CN109028404B - Ice water mixture cold accumulation air conditioning system and control method thereof - Google Patents
Ice water mixture cold accumulation air conditioning system and control method thereof Download PDFInfo
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- CN109028404B CN109028404B CN201810892777.1A CN201810892777A CN109028404B CN 109028404 B CN109028404 B CN 109028404B CN 201810892777 A CN201810892777 A CN 201810892777A CN 109028404 B CN109028404 B CN 109028404B
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- 238000009825 accumulation Methods 0.000 title claims abstract description 29
- 238000004378 air conditioning Methods 0.000 title claims abstract description 29
- 238000000034 method Methods 0.000 title claims abstract description 26
- 239000005457 ice water Substances 0.000 title claims abstract description 22
- 239000000203 mixture Substances 0.000 title claims abstract description 22
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims abstract description 175
- 238000001816 cooling Methods 0.000 claims abstract description 46
- 239000003507 refrigerant Substances 0.000 claims abstract description 44
- 230000007246 mechanism Effects 0.000 claims abstract description 36
- 239000006096 absorbing agent Substances 0.000 claims abstract description 14
- 230000001105 regulatory effect Effects 0.000 claims abstract description 8
- 230000001276 controlling effect Effects 0.000 claims description 4
- 230000008569 process Effects 0.000 abstract description 13
- 238000005265 energy consumption Methods 0.000 abstract description 10
- LYCAIKOWRPUZTN-UHFFFAOYSA-N Ethylene glycol Chemical compound OCCO LYCAIKOWRPUZTN-UHFFFAOYSA-N 0.000 description 14
- 239000000498 cooling water Substances 0.000 description 13
- 239000007788 liquid Substances 0.000 description 12
- 230000005611 electricity Effects 0.000 description 9
- 230000006872 improvement Effects 0.000 description 8
- WGCNASOHLSPBMP-UHFFFAOYSA-N hydroxyacetaldehyde Natural products OCC=O WGCNASOHLSPBMP-UHFFFAOYSA-N 0.000 description 7
- 239000007864 aqueous solution Substances 0.000 description 6
- 238000010586 diagram Methods 0.000 description 4
- 238000002844 melting Methods 0.000 description 4
- 239000012782 phase change material Substances 0.000 description 4
- 238000005057 refrigeration Methods 0.000 description 4
- 230000008018 melting Effects 0.000 description 3
- 239000000243 solution Substances 0.000 description 3
- 230000007547 defect Effects 0.000 description 2
- 230000003068 static effect Effects 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- WYTGDNHDOZPMIW-RCBQFDQVSA-N alstonine Natural products C1=CC2=C3C=CC=CC3=NC2=C2N1C[C@H]1[C@H](C)OC=C(C(=O)OC)[C@H]1C2 WYTGDNHDOZPMIW-RCBQFDQVSA-N 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 239000012267 brine Substances 0.000 description 1
- 238000004140 cleaning Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000004146 energy storage Methods 0.000 description 1
- 230000007613 environmental effect Effects 0.000 description 1
- 230000008014 freezing Effects 0.000 description 1
- 238000007710 freezing Methods 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 238000010309 melting process Methods 0.000 description 1
- 238000002156 mixing Methods 0.000 description 1
- HPALAKNZSZLMCH-UHFFFAOYSA-M sodium;chloride;hydrate Chemical compound O.[Na+].[Cl-] HPALAKNZSZLMCH-UHFFFAOYSA-M 0.000 description 1
- 238000007711 solidification Methods 0.000 description 1
- 230000008023 solidification Effects 0.000 description 1
- 238000010408 sweeping Methods 0.000 description 1
Classifications
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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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/62—Control or safety arrangements characterised by the type of control or by internal processing, e.g. using fuzzy logic, adaptive control or estimation of values
- F24F11/63—Electronic processing
- F24F11/64—Electronic processing using pre-stored data
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/62—Control or safety arrangements characterised by the type of control or by internal processing, e.g. using fuzzy logic, adaptive control or estimation of values
- F24F11/63—Electronic processing
- F24F11/65—Electronic processing for selecting an operating mode
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/70—Control systems characterised by their outputs; Constructional details thereof
- F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
- F24F11/86—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling compressors within refrigeration or heat pump circuits
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
- F24F13/30—Arrangement or mounting of heat-exchangers
-
- 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
Abstract
The invention discloses an ice water mixture cold accumulation air conditioning system which structurally comprises a compressor, a reversing device, a cooling device, an evaporator, a cold accumulator, a first throttling mechanism, a second throttling mechanism, a water absorber, a low-temperature water circulating pump, a first regulating valve, a water distributor and a tail end chilled water circulating system. When the system stores ice, a low-temperature water circulation area is established around the evaporator through the low-temperature water circulation system, so that the refrigerant and water perform convection heat exchange to make ice, and meanwhile, the low-temperature water circulation area can also accelerate the ice making speed of the evaporator. In addition, the invention also provides a control method to separate the ice layer from the evaporator in time in the ice storage process, so that the heat exchange strength of the refrigerant and water of the refrigerating unit is maintained in an optimal state, thereby improving the heat exchange efficiency and reducing the energy consumption. Because the heat exchange link between the intermediate medium and the cold accumulation medium and a plurality of groups of circulating water pumps are omitted, the equipment and investment cost involved in the system can be greatly reduced.
Description
Technical Field
The invention relates to the technical field of cold accumulation air conditioners, in particular to an ice water mixture cold accumulation air conditioning system and a control method thereof.
Background
The ice cold-storage central air-conditioning system is an ideal effective measure for balancing the peak and valley unbalance of the electric energy of the city day and night by 'shifting peak and filling valley'. In the night low electricity price period, the refrigerating system of the ice cold accumulation central air conditioner makes ice for storing cold, and the energy consumption for making ice is higher than that of refrigerating water, but the low electricity price is only one fourth of the daytime peak electricity price, so that the cost of the air conditioner can be saved. In the daytime electricity consumption peak period, the air conditioner cold energy is from ice stored at night to melt and release cold, the air conditioner system only operates the cold energy conveying water pump, the air conditioner system has low electricity consumption, and the urban daytime electricity supply pressure is reduced.
The current ice-making heat exchange process of ice cold accumulation consists of a plurality of working mediums and a plurality of intermediate heat exchange loops. When ice is stored at night, the main cooling process is to pass through two heat exchange loops, namely a refrigerant and intermediate medium heat exchange loop of a refrigerating unit and a low-temperature water heat exchange loop in the intermediate medium and ice storage tank. The method comprises the steps of firstly, exchanging heat between a refrigerant in an evaporator of a low-temperature refrigerating unit and the glycol aqueous solution, reducing the temperature of the glycol aqueous solution to below minus 10 ℃, and then, conveying the low-temperature glycol aqueous solution into a coil pipe in an ice storage tank by a conveying pump to exchange heat with low-temperature water in the ice storage tank, so that the low-temperature water is gradually frozen into ice. In addition, as the outer ice layer of the coil pipe in the ice storage tank is gradually thickened, the heat exchange strength of the glycol aqueous solution in the coil pipe and the ice layer is gradually reduced, and the energy consumption of the refrigerating unit is gradually increased (namely, the energy consumption for obtaining 1 kg of ice is increased along with the increase of the thickness of the ice layer). During daytime ice melting, the main cooling process also passes through two heat exchange loops, namely a loop for heat exchange between glycol aqueous solution and ice in the ice storage tank and a loop for heat exchange between low-temperature glycol aqueous solution and chilled water at the tail end of an air conditioner. For example, chinese patent CN101082434a discloses a self-circulation cold-storage air-conditioning system, which can omit low-temperature secondary refrigerant (such as brine or glycol solution) during cold storage, but the main cold-supply process still needs to pass through the two heat-exchange loops during cold storage, and the ice layer frozen outside the heat-exchange coil is not removed during cold storage, and the cold-storage medium is always in a static state, and the heat exchange form is heat conduction, so that as the thickness of the ice layer increases, the energy consumption of the system increases. For example, chinese patent CN104279667a discloses a phase-change energy-storage air conditioning system, in which the main cooling process during cold storage still needs to pass through the two heat exchange loops, the medium in the system is chilled water, firstly, the refrigerant in the evaporator of the low-temperature refrigerating unit exchanges heat with the chilled water, the chilled water is changed into low-temperature chilled water, then the low-temperature chilled water is conveyed into the ice storage tank by the conveying pump to exchange heat with the solid-liquid phase-change material in the ice storage tank, so that the solid-liquid phase-change material is gradually solidified, but the solidified phase-change material is not separated from the heat exchange surfaces of the two mediums in the cold storage process, and the solid-liquid phase-change material is still in a static state, and the heat exchange form is heat conduction, so that the energy consumption of the system increases with the increase of the thickness of the solidification layer.
In addition, because the heat exchange circuits are more, the circulating water pump sets, the pipelines and the valve components are more, the ice storage central air conditioning system occupies large space, and the initial investment cost is high.
In summary, the existing ice cold storage air conditioning system has the defects of multiple heat exchange links, large comprehensive thermal resistance, higher energy consumption and high initial investment cost in the ice storage and melting processes.
Disclosure of Invention
In order to overcome the defects of the prior art, the invention provides the ice-water mixture cold accumulation air conditioning system and the control method thereof, which omits a heat exchange link between an intermediate medium and a cold accumulation medium and a plurality of groups of circulating water pumps, greatly reduces equipment and investment cost involved in the system, reduces heat exchange resistance through convection heat transfer and timely deicing, improves heat exchange efficiency and reduces energy consumption of the system.
The technical scheme adopted for solving the technical problems is as follows:
an ice water mixture cold accumulation air conditioning system comprises an ice making and cooling system, a low-temperature water circulating system and a tail end chilled water circulating system; the ice making and cooling system comprises a compressor, a reversing device, a cooling device, a cold storage device, an evaporator, a first throttling mechanism and a second throttling mechanism, wherein the reversing device is respectively connected with an exhaust port of the compressor, an air suction port of the compressor, a refrigerant inlet of the cooling device and an outlet of the evaporator, a refrigerant outlet of the cooling device is respectively connected with an inlet of the first throttling mechanism and an outlet of the second throttling mechanism, an inlet of the evaporator is respectively connected with an outlet of the first throttling mechanism and an inlet of the second throttling mechanism, cold storage medium is filled in the cold storage device, and the evaporator is immersed in the cold storage medium; the low-temperature water circulation system comprises a water absorber, a low-temperature water circulation pump, a first regulating valve, a water distributor and a first connecting pipe, wherein the water absorber and the water distributor are arranged in the cold storage device, the water absorber and the water distributor are respectively positioned above and below the evaporator, the first connecting pipe is arranged outside the cold storage device, one end of the first connecting pipe is connected with an outlet of the water absorber, the other end of the first connecting pipe is connected with an inlet of the water distributor, and the low-temperature water circulation pump and the first regulating valve are arranged on the first connecting pipe; the low-temperature water circulation system establishes a low-temperature water circulation area around the evaporator and between heat exchange elements of the evaporator, and the low-temperature water circulation area has the advantages that the water flow direction is consistent, the flow speed is stable, and the water flow state is a laminar flow state or a critical state of laminar flow and turbulent flow; the tail end chilled water circulation system comprises a tail end, a chilled water circulation water pump, a first three-way valve and a converging three-way valve, wherein the chilled water circulation water pump, the first three-way valve and the converging three-way valve are sequentially arranged on a pipeline connected with an inlet of the tail end, an outlet of the chilled water circulation water pump is connected with an inlet of the first three-way valve, a first outlet of the first three-way valve is connected with an inlet of the cold storage device, a second outlet of the first three-way valve is connected with a first inlet of the converging three-way valve, and a second inlet of the converging three-way valve is connected with an outlet of the cold storage device.
As an improvement of the technical scheme, the inlet end of the first throttling mechanism is further provided with a first stop valve, the inlet end of the second throttling mechanism is further provided with a second stop valve, and the first stop valve and the second stop valve are normally closed electromagnetic valves.
As an improvement of the technical scheme, the reversing device is a four-way valve.
As an improvement of the above technical solution, the cooling device is an air-cooled condenser or a water-cooled condenser or an evaporation-cooled condenser.
As an improvement of the technical scheme, the evaporator is a plate heat exchanger.
As an improvement of the technical scheme, the first throttling mechanism and the second throttling mechanism are both electronic expansion valves or thermal expansion valves.
As an improvement of the above technical solution, the cold storage medium is water.
As an improvement of the technical scheme, the first three-way valve is a proportional-integral-split three-way valve.
As an improvement of the technical scheme, the compressor is a centrifugal compressor or a screw compressor or a scroll compressor.
An ice water mixture cold accumulation air conditioning system control method is used for controlling the ice water mixture cold accumulation air conditioning system, and the method comprises the following steps: when the thickness of the ice layer on the heat exchange surface of the evaporator is smaller than 3mm, the system executes an ice making mode, and the reversing device sends high-pressure high-temperature refrigerant gas discharged by the compressor into the cooling device; when the thickness of the ice layer on the heat exchange surface of the evaporator reaches 3-5 mm, the system executes an ice removing mode, the reversing device switches the air suction and exhaust directions of the compressor, and high-pressure high-temperature refrigerant gas discharged by the compressor is sent into the evaporator, so that ice parts attached to the heat exchange surface of the evaporator are melted and fall off.
The invention has the beneficial effects that:
when the system stores ice, a low-temperature water circulation area is established around the evaporator through the low-temperature water circulation system, so that the refrigerant and water perform convection heat exchange to make ice, and meanwhile, the low-temperature water circulation area can also accelerate the ice making speed of the evaporator. In addition, the invention also provides a control method to separate the ice layer from the evaporator in time in the ice storage process, so that the heat exchange strength of the refrigerant and water of the refrigerating unit is maintained in an optimal state, thereby improving the heat exchange efficiency and reducing the energy consumption. Because the heat exchange link between the intermediate medium and the cold accumulation medium and a plurality of groups of circulating water pumps are omitted, the equipment and investment cost involved in the system can be greatly reduced.
Drawings
The invention will be further described with reference to the accompanying drawings and specific examples, in which:
FIG. 1 is a schematic diagram of an embodiment of the present invention;
FIG. 2 is a schematic diagram of an ice making mode structure according to an embodiment of the present invention;
FIG. 3 is a schematic view of the structure of an ice-removing mode according to an embodiment of the present invention;
FIG. 4 is a schematic diagram of a single ice melting and cooling mode structure according to an embodiment of the present invention;
FIG. 5 is a schematic diagram of a non-ice-storage and cooling mode structure according to an embodiment of the present invention.
Detailed Description
Referring to fig. 1, the ice water mixture cold accumulation air conditioning system of the invention comprises an ice making and cooling system 1, a low-temperature water circulation system 2 and a tail end chilled water circulation system 3.
The ice-making cooling system 1 comprises a compressor 11, a reversing device 12, a cooling device 13, a cold storage 14, an evaporator 15, a first throttling mechanism 16 and a second throttling mechanism 17, wherein the reversing device 12 is respectively connected with an exhaust port of the compressor 11, an air suction port of the compressor 11, a refrigerant inlet of the cooling device 13 and an outlet of the evaporator 15, a refrigerant outlet of the cooling device 13 is respectively connected with an inlet of the first throttling mechanism 16 and an outlet of the second throttling mechanism 17, an inlet of the evaporator 15 is respectively connected with an outlet of the first throttling mechanism 16 and an inlet of the second throttling mechanism 17, cold storage medium is filled in the cold storage 14, and the evaporator 15 is immersed in the cold storage medium.
The low-temperature water circulation system 2 comprises a water absorber 21, a low-temperature water circulation pump 22, a first regulating valve 23, a water distributor 24 and a first connecting pipe 25, wherein the water absorber 21 and the water distributor 24 are arranged in the cold storage 14, the water absorber 21 and the water distributor 24 are respectively positioned above and below the evaporator 15, the first connecting pipe 25 is arranged outside the cold storage 14, one end of the first connecting pipe 25 is connected with an outlet of the water absorber 21, the other end of the first connecting pipe is connected with an inlet of the water distributor 24, and the low-temperature water circulation pump 22 and the first regulating valve 23 are arranged on the first connecting pipe 25.
The low-temperature water circulation system 2 establishes a low-temperature water circulation zone 4 around the evaporator 15 and between the heat exchange elements thereof, the water flow direction in the low-temperature water circulation zone 4 is consistent, the flow speed is stable, and the water flow state is a laminar state or a critical state of laminar flow and turbulent flow.
The tail end chilled water circulation system 3 comprises a tail end 31, a chilled water circulation water pump 32, a first three-way valve 33 and a converging three-way valve 34, wherein the chilled water circulation water pump 32, the first three-way valve 33 and the converging three-way valve 34 are sequentially arranged on pipelines connected with the inlet and the outlet of the tail end 31, the outlet of the chilled water circulation water pump 32 is connected with the inlet of the first three-way valve 33, the first outlet of the first three-way valve 33 is connected with the inlet of the cold storage 14, the second outlet of the first three-way valve 33 is connected with the first inlet of the converging three-way valve 34, and the second inlet of the converging three-way valve 34 is connected with the outlet of the cold storage 14.
In order to prevent the refrigerant in the system from migrating when the compressor 11 is stopped, in this embodiment, the inlet end of the first throttle mechanism 16 is further provided with a first stop valve 18, the inlet end of the second throttle mechanism 17 is further provided with a second stop valve 19, the first stop valve 18 and the second stop valve 19 are both normally closed electromagnetic valves, and the first stop valve 18 and the second stop valve 19 are both in a closed state when the compressor 11 is stopped.
As shown in fig. 2, in order to make the reversing structure simple and easy to operate, the reversing device 12 is a four-way valve 120, and the four-way valve 120 includes a first inlet 121, a first outlet 122, a second outlet 123, and a third outlet 124.
To adapt to different climate areas, the cooling device 13 is an air-cooled condenser or a water-cooled condenser or an evaporation-cooled condenser in the present embodiment, so as to meet the local use convenience.
In order to facilitate ice making, ice removing and scale cleaning during routine maintenance, in this embodiment, the evaporator 15 is a plate heat exchanger, and the plate heat exchanger is formed by connecting a plurality of plate heat exchange plates in parallel, wherein an inlet and an outlet are arranged in each plate heat exchange plate, a serpentine refrigerant channel is further arranged between the inlet and the outlet for refrigerant circulation, and the outside is a cold storage medium channel.
In order to accurately control the suction superheat of the compressor and improve the stability of the refrigeration system, in this embodiment, the first throttling mechanism 16 and the second throttling mechanism 17 are both electronic expansion valves or thermal expansion valves.
In order to facilitate the retrieval and timely replenishment of the cold storage medium in the cold reservoir 14, in this embodiment, the cold storage medium is water.
To facilitate adjusting the chilled water temperature entering the tip 31 to be within a set range, in this embodiment, the first three-way valve 33 is a proportional-integral-split three-way valve.
In order to adapt to different applications, different environmental conditions and different cooling requirements, in this embodiment, the compressor 11 is a centrifugal compressor or a screw compressor or a scroll compressor.
The invention also provides a control method of the ice water mixture cold accumulation air conditioning system, which is used for controlling the ice water mixture cold accumulation air conditioning system, and comprises the following steps: when the thickness of the ice layer on the heat exchange surface of the evaporator 15 is less than 3mm, the system executes an ice making mode, and the reversing device 12 sends the high-pressure high-temperature refrigerant gas discharged by the compressor 11 into the cooling device 13; when the thickness of the ice layer on the heat exchange surface of the evaporator 15 reaches 3-5 mm, the system executes an ice removing mode, the reversing device 12 switches the air suction and exhaust directions of the compressor 11, and high-pressure high-temperature refrigerant gas discharged by the compressor 11 is sent into the evaporator 15, so that the ice part closely attached to the heat exchange surface of the evaporator 15 is melted and falls off.
The specific working modes of the invention are as follows: a single ice making cold storage mode, a single ice melting cold releasing mode and a non-ice storing cold supplying mode.
As shown in fig. 2, in the present embodiment, the compressor 11 is a screw compressor, the first throttle mechanism 16 and the second throttle mechanism 17 are both electronic expansion valves, and the cooling device 13 is a water-cooled condenser including a condenser 131 and a water cooling tower 132.
As shown in fig. 2, during the night off-peak electricity rate and the building does not require a cooling period, the air conditioning system operates in a single ice making cold storage mode, which has two sub-modes, one is an ice making mode and the other is an ice removing mode, and it is necessary to turn off the chilled water circulation water pump 32 regardless of which mode is performed, and only the ice making cold supply system 1 and the low temperature water circulation system 2 are operated. When the ice making mode is executed, the low-temperature water circulating water pump 22 of the low-temperature water circulating system 2 drives water between the water absorber 21 and the water distributor 24 in the cold storage device to continuously circulate, and the water flow speed is controlled to be stabilized at 1.1-1.2 m/s through the first regulating valve 23, so that a stable low-temperature water circulating area 4 is established around the evaporator 15 and between heat exchange elements thereof, the water flow direction in the low-temperature water circulating area 4 is consistent, the flow speed is stable, the water flow state is in a laminar state or in a critical state of laminar flow and turbulent flow, and the water in the low-temperature water circulating area 4 continuously circulates outside the heat exchange elements of the evaporator 15. Meanwhile, the first inlet 121 of the four-way valve 120 of the ice making and cooling system 1 is communicated with the first outlet 122, the second outlet 123 of the four-way valve 120 is communicated with the third outlet 124, the high-pressure high-temperature gaseous refrigerant discharged by the compressor 11 enters the condenser 131 through the four-way valve 120 to exchange heat with low-temperature cooling water and then becomes high-pressure low-temperature liquid refrigerant, the high-pressure low-temperature liquid refrigerant exiting the condenser 131 is throttled by the first throttling mechanism 16 to become low-pressure low-temperature gas-liquid two-phase refrigerant, then enters the evaporator 15 to exchange heat with water outside the heat exchange element of the evaporator 15 in a convection way, the gas-liquid two-phase refrigerant absorbs heat of the water to be evaporated into low-pressure low-temperature gas-state refrigerant, and returns to the compressor 11 through the four-way valve 120 to be compressed, so that one refrigeration cycle is completed, meanwhile, the water on the surface of the evaporator 15 is heat-released and frozen into ice to be adhered to the heat exchange surface of the evaporator 15, after a plurality of refrigeration cycles, the thickness of ice layer is gradually increased, and when the thickness of the ice layer is detected to be smaller than 3mm by the ice layer thickness sensor, the ice layer thickness sensor continuously operates to increase the thickness. The ice layer thickness sensor is arranged on the heat exchange surface of the evaporator 15 and is used for detecting the freezing degree frozen on the heat exchange surface of the evaporator 15 and sending out an ice layer thickness signal.
Meanwhile, the low-temperature cooling water in the condenser 131 exchanges heat with the high-pressure high-temperature gaseous refrigerant to become high-temperature cooling water, and then enters the cooling tower 132. In the cooling tower 132, the high-temperature cooling water exchanges heat with the atmospheric environment to become low-temperature cooling water, which re-enters the condenser 131, thereby completing one cooling water cycle.
In the process of ice making, the low-temperature water circulation zone 4 established by the low-temperature water circulation system 2 enables the water temperature around the evaporator 15 and between the heat exchange elements thereof to be lower than the water temperature outside the low-temperature water circulation zone 4, thereby accelerating the ice making speed of the zone and improving the efficiency of the refrigerating unit.
As shown in fig. 3, when the ice layer thickness sensor detects that the thickness of the ice layer on the heat exchange surface of the evaporator 15 reaches 3 to 5mm, the system performs an ice removing mode. When the system is de-iced, the first inlet 121 of the four-way valve 120 of the ice-making cooling system 1 is communicated with the third outlet 124, the second outlet 123 of the four-way valve 120 is communicated with the first outlet 122, and the high-pressure high-temperature gaseous refrigerant discharged by the compressor 11 enters the evaporator 15 through the four-way valve 120 to rapidly heat the heat exchange surface of the evaporator, so that the ice part closely attached to the heat exchange surface of the evaporator 15 is melted and separated from the heat exchange surface of the evaporator under the driving of water flow continuously circulating and sweeping the heat exchange element of the evaporator 15, and the separated ice flakes float to the area above the evaporator 15 under the action of buoyancy. At the same time, the high-pressure high-temperature gaseous refrigerant entering the evaporator 15 is cooled to become a high-pressure low-temperature liquid refrigerant, the high-pressure low-temperature liquid refrigerant exiting the evaporator 15 is throttled by the second throttle mechanism to become a low-pressure low-temperature gas-liquid two-phase refrigerant, and then enters the condenser 131 to exchange heat with high-temperature cooling water, and the gas-liquid two-phase refrigerant absorbs the heat of the cooling water to be evaporated to be a low-pressure low-temperature gas refrigerant, and returns to the compressor 11 again to be compressed by the four-way valve 120, thereby completing one refrigeration cycle.
Meanwhile, the high-temperature cooling water in the condenser 131 exchanges heat with the low-pressure low-temperature gas-liquid two-phase refrigerant to become low-temperature cooling water, and then enters the cooling tower 132. In the cooling tower 132, the low-temperature cooling water exchanges heat with the atmospheric environment to become high-temperature cooling water, which is then re-introduced into the condenser 131, thereby completing one cooling water cycle.
In the process of deicing, the high-pressure high-temperature refrigerant which is discharged into the evaporator through the four-way valve 120 in a reversing way has the characteristic of high flow speed, and the compressor refrigerating oil which is reserved in the evaporator 15 in the process of making ice by the system can be brought back into the compressor 11 while the ice on the heat exchange surface of the evaporator 15 is heated rapidly, so that the compressor 11 can return oil effectively, oil stains on the inner wall of a refrigerant channel in the evaporator 15 can be cleaned, the heat exchange strength of the refrigerant and water of a refrigerating unit is maintained in an optimal state, the heat exchange efficiency is improved, and the energy consumption is reduced.
The ice layer thickness on the heat exchange surface of the evaporator 15 after de-icing is less than 3mm and the system will again re-execute the ice making mode.
The above-mentioned ice making and removing processes are continuously circulated processes, and after several ice making-removing circulation cycles, a large quantity of ice flakes can be stored in the interior of cold storage device.
As shown in fig. 4, during peak daytime electricity prices and when the building requires cooling, the air conditioning system operates in a separate ice-melting and cooling mode that requires the chilled water circulation pump 32 to be turned on, and operates only the end chilled water circulation system 3. The cold storage medium in the cold storage 14 is an ice-water mixture, the temperature of the ice-water mixture is low and stable, the high-temperature frozen water from the tail end 31 enters the first three-way valve 33 through the frozen water circulating water pump 32 and then is divided into two parts, one part of the high-temperature frozen water enters the cold storage 14 from the first outlet of the first three-way valve 33 to exchange heat with the flake ice, the direct heat exchange mode has high heat exchange strength and high heat exchange efficiency due to no heat exchange resistance, the released cold quantity is high in speed, the part of the high-temperature frozen water entering the cold storage 14 is quickly cooled to be low-temperature frozen water, the other part of the high-temperature frozen water is mixed with the low-temperature frozen water from the cold storage 14 through the second outlet of the first three-way valve 33 at the merging valve 34 to be mixed frozen water with the required cold supply temperature of the air conditioning system, then the mixed frozen water enters the tail end 31 to exchange heat with hot air, the mixed frozen water absorbs the hot air heat to be changed into the high-temperature frozen water, and then flows into the cold storage 14 through the first three-way valve 33 to be cooled, so that a frozen water circulation is completed, and the hot air is cooled down to the mixed frozen water is continuously and cooled down to the indoor building after the mixed frozen water is cooled, and the mixed frozen water is cooled to a plurality of indoor buildings, and the temperature is kept constant. In this embodiment, the first three-way valve 33 is a proportional-integral-split three-way valve, which can adjust the flow rate of the high-temperature chilled water flowing into the cold storage 14 according to the temperature of the mixed chilled water obtained by mixing the high-temperature chilled water with the low-temperature chilled water, so as to achieve the purpose of controlling the temperature of the mixed chilled water within a set temperature range.
Referring further to fig. 5, during peak electricity prices during the daytime and the ice storage of the cold storage 14 cannot meet the cooling capacity period required for the air conditioner of the building, at which time the ice storage in the cold storage 14 has been completely melted, the air conditioning system operates in a non-ice storage and cooling mode that requires the simultaneous operation of the ice making and cooling system 1, the low temperature water circulation system 2, and the end chilled water circulation system 3. When the temperature of the mixed chilled water is higher than a set value, starting a non-ice storage cooling mode, and executing an ice making mode by the system because the thickness of an ice layer on the heat exchange surface of the evaporator 15 of the ice making cooling system 1 is smaller than 3 mm; the water temperature of the low-temperature water circulation zone 4 established by the low-temperature water circulation system 2 is lower than the water temperature outside the zone, so that the ice making speed by water is high, and the cooling efficiency of the system is improved; the high-temperature chilled water which is shunted into the cold storage 14 through the first outlet of the first three-way valve 33 flows in a laminar flow state in the cold storage 14, the low-temperature chilled water in the low-temperature water circulation zone is extruded out of the cold storage 14, and the high-temperature chilled water is cooled into low-temperature chilled water by the evaporator 15 in the low-temperature water circulation zone 4; the low temperature chilled water from the cold reservoir 14 is mixed with the high temperature chilled water tapped from the second outlet of the first three-way valve 33 and then fed into the terminal end 31 to cool the building.
The present invention is not limited to the above embodiments, but is intended to be within the scope of the present invention as long as the technical effects of the present invention can be achieved by any same or similar means.
Claims (8)
1. An ice water mixture cold-storage air conditioning system which is characterized in that: comprises an ice making and cooling system (1), a low-temperature water circulating system (2) and a tail end chilled water circulating system (3);
the ice making and cooling system (1) comprises a compressor (11), a reversing device (12), a cooling device (13), a cold accumulator (14), an evaporator (15), a first throttling mechanism (16) and a second throttling mechanism (17), wherein the reversing device (12) is respectively connected with an exhaust port of the compressor (11), an air suction port of the compressor (11), a refrigerant inlet of the cooling device (13) and an outlet of the evaporator (15), a refrigerant outlet of the cooling device (13) is respectively connected with an inlet of the first throttling mechanism (16) and an outlet of the second throttling mechanism (17), an inlet of the evaporator (15) is respectively connected with an outlet of the first throttling mechanism (16) and an inlet of the second throttling mechanism (17), a cold accumulation medium is filled in the cold accumulator (14), and the evaporator (15) is immersed in the cold accumulation medium;
the low-temperature water circulation system (2) comprises a water absorber (21), a low-temperature water circulation pump (22), a first regulating valve (23), a water distributor (24) and a first connecting pipe (25), wherein the water absorber (21) and the water distributor (24) are arranged in the cold storage device (14), the water absorber (21) and the water distributor (24) are respectively positioned above and below the evaporator (15), the first connecting pipe (25) is arranged outside the cold storage device (14), one end of the first connecting pipe (25) is connected with an outlet of the water absorber (21), the other end of the first connecting pipe is connected with an inlet of the water distributor (24), and the low-temperature water circulation pump (22) and the first regulating valve (23) are arranged on the first connecting pipe (25);
the low-temperature water circulation system (2) establishes a low-temperature water circulation zone (4) around the evaporator (15) and between heat exchange elements thereof, and the water flow direction in the low-temperature water circulation zone is consistent, the flow speed is stable, and the water flow state is a laminar flow state or a critical state of laminar flow and turbulent flow;
the tail end chilled water circulation system (3) comprises a tail end (31), a chilled water circulation water pump (32), a first three-way valve (33) and a converging three-way valve (34), wherein the chilled water circulation water pump (32), the first three-way valve (33) and the converging three-way valve (34) are sequentially arranged on a pipeline connected with the inlet and the outlet of the tail end (31), the outlet of the chilled water circulation water pump (32) is connected with the inlet of the first three-way valve (33), the first outlet of the first three-way valve (33) is connected with the inlet of the cold storage device (14), the second outlet of the first three-way valve (33) is connected with the first inlet of the converging three-way valve (34), and the second inlet of the converging three-way valve (34) is connected with the outlet of the cold storage device (14);
the cooling device is a water-cooled condenser, and the water-cooled condenser comprises a condenser and a water cooling tower;
the evaporator is a plate heat exchanger, the plate heat exchanger is formed by connecting a plurality of plate-shaped heat exchange plates in parallel, an inlet and an outlet are arranged in each plate-shaped heat exchange plate, a snake-shaped refrigerant channel is further arranged between the inlet and the outlet for refrigerant circulation, and the outside of the snake-shaped refrigerant channel is a cold accumulation medium channel.
2. The ice water mixture cold accumulation air conditioning system as claimed in claim 1, wherein: the inlet end of the first throttling mechanism (16) is further provided with a first stop valve (18), the inlet end of the second throttling mechanism (17) is further provided with a second stop valve (19), and the first stop valve (18) and the second stop valve (19) are normally closed electromagnetic valves.
3. The ice water mixture cold accumulation air conditioning system as claimed in claim 1, wherein: the reversing device (12) is a four-way valve.
4. The ice water mixture cold accumulation air conditioning system as claimed in claim 1, wherein: the first throttling mechanism (16) and the second throttling mechanism (17) are electronic expansion valves or thermal expansion valves.
5. The ice water mixture cold accumulation air conditioning system as claimed in claim 1, wherein: the cold accumulation medium is water.
6. The ice water mixture cold accumulation air conditioning system as claimed in claim 1, wherein: the first three-way valve (33) is a proportional-integral-split three-way valve.
7. The ice water mixture cold accumulation air conditioning system as claimed in claim 1, wherein: the compressor (11) is a centrifugal compressor or a screw compressor or a scroll compressor.
8. A control method of an ice water mixture cold accumulation air conditioning system is characterized by comprising the following steps of: a method for controlling an ice water mixture cold accumulation air conditioning system as claimed in any one of claims 1 to 7, the method comprising: when the thickness of the ice layer on the heat exchange surface of the evaporator (15) is smaller than 3mm, the system executes an ice making mode, and the reversing device (12) sends high-temperature and high-pressure refrigerant gas discharged by the compressor (11) into the cooling device (13); when the thickness of the ice layer on the heat exchange surface of the evaporator (15) reaches 3-5 mm, the system executes an ice removing mode, the reversing device (12) switches the air suction and exhaust directions of the compressor (11), and high-temperature and high-pressure refrigerant gas discharged by the compressor (11) is sent into the evaporator (15) so that the ice part attached to the heat exchange surface of the evaporator (15) is melted and falls off.
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| CN109945371B (en) * | 2019-04-11 | 2024-04-05 | 中国科学院广州能源研究所 | Cascade supercooling ice storage system |
| CN110388710A (en) * | 2019-08-15 | 2019-10-29 | 上海雪森林制冷设备有限公司 | Immersed plate type ice storage system |
| CN112728669A (en) * | 2020-12-29 | 2021-04-30 | 深圳市前海能源科技发展有限公司 | Cold storage device, method and regional cold supply system |
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