specially adapted for use in air-conditioning
- F24F5/0017—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater cooling apparatus specially adapted for use in air-conditioning using cold storage bodies, e.g. ice
- F24F5/0021—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater cooling apparatus specially adapted for use in air-conditioning using cold storage bodies, e.g. ice using phase change material [PCM] for storage
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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
- F25B13/00—Compression machines, plants or systems, with reversible cycle
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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
- F25B31/00—Compressor arrangements
- F25B31/006—Cooling of compressor or motor
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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
- F25B41/00—Fluid-circulation arrangements
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control 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
- F25B41/00—Fluid-circulation arrangements
- F25B41/40—Fluid line arrangements
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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
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
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- 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
- F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
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- 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
- F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
- F28D20/0034—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00 using liquid heat storage material
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
- F24F5/0007—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater cooling apparatus specially adapted for use in air-conditioning
- F24F5/0017—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater cooling apparatus specially adapted for use in air-conditioning using cold storage bodies, e.g. ice
- F24F2005/0025—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater cooling apparatus specially adapted for use in air-conditioning using cold storage bodies, e.g. ice using heat exchange fluid storage tanks
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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
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/003—Indoor unit with water as a heat sink or heat source
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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
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/04—Refrigeration circuit bypassing means
- F25B2400/0401—Refrigeration circuit bypassing means for the compressor
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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
- F25B2600/2515—Flow 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
- F25B2700/2115—Temperatures of a compressor or the drive means therefor
- F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge side of the compressor
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- 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
- F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
- F28D2020/0065—Details, e.g. particular heat storage tanks, auxiliary members within tanks
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- 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
- F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
- F28D2020/0065—Details, e.g. particular heat storage tanks, auxiliary members within tanks
- F28D2020/0069—Distributing arrangements; Fluid deflecting means
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- 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
- F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
- F28D2020/0065—Details, e.g. particular heat storage tanks, auxiliary members within tanks
- F28D2020/0078—Heat exchanger arrangements
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- 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
- F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
- F28D2020/0065—Details, e.g. particular heat storage tanks, auxiliary members within tanks
- F28D2020/0086—Partitions
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
- Y02E60/14—Thermal energy storage
Definitions
- the present invention relates to a heat pump system, and more particularly, to a heat pump system in which an indoor unit and an outdoor unit are converted into a condenser and an evaporator according to selection of heating and cooling, and a heating and cooling system using the same.
- a typical heat pump system repeats the cycle in which the refrigerant flows back into the compressor via the condenser, the condenser, the expansion valve, and the evaporator.
- the refrigerant passing through the compressor is converted into a liquid phase in the condenser which is a heat exchanger, and is configured to release latent heat, absorb external heat in the evaporator, and evaporate to provide cooling and heating.
- the heat pump system has the advantages of fast and uniform heating of saturated steam according to latent heating, the relationship between pressure and temperature can be accurately set, and high thermal conductivity. has the problem of lowering. Therefore, in order to utilize the latent heat of the saturated steam of the heat pump system for heating and cooling, control conditions such as temperature and pressure on the load side should be optimized.
- Korean Utility Model No. 20-281266 includes a receiver installed between a condenser and an expansion valve to supply only liquid refrigerant to the expansion valve; an ejector to increase the refrigerant circulation amount by increasing the pressure of the refrigerant vapor evaporated in the evaporator; a superheat degree control device for controlling the superheat degree of the refrigerant at the inlet of the compressor; Capacity control device for adjusting the capacity by controlling the refrigerant flow rate; and a multi-stage condensing pressure control valve for controlling the condensing pressure in multiple stages.
- the heat pump system such as Korea Utility Model No. 20-281266, has a problem in that the cost of constructing the heat pump system is considerably increased, and the maintenance cost is increased because many additional devices need to be additionally installed. .
- the superheat control device of the heat pump system of Korea Utility Model No. 20-281266 has a disadvantage in that an additional heat exchanger is required for heat exchange between the refrigerant passing through the condenser and the refrigerant vapor at the inlet of the compressor.
- the plate heat exchanger is a device in which different types of heating medium flow alternately in each layer and heat exchange is performed.
- the heating medium is made of a liquid fluid, preferably antifreeze, water, or pure water.
- the plate heat exchanger is easy to assemble, has a small number of parts, so productivity is good, and the volume can be reduced, which is advantageous in securing space.
- the plate-type heat exchanger can design a complicated and diversified flow path by changing the shape of the plate.
- the heat medium for heat exchange flows into and out of the heat storage tank.
- a vortex may be generated inside the heat storage tank due to the high flow velocity of the heat medium while the heat medium, which is a fluid, is introduced into the heat storage tank.
- the present invention is to solve the above problems, and an object of the present invention is to provide a heat pump system capable of preventing a vortex generated while a fluid flows into a thermal storage tank, and a heating and cooling system using the same.
- Another object of the present invention is to achieve optimum efficiency of heat exchange at 13 ⁇ 18°C for heating and 3 ⁇ 7°C for cooling without additionally installing various additional devices including a superheat control device and a multi-stage condensing pressure control valve. It is to provide a heat pump system that can be implemented as a system and can supply and maintain constant temperature heating and cooling, and a heating and cooling system using the same.
- a heat pump system comprising: an indoor unit that functions as a condenser during heating and an evaporator during cooling; an outdoor unit that functions as an evaporator for heating and a condenser for cooling; a heating medium heat-exchanged while passing through the indoor unit; and a heat storage tank into which a heating medium, which has become cold or hot water while passing through the indoor unit, is introduced;
- a first inlet pipe for guiding the heating medium returning after passing through the indoor unit to flow into the heat storage tank; a first water outlet pipe for guiding the heat medium introduced into the heat storage tank through the first water inlet pipe to flow out to a load outside the heat storage tank; a second inlet pipe for guiding the heat medium returning to the load side outside the heat storage tank through the first water outlet pipe to flow into the heat storage tank; and a second water outlet pipe for guiding the heating medium flowing into the heat storage tank through the second water inlet pipe to flow out toward the indoor unit.
- the first inlet pipe may include: a first inlet portion formed in a structure introduced into the heat storage tank; and a plurality of through-holes formed through a portion of the first inlet portion facing an upper direction of the heat storage tank.
- the first water outlet pipe includes a first inlet formed in communication with the inside of the heat storage tank so that the heat medium in the heat storage tank can be introduced into the first water outlet pipe.
- the first inlet is formed to be located in an area higher than an area in which the first inlet is located in the heat storage tank.
- the second inlet pipe may include a second inlet portion formed in a structure introduced into the heat storage tank; and a plurality of through-holes formed through a portion of the second inlet portion facing a lower direction of the heat storage tank.
- the second water outlet pipe includes a second inlet formed in communication with the inside of the heat storage tank so that the heat medium in the heat storage tank can be introduced into the second outlet pipe.
- the second inlet is formed to be located in an area lower than an area in which the second inlet is located in the heat storage tank.
- the heat pump system and the heating/cooling system using the same it is possible to effectively disperse and diffuse the water pressure of the fluid flowing into the heat storage tank, thereby preventing vortex generation and minimizing heat loss. Accordingly, it is possible to ensure the continuous and uniform supply of the heating medium, to enable the efficient transfer and exchange of heat, there is an effect that can promote the stable operation of the heating and cooling supply and the system at a constant temperature.
- FIG. 1 is a block diagram of a heat pump system according to a first embodiment of the present invention.
- FIG. 2 is a perspective view of a first heat exchanger according to an embodiment of the present invention.
- Figure 3 is an exploded perspective view of Figure 2;
- FIG. 4 is a perspective view of a second heat exchanger according to an embodiment of the present invention.
- Figure 5 is an exploded perspective view of Figure 4.
- FIG. 6 is a cross-sectional view of a heat storage tank and a vortex prevention device installed therein according to the present invention.
- Figure 7 is a cross-sectional view of the first inlet of the first inlet pipe according to the present invention.
- Figure 8 is a cross-sectional view of the second inlet of the second inlet pipe according to the present invention.
- FIG. 9 is a block diagram of a heat pump system according to a second embodiment of the present invention.
- FIG. 10 is a block diagram of a heat pump system according to a third embodiment of the present invention.
- FIG. 11 is a block diagram of a heat pump system according to a fourth embodiment of the present invention.
- FIG. 12 is a block diagram of a heat pump system according to an extended embodiment of the present invention.
- FIG. 13 is a view showing a fluid flow and a heat exchange operation thereof during a heating operation of the heat pump system according to the present invention.
- FIG. 14 is a view showing a fluid flow and a heat exchange operation thereof during a cooling operation of the heat pump system according to the present invention.
- 15 is a block diagram of a heating and cooling system using the heat pump system of the present invention.
- first fluid line 93 second fluid line
- first channel 150 second channel
- first inlet 411 first inlet through hole
- first inlet 430 second inlet pipe
- on or on top of means to be located above or below the target part, which does not necessarily mean to be located above the direction of gravity. That is, the term “on or on top of” referred to in the present specification includes not only a case located above or below the target part, but also a case located in front or behind the target part.
- the heat pump system according to the present invention includes an indoor unit 10 , an outdoor unit 20 , a compressor 30 , an expansion valve 50 , a four-way valve 40 , a heat medium, a first heat exchanger 100 , It includes a heat storage tank 90 and a second heat exchanger 200 .
- the indoor unit 10 is configured to be converted into a condenser or an evaporator according to selection of a heating/cooling mode. Specifically, the indoor unit 10 is configured to function as a condenser during heating and as an evaporator during cooling.
- the outdoor unit 20 is configured to be converted into an evaporator or a condenser according to selection of a heating/cooling mode. Specifically, the outdoor unit 20 is configured to function as an evaporator during heating and as a condenser during cooling. Meanwhile, a fan 25 may be installed on the outdoor unit 20 side to blow air toward the outdoor unit 20 side.
- the compressor 30 is configured to compress the refrigerant delivered from the evaporator. Specifically, the compressor 30 compresses the dry saturated refrigerant delivered from the evaporator and converts it to a superheated steam state.
- the condenser is configured to phase-convert and condense the refrigerant transferred from the compressor 30 into a liquid phase.
- the expansion valve 50 is configured to expand the refrigerant passing through the condenser.
- the refrigerant that has passed through the expansion valve 50 is converted into a wet steam state and then introduced into the evaporator.
- the evaporator is configured to evaporate the refrigerant passing through the expansion valve 50 to convert it into a dry saturated vapor state.
- the four-way valve 40 is configured to switch the refrigerant flow according to heating and cooling. Specifically, the four-way valve 40 is installed in the middle of the refrigerant flow path between the indoor unit 10 and the outdoor unit 20 to change the path through which the refrigerant flows. function to enable
- the heat medium circulates through the indoor unit 10 and the first heat exchanger 100 through the heat medium line 81 to exchange heat.
- the heating medium is made of a liquid fluid, preferably antifreeze, water, or pure water.
- the heating medium line 81 is configured in a closed circuit form that passes through the indoor unit 10 and then passes through the first heat exchanger 100 again, and is filled with a heating medium.
- 'W1' denotes a second fluid that is used for heat exchange in a load (ie, a user device) and then flows back into the second plate heat exchanger 200
- 'W2' denotes the second heat exchange. It means a second fluid that is heat-exchanged with the first fluid in the unit 200 and flows toward the cold/hot water supply header 310 to be described later.
- FIG. 2 is a perspective view of a first heat exchanger according to an embodiment of the present invention
- FIG. 3 is an exploded perspective view of FIG. 2 .
- the first heat exchanger of the present invention will be described as follows.
- the first heat exchanger 100 is a device for exchanging heat or cold energy generated in the indoor unit 10 and the fluid in the heat storage tank 90 .
- the first heat exchanger 100 is connected to the indoor unit 10 through a heating medium line 81 and is connected to the heat storage tank 90 through a fluid line (hereinafter, referred to as a 'first fluid line 91'). .
- a fluid (hereinafter referred to as a 'first fluid') flows out from the heat storage tank 90 and is recovered to the heat storage tank 90 after passing through the first heat exchanger 100 .
- the first fluid may be water supplied from a supervise.
- the heat medium line 81 forms a closed circuit passing through the indoor unit 10 and the first heat exchanger 100 , and the first fluid line 91 passes through the first heat exchanger 100 and the heat storage tank 90 . form a closed circuit.
- the heat medium heat-exchanged while passing through the indoor unit 10 is heat-exchanged with the first fluid while passing through the first heat exchanger 100 .
- the first heat exchanger 100 is configured to exchange heat between the high-temperature fluid and the low-temperature fluid while fluids of different temperatures (ie, the heat medium, the first fluid) flow in opposite directions between the heat transfer plates.
- the first heat exchanger may be configured as a plate heat exchanger.
- the first heat exchanger 100 includes a first channel 140 , a second channel 150 , a plurality of heat transfer plates 110 , a first pipe, and a second pipe.
- the first channel 140 is a passage through which the heating medium passes and is formed between a pair of heat transfer plates
- the second channel 150 is a passage through which the first fluid passes and is formed between another pair of heat transfer plates.
- a plurality of heat transfer plates 110 are arranged at predetermined intervals to form a stacked structure.
- the heat transfer plate 110 may be formed of a stainless material, and a space through which a fluid flows is formed so that heat can be efficiently transferred.
- the flow path (ie, the first channel 140 ) through which the heating medium passes and the flow path (ie, the second channel 150 ) through which the first fluid passes are alternately provided along the stacking direction of the heat transfer plates 110 . .
- the first pipe is connected to the first channel 140 to guide the inflow (D1)/outflow (D2) of the first channel 140 of the heating medium.
- the first pipe includes a pipe 1a connected to an inlet 120 for injecting the heating medium into the first channel 140 , and a first channel 140 through the heating medium passing through the first channel 140 . and a 1b pipe connected to an outlet 121 for recovering from the .
- the second pipe is connected to the second channel 150 to guide the inflow (K1) / outflow (K2) of the second channel 150 of the first fluid.
- the second pipe includes a pipe 2a connected to an inlet 131 for injecting the first fluid into the second channel 150 , and a second pipe that passes the first fluid passing through the second channel 150 to the second pipe. and a 2b pipe connected to an outlet 130 for recovery from the channel 150 .
- the thermal storage tank 90 is a water tank that stores cooling or thermal storage energy generated by the indoor unit 10, and stores a heat source during heating and a cooling source during cooling, so as to selectively provide cooling and cooling according to the season. do.
- a vortex prevention device may be installed in the heat storage tank 90 .
- a first fluid is stored in the heat storage tank 90 , and the first fluid passes through the first heat exchanger 100 through the first fluid line 91 to exchange heat with the heating medium, and the second fluid line 93 .
- the first fluid stored in the heat storage tank 90 may be water supplied from the dormitor.
- FIG. 4 is a perspective view of a second heat exchanger according to an embodiment of the present invention
- FIG. 5 is an exploded perspective view of FIG. 4 .
- the first heat exchanger of the present invention will be described as follows.
- the second heat exchanger 200 is configured to exchange heat between the high-temperature fluid and the low-temperature fluid while fluids of different temperatures flow in opposite directions between the heat transfer plates 110 .
- the second heat exchanger may be configured as a plate heat exchanger.
- the second heat exchanger 200 includes a third channel 240 , a fourth channel 250 , a plurality of heat transfer plates 210 , a third pipe, and a fourth pipe.
- the third channel 240 is formed between the heat transfer plates as a passage through which the first fluid (heat medium in the case of the third and fourth embodiments) passes, and the fourth channel 250 is another heat transfer plate as a passage through which the second fluid passes. formed between
- a plurality of heat transfer plates 210 form a stacked structure arranged at predetermined intervals.
- the heat transfer plate 210 may be formed of a stainless material, and a space through which a fluid flows is formed so that heat can be efficiently transferred.
- the flow path (ie, the third channel 240) through which the first fluid (ie, the heat medium in the third and fourth embodiments) passes and the flow path through which the second fluid (ie, the fourth channel 250) pass are the heat transfer plates 210 . It consists of a structure provided alternately along the stacking direction of
- the third pipe is connected to the third channel 240 to guide the inlet (D1')/outlet (D2') of the third channel 240 of the first fluid (heat medium in the case of the third and fourth embodiments).
- the third pipe includes a pipe 3a connected to an inlet 220 for injecting the first fluid (heat medium in the case of the third and fourth embodiments) into the third channel 240 , and the third channel 240 . ) and a 3b pipe connected to an outlet (Outlet) 221 for recovering the first fluid passing therethrough.
- the fourth pipe is connected to the fourth channel 250 to guide the inflow (K1 ′)/outflow (K2 ′) of the fourth channel 250 of the second fluid.
- the fourth pipe is a pipe 4a connected to an inlet 231 for injecting the second fluid into the fourth channel 250 , and the second fluid passing through the fourth channel 250 is recovered. It includes a 4b pipe connected to the outlet (Outlet) 230 for the.
- the first fluid flows back into the heat storage tank 90 after passing through the first heat exchanger or the second heat exchanger. At this time, a vortex may be generated inside the heat storage tank 90 due to the high flow rate of the first fluid.
- the vortex prevention device of the present invention functions to prevent a vortex that may be generated while the first fluid is introduced into the heat storage tank 90 as described above.
- Figure 6 is a cross-sectional view of the heat storage tank and the vortex prevention device installed therein according to the present invention
- Figure 7 is a cross-sectional view of the first inlet of the first inlet pipe according to the present invention
- Figure 8 is the second inlet pipe according to the present invention A cross-sectional view of the second inlet.
- the vortex prevention device of the present invention includes a first inlet pipe 400 , a first water outlet pipe 420 , a second inlet pipe 430 , a second water outlet pipe 450 , and a vortex. and a prevention plate 460 .
- the first inlet pipe 400 is configured to guide the first fluid returning after passing through the first heat exchanger to be introduced into the heat storage tank 90 .
- the first inlet pipe 400 may be composed of a pipe body connected to the inside of the heat storage tank 90 .
- the first inlet pipe 400 has a first inlet 410 formed in a structure introduced into the heat storage tank 90, and a portion of the first inlet 410 that faces upward of the heat storage tank 90 It includes a plurality of through-holes 411 that are formed through the .
- the "part facing the upper direction of the heat storage tank 90" of the first inlet 410 is an area visible when the first inlet 410 is viewed from the vertical upper portion of the first inlet 410. refers to Accordingly, assuming that the first inlet 410 is a tube having a circular cross section as in the example of FIG. 7 , the 'B1' region faces the first inlet 410 from the vertical upper portion of the first inlet 410 . When viewed (A1), it corresponds to the visible area B1, that is, the "part B1 facing upward of the heat storage tank 90".
- one end of the first inlet 410 may be opened in the form of an opening 413 .
- a portion of the first fluid moving inside the first inlet pipe 400 is discharged in the upper direction of the first inlet 410 through the through hole 411 and flows into the heat storage tank 90, the rest is discharged in the right direction (refer to FIG. 3 ) of the first inlet 410 through the opening 413 and flows into the heat storage tank 90 .
- the first water outlet pipe 420 is configured to guide the first fluid introduced into the heat storage tank 90 through the first inlet pipe 400 to flow out toward the second heat exchanger.
- the first water outlet pipe 420 may be configured as a pipe body connected to the inside of the heat storage tank 90 .
- the first water outlet pipe 420 is a first inlet 423 formed in communication with the inside of the heat storage tank 90 so that the first fluid stored in the heat storage tank 90 can be introduced into the first water outlet pipe 420 .
- first inlet 423 is formed to be located in an area higher than the area in which the first inlet 410 of the first inlet pipe 400 is located in the heat storage tank 90 .
- the second water inlet pipe 430 is configured to guide the first fluid returning after passing through the second heat exchanger to be introduced into the heat storage tank 90 .
- the first inlet pipe 400 may be composed of a pipe body connected to the inside of the heat storage tank 90 .
- the second inlet pipe 430 includes a second inlet 440 formed in a structure introduced into the heat storage tank 90 , and a portion of the second inlet 440 facing the lower side of the heat storage tank 90 . It includes a plurality of through-holes 441 that are formed through the.
- the "portion facing the lower direction of the heat storage tank 90" of the second inlet 440 is an area visible when the second inlet 440 is viewed from the vertical lower portion of the second inlet 440 . refers to Accordingly, assuming that the second inlet 440 is a tube having a circular cross-section as in the example of FIG. 8 , the 'B2' region faces the second inlet 440 from the vertical lower portion of the second inlet 440 . It corresponds to the visible area B2 when viewed (A2), that is, the "part B2 facing downward of the heat storage tank 90".
- one end of the second inlet 440 may be opened in the form of an opening 443 .
- a portion of the first fluid moving inside the second inlet pipe 430 is discharged in the downward direction of the second inlet 440 through the through hole 441 and flows into the heat storage tank 90, and the rest is discharged in the left direction (refer to FIG. 3 ) of the second inlet 440 through the opening 443 and introduced into the heat storage tank 90 .
- the second water outlet pipe 450 is configured to guide the first fluid introduced into the heat storage tank 90 through the second inlet pipe 430 to flow out toward the first heat exchanger.
- the second water outlet pipe 450 may be configured with the inside of the heat storage tank 90 and a tubular body.
- the second water outlet pipe 450 is a second inlet 453 formed in communication with the inside of the heat storage tank 90 so that the first fluid stored in the heat storage tank 90 can be introduced into the second water outlet pipe 450 . ) is included.
- the second inlet 453 is formed to be located in a lower area than the area in which the second inlet 440 of the second inlet pipe 430 is located in the heat storage tank 90 .
- the first inlet 410 of the first inlet pipe 400 is greater than the area in which the second inlet 440 of the second inlet 430 in the heat storage tank 90 is located. It may be formed to be located in a higher area.
- the vortex prevention plate 460 may be formed of a plate body disposed in an area that is lower than the area in which the first lead-in part 410 is positioned and is higher than the area in which the second lead-in part 440 is positioned.
- the vortex prevention plate 460 may be disposed in a structure lying inside the heat storage tank 90 .
- the vortex prevention plate 460 may be disposed so that its long axis is perpendicular to the height direction of the heat storage tank 90 .
- the vortex prevention plate 460 may be composed of a plate body having a diameter of 3 to 5 times the inner diameter of the first inlet pipe 400 or the second inlet pipe 430 .
- the vortex prevention device as described above, it is possible to effectively disperse and diffuse the water pressure of the first fluid flowing into the heat storage tank 90 to prevent the occurrence of a vortex, and to minimize heat loss, thereby improving heat exchange efficiency, It is possible to promote stable operation of the system and supply of heating and cooling at a constant temperature.
- FIG. 9 is a block diagram of a heat pump system according to a second embodiment of the present invention.
- the heat pump system according to the second embodiment has basically the same configuration as the heat pump system of the first embodiment, except that the second heat exchanger of the first embodiment is not included.
- a description will be given mainly of differences due to not including the second heat exchanger.
- the first fluid of cold water or hot water stored in the heat storage tank 90 is heat-exchanged with the second fluid while passing through the second heat exchanger 200 through the second fluid line 93, and then again It returns to the heat storage tank (90).
- the heat pump system according to the second embodiment does not include the second heat exchanger, the first fluid of cold water or hot water stored in the heat storage tank 90 is directly supplied to the load side and used for heat exchange at the load side. After that, it returns to the heat storage tank (90).
- the difference is that the first fluid of the cold/hot water of the first embodiment does not flow directly to the load side, whereas the first fluid of the cold/hot water of the second embodiment flows to the load side and is directly used for heating and cooling of the load side. am.
- the 'load' refers to a user device such as an air conditioner, a heater, a heating distribution, or a hot water heater.
- the same vortex prevention device as described in the first embodiment may be provided.
- the differences will be mainly described.
- the first water outlet pipe 420 of the vortex prevention device is configured such that the first fluid introduced into the thermal storage tank 90 through the first inlet pipe 400 flows out toward the load (ie, the user device).
- the second inlet pipe 430 of the vortex prevention device guides the first fluid returning after being used (heat exchange, etc.) on the load (ie, user device) side to flow into the heat storage tank 90 . do.
- 'W1' means the first fluid that is used for heat exchange on the load (user device) side and then re-introduced into the thermal storage tank 90 , and 'W2' is discharged from the thermal storage tank 90 . It means a first fluid of cold/hot water flowing toward the cold/hot water supply header 310 to be described later.
- FIG. 10 is a block diagram of a heat pump system according to a third embodiment of the present invention.
- the heat pump system according to the third embodiment has basically the same configuration as the heat pump system of the first embodiment, except that it does not include the first heat exchanger of the first embodiment.
- a description will be given mainly of differences due to not including the first heat exchanger.
- the first fluid contained in the thermal storage tank 90 passes through the first heat exchanger 100 through the first fluid line 91 to exchange heat with the heating medium, and then returns to the thermal storage tank 90 again. come.
- the difference is that the heat medium flows into/outs the heat storage tank 90 instead of the first fluid of the first embodiment.
- the thermal medium of the third embodiment flows out from the thermal storage tank 90 toward the indoor unit 10 and then passes through the indoor unit 10 through the thermal medium line 81 . Then, the heating medium becomes cold water or hot water while passing through the indoor unit 10 , and then flows back into the heat storage tank 90 .
- the heat medium of the cold water or hot water introduced into the heat storage tank 90 is discharged toward the second heat exchanger. Then, the heat medium is heat-exchanged with the second fluid while passing through the second heat exchanger 200 through the second fluid line 93 , and then returns to the heat storage tank 90 again.
- the same vortex prevention device as described in the first embodiment may be provided. In this case, there are the following differences from the vortex prevention device described in the first embodiment.
- the difference is that the first intake pipe 400 of the vortex prevention device guides the heating medium returning after passing through the indoor unit 10 to flow into the thermal storage tank 90 .
- 'W1' denotes a second fluid that is used for heat exchange in a load (ie, a user device) and then flows back into the second plate heat exchanger 200
- 'W2' denotes the second heat exchange. It means a second fluid that is heat-exchanged with the heating medium in the unit 200 and flows toward the cold/hot water supply header 310 to be described later.
- FIG. 11 is a block diagram of a heat pump system according to a fourth embodiment of the present invention.
- the heat pump system according to the fourth embodiment has basically the same configuration as the heat pump system of the first embodiment, except that the first heat exchanger and the second heat exchanger of the first embodiment are not included. The difference is.
- the differences according to the absence of the first and second heat exchangers will be mainly described.
- the first fluid contained in the thermal storage tank 90 passes through the first heat exchanger 100 through the first fluid line 91 to exchange heat with the heating medium, and then returns to the thermal storage tank 90 again. come.
- the difference is that the heat medium flows in/out of the heat storage tank 90 instead of the first fluid of the first embodiment.
- the thermal medium of the fourth embodiment flows out from the thermal storage tank 90 toward the indoor unit 10 and then passes through the indoor unit 10 through the thermal medium line 81 . Then, the heating medium becomes cold water or hot water while passing through the indoor unit 10 , and then flows back into the heat storage tank 90 .
- the heat pump system according to the fourth embodiment does not include the second heat exchanger, the heat medium of cold or hot water stored in the heat storage tank 90 is directly supplied to the load side and used for heat exchange at the load side. It returns to the heat storage tank 90 again.
- the difference is that the first fluid of the cold/hot water of the first embodiment does not flow directly to the load side, whereas the heat medium of the cold/hot water of the fourth embodiment flows to the load side and is directly used for heating and cooling of the load side.
- 'W1' means a heat medium that is used for heat exchange on the load (user device) side and then re-introduced into the heat storage tank 90, and 'W2' is discharged from the heat storage tank 90 and will be described later. It means a heating medium of cold and hot water flowing toward the cold and hot water supply header 310 to do.
- FIG. 12 is a block diagram of a heat pump system according to an extended embodiment of the present invention.
- the extended embodiment of the present invention is the same as the heat pump system described in the first embodiment of FIG. 1 except that it further includes a liquid heat generator 60 and a sensor 65 .
- the liquid heater (60) functions to extract a portion of the liquid refrigerant from the outlet side of the condenser and mix it with the dry saturated steam flowing into the compressor (30).
- the liquid heater 60 draws a small amount of refrigerant from the outlet side of the condenser and injects it into the inlet side of the compressor 30 , thereby increasing the temperature of the low-temperature/low-pressure dry saturated steam flowing into the compressor 30 .
- the liquid heat generator 60 may be configured to evaporate the refrigerant transferred from the outlet side of the condenser and mix it with the dry saturated steam flowing into the compressor 30 .
- the liquid heater 60 may be formed in a valve structure capable of adjusting the amount of refrigerant drawn out from the outlet side of the condenser as necessary.
- valve of the liquid heater 60 is opened or closed and the degree of opening and closing (ie, refrigerant withdrawal amount) is adjusted according to the temperature of the refrigerant detected by the sensor 65 mounted on the outlet side of the compressor 30 .
- the temperature of the refrigerant flowing into the compressor 30 can be appropriately adjusted. Accordingly, it is possible to reduce the load on the compressor 30 to improve the stability and efficiency of the heat pump system.
- the heat pump system of the present invention may further include an auxiliary tank (70).
- the auxiliary tank 70 may be connected to the indoor unit 10 to receive heating or cooling heat generated from the indoor unit 10 and store it in the form of hot or cold water.
- FIG. 12 has been described based on the heat pump system according to the first embodiment of FIG. 1 , but the liquid heater 60 and the sensor 65 are the second embodiment, the third embodiment and the It is natural that it can be applied to the heat pump system according to the fourth embodiment.
- FIG. 13 is a view showing the flow of a refrigerant, a heat medium, a first fluid and a second fluid, and a heat exchange operation thereof when the heat pump system according to the present invention operates for heating.
- the indoor unit 10 functions as a condenser and the outdoor unit 20 functions as an evaporator.
- the compressor 30 compresses the dry saturated refrigerant delivered from the evaporator and converts it to a superheated steam state.
- the superheated steam passing through the compressor 30 is converted into a liquid phase in the indoor unit 10 (ie, a condenser), and latent heat is emitted. That is, the refrigerant of the indoor unit 10 dissipates heat during the condensation process, and heat exchange with the heating medium passing through the indoor unit 10 enables heat storage.
- the heat dissipated in the condensation process is transferred to the heating medium passing through the indoor unit 10 , and this heating medium is heat-exchanged with the first fluid while passing through the first heat exchanger 100 , and eventually the high temperature in the heat storage tank 90 . is filled with the first fluid of
- the high-temperature first fluid stored in the heat storage tank 90 passes through the second heat exchanger 200 through the second fluid line 93 to exchange heat with the second fluid, and the second fluid to which heat is transferred is supplied to a user device such as an air conditioner or a heater for a desired use.
- the refrigerant that has passed through the indoor unit 10 (ie, the condenser) flows into the expansion valve 50 and is converted into wet steam.
- the wet steam introduced into the outdoor unit 20 instantly drops in temperature to -20 to -30°C and heats up with the outside, and the temperature rises. If we look only at the external part without considering the instantaneous temperature drop, the low-temperature and low-pressure wet steam of about 15°C flowing into the evaporator by the wind by the fan is converted into dry saturated steam of 0-5°C low-temperature and low pressure while passing through the evaporator. .
- the low-temperature, low-pressure dry saturated steam passing through the outdoor unit 20 ie, the evaporator
- the compressor 30 is introduced into the compressor 30 through the four-way valve 40 and is compressed.
- the refrigerant passing through the compressor 30 is again introduced into the condenser through the four-way valve 40 to form a new heating cycle.
- the liquid heater 60 draws a portion of the liquid refrigerant from the outlet side of the indoor unit 10 (ie, the condenser) and mixes it with the dry saturated steam flowing into the compressor 30 .
- the liquid heater 60 draws a small amount of refrigerant from the outlet side of the indoor unit 10 and injects it into the inlet side of the compressor 30 , thereby increasing the temperature of the low-temperature/low-pressure dry saturated steam flowing into the compressor 30 .
- the inventors of the present invention have developed the following conditions so that heat exchange of 13 to 18° C. can be implemented with optimal efficiency during heating, and heating at a constant temperature can be supplied at all times.
- the 'constant temperature' means a heating temperature of 13 ⁇ 18 °C.
- the refrigerant of the heat pump system of the present invention may be R407C.
- the heat medium of the heat pump system of the present invention may use an antifreeze.
- the antifreeze may be used by diluting it with water.
- the proportion of water diluted in the antifreeze may be 20 to 25% by volume relative to the total solution.
- the heat pump system of the present invention should be designed to satisfy at least the following conditions 1 and 2, preferably designed to further satisfy conditions 3 to 5 .
- the first heat exchanger 100 is configured as a plate heat exchanger.
- the first heat exchanger 100 may be configured as a plate heat exchanger as described and illustrated in FIGS. 2 and 3 .
- the first heat exchanger 100 should be configured to satisfy the following conditions.
- the above-described antifreeze flows in the first channel 140 at an average flow rate of 0.8 to 1.2 m/s, preferably at an average flow rate of 0.9 to 1.1 m/s. is configured to flow in s.
- the first heat exchanger 100 may be configured to further satisfy the following conditions.
- the above-described first fluid flows in the second channel 150 at an average flow rate of 2.8 to 3.2 m/s, preferably an average flow rate of 2.9 to 3.1. It is configured to flow at m/s.
- the second heat exchanger 200 is configured as a plate heat exchanger.
- the second heat exchanger 200 may be configured as a plate heat exchanger as described and illustrated in FIGS. 4 and 5 .
- the second heat exchanger 200 should be configured to satisfy the following conditions.
- the above-described first fluid flows in the third channel 240 at an average flow rate of 2.8 to 3.2 m/s, preferably an average flow rate of 2.9 to 3.1. It is configured to flow at m/s.
- the compressor 30 of the present invention compresses the refrigerant delivered from the evaporator to make superheated steam. At this time, the compressor 30 is configured to compress so that the ratio of the superheated steam to the total refrigerant gas is 68 to 82%.
- Conventional heat pumps have a low pressure of 6-7kgf/cm2 and a high pressure of 15kgf/cm2 during compression, and at this time, the refrigerant compression temperature was designed based on 54.5°C. Accordingly, the conventional heat pump has almost no control function according to the change of the outdoor temperature, so that the flow of the refrigerant cannot be continuously maintained constant.
- the temperature of the refrigerant gas flowing into the compressor 30 can be directly controlled through the liquid heat generator 60, so that the pressure of the compressor 30 is raised above the critical pressure of the existing heat pump system. be able to
- the compressor 30 of the present invention is configured to satisfy the following conditions. That is, the compressor 30 has a high pressure of 26 kgf/cm 2 during compression, and the temperature of the refrigerant discharged from the compressor 30 is configured to satisfy 128 to 132° C. (preferably 129 to 131° C.).
- the temperature is It is configured to drop by 1°C.
- the cooling heat is transferred to the indoor unit 10 (evaporator) ⁇ the first heat exchanger 100 ⁇ the heat storage tank 90 ⁇ the second heat exchanger 200.
- the temperature is configured to rise by 1°C.
- the cooling heat exchanged in (200) is configured to be 5 °C.
- FIG. 14 is a view showing the flow of a refrigerant, a heat medium, a first fluid and a second fluid, and a heat exchange operation thereof when the heat pump system according to the present invention operates for cooling.
- the indoor unit 10 functions as an evaporator and the outdoor unit 20 functions as a condenser.
- the high-pressure refrigerant compressed in the compressor 30 flows into the outdoor unit 20 (ie, the condenser).
- the outdoor unit 20 condenses the refrigerant transferred from the compressor 30 .
- the refrigerant flows into the indoor unit 10 (ie, the evaporator) after passing through the expansion valve 50 to exchange heat with the antifreeze. That is, the refrigerant absorbs the thermal energy of the antifreeze in the indoor unit 10 (ie, the evaporator) and evaporates, and thereby the refrigerant exchanges heat with the antifreeze passing through the outdoor unit 20 (ie, the condenser), so that storage can be performed.
- the low-temperature antifreeze deprived of heat during the condensation process of the refrigerant exchanges heat with the first fluid while passing through the first heat exchanger 100, so that the low-temperature first fluid, that is, cold water, is eventually filled in the heat storage tank 90. do.
- the low-temperature first fluid stored in the heat storage tank 90 is heat-exchanged with the second fluid by passing through the second heat exchanger 200 through the second fluid line 93 , and thereby the second low-temperature fluid
- the fluid is supplied and used for its intended purpose.
- the evaporated refrigerant enters the compressor 30 again to form a cooling cycle.
- the four-way valve 40 changes the path through which the refrigerant flows, so that the indoor unit 10 functions as an evaporator and the outdoor unit 20 functions as a condenser.
- liquid refrigerant Before the low-temperature, low-pressure dry saturated steam passing through the indoor unit 10 (ie, the evaporator) flows into the compressor 30 , a small amount of liquid refrigerant may be mixed by the liquid heater 60 .
- the liquid heater 60 draws a small amount of refrigerant from the outlet side of the indoor unit 10 (that is, the condenser) through the first refrigerant withdrawal line 62 and passes through the first refrigerant injection line 66 . It is configured to inject into the inlet side of the compressor (30).
- the liquid heater 60 draws a small amount of refrigerant from the outlet side of the outdoor unit 20 (that is, the condenser) through the second refrigerant withdrawal line 64 and passes through the second refrigerant injection line 68 . It is configured to inject into the inlet side of the compressor (30).
- first refrigerant withdrawal line 62 and the second refrigerant withdrawal line 64 are selectively used according to the heating/cooling operation, and the first refrigerant injection line 66 and the second refrigerant injection line 68 are also selectively used. is used
- a valve 61 may be installed.
- a valve 63 may be installed.
- the inventors of the present invention have developed the following conditions so that heat exchange of 3 to 7° C. can be implemented with optimum efficiency during cooling, and cooling of a constant temperature can be supplied at all times.
- the 'constant temperature' means a cooling temperature of 3 ⁇ 7 °C.
- the refrigerant of the heat pump system of the present invention may be R407C.
- the heat medium of the heat pump system of the present invention may use an antifreeze.
- the antifreeze may be used by diluting it with water.
- the proportion of water diluted in the antifreeze may be 20 to 25% by volume relative to the total solution.
- the heat pump system of the present invention should be designed to satisfy at least the above-described conditions 1 and 2, preferably designed to further satisfy conditions 3 to 5 .
- the conditions 1 to 5 are the same as the conditions described in the heating operation section of the heat pump system of FIG. 13 , a detailed description thereof will be omitted.
- 15 is a block diagram of a heating and cooling system using the heat pump system of the present invention.
- heating and cooling system of FIG. 15 has been described and illustrated based on the heat pump system according to the first embodiment, this heating and cooling system is also applied to the heat pump system according to the second embodiment, the third embodiment, and the fourth embodiment. Of course, it can be applied.
- the cooling/heating system of the present invention includes a heat pump system, a hot/cold water supply header 310 , a cold/hot water return header 320 , and a differential pressure valve 330 .
- the high-temperature first fluid stored in the heat storage tank 90 passes through the second heat exchanger 200 through the second fluid line 93 to exchange heat with the second fluid, and the second fluid to which the heat is transferred is supplied and used for
- 'W1' refers to the second fluid flowing into the second heat exchanger 200
- 'W2' is heat-exchanged with the first fluid in the second heat exchanger 200 to provide a cold/hot water supply header ( 310) means the second fluid flowing to the side.
- 'W1' denotes a fluid that is used for heat exchange in a load (ie, a user device) and then flows back into the heat pump system
- 'W2' denotes a fluid that has become cold or hot water in the heat pump system. denotes a fluid flowing toward the cold/hot water supply header 310, which will be described later.
- the 'purpose use' may be a user device 340 such as an air conditioner 341 , a heater 342 , a heating distributor 343 , or a hot water heater 344 .
- the cold and hot water supply header 310 transfers the cold and hot second fluid heat-exchanged in the second heat exchanger 200 of the heat pump system to the user device 340 . It is configured to supply to the side.
- the hot and cold water supply header 310 is configured to supply the first fluid of the cold and hot water discharged and supplied from the heat storage tank of the heat pump system to the user device 340 .
- the hot and cold water supply header 310 is configured to supply the hot and cold heat medium discharged and supplied from the heat storage tank of the heat pump system to the user device 340 .
- the cold/hot water exchange header 320 is a device that recovers the second fluid (the first fluid in the second embodiment, the heating medium in the fourth embodiment) used in the user device 340 and returns it to the second heat exchanger 200 side. .
- the second fluid (the first fluid in the case of the second embodiment, the heating medium in the case of the fourth embodiment) returned to the heat pump system by the cold and hot water return header 320 is heat-exchanged with cold water or hot water in the heat pump system, and then back to the user device 340 is supplied with
- the differential pressure valve 330 is installed between the cold and hot water supply header 310 and the return header 320 to adjust the pressure when the pressure of any one of the cold and hot water supply header 310 and the return header 320 rises rapidly.
Abstract
Description
Claims (14)
- 난방시 응축기로 기능하고 냉방시 증발기로 기능하는 실내기; 난방시 증발기로 기능하고 냉방시 응축기로 기능하는 실외기; 상기 실내기를 거치면서 열교환되는 열매체; 및 상기 실내기를 거치면서 냉수 또는 온수가 된 상기 열매체가 유입되는 축열탱크;를 포함하는 히트펌프 시스템에 있어서,상기 실내기를 경유한 후 되돌아오는 상기 열매체가 상기 축열탱크로 유입되도록 안내하는 제1 입수관; 상기 제1 입수관을 통해 상기 축열탱크로 유입된 상기 열매체가 상기 축열탱크 외부로 유출되도록 안내하는 제1 출수관; 상기 제1 출수관을 통해 상기 축열탱크 외부로 유출된 후 되돌아오는 상기 열매체가 상기 축열탱크로 유입되도록 안내하는 제2 입수관; 및 상기 제2 입수관을 통해 상기 축열탱크로 유입된 상기 열매체가 상기 실내기 측으로 유출되도록 안내하는 제2 출수관;을 포함하고,상기 제1 입수관은,상기 축열탱크 내부로 인입된 구조로 형성되는 제1 인입부; 및 상기 제1 인입부 중 상기 축열탱크의 상측 방향을 향하는 부위에 관통 형성되는 다수 개의 통공을 포함하고,상기 제1 출수관은,상기 축열탱크 내의 상기 열매체가 상기 제1 출수관 내부로 유입될 수 있도록, 상기 축열탱크 내부와 연통되게 형성되는 제1 유입구를 포함하고,상기 제1 유입구는,상기 축열탱크에 있어서 상기 제1 인입부가 위치하고 있는 영역보다 더 위쪽 영역에 위치하도록 형성되고,상기 제2 입수관은,상기 축열탱크 내부로 인입된 구조로 형성되는 제2 인입부; 및 상기 제2 인입부 중 상기 축열탱크의 하측 방향을 향하는 부위에 관통 형성되는 다수 개의 통공을 포함하고,상기 제2 출수관은,상기 축열탱크 내의 상기 열매체가 상기 제2 출수관 내부로 유입될 수 있도록, 상기 축열탱크 내부와 연통되게 형성되는 제2 유입구를 포함하고,상기 제2 유입구는,상기 축열탱크에 있어서 상기 제2 인입부가 위치하고 있는 영역보다 더 아래쪽 영역에 위치하도록 형성되는 것을 특징으로 하는 히트펌프 시스템.
- 제1 항에 있어서,상기 제1 출수관을 통해 상기 축열탱크 외부로 유출된 상기 열매체와 제2 유체 간의 열교환이 이루어지는 제2 열교환기;를 더 포함하고,상기 제1 출수관은, 상기 제1 입수관을 통해 상기 축열탱크로 유입된 상기 열매체가 상기 제2 열교환기 측으로 유출되도록 안내하며,상기 제2 입수관은, 상기 제2 열교환기를 경유한 후 되돌아오는 상기 열매체가 상기 축열탱크로 유입되도록 안내하는 것을 특징으로 하는 히트펌프 시스템.
- 난방시 응축기로 기능하고 냉방시 증발기로 기능하는 실내기; 난방시 증발기로 기능하고 냉방시 응축기로 기능하는 실외기; 상기 실내기를 거치면서 열교환되는 열매체; 상기 열매체와 제1 유체 간의 열교환이 이루어지는 제1 열교환기; 및 상기 제1 열교환기를 거치면서 냉수 또는 온수가 된 상기 제1 유체가 유입되는 축열탱크;를 포함하는 히트펌프 시스템에 있어서,상기 제1 열교환기를 경유한 후 되돌아오는 상기 제1 유체가 상기 축열탱크로 유입되도록 안내하는 제1 입수관; 상기 제1 입수관을 통해 상기 축열탱크로 유입된 상기 제1 유체가 상기 축열탱크 외부로 유출되도록 안내하는 제1 출수관; 상기 제1 출수관을 통해 상기 축열탱크 외부로 유출된 후 되돌아오는 상기 제1 유체가 상기 축열탱크로 유입되도록 안내하는 제2 입수관; 및 상기 제2 입수관을 통해 상기 축열탱크로 유입된 상기 제1 유체가 상기 제1 열교환기 측으로 유출되도록 안내하는 제2 출수관;을 포함하고,상기 제1 입수관은,상기 축열탱크 내부로 인입된 구조로 형성되는 제1 인입부; 및 상기 제1 인입부 중 상기 축열탱크의 상측 방향을 향하는 부위에 관통 형성되는 다수 개의 통공을 포함하고,상기 제1 출수관은,상기 축열탱크 내의 상기 제1 유체가 상기 제1 출수관 내부로 유입될 수 있도록, 상기 축열탱크 내부와 연통되게 형성되는 제1 유입구를 포함하고,상기 제1 유입구는,상기 축열탱크에 있어서 상기 제1 인입부가 위치하고 있는 영역보다 더 위쪽 영역에 위치하도록 형성되고,상기 제2 입수관은,상기 축열탱크 내부로 인입된 구조로 형성되는 제2 인입부; 및 상기 제2 인입부 중 상기 축열탱크의 하측 방향을 향하는 부위에 관통 형성되는 다수 개의 통공을 포함하고,상기 제2 출수관은,상기 축열탱크 내의 상기 제1 유체가 상기 제2 출수관 내부로 유입될 수 있도록, 상기 축열탱크 내부와 연통되게 형성되는 제2 유입구를 포함하고,상기 제2 유입구는,상기 축열탱크에 있어서 상기 제2 인입부가 위치하고 있는 영역보다 더 아래쪽 영역에 위치하도록 형성되는 것을 특징으로 하는 히트펌프 시스템.
- 제3 항에 있어서,상기 제1 출수관을 통해 상기 축열탱크 외부로 유출된 상기 제1 유체와 제2 유체 간의 열교환이 이루어지는 제2 열교환기;를 더 포함하고,상기 제1 출수관은, 상기 제1 입수관을 통해 상기 축열탱크로 유입된 상기 제1 유체가 상기 제2 열교환기 측으로 유출되도록 안내하며,상기 제2 입수관은, 상기 제2 열교환기를 경유한 후 되돌아오는 상기 제1 유체가 상기 축열탱크로 유입되도록 안내하는 것을 특징으로 하는 히트펌프 시스템.
- 제1 항 내지 제4 항 중 어느 한 항에 있어서,상기 제1 인입부는,상기 축열탱크에 있어서 상기 제2 인입부가 위치하고 있는 영역보다 더 위쪽 영역에 위치하도록 형성되는 것을 특징으로 하는 히트펌프 시스템.
- 제1 항 내지 제4 항 중 어느 한 항에 있어서,상기 제1 인입부의 일단부에 개방 형성되는 개방구; 및상기 제2 인입부의 일단부에 개방 형성되는 개방구;를 더 포함하는 것을 특징으로 하는 히트펌프 시스템.
- 제5 항에 있어서,상기 축열탱크 내부에 설치되는 와류 방지판을 더 포함하고,상기 와류 방지판은,상기 제1 인입부가 위치하고 있는 영역보다는 더 아래쪽이면서, 상기 제2 인입부가 위치하고 있는 영역보다는 더 위쪽에 해당하는 영역에 배치되는 판체로 이루어진 것을 특징으로 하는 히트펌프 시스템.
- 제2 항에 있어서,상기 제2 열교환기는 판형 열교환기인 것을 특징으로 하는 히트펌프 시스템.
- 제1 항 내지 제4 항 중 어느 한 항에 있어서,상기 증발기로부터 전달된 냉매를 압축하는 압축기; 상기 응축기를 거친 냉매를 팽창시키는 팽창변; 및 난방과 냉방에 따라 냉매흐름을 전환시키기 위한 사방밸브;를 더 포함하는 것을 특징으로 하는 히트펌프 시스템.
- 제9 항에 있어서,상기 응축기의 배출구 측에서 냉매의 일부를 인출하여 상기 압축기로 유입되는 건조포화증기에 혼합시키는 액열기를 더 포함하는 것을 특징으로 하는 히트펌프 시스템.
- 제10 항에 있어서,상기 액열기는,상기 압축기의 배출구 측에 설치된 센서에서 검출되는 냉매의 온도에 따라 상기 냉매의 인출량을 조절하는 것을 특징으로 하는 히트펌프 시스템.
- 제3 항 또는 제4 항에 있어서,상기 열매체는 부동액을 포함하는 것을 특징으로 하는 히트펌프 시스템.
- 냉난방 시스템에 있어서,제1 항 내지 제4 항 중 어느 한 항의 히트펌프 시스템;상기 히트펌프 시스템에서 열교환 완료된 냉수 또는 온수를 사용자 장치 측으로 공급하는 냉온수 공급헤더; 및사용자 장치에서 사용된 상기 냉수 또는 온수를 회수하여 상기 히트펌프 시스템 측으로 돌려보내는 냉온수 환수헤더;를 포함하는 것을 특징으로 하는 히트펌프 시스템을 이용한 냉난방 시스템.
- 제13 항에 있어서,상기 냉온수 공급헤더와 상기 냉온수 환수헤더 사이에 설치되는 차압밸브를 더 포함하는 것을 특징으로 하는 히트펌프 시스템을 이용한 냉난방 시스템.
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Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR20100037445A (ko) * | 2008-10-01 | 2010-04-09 | 엘지전자 주식회사 | 공기 조화 시스템 |
JP2014149147A (ja) * | 2013-01-09 | 2014-08-21 | Osaka Gas Co Ltd | 熱供給システム |
KR101593051B1 (ko) * | 2015-09-21 | 2016-02-11 | 김수섭 | 축냉 효율 증대를 위한 유로를 갖는 빙축열 냉각시스템의 축열조 |
JP2016169931A (ja) * | 2015-03-16 | 2016-09-23 | 東レ株式会社 | 熱交換器およびそれを有するテンター、フィルムの製造装置、フィルムの製造方法 |
KR20190128821A (ko) * | 2018-05-09 | 2019-11-19 | 주식회사 탑솔 | 태양열 히트펌프용 축열조 |
Family Cites Families (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS62206337A (ja) * | 1986-03-05 | 1987-09-10 | Taikisha Ltd | 蓄熱式空調装置 |
US5937663A (en) | 1997-12-23 | 1999-08-17 | Yang Fan Development Co., Ltd. | Multipurpose heat pump system |
KR200281266Y1 (ko) | 2002-02-18 | 2002-07-13 | 류옥란 | 히트 펌프 시스템 |
KR100504882B1 (ko) * | 2003-04-14 | 2005-07-29 | 엘지전자 주식회사 | 보텍스튜브를 구비한 냉난방 겸용 공기조화기 |
JP4239658B2 (ja) * | 2003-04-17 | 2009-03-18 | トヨタ自動車株式会社 | 蓄熱タンク |
KR100551217B1 (ko) * | 2003-09-18 | 2006-02-14 | (주)이노션 | 히트펌프식 온수발생시스템 |
CN201196513Y (zh) * | 2008-01-30 | 2009-02-18 | 刘克里 | 整体冷却和分级冷凝热泵型余热回收淋浴器 |
KR101027134B1 (ko) * | 2010-06-09 | 2011-04-05 | 차상진 | 볼텍스 발열장치를 이용한 고효율 히트펌프 시스템 |
CN103486683B (zh) | 2013-10-15 | 2016-03-23 | 广州市设计院 | 一种蓄冷水池温度自然分层的方法及均匀布、集水装置 |
CN109883232B (zh) * | 2019-04-01 | 2020-10-20 | 中国科学院上海应用物理研究所 | 一种固体蓄热体 |
CN110057001A (zh) * | 2019-05-13 | 2019-07-26 | 燕河能源技术(北京)股份有限公司 | 一种污水源热泵设备 |
CN210740587U (zh) | 2019-07-06 | 2020-06-12 | 广东邦的机电设备有限公司 | 一种基于水蓄冷的新型储水装置 |
CN110469891B (zh) * | 2019-07-26 | 2021-05-18 | 浙江大学 | 一种固体显热蓄热供热系统及方法 |
CN110793369A (zh) * | 2019-12-02 | 2020-02-14 | 思安新能源股份有限公司 | 一种超临界水氧化反应产物余热余压利用系统 |
-
2020
- 2020-03-20 KR KR1020200034611A patent/KR102280276B1/ko active IP Right Grant
-
2021
- 2021-03-19 JP JP2022556673A patent/JP7390761B2/ja active Active
- 2021-03-19 WO PCT/KR2021/003412 patent/WO2021187937A1/ko active Application Filing
- 2021-03-19 US US17/910,126 patent/US20230123982A1/en active Pending
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Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR20100037445A (ko) * | 2008-10-01 | 2010-04-09 | 엘지전자 주식회사 | 공기 조화 시스템 |
JP2014149147A (ja) * | 2013-01-09 | 2014-08-21 | Osaka Gas Co Ltd | 熱供給システム |
JP2016169931A (ja) * | 2015-03-16 | 2016-09-23 | 東レ株式会社 | 熱交換器およびそれを有するテンター、フィルムの製造装置、フィルムの製造方法 |
KR101593051B1 (ko) * | 2015-09-21 | 2016-02-11 | 김수섭 | 축냉 효율 증대를 위한 유로를 갖는 빙축열 냉각시스템의 축열조 |
KR20190128821A (ko) * | 2018-05-09 | 2019-11-19 | 주식회사 탑솔 | 태양열 히트펌프용 축열조 |
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CN115335648A (zh) | 2022-11-11 |
US20230123982A1 (en) | 2023-04-20 |
KR102280276B1 (ko) | 2021-07-22 |
JP7390761B2 (ja) | 2023-12-04 |
JP2023518094A (ja) | 2023-04-27 |
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