Ice slurry storage system and method for regulating an ice slurry storage system

Abstract

This invention discloses an ice slurry cold storage system and its control method, relating to the field of subcooled water ice-making technology. The ice slurry cold storage system includes an evaporator, a circulating refrigeration component, an ice-making component, and a high-temperature heat exchange medium supply component. The evaporator includes a shell with a cavity. The cavity contains a refrigerant spiral channel and two subcooled water spiral channels. The refrigerant spiral channel is located between the two subcooled water spiral channels. A high-temperature channel is formed between the inner spiral of one subcooled water spiral channel and the outer spiral of the other subcooled water spiral channel, and this high-temperature channel is connected to the cavity. The circulating refrigeration component is connected to both ends of the refrigerant spiral channel. The ice-making component is connected to both ends of the two subcooled water spiral channels. The high-temperature heat exchange medium supply component is connected to both ends of the high-temperature channel. The technical solution provided by this invention can reduce system energy consumption and the risk of ice blockage.

Description

Technical Field

[0001] This invention relates to the field of supercooled water ice-making technology, and in particular to an ice slurry cold storage system and a method for controlling the ice slurry cold storage system. Background Technology

[0002] Energy storage technology is one of the key technologies for addressing the volatility and randomness of renewable electricity production, and it is crucial for realizing my country's "dual-carbon" strategy. Compared with various energy storage methods such as electrochemical energy storage and compressed air energy storage, cold storage energy storage has the advantages of low cost, high energy density, and long service life. It has significant application value for smoothing the peak-valley difference in electricity load caused by air conditioning in large buildings and industrial and commercial refrigeration, and for large-scale consumption of electricity generated by renewable energy.

[0003] Traditional ice storage methods commonly use coil-type ice storage air conditioning, which combines ice storage technology with air conditioning systems. Ice is stored at night using off-peak electricity, keeping the cooling capacity in low-temperature ice. During peak daytime electricity consumption, the cooling capacity is released by melting the ice, achieving both peak shaving and valley filling, and increasing the proportion of renewable energy consumption. However, coil-type ice storage systems cannot avoid the density reversal of water at 4.0℃, leading to significant temperature stratification within the ice storage unit. This results in uneven ice thickness on the upper and lower surfaces of the coils, and natural convection also prolongs the ice storage time.

[0004] To address the problems of traditional ice storage methods, a novel ice storage method—ice slurry storage—is adopted. Ice slurry storage utilizes the high latent heat of fusion of ice crystals, resulting in a large storage density. Simultaneously, the large heat transfer area of ​​ice crystals provides a faster cooling rate and better temperature regulation characteristics. Compared to traditional coil-type (internal or external ice melting) and encapsulated (ice ball, ice plate) ice storage systems, ice slurry storage systems do not form ice layers on the heat exchanger walls, thus reducing thermal resistance and improving heat transfer efficiency.

[0005] However, existing ice slurry storage systems often encounter ice blockage problems when producing supercooled water. To eliminate ice blockage, there is a significant imbalance between heat and cold. The energy consumption of the supercooled water release process for crystallization is also high, making it difficult to achieve high ice content (IPF) ice slurry production and reduce agglomeration during long-term storage of ice slurry. Summary of the Invention

[0006] The main objective of this invention is to propose an ice slurry cold storage system and a method for controlling the ice slurry cold storage system, which aims to reduce system energy consumption and the risk of ice blockage.

[0007] To achieve the above objectives, the present invention proposes an ice slurry cold storage system, comprising:

[0008] An evaporator includes a shell with a cavity. The cavity contains a refrigerant spiral channel and two subcooled water spiral channels. The refrigerant spiral channel is located between the two subcooled water spiral channels. A high-temperature channel is formed between the inner spiral of one subcooled water spiral channel and the outer spiral of the other subcooled water spiral channel. The high-temperature channel is connected to the cavity.

[0009] A circulating refrigeration assembly, wherein the circulating refrigeration assembly is connected to both ends of the refrigerant spiral channel;

[0010] An ice-making assembly, wherein the ice-making assembly is connected to both ends of the two subcooled water spiral channels; and

[0011] A high-temperature heat exchange medium supply assembly is connected to both ends of the high-temperature channel.

[0012] In one embodiment, in the cross-section along the length of the housing, both the refrigerant spiral channel and the subcooled water spiral channel are arranged to extend along the length of the housing.

[0013] In one embodiment, the inner spiral of the refrigerant spiral channel coincides with the outer spiral of one of the subcooled water spiral channels, and the outer spiral of the refrigerant spiral channel coincides with the inner spiral of the other subcooled water spiral channel.

[0014] In one embodiment, the circulating refrigeration assembly includes an evaporator, a gas-liquid separator, a compressor, a condenser, and an expansion valve arranged sequentially. The gas-liquid separator is connected to the outlet of the refrigerant spiral channel, and the expansion valve is connected to the inlet of the refrigerant spiral channel.

[0015] In one embodiment, the high-temperature heat exchange medium supply assembly includes a first regulating valve, the inlet of the high-temperature channel is connected to the outlet of the condenser through the first regulating valve, and the outlet of the high-temperature channel is connected to the inlet of the gas-liquid separator.

[0016] In one embodiment, the ice-making assembly includes an ice storage tank, a pretreatment unit, and an ice-making unit. The pretreatment unit includes a primary filter, a secondary filter, a water pump, and a regenerator arranged sequentially. The ice-making unit includes a crystallizer and an ice slurry buffer tank. The regenerator is connected to the inlet of the two subcooled water spiral channels, and the crystallizer is connected to the outlet of the two subcooled water spiral channels. The ice storage tank is connected to the primary filter and the ice slurry buffer tank, respectively.

[0017] In one embodiment, the ice-making assembly further includes a first pressure sensor, a second pressure sensor, a first temperature sensor, and a second temperature sensor. The first pressure sensor and the first temperature sensor are sequentially disposed between the regenerator and the inlet of the two subcooled water spiral channels, and the second temperature sensor and the second pressure sensor are sequentially disposed between the outlet of the two subcooled water spiral channels and the crystallizer; and / or

[0018] The ice-making component also includes a flow meter, which is located between the outlet of the two subcooled water spiral channels and the crystal promoter.

[0019] In one embodiment, the high-temperature heat exchange medium supply assembly includes a cooling tower, a medium-low temperature chiller, a second regulating valve, a third regulating valve, a fourth regulating valve, and a fifth regulating valve. The chilled water return port of the medium-low temperature chiller is connected to the inlet of the high-temperature channel through the second regulating valve, and the chilled water supply port of the medium-low temperature chiller is connected to the outlet of the high-temperature channel through the third regulating valve. The outlet of the cooling tower is connected to the inlet of the high-temperature channel through the fourth regulating valve, and the inlet of the cooling tower is connected to the outlet of the high-temperature channel through the fifth regulating valve.

[0020] In one embodiment, the high-temperature heat exchange medium supply assembly includes a first cooling pump connected to the outlet of the cooling tower and the fourth regulating valve, and located between the outlet of the cooling tower and the fourth regulating valve; and / or

[0021] In one embodiment, the high-temperature heat exchange medium supply assembly further includes a second cooling pump, which is connected to the outlet of the cooling tower and the inlet of the circulating refrigeration assembly, and the inlet of the cooling tower is connected to the outlet of the circulating refrigeration assembly.

[0022] The present invention also proposes a method for regulating an ice slurry cold storage system. This method is applied to the ice slurry cold storage system described in any of the above embodiments. The method includes the following steps:

[0023] The temperature values ​​at the inlet and outlet of the subcooled water spiral channel are T1 and T2 respectively, the pressure difference between the inlet and outlet of the subcooled water spiral channel is ΔP, and the critical value for the proposed system ice blockage frequency is set to τ, while the actual system ice blockage frequency value is τ1.

[0024] Determine whether T1 is greater than the first preset value. If it is greater than the first preset value, the subcooled water spiral channel and system fault need to be detected. If T1 is less than or equal to the first preset value, and T2 and ΔP are respectively within the range of the second preset value, and ΔP is less than or equal to and within the range of the third preset value, then there is no ice blockage in the system.

[0025] If T2 is greater than the maximum value of the second preset value range, the cooling frequency of the circulating cooling component is increased until T2 is within the second preset value range; if T2 is less than the minimum value of the second preset value range, the cooling frequency of the circulating cooling component is decreased until T2 is within the second preset value range.

[0026] If ΔP is less than or equal to the third preset value, the system operates normally; if ΔP is greater than the third preset value and τ1 is less than or equal to τ, the high-temperature heat exchange medium supply component supplies a high-temperature heat exchange medium with a lower temperature or lower flow rate until the system operates normally; if ΔP is greater than the third preset value and τ1 is greater than τ, the high-temperature heat exchange medium supply component supplies a high-temperature heat exchange medium with a higher temperature or higher flow rate until the system operates normally.

[0027] In this invention, the circulating refrigeration component is connected to both ends of the refrigerant spiral channel for compressing and circulating the refrigerant, ensuring continuous refrigerant flow in the system and providing cooling capacity. The ice-making component is connected to both ends of the two subcooled water spiral channels for cooling the subcooled water and generating ice slurry, which is then stored. The high-temperature heat exchange medium supply component is connected to both ends of the high-temperature channel for providing cooling water, chilled water return water, or hot refrigerant. Heat exchange occurs between the high-temperature channel and the subcooled water, eliminating ice blockage. The high-temperature channel is used to exchange heat with the subcooled water through a high-temperature heat exchange medium to eliminate ice blockage. The high-temperature heat exchange medium can be chilled water return water, cooling water, or hot refrigerant, which can be selected according to the system status. The refrigerant spiral channel is used to allow the refrigerant to absorb heat from the subcooled water, increasing its own temperature and engaging in counter-current heat exchange with the subcooled water to improve heat exchange efficiency. The subcooled water spiral channel is used to allow the subcooled water to flow through, where it engages in counter-current heat exchange with the refrigerant, lowering the temperature to approximately -3°C. Low-temperature subcooled water is produced within the subcooled water spiral channel, and the ice-making component generates ice slurry. The circulating refrigeration component is connected to both ends of the refrigerant spiral channel to ensure continuous refrigerant circulation in the system. The circulating refrigeration component typically includes an evaporator, compressor, condenser, and expansion valve, forming a complete refrigeration cycle. The ice-making component is connected to both ends of the two subcooled water spiral channels to cool the subcooled water and generate ice slurry. The ice-making component typically includes a crystallizer and an ice storage tank. The subcooled water generates ice slurry in the crystallizer and then stores it in the ice storage tank. The high-temperature heat exchange medium supply component is connected to both ends of the high-temperature channel to provide cooling water or chilled water return water or hot refrigerant. The high-temperature heat exchange medium supply component can typically be a cooling tower, a medium-low temperature chiller, or a compressor. The cooling water or chilled water return water or hot refrigerant exchanges heat with the subcooled water through the high-temperature channel. The subcooled water absorbs heat from the high-temperature heat exchange medium, eliminating ice blockage. The ice slurry cold storage system proposed in this solution separates the refrigerant spiral channel from the high-temperature channel using a subcooled water spiral channel, optimizing the system's heat exchange process, reducing heat loss and cooling, and lowering system energy consumption. It uses a high-temperature heat exchange medium to exchange heat with the subcooled water, eliminating ice crystals generated in the water and reducing the risk of ice blockage. Furthermore, it uses a high-temperature heat exchange medium (cooling water, chilled water return water, or hot refrigerant) supplied by the components, eliminating the need for an external heat source and further reducing operating costs. Attached Figure Description

[0028] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on the structures shown in these drawings without creative effort.

[0029] Figure 1 A schematic diagram of an embodiment of the evaporator is provided for this invention;

[0030] Figure 2 A first-view sectional view of the evaporator is provided for the present invention;

[0031] Figure 3 A second-view sectional view of the evaporator is provided for the present invention;

[0032] Figure 4 A third-view sectional view of the evaporator is provided for this invention;

[0033] Figure 5 A schematic diagram of an embodiment of the ice slurry cold storage system provided by the present invention;

[0034] Figure 6 A control logic flowchart of an embodiment of the ice slurry cold storage system is provided for this invention;

[0035] Figure 7 A schematic diagram of another embodiment of the ice slurry cold storage system provided by the present invention;

[0036] Figure 8 A control logic flowchart of another embodiment of the ice slurry cold storage system is provided for this invention;

[0037] Figure 9 This is a schematic flowchart of an embodiment of the control method for an ice slurry cold storage system provided by the present invention.

[0038] Explanation of icon numbers:

[0039] 100. Ice Slurry Cold Storage System; 1. Evaporator; 11. Shell; 12. Chamber; 13. Refrigerant Spiral Channel; 131. Inlet of Refrigerant Spiral Channel; 132. Outlet of Refrigerant Spiral Channel; 14. Subcooled Water Spiral Channel; 141. Inlet of Subcooled Water Spiral Channel; 142. Outlet of Subcooled Water Spiral Channel; 15. High-Temperature Channel; 151. Inlet of High-Temperature Channel; 152. Outlet of High-Temperature Channel; 2. Circulating Refrigeration Components; 21. Gas-Liquid Separator; 22. Compressor; 23. Condenser; 24. Expansion Valve; 3. Ice Making Components; 31. Ice Storage Tank; 32. Pretreatment Components; 321. Primary Filter; 322. Secondary filter; 323, water pump; 324, regenerator; 33, ice maker; 331, crystallizer; 332, ice slurry buffer tank; 333, flow meter; 34, first pressure sensor; 35, second pressure sensor; 36, first temperature sensor; 37, second temperature sensor; 4, high-temperature heat exchange medium supply assembly; 41, first regulating valve; 42, cooling tower; 43, chilled water return port of medium-low temperature chiller; 44, chilled water supply port of medium-low temperature chiller; 45, second regulating valve; 46, third regulating valve; 47, fourth regulating valve; 48, fifth regulating valve; 49, first cooling pump; 5, second cooling pump.

[0040] The realization of the objective, functional features and advantages of the present invention will be further explained in conjunction with the embodiments and with reference to the accompanying drawings. Detailed Implementation

[0041] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the scope of protection of the present invention.

[0042] It should be noted that if the embodiments of the present invention involve directional indicators (such as up, down, left, right, front, back, etc.), the directional indicators are only used to explain the relative positional relationship and movement of the components in a specific posture. If the specific posture changes, the directional indicators will also change accordingly.

[0043] Furthermore, if the embodiments of this invention involve descriptions such as "first" or "second," these descriptions are for descriptive purposes only and should not be construed as indicating or implying their relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined with "first" or "second" may explicitly or implicitly include at least one of those features. Additionally, the use of "and / or" or "and / or" throughout the text includes three parallel solutions. For example, "A and / or B" includes solution A, solution B, or a solution where both A and B are satisfied simultaneously. Furthermore, the technical solutions of the various embodiments can be combined with each other, but this must be based on the ability of those skilled in the art to implement them. When the combination of technical solutions is contradictory or impossible to implement, it should be considered that such a combination of technical solutions does not exist and is not within the scope of protection claimed by this invention.

[0044] This invention proposes an ice slurry cold storage system 100.

[0045] Please see Figures 1 to 9In one embodiment of the present invention, the ice slurry cold storage system 100 includes an evaporator 1, a circulating refrigeration component 2, an ice-making component 3, and a high-temperature heat exchange medium supply component 4. The evaporator 1 includes a shell 11, and the shell 11 has a cavity 12. The cavity 12 has a refrigerant spiral channel 13 and two subcooled water spiral channels 14. The refrigerant spiral channel 13 is located between the two subcooled water spiral channels 14. A high-temperature channel 15 is formed between the inner spiral of one subcooled water spiral channel 14 and the outer spiral of the other subcooled water spiral channel 14. The high-temperature channel 15 is connected to the cavity 12. The circulating refrigeration component 2 is connected to both ends of the refrigerant spiral channel 13. The ice-making component 3 is connected to both ends of the two subcooled water spiral channels 14. The high-temperature heat exchange medium supply component 4 is connected to both ends of the high-temperature channel 15.

[0046] In the technical solution of this invention, the circulating refrigeration component 2 is connected to both ends of the refrigerant spiral channel 13 for compressing and circulating the refrigerant, ensuring continuous flow of the refrigerant in the system and providing cooling capacity; the ice-making component 3 is connected to both ends of the two subcooled water spiral channels 14 for cooling the subcooled water and generating ice slurry, and storing the ice slurry; the high-temperature heat exchange medium supply component 4 is connected to both ends of the high-temperature channel 15 for providing a high-temperature heat exchange medium, which exchanges heat with the subcooled water to eliminate ice blockage. The high-temperature heat exchange medium can be chilled water return water, cooling water, or hot refrigerant, which can be selected according to the system status; the refrigerant spiral channel 13 is used to pass refrigerant, absorb heat from the subcooled water, increase its own temperature, and exchange heat with the subcooled water in a countercurrent manner to improve heat exchange efficiency; the subcooled water spiral channel 14 is used to pass subcooled water, which exchanges heat with the refrigerant in a countercurrent manner, reducing the temperature to about -3°C, producing low-temperature subcooled water in the subcooled water spiral channel, and generating ice slurry by the ice-making component. The circulating refrigeration component 2 is connected to both ends of the refrigerant spiral channel 13 to ensure continuous circulation of refrigerant in the system. The circulating refrigeration component 2 typically includes a compressor 22, a condenser 23, and an expansion valve 24, forming a complete refrigeration cycle. The ice-making component 3 is connected to both ends of the two subcooled water spiral channels 14 to cool the subcooled water and generate ice slurry. The ice-making component 3 typically includes a crystallizer 331 and an ice storage tank 31. The subcooled water generates ice slurry in the crystallizer 331 and then stores it in the ice storage tank 31. The high-temperature heat exchange medium supply component 4 is connected to both ends of the high-temperature channel 15 to provide cooling water or chilled water return water or hot refrigerant. The high-temperature heat exchange medium supply component 4 can typically be a cooling tower 42, a medium-low temperature chiller 44, or a compressor 22. The high-temperature heat exchange medium exchanges heat with the subcooled water through the high-temperature channel 15, absorbing heat from the subcooled water and eliminating ice blockage. The ice slurry cold storage system 100 proposed in this solution separates the refrigerant spiral channel 13 from the high-temperature channel 15 by using a subcooled water spiral channel 14, thereby optimizing the heat exchange process of the system, reducing heat loss and cooling, and reducing system energy consumption. It uses a high-temperature heat exchange medium to exchange heat with subcooled water, eliminating ice crystals generated in the water and reducing the risk of ice blockage. Furthermore, it uses a high-temperature heat exchange medium (cooling water or chilled water return water or hot fluorine) supplied by the high-temperature heat exchange medium supply component 4, eliminating the need for an external heat source and further reducing operating costs.

[0047] Specifically, please refer to Figure 3In one embodiment of the present invention, the outer peripheral walls of the refrigerant spiral channel 13 and the subcooled water spiral channel 14 are both extended along the length of the housing 11 in the cross-section along the length of the housing 11. This design significantly increases the outer peripheral wall area of ​​the refrigerant spiral channel 13 and the subcooled water spiral channel 14. A larger contact area means more thorough heat exchange, thereby improving heat exchange efficiency. Compared with the traditional straight-channel design, the spiral channel can make fuller use of the space within the housing 11, ensuring that the refrigerant and subcooled water maintain a large temperature difference during heat exchange, further improving the heat exchange effect. The refrigerant spiral channel 13 and the subcooled water spiral channel 14 extend along the length of the housing 11, forming a counter-current heat exchange structure. This design ensures that the refrigerant and subcooled water maintain a large temperature difference during heat exchange, thereby improving heat exchange efficiency.

[0048] Please see Figure 2 In one embodiment of the present invention, the inner spiral of the refrigerant spiral channel 13 coincides with the outer spiral of one of the subcooled water spiral channels 14, and the outer spiral of the refrigerant spiral channel 13 coincides with the inner spiral of the other subcooled water spiral channel 14. This coincidence design means that the inner side of the refrigerant spiral channel 13 is in close contact with the outer side of one subcooled water spiral channel 14, and the outer side of the refrigerant spiral channel 13 is in close contact with the inner side of another subcooled water spiral channel 14. That is, the distance between the refrigerant spiral channel 13 and each subcooled water spiral channel 14 is very small, almost zero. Due to the very short heat transfer distance, the heat exchange between the refrigerant and the subcooled water is more efficient, and the heat exchange between the refrigerant and the subcooled water is also more uniform.

[0049] For more details, please refer to Figure 5In one embodiment of the present invention, the circulating refrigeration assembly 2 includes a gas-liquid separator 21, a compressor 22, a condenser 23, and an expansion valve 24 arranged sequentially. The gas-liquid separator 21 is connected to the outlet 132 of the refrigerant spiral channel, and the expansion valve 24 is connected to the inlet 131 of the refrigerant spiral channel. The gas-liquid separator 21, connected to the outlet 132 of the refrigerant spiral channel, primarily functions to separate the gas and liquid in the refrigerant, ensuring that the refrigerant entering the compressor 22 is a pure gas, preventing liquid slugging, and protecting the compressor 22. The compressor 22 is located between the gas-liquid separator 21 and the condenser 23. Its main function is to compress low-temperature, low-pressure refrigerant gas into high-temperature, high-pressure refrigerant gas to provide the cooling capacity required by the system. The condenser 23 is located between the compressor 22 and the expansion valve 24. Its main function is to cool the high-temperature, high-pressure refrigerant gas into a liquid state and release heat into the environment. The condenser 23 achieves refrigerant condensation by exchanging heat with cooling water or air. The expansion valve 24 is connected to the inlet 131 of the refrigerant spiral channel. Its main function is to control the flow rate of the refrigerant, throttle and reduce the pressure of the high-temperature, high-pressure liquid refrigerant, and turn it into a low-temperature, low-pressure liquid refrigerant, which then enters the evaporator 1 for heat exchange.

[0050] Please see Figure 7In one embodiment of the present invention, the high-temperature heat exchange medium supply assembly 4 includes a first regulating valve 41. The inlet 151 of the high-temperature channel is connected to the outlet of the condenser 23 through the first regulating valve 41, and the outlet 152 of the high-temperature channel is connected to the inlet of the gas-liquid separator 21. When the system detects ice blockage, the first regulating valve 41 is opened by the control system to allow high-temperature hot fluorine to enter the high-temperature channel 15. The high-temperature and high-pressure hot fluorine generated by the compressor 22 is led out from the inlet of the condenser 23 through a hot fluorine channel, so that the high-temperature and high-pressure hot fluorine does not dissipate heat through the condenser 23 and directly enters the high-temperature channel 15 through the first regulating valve 41 to exchange heat with the subcooled water. The high-temperature hot fluorine exchanges heat with the subcooled water in the high-temperature channel 15, and the subcooled water absorbs the heat from the high-temperature hot fluorine, causing the subcooled water temperature to rise and the ice crystals to melt, thereby eliminating the ice blockage. The hot fluorine after heat exchange enters the gas-liquid separator 21 through the outlet 152 of the high-temperature channel. The separated gas returns to the compressor 22, and the liquid enters the condenser 23, completing one cycle. After heat exchange with subcooled water in the high-temperature channel 15, the refrigerant enters the gas-liquid separator 21. The gas-liquid separator 21 separates the gas and liquid in the high-temperature hot refrigerant, ensuring that the refrigerant entering the compressor 22 is a pure gas, preventing liquid slugging and protecting the compressor 22. The gas-liquid separator 21 allows the separated gas to enter the compressor 22, where it is compressed into a high-temperature, high-pressure refrigerant gas, which then re-enters the condenser 23, completing one cycle. The first regulating valve 41 is used to control the flow rate of the high-temperature hot refrigerant, ensuring that the flow rate and pressure of the high-temperature hot refrigerant in the high-temperature channel 15 meet the system requirements. By adjusting the opening of the first regulating valve 41, the flow rate of the high-temperature hot refrigerant can be precisely controlled, thereby achieving precise control of the heat exchange effect of the subcooled water and improving the stability and reliability of the system.

[0051] Please see Figure 5In one embodiment of the present invention, the ice-making assembly 3 includes an ice storage tank 31, a pretreatment component 32, and an ice-making component 33. The pretreatment component 32 includes a primary filter 321, a secondary filter 322, a water pump 323, and a regenerator 324 arranged sequentially. The ice-making component 33 includes a crystallizer 331 and an ice slurry buffer tank 332. The regenerator 324 is connected to the inlet 141 of the two subcooled water spiral channels, and the crystallizer 331 is connected to the outlet 142 of the two subcooled water spiral channels. The ice storage tank 31 is connected to the primary filter 321 and the ice slurry buffer tank 332 respectively. Ice storage tank 31 is used to store the generated ice slurry, ensuring that the system can provide sufficient cooling capacity when needed. Primary filter 321 is used to initially filter the water entering the system, removing larger impurities and particles to ensure initial water cleanliness. Secondary filter 322 is used to further filter the water after primary filter 321, removing finer impurities and particles to improve water purity. Water pump 323 provides power to transport the filtered water to the regenerator 324 and the subcooled water spiral channel 14 of evaporator 1. Regenerator 324 preheats the water entering evaporator 1, increasing the water temperature, reducing the load on evaporator 1, and improving system energy efficiency. Crystallizer 331 is used to promote the generation of ice slurry from subcooled water, ensuring that the subcooled water freezes rapidly at low temperatures to generate uniform ice slurry. Ice slurry buffer tank 332 is used to temporarily store the generated ice slurry, ensuring the stability and uniformity of the ice slurry before entering ice storage tank 31.

[0052] Please see Figure 5 In one embodiment, the ice-making assembly 3 further includes a first pressure sensor 34, a second pressure sensor 35, a first temperature sensor 36, and a second temperature sensor 37. The first pressure sensor 34 and the first temperature sensor 36 are sequentially disposed between the regenerator 324 and the inlet 141 of the two subcooled water spiral channels, and the second temperature sensor 37 and the second pressure sensor 35 are sequentially disposed between the outlet 142 of the two subcooled water spiral channels and the crystallizer 331.

[0053] The temperature detected by the first temperature sensor 36 is set to T1, the temperature detected by the second temperature sensor 37 is set to T2, the pressure detected by the first pressure sensor 34 is set to P1, and the pressure detected by the second pressure sensor 35 is set to P2. The difference in pressure values ​​is then obtained as ΔP.

[0054] When T1 in the system is greater than 0.5℃, the temperature of the water entering evaporator 1 for heat exchange is high, and it is necessary to check the insulation performance of the subcooled water pipe and whether the system has malfunctioned. When T1 is less than or equal to 0.5℃, and the subcooled water temperature T2 is in the range of -3℃ to 0℃ during system operation, the pressure difference is less than or equal to P1. At this time, the system is operating normally and there is no ice blockage.

[0055] Taking the system using the hot fluorine produced by compressor 22 as the high-temperature heat exchange medium as an example (see [link]). Figure 7 and Figure 8 When T2 > 0℃, it indicates that the unit's cooling temperature is insufficient, and the frequency H of compressor 22 needs to be increased. Observe the T2 value of the second temperature sensor 37 after increasing H. If T2 is still > 0℃, continue to increase the frequency H of compressor 22. When T2 < -3℃, it indicates that the unit's cooling temperature is too low, and the frequency H of compressor 22 needs to be decreased until the subcooled water temperature T is -3℃ ≤ T2 ≤ 0℃. Then observe the ΔP value of the differential pressure sensor in the system pipeline.

[0056] When ΔP≤P1, the pressure difference is normal and the system is operating normally.

[0057] When ΔP > P1, it indicates that ice blockage has occurred in the system (the critical value for the ice blockage frequency is τ, and selecting chilled water return at a lower temperature can eliminate the ice blockage; in actual operation, the ice blockage frequency is τ1). When τ1 ≤ τ, adjust the opening of the first regulating valve 41 to introduce a low flow rate of hot refrigerant into the evaporator 1 to exchange heat with the subcooled water and eliminate the ice blockage until ΔP ≤ P1, allowing the system to operate normally. When ΔP > P1 and τ1 > τ, it indicates that the frequency of ice blockage in the system is too high, and heat exchange with a low flow rate of hot refrigerant is insufficient to eliminate the ice blockage. In this case, adjust the opening of the first regulating valve 41 to introduce a high flow rate of hot refrigerant into the evaporator 1 to exchange heat with the subcooled water and eliminate the ice blockage until ΔP ≤ P1, allowing the system to operate normally.

[0058] When ΔP > P2 (P2 > P1), the system pressure difference is too large, indicating that the frequency of ice blockage in the system is too high. In this case, adjust the valve opening of the first regulating valve 41 to introduce high-flow-rate hot refrigerant into the evaporator 1 to exchange heat with the subcooled water to eliminate ice blockage until ΔP ≤ P1, so that the system can operate normally.

[0059] Please see Figure 5 In another embodiment, the ice-making component 33 further includes a flow meter 333, which is located between the outlet 142 of the two subcooled water spiral channels and the crystallizer 331. The flow meter 333 monitors the flow rate of the subcooled water in real time, ensuring that the flow rate of the subcooled water entering the crystallizer 331 is stable and meets the design requirements. Through the precise measurement of the flow meter 333, system parameters can be adjusted in a timely manner to ensure the stability and efficiency of the ice-making process. Fluctuations in the subcooled water flow rate affect the quality and yield of the ice slurry, which is crucial for generating uniform ice slurry. The data provided by the flow meter 333 can help adjust the operating speed of the water pump 323 to ensure that the system operates in the most energy-efficient state, thereby reducing operating costs. The flow meter 333 can also detect abnormal changes in flow rate in a timely manner, helping to quickly diagnose potential problems in the system, such as pipe blockage, pump failure, or valve leakage. This helps to take timely measures to prevent system failure and equipment damage.

[0060] Please see Figure 5 In one embodiment of the present invention, the high-temperature heat exchange medium supply assembly 4 includes a cooling tower 42, a medium-low temperature chiller unit, a second regulating valve 45, a third regulating valve 46, a fourth regulating valve 47, and a fifth regulating valve 48. The chilled water return port 43 of the medium-low temperature chiller unit is connected to the inlet 151 of the high-temperature channel through the second regulating valve 45, and the chilled water supply port 44 of the medium-low temperature chiller unit is connected to the outlet 152 of the high-temperature channel through the third regulating valve 46. The outlet of the cooling tower 42 is connected to the inlet 151 of the high-temperature channel through the fourth regulating valve 47, and the inlet of the cooling tower 42 is connected to the outlet 152 of the high-temperature channel through the fifth regulating valve 48. Cooling tower 42 provides cooling water, raising the water temperature through an evaporative cooling process to eliminate ice blockage. The outlet of cooling tower 42 is connected to the inlet 151 of the high-temperature channel via a fourth regulating valve 47, and the inlet of cooling tower 42 is connected to the outlet 152 of the high-temperature channel via a fifth regulating valve 48. The chilled water return port 43 of the medium-low temperature chiller provides chilled water return for heat exchange with subcooled water to eliminate ice blockage. The chilled water return port 43 of the medium-low temperature chiller is connected to the inlet 151 of the high-temperature channel via a second regulating valve 45, and the chilled water supply port 44 of the medium-low temperature chiller is connected to the outlet 152 of the high-temperature channel via a third regulating valve 46. The second regulating valve 45 controls the flow rate of the chilled water return to ensure that the flow rate of the chilled water returning to the high-temperature channel 15 meets the system requirements, and the third regulating valve 46 controls the flow rate of the water flowing to the chilled water supply port 44 of the medium-low temperature chiller to ensure that the water entering it meets the system requirements.

[0061] Please see Figure 5 and Figure 6 In this embodiment, when T1 > 0.5℃ in the system, the temperature of the water entering the evaporator 1 for heat exchange is high, and it is necessary to check the insulation performance of the subcooled water pipe and whether the system has malfunctioned; when T1 ≤ 0.5℃, the subcooled water temperature T2 is in the range of -3℃ to 0℃ during system operation, and the pressure difference is less than or equal to P1. At this time, the system is operating normally and there is no ice blockage.

[0062] When T2 > 0℃, it indicates that the unit's cooling temperature is insufficient, and the frequency H of compressor 22 needs to be increased. Observe the T2 value of the second temperature sensor 37 after increasing H. If T2 is still > 0℃, continue to increase the frequency H of compressor 22. When T2 < -3℃, it indicates that the unit's cooling temperature is too low, and the frequency H of compressor 22 needs to be decreased until the subcooled water temperature T is -3℃ ≤ T2 ≤ 0℃. Then observe the ΔP value of the differential pressure sensor in the system pipeline.

[0063] When ΔP≤P1, the pressure difference is normal and the system is operating normally.

[0064] When ΔP > P1, it indicates that ice blockage has occurred in the system (the critical value for the ice blockage frequency is τ, and selecting chilled water return at a lower temperature can eliminate the ice blockage; in actual operation, the ice blockage frequency is τ1). When τ1 ≤ τ, open the second regulating valve 45 and the third regulating valve 46, and close the fourth regulating valve 47 and the fifth regulating valve 48. Use the chilled water return as a high-temperature heat exchange medium to exchange heat with the subcooled water in the evaporator 1 to eliminate the ice blockage until ΔP ≤ P1, allowing the system to operate normally. When ΔP > P1 and τ1 > τ, it indicates that the frequency of ice blockage in the system is too high, and the temperature of the chilled water return is insufficient to eliminate the ice blockage. In this case, open the fourth regulating valve 47 and the fifth regulating valve 48, and close the second regulating valve 45 and the third regulating valve 46. Use the cooling water as a high-temperature heat exchange medium to exchange heat with the subcooled water in the evaporator 1 to eliminate the ice blockage until ΔP ≤ P1, allowing the system to operate normally.

[0065] When ΔP > P2 (P2 > P1), the system pressure difference is too large, indicating that the frequency of ice blockage in the system is too high. Open the fourth regulating valve 47 and the fifth regulating valve 48, close the second regulating valve 45 and the third regulating valve 46, and pass the cooling water as a high-temperature heat exchange medium into the evaporator 1 to exchange heat with the subcooled water to eliminate ice blockage until ΔP ≤ P1, so that the system can operate normally.

[0066] Please see Figure 5 In one embodiment of the present invention, the high-temperature heat exchange medium supply assembly 4 includes a first cooling pump 49. The first cooling pump 49 is connected to the outlet of the cooling tower 42 and the fourth regulating valve 47, and is located between the outlet of the cooling tower 42 and the fourth regulating valve 47. The first cooling pump 49 provides power to transport cooling water in the cooling tower 42 to the high-temperature channel 15, ensuring continuous flow of cooling water in the system and maintaining normal system operation. The first cooling pump 49 is connected to the outlet of the cooling tower 42 and the fourth regulating valve 47, and is located between the outlet of the cooling tower 42 and the fourth regulating valve 47. The fourth regulating valve 47 is used to control the flow rate of cooling water to ensure that the flow rate of cooling water entering the high-temperature channel 15 meets the system requirements. Through the precise control of the first cooling pump 49, the flow rate and pressure of cooling water are ensured to meet the system requirements, improving the stability and reliability of the system.

[0067] Please see Figure 5In one embodiment of the present invention, the high-temperature heat exchange medium supply component 4 further includes a second cooling pump 5. The second cooling pump 5 is connected to the outlet of the cooling tower 42 and the inlet of the circulating refrigeration component 2, and the inlet of the cooling tower 42 is connected to the outlet of the circulating refrigeration component 2. The second cooling pump 5 provides power to transport cooling water from the cooling tower 42 to the circulating refrigeration component 2, ensuring continuous flow of cooling water in the system and maintaining normal system operation. Through precise control of the second cooling pump 5, the flow rate and pressure of cooling water in the circulating refrigeration component 2 are ensured to meet system requirements, ensuring continuous flow of cooling water between the cooling tower 42 and the circulating refrigeration component 2. This not only improves the stability and reliability of the system but also ensures efficient circulation of cooling water in the system, maintaining normal system operation. With the assistance of the second cooling pump 5, efficient circulation of cooling water between the cooling tower 42 and the circulating refrigeration component 2 is ensured, improving the heat exchange efficiency of the system. The optimized heat exchange design ensures efficient operation of the system under different operating conditions and reduces energy waste.

[0068] This invention also proposes a method for regulating an ice slurry cold storage system. This method is applied to the ice slurry cold storage system 100 described in any of the above embodiments. The specific structure of the ice slurry cold storage system 100 is as described in the above embodiments. Since this method for regulating the ice slurry cold storage system adopts all the technical solutions of all the above embodiments, it has at least all the beneficial effects brought about by the technical solutions of the above embodiments, which will not be described in detail here. The method for regulating the ice slurry cold storage system includes the following steps:

[0069] Please see Figure 9 Step S100: Obtain the temperature values ​​T1 and T2 at the inlet and outlet of the subcooled water spiral channel 14, respectively, and the pressure difference between the inlet and outlet of the subcooled water spiral channel 14 is ΔP. ​​Set the proposed critical value for the frequency of ice blockage in the system to τ, and the actual frequency of ice blockage in the system to τ1.

[0070] In this embodiment, by setting temperature sensors and pressure sensors at the inlet and outlet of the subcooled water spiral channel 14 respectively, T1, T2, P1 and P2 (P2 is greater than P1) can be obtained by the temperature sensors and pressure sensors during system operation, and ΔP is the difference between P2 and P1.

[0071] Step S200: Determine whether T1 is greater than the first preset value. If it is greater than the first preset value, then the subcooled water spiral channel 14 and system faults need to be detected. If T1 is less than or equal to the first preset value, and T2 and ΔP are respectively within the range of the second preset value, and ΔP is less than or equal to and within the range of the third preset value, then there is no ice blockage in the system.

[0072] In this embodiment, when T1 > 0.5℃ in the system, it indicates that the temperature of the water entering the evaporator 1 for heat exchange is high, and it is necessary to check the insulation performance of the subcooled water spiral channel 14 and whether the system has malfunctioned; when T1 ≤ 0.5℃, and the subcooled water temperature T2 is in the range of -3℃ to 0℃ during system operation, the pressure difference is less than or equal to P1, at this time the system is operating normally and there is no ice blockage.

[0073] Step S300: If T2 is greater than the maximum value of the second preset value range, increase the cooling frequency of the circulating cooling component 2 until T2 is within the second preset value range; if T2 is less than the minimum value of the second preset value range, decrease the cooling frequency of the circulating cooling component 2 until T2 is within the second preset value range.

[0074] In this embodiment, when T2 > 0℃, it indicates that the cooling temperature of the circulating cooling component 2 is insufficient, and the cooling frequency of the circulating cooling component 2 needs to be increased. The value of the temperature sensor at the outlet of the subcooled water spiral channel 14 is observed after the cooling frequency is increased. If T2 > 0℃, the cooling frequency of the circulating cooling component 2 is further increased until -3℃ ≤ T2 ≤ 0℃. When T2 < -3℃, it indicates that the cooling temperature of the circulating cooling component 2 is too low, and the cooling frequency of the circulating cooling component 2 needs to be reduced until -3℃ ≤ T2 ≤ 0℃.

[0075] Step S400: If ΔP is less than or equal to the third preset value, the system operates normally; if ΔP is greater than the third preset value and τ1 is less than or equal to τ, the high-temperature heat exchange medium supply component 4 supplies a high-temperature heat exchange medium with a lower temperature or lower flow rate until the system operates normally; if ΔP is greater than the third preset value and τ1 is greater than τ, the high-temperature heat exchange medium supply component 4 supplies a high-temperature heat exchange medium with a higher temperature or higher flow rate until the system operates normally.

[0076] In this embodiment, the ΔP value in the system pipeline is observed. When ΔP ≤ P1, the differential pressure is normal and the system is operating normally. When ΔP > P1, it indicates that ice blockage has occurred in the system (the proposed critical value for the frequency of ice blockage is exactly τ, and selecting chilled water return at a lower temperature can eliminate the ice blockage; in actual operation, the frequency of ice blockage is τ1). When τ1 ≤ τ, chilled water return at a lower temperature or hot refrigerant at a lower flow rate is introduced into evaporator 1 as a high-temperature heat exchange medium to exchange heat with the subcooled water to eliminate the ice blockage until ΔP ≤ P1, allowing the system to operate normally. When ΔP > P1 and τ1 > τ, it indicates that the system is experiencing ice blockage. If the frequency of ice blockage is too high, using low-temperature chilled water return or low-flow hot refrigerant as a high-temperature heat exchange medium is insufficient to eliminate the ice blockage. In this case, high-temperature cooling water or high-flow hot refrigerant is introduced into evaporator 1 as a high-temperature heat exchange medium to exchange heat with the subcooled water to eliminate the ice blockage until ΔP≤P1, allowing the system to operate normally. When ΔP>P2 (P2>P1), the system pressure difference is too large, indicating that the frequency of ice blockage in the system is too high. In this case, high-temperature cooling water or high-flow hot refrigerant is introduced into evaporator 1 as a high-temperature heat exchange medium to exchange heat with the subcooled water to eliminate the ice blockage until ΔP≤P1, allowing the system to operate normally.

[0077] Through precise temperature and pressure monitoring, combined with assessment of ice blockage frequency, the system can adjust operating parameters in real time to ensure stable operation, prevent ice blockage caused by abnormal temperature or pressure, protect equipment, and extend its service life. By dynamically adjusting the temperature and flow rate of the high-temperature heat exchange medium, the system can effectively eliminate ice blockage, reduce downtime and maintenance costs caused by ice blockage, and optimize cooling effect according to actual needs, reducing energy waste. The optimized heat exchange design reduces heat loss and avoids ice blockage caused by excessive temperature changes, improving effective cooling capacity and increasing chiller efficiency by approximately 15%-20%, thus reducing operating costs. Through real-time monitoring and automatic control, this system achieves intelligent operation, reduces manual intervention, improves operating efficiency and reliability, and has significant energy-saving effects and economic benefits in practical applications.

[0078] The above description is merely an exemplary embodiment of the present invention and does not limit the patent scope of the present invention. Any equivalent structural transformations made using the contents of the present invention specification and drawings under the technical concept of the present invention, or direct / indirect applications in other related technical fields, are included within the patent protection scope of the present invention.

Claims

1. An ice slurry cold storage system, characterized in that, include: An evaporator includes a shell with a cavity. The cavity contains a refrigerant spiral channel and two subcooled water spiral channels. The refrigerant spiral channel is located between the two subcooled water spiral channels. A high-temperature channel is formed between the inner spiral of one subcooled water spiral channel and the outer spiral of the other subcooled water spiral channel. The high-temperature channel is connected to the cavity. A circulating refrigeration assembly, wherein the circulating refrigeration assembly is connected to both ends of the refrigerant spiral channel; An ice-making assembly, wherein the ice-making assembly is connected to both ends of the two subcooled water spiral channels; as well as A high-temperature heat exchange medium supply assembly, wherein the high-temperature heat exchange medium supply assembly is connected to both ends of the high-temperature channel; In the cross-section along the length of the housing, both the refrigerant spiral channel and the subcooled water spiral channel are arranged to extend along the length of the housing; The inner spiral of the refrigerant spiral channel coincides with the outer spiral of one of the subcooled water spiral channels, and the outer spiral of the refrigerant spiral channel coincides with the inner spiral of the other subcooled water spiral channel.

2. The ice slurry cold storage system as described in claim 1, characterized in that, The circulating refrigeration assembly includes an evaporator, a gas-liquid separator, a compressor, a condenser, and an expansion valve arranged in sequence. The gas-liquid separator is connected to the outlet of the refrigerant spiral channel, and the expansion valve is connected to the inlet of the refrigerant spiral channel.

3. The ice slurry cold storage system as described in claim 2, characterized in that, The high-temperature heat exchange medium supply assembly includes a first regulating valve. The inlet of the high-temperature channel is connected to the outlet of the condenser through the first regulating valve, and the outlet of the high-temperature channel is connected to the inlet of the gas-liquid separator.

4. The ice slurry cold storage system as described in claim 1, characterized in that, The ice-making assembly includes an ice storage tank, a pretreatment unit, and an ice-making unit. The pretreatment unit includes a primary filter, a secondary filter, a water pump, and a regenerator arranged in sequence. The ice-making unit includes a crystallizer and an ice slurry buffer tank. The regenerator is connected to the inlet of the two subcooled water spiral channels, and the crystallizer is connected to the outlet of the two subcooled water spiral channels. The ice storage tank is connected to the primary filter and the ice slurry buffer tank, respectively.

5. The ice slurry cold storage system as described in claim 4, characterized in that, The ice-making assembly further includes a first pressure sensor, a second pressure sensor, a first temperature sensor, and a second temperature sensor. The first pressure sensor and the first temperature sensor are sequentially disposed between the regenerator and the inlet of the two subcooled water spiral channels. The second temperature sensor and the second pressure sensor are sequentially disposed between the outlet of the two subcooled water spiral channels and the crystallizer; and / or The ice-making component also includes a flow meter, which is located between the outlet of the two subcooled water spiral channels and the crystal promoter.

6. The ice slurry cold storage system as described in claim 1, characterized in that, The high-temperature heat exchange medium supply assembly includes a cooling tower, a medium-low temperature chiller, a second regulating valve, a third regulating valve, a fourth regulating valve, and a fifth regulating valve. The chilled water return port of the medium-low temperature chiller is connected to the inlet of the high-temperature channel through the second regulating valve, and the chilled water supply port of the medium-low temperature chiller is connected to the outlet of the high-temperature channel through the third regulating valve. The outlet of the cooling tower is connected to the inlet of the high-temperature channel through the fourth regulating valve, and the inlet of the cooling tower is connected to the outlet of the high-temperature channel through the fifth regulating valve.

7. The ice slurry cold storage system as described in claim 6, characterized in that, The high-temperature heat exchange medium supply assembly includes a first cooling pump, which is connected to the outlet of the cooling tower and the fourth regulating valve, and is located between the outlet of the cooling tower and the fourth regulating valve; and / or The high-temperature heat exchange medium supply assembly also includes a second cooling pump, which is connected to the outlet of the cooling tower and the inlet of the circulating refrigeration assembly. The inlet of the cooling tower is connected to the outlet of the circulating refrigeration assembly.

8. A method for regulating an ice slurry cold storage system, characterized in that, The control method for the ice slurry cold storage system is applied to the ice slurry cold storage system as described in any one of claims 1 to 7, and the control method for the ice slurry cold storage system includes the following steps: The temperature values ​​at the inlet and outlet of the subcooled water spiral channel are T1 and T2 respectively, the pressure difference between the inlet and outlet of the subcooled water spiral channel is ΔP, and the critical value for the proposed system ice blockage frequency is set to τ, while the actual system ice blockage frequency value is τ1. Determine whether T1 is greater than the first preset value. If it is greater than the first preset value, the subcooled water spiral channel and system fault need to be checked. If T1 is less than or equal to the first preset value, and T2 is within the range of the second preset value, and ΔP is less than or equal to the third preset value, then there is no ice blockage in the system. If T2 is greater than the maximum value of the second preset value range, the cooling frequency of the circulating cooling component is increased until T2 is within the second preset value range; if T2 is less than the minimum value of the second preset value range, the cooling frequency of the circulating cooling component is decreased until T2 is within the second preset value range. If ΔP is less than or equal to the third preset value, the system operates normally; if ΔP is greater than the third preset value and τ1 is less than or equal to τ, the high-temperature heat exchange medium supply component supplies a high-temperature heat exchange medium with a lower temperature or lower flow rate until the system operates normally; if ΔP is greater than the third preset value and τ1 is greater than τ, the high-temperature heat exchange medium supply component supplies a high-temperature heat exchange medium with a higher temperature or higher flow rate until the system operates normally.

Images