CN113970138A - an air conditioning system - Google Patents
an air conditioning system Download PDFInfo
- Publication number
- CN113970138A CN113970138A CN202111439565.6A CN202111439565A CN113970138A CN 113970138 A CN113970138 A CN 113970138A CN 202111439565 A CN202111439565 A CN 202111439565A CN 113970138 A CN113970138 A CN 113970138A
- Authority
- CN
- China
- Prior art keywords
- liquid
- cooling
- evaporator
- liquid outlet
- heating
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
- 238000004378 air conditioning Methods 0.000 title claims abstract description 32
- 239000007788 liquid Substances 0.000 claims abstract description 233
- 238000001816 cooling Methods 0.000 claims abstract description 128
- 238000011084 recovery Methods 0.000 claims abstract description 11
- 238000006243 chemical reaction Methods 0.000 claims abstract description 8
- 238000010438 heat treatment Methods 0.000 claims description 82
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 25
- 239000000110 cooling liquid Substances 0.000 claims description 24
- 238000007791 dehumidification Methods 0.000 claims description 19
- 238000005057 refrigeration Methods 0.000 claims description 5
- 239000013589 supplement Substances 0.000 claims description 5
- 230000000153 supplemental effect Effects 0.000 claims 3
- 230000005494 condensation Effects 0.000 abstract description 4
- 238000009833 condensation Methods 0.000 abstract description 4
- 239000003507 refrigerant Substances 0.000 description 31
- 238000004891 communication Methods 0.000 description 17
- 239000012530 fluid Substances 0.000 description 7
- 230000001502 supplementing effect Effects 0.000 description 7
- 230000009182 swimming Effects 0.000 description 7
- 238000005265 energy consumption Methods 0.000 description 5
- 238000010586 diagram Methods 0.000 description 2
- 238000006467 substitution reaction Methods 0.000 description 2
- 238000010521 absorption reaction Methods 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000004064 recycling Methods 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
- F24F3/12—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling
- F24F3/14—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification
- F24F3/1405—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification in which the humidity of the air is exclusively affected by contact with the evaporator of a closed-circuit cooling system or heat pump circuit
-
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F12/00—Use of energy recovery systems in air conditioning, ventilation or screening
- F24F12/001—Use of energy recovery systems in air conditioning, ventilation or screening with heat-exchange between supplied and exhausted air
- F24F12/002—Use of energy recovery systems in air conditioning, ventilation or screening with heat-exchange between supplied and exhausted air using an intermediate heat-transfer fluid
- F24F12/003—Use of energy recovery systems in air conditioning, ventilation or screening with heat-exchange between supplied and exhausted air using an intermediate heat-transfer fluid using a heat pump
-
- 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
- F24F5/001—Compression cycle type
-
- 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
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/12—Hot water central heating systems using heat pumps
-
- 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
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/52—Heat recovery pumps, i.e. heat pump based systems or units able to transfer the thermal energy from one area of the premises or part of the facilities to a different one, improving the overall efficiency
-
- 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
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/56—Heat recovery units
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Life Sciences & Earth Sciences (AREA)
- Sustainable Development (AREA)
- Other Air-Conditioning Systems (AREA)
Abstract
The invention discloses an air conditioning system, and relates to the technical field of air conditioners. The heat pump heat recovery unit comprises a first evaporator and a first condenser. One end of the first condenser is communicated with a first liquid outlet of the heat supply system, and the other end of the first condenser is communicated with a first liquid inlet of the heat supply system. One end of the first evaporator is communicated with a second liquid outlet of the cooling system, and the other end of the first evaporator is communicated with a second liquid inlet of the cooling system. The first evaporator is used for cooling the liquid from the second liquid outlet and then outputting the liquid to the second liquid inlet, the first condenser is used for carrying out heat conversion with the first evaporator, and the liquid from the first liquid outlet of the heat supply system is heated and then input to the first liquid inlet. The invention is used for recovering condensation heat of the natatorium.
Description
Technical Field
The invention relates to the technical field of air conditioners, in particular to an air conditioning system.
Background
In some locations, such as indoor spas, swimming pools, indoor water amusement parks, etc., the energy consumption for operation is large. Not only needs to keep a certain temperature in the natatorium, but also needs to remove the indoor air humidity, so that additional dehumidification equipment and cold energy are needed for dehumidification, and the operating cost is increased. If the heat in the natatorium can be recovered and utilized, the operating cost of the natatorium can be reduced.
Disclosure of Invention
The embodiment of the invention provides an air conditioning system, which solves the problems of difficult heat recovery and indoor dehumidification and reduces the operation cost.
In order to achieve the above purpose, the embodiment of the invention adopts the following technical scheme:
the embodiment of the invention provides an air conditioning system which comprises a heating system, a cooling system and at least one heat pump heat recovery unit. Wherein, the heating system has first liquid outlet and first inlet. The cooling system is provided with a second liquid outlet and a second liquid inlet. At least one heat pump heat recovery unit includes first evaporator and first condenser. One end of the first condenser is communicated with a first liquid outlet of the heat supply system, and the other end of the first condenser is communicated with a first liquid inlet of the heat supply system. One end of the first evaporator is communicated with a second liquid outlet of the cooling system, and the other end of the first evaporator is communicated with a second liquid inlet of the cooling system. The first evaporator is used for cooling the liquid from the second liquid outlet of the cooling system and outputting the cooled liquid to the second liquid inlet, and the first condenser is used for carrying out heat conversion with the first evaporator and heating the liquid from the first liquid outlet of the heating system and inputting the heated liquid to the first liquid inlet.
In the air conditioning system provided by the embodiment of the invention, the refrigerant liquid in the first evaporator is gasified to absorb the liquid heat of the second liquid outlet of the cooling system, so that the temperature of the liquid outlet of the first evaporator is reduced and the liquid outlet of the first evaporator can enter the second liquid inlet of the cooling system again for use. The gasified refrigerating fluid is liquefied and released heat in the first condenser, and the heat is absorbed by the liquid flowing into the first condenser from the first liquid outlet of the heat supply system, so that the temperature of the first condenser entering the first liquid inlet of the heat supply system is heated for reuse, the heat of the heat supply system is recovered, and the energy consumption of the whole natatorium is saved.
Further, the air conditioning system also comprises a heat supplementing system and a cold supplementing system. One end of the heat supplementing system is communicated with the first liquid inlet of the heat supply system, the other end of the heat supplementing system is communicated with the first liquid outlet of the heat supply system, and the heat supplementing system is used for providing a heat source for the first liquid inlet of the heat supply system. One end of the cold supplement system is communicated with a second liquid inlet of the cold supply system, the other end of the cold supplement system is communicated with a second liquid outlet of the cold supply system, and the cold supplement system is used for providing a cold source for the cold supply system.
Further, the supplementary cooling system comprises at least one refrigerating unit and a cooling tower. The at least one refrigeration unit includes a second evaporator and a second condenser. One end of the second evaporator is communicated with a second liquid outlet of the cooling system, and the other end of the second evaporator is communicated with a second liquid inlet of the cooling system. The cooling tower is provided with a cooling tower liquid outlet and a cooling tower liquid inlet, and the cooling tower liquid outlet is communicated with the liquid inlet of the second condenser. The liquid inlet of the cooling tower is communicated with the liquid outlet of the second condenser. The cold supplement system also comprises a cooling circulating pump. The cooling circulating pump is positioned between the second condenser and the liquid outlet of the cooling tower.
Further, the air conditioning system also comprises at least one hot water circulating pump and at least one cold liquid circulating pump. The hot water circulating pump is located between a first liquid outlet of the heating system and the first condenser. At least one cold liquid circulating pump is located between the second liquid outlet of the cold supply system and the first evaporator.
Further, the heating system comprises a wind-heat assembly, and the wind-heat assembly is provided with a heating liquid inlet and a heating liquid outlet. The heat supply liquid inlet is communicated with a liquid outlet of the first condenser, the heat supply liquid outlet is communicated with a liquid inlet of the first condenser, and the wind-heat assembly is used for heating the exhaust air entering the room.
Further, the cooling system comprises a dehumidifying assembly, the dehumidifying assembly is provided with a cooling liquid inlet and a cooling liquid outlet, the cooling liquid inlet is communicated with the liquid outlet of the first evaporator, and the cooling liquid outlet is communicated with the liquid inlet of the first evaporator.
Furthermore, the water inlet temperature of the first evaporator and the second evaporator is 10-15 ℃, and the water outlet temperature of the first evaporator and the second evaporator is 5-10 ℃. The water inlet temperature of the first condenser is 37-45 ℃, and the water outlet temperature of the first condenser is 42-50 ℃.
Furthermore, the temperature of the heat supply liquid inlet of the air heating assembly is 42-50 ℃, and the temperature of the heat supply liquid outlet of the air heating assembly is 37-45 ℃.
Furthermore, the temperature of the cooling liquid inlet of the dehumidification component is 5-10 ℃, and the temperature of the cooling liquid outlet of the dehumidification component is 10-15 ℃.
Drawings
FIG. 1 is a schematic diagram of an air conditioning system according to an embodiment of the present invention;
FIG. 2 is a schematic view of another air conditioning system according to an embodiment of the present invention;
FIG. 3 is a schematic view of another air conditioning system according to an embodiment of the present invention;
FIG. 4 is a schematic view of another air conditioning system according to an embodiment of the present invention;
fig. 5 is a schematic diagram of a final air conditioning system according to an embodiment of the present invention.
Detailed Description
Embodiments of the present invention will be described in detail below with reference to the accompanying drawings.
In the description of the present invention, it is to be understood that the terms "center", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", and the like indicate orientations or positional relationships based on those shown in the drawings, and are only for convenience of description and simplicity of description, and do not indicate or imply that the referenced devices or elements must have a particular orientation, be constructed and operated in a particular orientation, and thus, are not to be construed as limiting the present invention.
The terms "first", "second" and "first" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of the present invention, "a plurality" means two or more unless otherwise specified.
In the description of the present invention, it should be noted that, unless otherwise explicitly specified or limited, the terms "mounted," "connected," and "connected" are to be construed broadly, e.g., as meaning either a fixed connection, a removable connection, or an integral connection; may be a mechanical connection; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meanings of the above terms in the present invention can be understood in specific cases to those skilled in the art.
In some places, such as indoor hot springs, swimming pools, indoor water amusement parks and the like, the energy consumption of operation is large, in order to recover heat in indoor air and reduce operation cost. In order to express the technical scheme of the application more clearly, the air conditioning system in the natatorium is taken as an example for illustration. As shown in fig. 1, the air conditioning system includes a heating system 1, a cooling system 2, and at least one heat pump heat recovery unit 3. The heating system 1 may include one or more of a swimming pool water heating device, a heating device, a shower heating device, and the like. The present application does not limit the specific type of equipment in the heating system 1, and the equipment that has a demand for heat may be referred to as the heating system 1. The cooling system 2 may comprise other room air conditioning refrigeration equipment or other cooling systems, etc. The heat pump heat recovery unit 3 is used for recovering the condensation heat generated by the cooling system 2 and transferring the heat to the heating system 1, for example, when the heating system 1 is a swimming pool water heating device, the swimming pool water heating device can convert the heat into the intake water of the swimming pool water. Therefore, the condensation heat of the indoor air is recovered and utilized, the total use energy consumption can be reduced, and the operation cost is saved.
As shown in fig. 1, the heating system 1 has a first liquid outlet a2 and a first liquid inlet a 1. The cooling system 2 has a second liquid outlet port B2 and a second liquid inlet port B1. The at least one heat pump heat recovery unit 3 comprises a first evaporator 31 and a first condenser 32. The first condenser liquid inlet D1 may be connected to the first liquid outlet a2 of the heating system 1 by a pipeline, and the first condenser liquid outlet D2 may be connected to the first liquid inlet a1 of the heating system 1 by a pipeline. The heating system 1 and the first condenser 32, which are communicated in this case, may constitute a first path L1 as shown in fig. 1.
Further, the first evaporator liquid inlet C1 may be communicated with the second liquid outlet B2 of the cooling system 2 by a pipe, and the first evaporator liquid outlet C2 may be communicated with the second liquid inlet B1 of the cooling system 2 by a pipe. In this case, the cooling system 2 and the first evaporator 31 communicated with each other may constitute the second path L2 shown in fig. 1 through a pipe.
Accordingly, the refrigerant having a low temperature in the first evaporator 31 flows into the first evaporator 31 from the second liquid outlet B2 of the cooling system 2 through the second path L2, and then, the liquid and the refrigerant in the first evaporator 31 can be subjected to heat conversion. That is, the low-temperature refrigerant absorbs the heat of the liquid in the second path L2 during the heat conversion process and is vaporized, thereby achieving the effect of cooling the liquid in the second path L2. Therefore, the first evaporator 31 in the second path L2 can cool the liquid from the second liquid outlet B2 of the cooling system 2 and output the cooled liquid to the second liquid inlet B1 of the cooling system 2, so that the temperature of the second liquid inlet B1 of the cooling system 2 is lower than the temperature of the second liquid outlet B2 of the cooling system 2. For example, for convenience of description, the temperature of the liquid in the second liquid inlet B1 of the cooling system 2 can be referred to as the temperature before use, and the temperature before use of the liquid is generally 5 ℃ to 10 ℃. The temperature of the liquid in the second liquid outlet B2 of the cooling system 2 may be referred to as the temperature after use, and may be 10 ℃ to 15 ℃. Wherein the temperature of the liquid after use is higher than the temperature before use.
In addition, the liquid passing through the first condenser 32 is heat-converted from the vaporized refrigerant, and the vaporized refrigerant is liquefied and releases heat by the first condenser 32, thereby heating the first path L1 to the liquid passing through the first condenser 32. The liquid from the first liquid outlet A2 of the heating system 1 is heated and then input into the first liquid inlet A1.
In summary, in the air conditioning system according to the embodiment of the present invention, in the second path L2, the liquid flowing out from the second liquid outlet B2 of the cooling system 2 absorbs heat and cools through the first evaporator 31, and then is transported to the cooling system 2 through the second path L2. The cooling system 2 can be recycled into the cooling system 2 for cooling exchange after receiving the cooled liquid from the first evaporator liquid outlet C2. As can be seen from the above description, the temperature of the liquid output from the first condenser 32 increases after the first condenser 32 and the first evaporator 31 perform heat conversion by the refrigerant. Based on this, the liquid heated by the first condenser 32 can be used for the heating system 1 to perform heat conversion and recycling, so that the liquid in the first path L1 is heated to recover the heat generated by the cooling system 2, and the energy consumption of the whole natatorium is saved.
The above-mentioned structure of the cooling system 2 is exemplified below, for example, in some embodiments of the present application, in order to solve the problem of indoor dehumidification due to high humidity (e.g., in summer in a natatorium). As shown in fig. 2, the cooling system 2 may include a dehumidifying component 21 in the air conditioning unit 100, where the dehumidifying component 21 has a cooling inlet and a cooling outlet, and the cooling inlet is communicated with the first evaporator outlet C2 (it should be noted that the communication here may be direct communication or indirect communication, for example, the indirect communication may be that liquid enters the second inlet B1 of the cooling system 2 from the first evaporator outlet C2 and then enters the cooling inlet, for example, the cooling inlet is equivalent to the second inlet B1, which will not be described in detail later). The cooling liquid outlet is in communication with the first evaporator liquid inlet C1 (it should be noted that the communication here may be direct communication or indirect communication, for example, the indirect communication may be that liquid comes out from the cooling liquid outlet of the dehumidification assembly through the second liquid outlet B2 of the cooling system 2 and then enters the first evaporator liquid inlet C1. of course, the indirect communication may also be direct communication, for example, the cooling liquid outlet is equivalent to the second liquid outlet B2, and will not be described in detail later).
In this case, the dehumidifying unit 21 is used to condense the humid air in the indoor natatorium (the temperature of the humid air in the natatorium is generally maintained in the range of 27 to 29 ℃) to a dew point temperature or lower, to precipitate water, and to reduce water vapor in the air. For example, as shown in fig. 2, since the humid air is condensed to release heat, the liquid for condensation in the dehumidifying module 21 is heated, and the liquid at the cooling liquid outlet of the dehumidifying module 21 is heated and then delivered to the first evaporator 31.
The heated liquid enters the first evaporator 31 through the second path L2, the refrigerant in the first evaporator 31 absorbs heat and cools the liquid in the second path L2, and the cooled liquid returns to the dehumidification module 21 through the second path L2 for use. The vaporized refrigerant is liquefied and released heat in the first condenser 32, so that the liquid in the first path L1 passing through the first condenser 32 is heated and then delivered to the heating system 1 for use, and thus, the dehumidifying component 21 can achieve the purpose of dehumidification to recycle heat.
The temperature parameter of the liquid in the above structure is exemplified below, for example, in some embodiments of the present application, since the temperature of the dehumidifying component 21 for dehumidifying is generally 5 ℃ to 10 ℃, that is, the temperature of the cooling liquid inlet of the dehumidifying component 21. The temperature of the dehumidifying component 21 after dehumidifying the humid air in the natatorium can be raised to 10-15 ℃, namely the temperature of the cooling liquid outlet of the dehumidifying component 21.
For example, in some embodiments of the present application, the dehumidification temperature required by the dehumidification unit 21 is 7 ℃, the temperature of the liquid outlet for cooling by the dehumidification unit 21 can be increased to 12 ℃ after dehumidification by the dehumidification unit 21, the heated liquid enters the first evaporator 31, and after cooling by heat exchange with the refrigerant liquid in the first evaporator 31 to 7 ℃, the heated liquid flows out from the liquid outlet of the first evaporator 31 and flows into the dehumidification unit 21 again through the second path L2, so as to form a cycle operation.
As an example, the cooling supply inlet temperature of the dehumidifying module 21 may be 5 ℃, 7 ℃ and 10 ℃. The temperature of the cooling liquid outlet of the dehumidifying module 21 may be 10 ℃, 12 ℃ and 15 ℃. The temperature of the first evaporator inlet C1 can be 10 ℃, 12 ℃ and 15 ℃, and the temperature of the first evaporator outlet C2 can be 5 ℃, 7 ℃ and 10 ℃.
Since the temperature in the natatorium room needs to be maintained in the range of 27-29 ℃, the heating system 1 of the present application may further include a wind heating module 11 in the air conditioning unit 100 in fig. 2, wherein the wind heating module 11 has a heating liquid inlet and a heating liquid outlet. The heat supply liquid inlet is communicated with the first condenser liquid outlet D2 (the communication mentioned here can be direct communication or indirect communication, which is not described in detail), and the heat supply liquid outlet is communicated with the first condenser liquid inlet D1 (the communication mentioned here can be direct communication or indirect communication, which is not described in detail), and the air heating assembly 11 is used for heating air entering the room so that the room temperature is in the range of 27-29 ℃.
The temperature parameters are partially exemplified below, for example, in some embodiments of the present application, the desired liquid temperature of the air heating assembly 11 may be 42 ℃ to 50 ℃, i.e., the heated liquid inlet of the air heating assembly 11. Because the air heating assembly 11 heats the passing air, a part of liquid heat in the air heating assembly 11 is taken away by the air, and thus, the temperature of a heat supply liquid outlet of the air heating assembly 11 can be 37-45 ℃.
For example, in some embodiments of the present application, when the temperature of the liquid required by the air heating element 11 is 45 ℃, the temperature of the heated liquid outlet after passing through the air heating element 11 may be 40 ℃, and the liquid enters the first condenser inlet port D1 via the first path L1 and then exchanges heat with the refrigerant liquid in the first evaporator 31 to heat the liquid, so that the temperature of the first condenser outlet port D2 may be 45 ℃, and thus the temperature of the liquid entering the air heating element 11 via the first path L1 may be 45 ℃, so as to form a cycle.
For example, the temperature of the first condenser inlet port D1 may be 37 ℃, 40 ℃ and 45 ℃, and the temperature via the first condenser outlet port D2 may be 42 ℃, 45 ℃ and 50 ℃. The temperature of the heat supply liquid inlet of the air heating component 11 can be 42 ℃, 45 ℃ and 50 ℃, and the temperature of the heat supply liquid outlet of the air heating component 11 can be 37 ℃, 40 ℃ and 45 ℃.
From the above, the following conclusions can be drawn:
the temperature difference Δ T1 before and after the liquid in the first path L1 passes through the first condenser 32 is 45 ℃ to 40 ℃ to 5 ℃.
The temperature difference Δ T2 between the liquid in the second path L2 before and after passing through the first evaporator 31 is 7 ℃ to 12 ℃ to-5 ℃.
In this way, the liquid in the first path L1 rises by 5 ℃, and the liquid in the second path L2 falls by 5 ℃, that is, the heat conversion between the first path L1 and the second path L2 is realized by the heat pump heat recovery unit 3.
It should be noted that:
the heat pump heat recovery unit 3 may further include an expansion valve, a compressor, a control system, and the like, wherein the compressor is used for compressing the low-pressure low-temperature refrigerant vapor into the high-pressure high-temperature refrigerant vapor to create a condition for condensing at a higher temperature. The control system is used for controlling the operation of each component.
The liquid refrigerant in the first evaporator 31 absorbs the liquid heat in the first path L1, and the liquid refrigerant absorbs heat to form low-temperature low-pressure refrigerant vapor, and the compressor applies work to the low-temperature low-pressure refrigerant vapor, so that the low-temperature low-pressure refrigerant vapor becomes high-temperature high-pressure refrigerant vapor. When the high-temperature and high-pressure refrigerant vapor passes through the first condenser 32, the refrigerant vapor starts to liquefy and release heat, so that the high-temperature and high-pressure refrigerant vapor forms a low-temperature and high-pressure liquid refrigerant, the refrigerant is throttled by the expansion valve to form a low-temperature and low-pressure liquid refrigerant, and the refrigerant returns to the first evaporator 31 again to absorb the heat of the liquid in the first path L1 to form low-temperature and low-pressure refrigerant vapor, thereby forming a cycle.
In order to ensure that the liquid in the pipe between the heating system 1 and the first condenser 32 has sufficient kinetic energy to circulate, at least one hot water circulation pump 6 may be arranged between the first liquid outlet a2 and the first condenser inlet D1 of the heating system 1, as shown in fig. 2. In order to ensure that the liquid in the conduit between the cooling system 2 and the first evaporator 31 has sufficient kinetic energy to circulate, at least one cooling liquid circulation pump 7 may be provided between the second liquid outlet B2 of the cooling system 2 and the first evaporator liquid inlet C1.
When the heat demand in the natatorium room is large (for example, in winter), not only the hot water of the natatorium shower device and the swimming pool but also the heating device needs heat supply, therefore, in order to ensure normal operation, as shown in fig. 3, the air conditioning system may further include an auxiliary heating system 4, a pipeline between the auxiliary heating system 4 and the heating system 1 forms a third path L3, and the auxiliary heating system 4 has an auxiliary heating system inlet E1 and an auxiliary heating system outlet E2. The fluid inlet E1 of the heat supplementing system is communicated with the first fluid outlet A2 of the heat supply system 1, and the fluid outlet E2 of the heat supplementing system is communicated with the first fluid inlet A1 of the heat supply system. The heat supply system 1 is provided with a first inlet port A1 for supplying heat to the heat supply system 4. When the first condenser 32 provides insufficient heat to the heating system 1, the thermal compensation system 4 may be activated to meet the heat requirement, and the thermal compensation system 4 may be turned on according to the requirement in the natatorium and adjust the liquid flow in the third path L3 accordingly.
For example, in summer, the requirement for cooling capacity in the natatorium is large, and refrigeration equipment in the natatorium needs to be refrigerated, so as shown in fig. 4, the cooling system 2 may further include a supplementary cooling system 5, a pipeline between the supplementary cooling system 5 and the cooling system 2 forms a fourth path L4, and the supplementary cooling system 5 has a supplementary cooling system liquid inlet F1 and a supplementary cooling system liquid outlet F2. The liquid inlet F1 of the cold supply system is communicated with the second liquid outlet B2 of the cold supply system 2, the liquid outlet F2 of the cold supply system is communicated with the second liquid inlet B1 of the cold supply system, and the cold supply system 5 is used for providing a cold source for the cold supply system 2. When the first evaporator 31 provides insufficient cooling capacity, the supplementary cooling system 5 can be activated to meet the cooling capacity demand. The flow rate of the liquid in the fourth path L4 of the cooling system 5 can be switched on and adjusted accordingly according to the requirements in the natatorium.
The above-mentioned structure of the supplementary cooling system 5 is exemplified below, for example, in some embodiments of the present application, as shown in fig. 5, the supplementary cooling system 5 may include at least one refrigerator group 51 and a cooling tower 52. The refrigeration unit 51 may include a second evaporator 511 and a second condenser 512. The piping between the second evaporation 511 and the cooling system 2 constitutes a fourth path L4. The second evaporator 511 has a second evaporator liquid inlet G1 and a second evaporator liquid outlet G2. In this case, the second evaporator liquid inlet G1 is communicated with the second liquid outlet B2 of the cooling system 2, and the second evaporator liquid outlet G2 is communicated with the second liquid inlet B1 of the cooling system 2. In this way, the second evaporator 511 can cool the liquid in the fourth path L4.
Furthermore, the pipeline between the cooling tower 52 and the second condenser 512 forms a fifth path L5, the cooling tower 52 has a cooling tower 52 liquid outlet and a cooling tower 52 liquid inlet, the cooling tower 52 liquid outlet is communicated with the liquid inlet of the second condenser 512, and the cooling tower 52 liquid inlet is communicated with the liquid outlet of the second condenser 512. In this way, the cooling tower 52 can take away the heat of the liquefied refrigerant fluid in the second condenser 512, so that the refrigerant fluid can enter the second evaporator 511 again for use. The supplementary cooling system 5 further includes a cooling circulation pump 53. The cooling circulation pump 12 is located between the second condenser 512 and the liquid outlet of the cooling tower 52 to provide the kinetic energy of the circulation in the pipe of the fifth path L5.
For example, in some embodiments of the present application, in the fourth path L4, the temperature of the cooling liquid required by the cooling system 2 is 5 ℃ to 10 ℃, the temperature of the cooling liquid after the cooling system 2 is 10 ℃ to 15 ℃, and the temperature of the second evaporator liquid inlet G1 communicating with the second liquid outlet B2 of the cooling system is 10 ℃ to 15 ℃. The temperature of the inlet water to the cooling tower 52 is generally 35-42 ℃, and the temperature of the inlet water cooled by the cooling tower 52 and sent to the second condenser 512 in the fifth path may be 30-37 ℃.
To more clearly express the relationship between the temperature parameters mentioned above, the temperature parameters are partially illustrated, for example, in some embodiments of the present application, the liquid temperature before use of the cooling system 2 is 7 ℃, the liquid temperature after use is increased to 12 ℃, the liquid temperature enters the second evaporator liquid inlet port G1 through the second liquid outlet port B2 of the cooling system 2 in the fourth path, the temperature of the second evaporator liquid outlet port G2 may be decreased to 7 ℃ after the heat absorption and the cooling of the second evaporator 511, and then the liquid temperature is transmitted to the second liquid inlet port B1 of the cooling system through the fourth path L4, so as to be recycled.
In this case, the liquid in the fourth path L4 cools and transfers heat to the refrigerant liquid in the second evaporator 511, and the refrigerant liquid heats and vaporizes, thereby liquefying and releasing heat in the second condenser 512 and heating the liquid flowing in the second condenser. The outlet temperature of the cooling tower 52 may be 32 ℃, the temperature of the liquid in the fifth path L5 may be raised to 37 ℃ after the heat is converted by the second condenser 512, and finally the liquid at 37 ℃ is transported to the inlet of the cooling tower 52 by the fifth path L5 to be cooled to 32 ℃, so as to be recycled.
For example, the inlet temperature of the second condenser 512 may be 30 ℃, 32 ℃ and 37 ℃, and the outlet temperature of the second condenser 512 may be 35 ℃, 37 ℃ and 42 ℃. The outlet temperature of the cooling tower 52 can be 30 ℃, 32 ℃ and 37 ℃, and the inlet temperature of the cooling tower 52 can be 35 ℃, 37 ℃ and 42 ℃.
In the description herein, particular features, structures, materials, or characteristics may be combined in any suitable manner in any one or more embodiments or examples.
The above description is only for the specific embodiments of the present invention, but the scope of the present invention is not limited thereto, and any person skilled in the art can easily conceive of the changes or substitutions within the technical scope of the present invention, and all the changes or substitutions should be covered within the scope of the present invention. Therefore, the protection scope of the present invention shall be subject to the protection scope of the appended claims.
Claims (9)
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111439565.6A CN113970138A (en) | 2021-11-30 | 2021-11-30 | an air conditioning system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111439565.6A CN113970138A (en) | 2021-11-30 | 2021-11-30 | an air conditioning system |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN113970138A true CN113970138A (en) | 2022-01-25 |
Family
ID=79590394
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202111439565.6A Pending CN113970138A (en) | 2021-11-30 | 2021-11-30 | an air conditioning system |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN113970138A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN115854671A (en) * | 2022-12-26 | 2023-03-28 | 林涛 | Air drying system with cold and hot recovery function |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH10267577A (en) * | 1997-03-25 | 1998-10-09 | Ebara Corp | Air conditioning system |
| CN206890919U (en) * | 2017-07-13 | 2018-01-16 | 诸暨市沃思环保技术有限公司 | A kind of natatorium source pump |
| WO2018182547A1 (en) * | 2017-03-29 | 2018-10-04 | Eneko Havalandirma Ve Isi Ekonomi̇si̇ Si̇stem Teknoloji̇leri̇ Maki̇ne San. Ve Ti̇c. A.Ş. | Dehumidification devices and method |
| US20190226694A1 (en) * | 2018-01-22 | 2019-07-25 | Desert Aire Corp. | Dehumidifying and energy recapture system |
| CN210892236U (en) * | 2019-11-08 | 2020-06-30 | 杭州卓邦环境设备有限公司 | Novel condensation heat recovery system of swimming pool dehumidification heat pump |
| CN113654123A (en) * | 2020-04-29 | 2021-11-16 | 北京航空航天大学 | Low-temperature regeneration heat and humidity independent treatment air conditioning system driven by two-stage compression heat pump |
| CN216744668U (en) * | 2021-11-30 | 2022-06-14 | 悉地（北京）国际建筑设计顾问有限公司 | Air conditioning system |
-
2021
- 2021-11-30 CN CN202111439565.6A patent/CN113970138A/en active Pending
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH10267577A (en) * | 1997-03-25 | 1998-10-09 | Ebara Corp | Air conditioning system |
| WO2018182547A1 (en) * | 2017-03-29 | 2018-10-04 | Eneko Havalandirma Ve Isi Ekonomi̇si̇ Si̇stem Teknoloji̇leri̇ Maki̇ne San. Ve Ti̇c. A.Ş. | Dehumidification devices and method |
| CN206890919U (en) * | 2017-07-13 | 2018-01-16 | 诸暨市沃思环保技术有限公司 | A kind of natatorium source pump |
| US20190226694A1 (en) * | 2018-01-22 | 2019-07-25 | Desert Aire Corp. | Dehumidifying and energy recapture system |
| CN210892236U (en) * | 2019-11-08 | 2020-06-30 | 杭州卓邦环境设备有限公司 | Novel condensation heat recovery system of swimming pool dehumidification heat pump |
| CN113654123A (en) * | 2020-04-29 | 2021-11-16 | 北京航空航天大学 | Low-temperature regeneration heat and humidity independent treatment air conditioning system driven by two-stage compression heat pump |
| CN216744668U (en) * | 2021-11-30 | 2022-06-14 | 悉地（北京）国际建筑设计顾问有限公司 | Air conditioning system |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN115854671A (en) * | 2022-12-26 | 2023-03-28 | 林涛 | Air drying system with cold and hot recovery function |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN110154683B (en) | Thermal management system and new energy automobile thereof | |
| CN107014015B (en) | Recovery type heat evaporating condensation type handpiece Water Chilling Units | |
| CN210821724U (en) | Thermal management system and new energy automobile thereof | |
| CN100538208C (en) | A kind of double-temperature refrigerator water/cold wind unit | |
| US5761925A (en) | Absorption heat pump and desiccant assisted air conditioner | |
| CN104121720A (en) | Electric automobile air conditioning system adopting air source heat pump | |
| US9920963B1 (en) | System for conditioning air with temperature and humidity control and heat utilization | |
| CN107504600A (en) | Monoblock type radiation air-conditioner unit | |
| CN107677010B (en) | Air conditioning system without dew point control and control method | |
| CN107477740A (en) | A kind of fresh air treatment system using two phase flow separate heat pipe temperature control | |
| CN108195007A (en) | The air-conditioning system of Temperature and Humidity Control and Btu utilization | |
| KR100702907B1 (en) | Energy-saving ball, water-cooled heat pump constant temperature and humidity | |
| US11493227B2 (en) | Switching flow water source heater chiller | |
| CN108759142A (en) | A kind of special overlapping air source high-temperature heat pump cooling/warming system | |
| CN103759468B (en) | A dual temperature heat source heat pump system | |
| KR101383244B1 (en) | Heat pump system with effective defrosting circuit using hot gas bypass method | |
| CN202066139U (en) | Dual temperature heat pipe constant temperature and humidity air conditioning unit | |
| CN109690198B (en) | Central air conditioning heat pump system with energy-saving device | |
| CN216744668U (en) | Air conditioning system | |
| US4732007A (en) | Auxiliary thermal interface to cooling/heating systems | |
| CN208881526U (en) | A kind of indirect type heat pump system, air-conditioning and automobile | |
| CN113970138A (en) | an air conditioning system | |
| JP7241830B2 (en) | Cooling/heating/ventilation multi air conditioner | |
| CN100458292C (en) | Refrigerating unit of air condition by dehumidifying, evaporative cooling solution | |
| CN205641655U (en) | Cascade refrigeration circulation system and have its air conditioner |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination |