Direct expansion type dynamic ice slurry unit

Abstract

The invention discloses a direct-expansion type dynamic ice slurry unit. The direct-expansion type dynamic ice slurry unit comprises a refrigerant flow path, an ice slurry inlet and an ice slurry outlet, a compressor; a condenser; the cold water flow path is suitable for being connected with the ice storage tank; the refrigerant subcooler comprises a first refrigerant flow channel and a first cold water flow channel; the supercooled water heat exchanger comprises a second refrigerant flow channel and a second cold water flow channel; wherein the inlet end of the first refrigerant flow channel is communicated with the refrigerant outlet end of the condenser, the outlet end of the second refrigerant flow channel is communicated with the inlet end of the compressor, the inlet end of the first cold water flow channel is communicated with the outlet end of the ice storage tank, and the outlet end of the second cold water flow channel is communicated with the inlet end of the ice storage tank. According to the direct expansion type dynamic ice slurry unit, the cold water from the ice storage tank is heated through sensible heat of the liquid refrigerant in the refrigerant subcooler, so that the liquid refrigerant is greatly subcooled, trace ice crystals carried in the cold water can be melted on the premise of not losing the cooling capacity of the unit, and ice blockage of the cold water in the subcooled water heat exchanger is avoided.

Description

Technical Field

[0001] The present invention relates to the technical field of air conditioning and refrigeration, and in particular to a direct expansion dynamic ice slurry unit. Background Art

[0002] Direct expansion dynamic ice slurry units are used to continuously produce ice slurry. Existing technologies typically use electric heating, cooling water flowing through the condenser, or condenser heat recovery to preheat and eliminate ice crystals. Electric heating is highly energy-inefficient, while cooling water flowing through the condenser or condenser heat recovery can lead to heat and cold cancellation, meaning that the reduced heat is wasted and released to the outside world. This compromises system energy efficiency and leaves room for improvement. Summary of the Invention

[0003] The present invention aims to address at least one of the technical problems existing in the prior art. To this end, the present invention proposes a direct expansion dynamic ice slurry unit that can achieve peak-shifting and valley-filling refrigeration. By utilizing a refrigerant subcooler, the unit heats cold water from the ice storage tank, saving energy while achieving a high degree of subcooling, significantly improving cooling capacity and system energy efficiency.

[0004] According to an embodiment of the present invention, the direct expansion dynamic ice slurry unit includes: a refrigerant flow path; a compressor, the compressor is arranged in the refrigerant flow path; a condenser, the condenser is arranged in the refrigerant flow path, the refrigerant inlet end of the condenser is connected to the outlet end of the compressor; a cold water flow path, the cold water flow path is suitable for being connected to the ice storage tank; a refrigerant subcooler, the refrigerant subcooler includes a first refrigerant flow path and a first cold water flow path for mutual heat exchange; a subcooled water heat exchanger, the subcooled water heat exchanger includes a second refrigerant flow path for mutual heat exchange channel and a second cold water channel; wherein, the first refrigerant channel and the second refrigerant channel are connected in series in the refrigerant channel, the inlet end of the first refrigerant channel is connected to the refrigerant outlet end of the condenser, the outlet end of the second refrigerant channel is connected to the inlet end of the compressor, the first cold water channel and the second cold water channel are connected in series in the cold water channel, the inlet end of the first cold water channel is connected to the outlet end of the ice storage tank, and the outlet end of the second cold water channel is connected to the inlet end of the ice storage tank.

[0005] According to the direct expansion dynamic ice slurry chiller of the present invention, the sensible heat of the liquid refrigerant in the refrigerant subcooler heats the cold water in the ice storage tank, while significantly supercooling the liquid refrigerant. This melts trace ice crystals in the cold water without sacrificing cooling capacity, preventing ice blockage in the chiller's subcooled water heat exchanger. Compared to solutions using an external heat source to melt ice crystals, this significantly improves the chiller's cooling capacity and energy efficiency, enabling peak-to-valley shifting and efficient consumption of renewable electricity.

[0006] According to some embodiments of the direct expansion dynamic ice slurry unit of the present invention, the compressor is configured as an oil-free compressor.

[0007] According to some embodiments of the present invention, the direct expansion dynamic ice slurry unit further includes a regenerator, which includes a first heat recovery channel and a second heat recovery channel for mutual heat exchange, the first heat recovery channel is connected between the inlet end of the first cold water channel and the outlet end of the ice storage tank, and the second heat recovery channel is connected between the outlet end of the first cold water channel and the inlet end of the second cold water channel.

[0008] According to some embodiments of the direct expansion dynamic ice slurry unit of the present invention, a preheater is provided between the outlet end of the first cold water flow channel and the inlet end of the second heat recovery flow channel, and the preheater is suitable for connecting to an external heat source.

[0009] According to some embodiments of the present invention, the direct expansion dynamic ice slurry unit further includes a gas-liquid separator, which is provided with a first inlet and a first outlet, wherein the first inlet is connected to the outlet end of the first refrigerant flow channel, and the first outlet is connected to the inlet end of the compressor.

[0010] According to some embodiments of the direct expansion dynamic ice slurry unit of the present invention, the gas-liquid separator is further provided with a second inlet and a second outlet, the second outlet is connected to the inlet end of the second refrigerant flow channel, and the second inlet is connected to the outlet end of the second refrigerant flow channel.

[0011] According to some embodiments of the present invention, the direct expansion dynamic ice slurry unit further includes an ice melting branch, the condenser is provided with a first condenser interface, the inlet end of the ice melting branch is connected to the first condenser interface, and the outlet end of the ice melting branch is connected between the second outlet and the inlet end of the second refrigerant flow channel.

[0012] According to some embodiments of the present invention, the direct expansion dynamic ice slurry unit further includes a diffusion preventer, a first branch is provided between the first inlet and the outlet end of the first refrigerant flow channel, and the flow path between the outlet end of the second cold water flow channel and the inlet end of the ice storage tank exchanges heat with the first branch through the diffusion preventer.

[0013] According to some embodiments of the direct expansion dynamic ice slurry unit of the present invention, a second branch is further provided between the first inlet and the outlet end of the first refrigerant flow channel, and the second branch is distributed in parallel with the first branch.

[0014] According to some embodiments of the present invention, the direct expansion dynamic ice slurry unit further includes an economizer, and an air supply branch is provided between the outlet end of the first refrigerant flow channel and the first interface of the compressor.

[0015] According to some embodiments of the direct expansion dynamic ice slurry unit of the present invention, the economizer is provided in the second branch, the compressor is provided with a first compressor interface, the air supply branch and the second branch exchange heat through the economizer, or the air supply branch exchanges heat with the part of the refrigerant flow path located between the condenser and the first refrigerant flow path through the economizer.

[0016] According to some embodiments of the present invention, the direct expansion dynamic ice slurry unit further includes a compressor cooling circuit, the condenser is provided with a condenser second interface, the compressor is provided with a compressor second interface, and the compressor cooling circuit is connected between the condenser second interface and the compressor second interface.

[0017] And / or, a pressure differential switch connected in parallel with the second cold water flow channel is further provided in the cold water flow channel.

[0018] According to some embodiments of the direct expansion dynamic ice slurry unit of the present invention, an ice-making pump and a second filter are provided between the inlet end of the first cold water flow channel and the outlet end of the ice storage tank, and a first check valve connected in series with the ice-making pump is also provided between the inlet end of the first cold water flow channel and the outlet end of the ice storage tank.

[0019] Additional aspects and advantages of the present invention will be set forth in part in the description which follows and, in part, will be obvious from the description which follows, or may be learned by practice of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0020] The above and / or additional aspects and advantages of the present invention will become apparent and readily understood from the following description of the embodiments with reference to the accompanying drawings, in which:

[0021] Figure 1 Schematic diagram of the structure of a direct expansion dynamic ice slurry unit according to some embodiments of the present invention;

[0022] Figure 2 Schematic diagrams of the structures of direct expansion dynamic ice slurry units according to other embodiments of the present invention;

[0023] Figure 3 Schematic diagram of the structure of direct expansion dynamic ice slurry units according to some other embodiments of the present invention;

[0024] Figure 4 Schematic diagram of the structure of direct expansion dynamic ice slurry units according to some further embodiments of the present invention.

[0025] Reference numerals:

[0026] Direct Expansion Dynamic Ice Slurry Unit 100,

[0027] Compressor 1, refrigerant flow path 11, compressor first interface 12, air supply branch 13, second expansion valve 131, solenoid valve 132, compressor second interface 14, second check valve 15,

[0028] Condenser 2, condenser first interface 21, condenser second interface 22, third filter 23,

[0029] Cold water flow path 3, ice storage tank 31, ice making pump 32, second filter 33, first check valve 34, pressure difference switch 35, crystal promoter 36, flow meter 37,

[0030] Refrigerant subcooler 4, first refrigerant flow channel 41, first cold water flow channel 42, first branch 43, third expansion valve 431, fourth expansion valve 432, second branch 44, economizer 441,

[0031] Subcooled water heat exchanger 5, second refrigerant flow channel 51, second cold water flow channel 52,

[0032] Regenerator 6, first regenerator channel 61, second regenerator channel 62,

[0033] Gas-liquid separator 7, first inlet 71, first outlet 72, second inlet 73, second outlet 74,

[0034] Ice melting branch 8, first expansion valve 81,

[0035] Anti-spam device 9,

[0036] Compressor cooling circuit 101, first filter 1011, ice melting pump 102, ice melting heat exchanger 103,

[0037] Preheater 200. DETAILED DESCRIPTION

[0038] The following describes embodiments of the present invention in detail. Examples of the embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals throughout represent the same or similar elements or elements having the same or similar functions. The embodiments described below with reference to the accompanying drawings are exemplary and are intended only to explain the present invention and are not to be construed as limiting the present invention.

[0039] In the description of the present invention, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", "clockwise", "counterclockwise", "axial", "radial", "circumferential" and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings. They are only for the convenience of describing the present invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as limiting the present invention. In addition, features defined as "first" or "second" may explicitly or implicitly include one or more of such features. In the description of the present invention, unless otherwise specified, "multiple" means two or more.

[0040] In the description of the present invention, it should be noted that, unless otherwise expressly specified or limited, the terms "mounted," "connected," and "connected" should be understood in a broad sense. For example, they may refer to fixed, detachable, or integral connections; mechanical or electrical connections; direct or indirect connections through an intermediate medium; and internal communication between two components. Those skilled in the art will understand the specific meanings of the above terms in the present invention based on the specific circumstances.

[0041] Reference below Figure 1 The direct expansion dynamic ice slurry unit 100 according to an embodiment of the present invention is described, including a refrigerant flow path 11, a compressor 1 and a condenser 2. The refrigerant flow path 11 is used to circulate refrigerant, wherein, during the flow of the refrigerant in the refrigerant flow path 11, the refrigerant can realize the transmission of cold and heat by switching between gas and liquid states. The compressor 1 is arranged in the refrigerant flow path 11, and the compressor 1 can compress and transport the refrigerant in the refrigerant flow path 11. The condenser 2 is arranged in the refrigerant flow path 11, and the refrigerant inlet end of the condenser 2 is connected to the outlet end of the compressor 1, that is, the condenser 2 is connected to the outlet end of the compressor 1, and the refrigerant compressed in the compressor 1 can enter the condenser 2 for cooling, so that the compressed gaseous refrigerant is converted into liquid refrigerant.

[0042] like Figure 1As shown, the direct expansion dynamic ice slurry unit 100 also includes a cold water flow path 3, wherein cold water flows through the cold water flow path 3. The cold water flow path 3 is suitable for connecting to an ice storage tank 31. That is, the ice storage tank 31 can be connected to the cold water flow path 3 so that the cold water in the ice storage tank 31 can participate in the cold water flow path 3. In other words, cold water can flow from the cold water flow path 3 into the ice storage tank 31, or from the ice storage tank 31 into the cold water flow path 3 and flow in the cold water flow path 3. In specific applications, the cold water in the cold water flow path 3 can exchange heat with the refrigerant in the refrigerant flow path 11. The ice storage tank 31 can be constructed as a separate structural component and flexibly connected to the cold water flow path 3.

[0043] like Figure 1 As shown, the direct expansion dynamic ice slurry unit 100 also includes a refrigerant subcooler 4, which includes a first refrigerant flow channel 41 and a first cold water flow channel 42 for mutual heat exchange. The first refrigerant flow channel 41 circulates refrigerant, and the first cold water flow channel 42 circulates cold water. The refrigerant and the cold water exchange heat in the refrigerant subcooler 4, wherein the temperature of the cold water is lower than the temperature of the refrigerant. The heat exchange between the cold water and the refrigerant realizes the heating of the cold water and the cooling of the refrigerant.

[0044] like Figure 1 As shown, the direct expansion dynamic ice slurry unit 100 also includes a supercooled water heat exchanger 5, which includes a second refrigerant flow channel 51 and a second cold water flow channel 52 for mutual heat exchange, the second refrigerant flow channel 51 flows refrigerant, and the second cold water flow channel 52 flows cold water, and the refrigerant and the cold water exchange heat in the supercooled water heat exchanger 5, wherein the temperature of the cold water is higher than the temperature of the refrigerant, and the cooling of the cold water and the heating of the refrigerant are achieved through heat exchange between the cold water and the refrigerant.

[0045] The first refrigerant flow channel 41 and the second refrigerant flow channel 51 are connected in series in the refrigerant flow path 11. The inlet end of the first refrigerant flow channel 41 is connected to the refrigerant outlet end of the condenser 2, and the outlet end of the second refrigerant flow channel 51 is connected to the inlet end of the compressor 1. Figure 1 As shown, the refrigerant flow path 11 includes a first refrigerant flow path 41 and a second refrigerant flow path 51 connected in series, the first refrigerant flow path 41 is connected to the refrigerant outlet end of the condenser 2, and the second refrigerant flow path 51 is connected to the inlet end of the compressor 1. The compressor 1 and the condenser 2 are connected to form a complete refrigerant flow path 11, and the connection between the compressor 1 and the condenser 2 is achieved. In this way, through the coordinated use of the compressor 1 and the condenser 2, the circulation flow of the refrigerant can be achieved, and the pressure and temperature of the refrigerant can be changed during the flow.

[0046] The first cold water channel 42 and the second cold water channel 52 are connected in series in the cold water channel 3. The inlet end of the first cold water channel 42 is connected to the outlet end of the ice storage tank 31, and the outlet end of the second cold water channel 52 is connected to the inlet end of the ice storage tank 31. Figure 1As shown, the cold water flow path 3 includes a first cold water flow path 42 and a second cold water flow path 52 connected in series. The first cold water flow path 42 and the second cold water flow path 52 are respectively connected to the inlet end and the outlet end of the ice storage tank 31, forming a complete cold water flow path 3, and the ice slurry can be prepared in the circulation flow of cold water.

[0047] And as Figure 1 As shown, the compressor 1, the condenser 2, the refrigerant subcooler 4 and the subcooled water heat exchanger 5 are connected in sequence through the first refrigerant flow channel 41 and the second refrigerant flow channel 51 respectively, and the ice storage tank 31, the refrigerant subcooler 4 and the subcooled water heat exchanger 5 are connected in sequence through the first cold water flow channel 42 and the second cold water flow channel 52, thereby forming a direct expansion dynamic ice slurry unit 100.

[0048] The direct expansion dynamic ice slurry unit 100 is used to produce ice slurry and is connected to the user end to achieve cooling for the user end. In actual use, after being compressed by compressor 1, compressor 1 discharges gaseous refrigerant to condenser 2 to condense into liquid refrigerant. The refrigerant then enters the refrigerant subcooler 4. At this time, the cold water in the ice storage tank 31 enters the refrigerant subcooler 4 through the first cold water flow channel 42. In the refrigerant subcooler 4, the refrigerant and the cold water exchange heat to heat the cold water and further cool the condensed refrigerant. The refrigerant and the cold water then exchange heat in the subcooled water heat exchanger 5 to cool the cold water. In this way, the refrigerant temperature can be lowered below the saturation temperature at the condensing pressure through the refrigerant subcooler 4, significantly increasing the subcooling degree of the refrigerant circuit. According to the refrigeration principle, the cooling capacity and energy efficiency of the refrigeration system can be significantly improved.

[0049] To ensure continuous ice slurry production and prevent ice blockage, the water entering the subcooled water heat exchanger 5 must be above 0°C, meaning it must be preheated. Existing direct expansion subcooled water ice slurry units draw 0°C water from the bottom of the ice storage tank 31, heat it in the condenser 2, and then feed it into the subcooled water heat exchanger 5. Alternatively, 0°C water is drawn from the bottom of the ice storage tank 31, heated by electrical heating, and then fed into the subcooled water heat exchanger 5. Another approach involves spraying water onto the air-cooled condenser 2, using the heat from the air-cooled condenser 2 to heat the spray water, which is then used to preheat the water in the ice storage tank 31. Some of these configurations allow for energy recovery and lower the condensing temperature, but these systems are less energy-efficient, and heating the cold water electrically wastes energy. In this embodiment, the cold water is heated directly through the refrigerant subcooler 4, saving energy while achieving a significantly higher degree of subcooling and improving ice production efficiency.

[0050] Also, in production, electricity consumption is high during the day and low at night. The process of making ice slurry by the direct expansion dynamic ice slurry unit 100 is to turn on the direct expansion dynamic ice slurry unit 100 to make ice slurry during the night-time low electricity price period, and concentrate the ice slurry in the ice storage tank 31. During the daytime peak and valley electricity price period, the direct expansion dynamic ice slurry unit 100 is turned off, and only the ice stored in the ice storage tank 31 is supplied to the user side for use. Among them, the power consumption of the direct expansion dynamic ice slurry unit 100 is the highest in the system. By making ice at night, the power peak during the daytime period can be effectively alleviated, which plays a role in shifting peak and filling valley, and plays an important role in matching user-side demand with grid-side supply, thereby improving the economy of grid operation.

[0051] According to an embodiment of the present invention, the direct expansion dynamic ice slurry unit 100, through the coordinated use of a compressor 1, a condenser 2, a refrigerant subcooler 4, and a subcooled water heat exchanger 5, can produce ice slurry. The refrigerant subcooler 4 heats cold water from the ice storage tank 31, saving energy while achieving a high degree of subcooling, significantly improving cooling capacity and system energy efficiency. The produced ice slurry is stored in the ice storage tank 31 for immediate user use, reducing energy consumption during daytime production and improving daytime user productivity.

[0052] The sensible heat of the liquid refrigerant in the refrigerant subcooler 4 heats the cold water in the ice storage tank 31, significantly supercooling the liquid refrigerant. This melts trace ice crystals in the cold water without sacrificing cooling capacity, preventing ice blockage in the subcooled water heat exchanger 5. Compared with solutions that use external heat sources to melt ice crystals, this significantly improves the cooling capacity and energy efficiency of the unit, enabling peak-load shifting and valley-loading of the power system and the efficient absorption of renewable electricity.

[0053] In some embodiments, the compressor is configured as an oil-free press, and no lubricating oil is set inside the oil-free press, which can prevent the refrigerant mixed with oil from flowing into the condenser, prevent oil from seeping into the condenser, reduce energy loss, and improve the heat exchange efficiency of the unit. There is no need for lubricating oil setting, which can save the setting of oil circuits, fundamentally eliminate the accumulation of oil in the condenser, reduce maintenance costs and workload, and without the interference of oil, the temperature control is more stable and the production of ice slurry is smoother.

[0054] Compressor 1 may employ a screw compressor or a scroll compressor. To maintain stable operation, lubricating oil is inevitably present in the system. On the one hand, oil affects the heat exchange of the heat exchanger. On the other hand, dynamic ice generation requires relatively stable temperature control. Oil accumulation can cause variations in the heat exchange temperature difference, thereby affecting the continuous and stable production of dynamic ice slurry. Generally, complex oil return devices, such as oil separators and oil return circuits, are required in the system. Because the heat exchanger operates under complex and variable operating conditions, flow rates and pressures are often not fixed values. These oil return devices cannot always maintain a good oil return state, further exacerbating the increase in the heat exchange temperature difference, affecting the stable production of ice slurry. In more serious cases, compressor 1 may be damaged due to oil starvation. In this embodiment, compressor 1 is configured as an oil-free compressor, eliminating the need for complex oil return system components in the refrigeration system. Furthermore, oil accumulation in the heat exchanger is eliminated, fundamentally eliminating the problem of oil accumulation in the condenser or piping, which causes fluctuations in the heat exchange temperature difference and results in inability to continuously produce ice slurry. This improves the efficiency and stability of ice slurry production.

[0055] In some embodiments, the oil-free hydraulic machine is configured as a magnetically suspended variable frequency centrifuge, an air-suspended variable frequency centrifuge, or a liquid-suspended variable frequency centrifuge.

[0056] Among them, magnetic levitation variable frequency centrifuges, gas levitation variable frequency centrifuges, or liquid levitation variable frequency centrifuges all have gas compression capabilities. Through the high-speed rotating impeller, work is performed on the refrigerant gas. After the gas gains energy, the pressure and flow rate increase. Then, the flow rate is reduced in the diffuser, the pressure continues to increase, and it is discharged from the volute and enters the condenser 2. Among them, the magnetic levitation variable frequency centrifuge uses magnetic levitation technology to eliminate the need for mechanical contact and mechanical friction during operation of the compressor 1, thereby improving energy efficiency and reducing maintenance costs. And the gas levitation variable frequency centrifuge uses gas levitation technology to enable the compressor 1 to achieve frictionless operation during operation, reducing energy loss. In addition, the liquid levitation variable frequency centrifuge (or positive pressure liquid levitation variable frequency centrifuge) is mainly used for material classification and purification, but in some designs, it can also be used for refrigerant compression. At the same time, combined with frequency conversion technology, the speed of the compressor 1 can be automatically adjusted according to the actual refrigeration or compression needs.

[0057] Therefore, the oil-free press can be configured as a magnetic levitation variable frequency centrifuge, an air levitation variable frequency centrifuge, or a liquid levitation variable frequency centrifuge, all of which can compress and transport the refrigerant. These configurations offer a variety of options and flexibility. Furthermore, the magnetic levitation bearings in all three oil-free presses require no lubricating oil, preventing oil from seeping into the heat exchanger, reducing energy loss and improving unit efficiency. The lack of lubricating oil eliminates the need for oil circuits, reducing maintenance costs and workload. Furthermore, without oil interference, temperature control is more stable, and ice slurry production is smoother.

[0058] In some embodiments, the direct expansion dynamic ice slurry unit 100 also includes a regenerator 6, which includes a first heat recovery channel 61 and a second heat recovery channel 62 for mutual heat exchange. The first heat recovery channel 61 is connected between the inlet end of the first cold water channel 42 and the outlet end of the ice storage tank 31, and the second heat recovery channel 62 is connected between the outlet end of the first cold water channel 42 and the inlet end of the ice storage tank 31.

[0059] Among them, the regenerator 6 is arranged between the ice storage tank 31 and the refrigerant supercooler 4. The regenerator 6 includes a first heat recovery channel 61 and a second heat recovery channel 62 for mutual heat exchange, and the first heat recovery channel 61, the first cold water channel 42 and the second heat recovery channel 62 are connected in sequence between the outlet end and the inlet end of the ice storage tank 31.

[0060] The regenerator 6 is used to reheat cold water. In actual application, the water in the ice storage tank 31 can be preheated to 0.2-0.5°C through the regenerator 6, and then further heat-exchanged with the refrigerant from the condenser 2 to be heated to 0.5-1°C. In this way, ice crystals can be completely eliminated (ice crystals are an important medium for converting supercooled water into ice. Eliminating ice crystals can make supercooled water less likely to freeze). The water then enters the supercooled water heat exchanger 5 and exchanges heat with the refrigerant in the second refrigerant flow channel 51 of the supercooled water heat exchanger 5 to obtain supercooled water at 0.2-0°C. Finally, the water flows into the ice storage tank 31 from the inlet end for storage.

[0061] Therefore, by installing a regenerator 6 between the ice storage tank 31 and the refrigerant subcooler 4, the water in the ice storage tank 31 can be preheated, preventing water from directly entering the refrigerant subcooler 4 and causing ice blockage in the system, thereby improving the system's ice-making stability. Furthermore, the use of a separate regenerator 6 to exchange heat with the refrigerant from the refrigeration system can improve the system's subcooling degree. The regenerator 6 and the refrigeration system form a self-contained design, which is more energy-efficient and eliminates the need to consume or control an external heat source, resulting in a simpler structure and lower costs.

[0062] And, in some embodiments, as Figure 3 As shown, a preheater 200 is provided between the outlet of the first cold water channel 42 and the inlet of the second heat recovery channel 62. The preheater 200 is adapted to be connected to an external heat source, which may include high-temperature cold water, unit cooling water, and other external heating sources.

[0063] Thus, the cooling water entering the second heat recovery flow channel 62 can be heated, thereby increasing the temperature of the cooling water in the second heat recovery flow channel 62, further facilitating the elimination of ice crystals and improving the supercooling degree of the system.

[0064] In some embodiments, the flow direction of the first heat regeneration channel 61 is opposite to the flow direction of the second heat regeneration channel 62. In this way, the water in the first heat regeneration channel 61 and the second heat regeneration channel 62 can flow in opposite directions, and the water in the first heat regeneration channel 61 and the second heat regeneration channel 62 can exchange heat in the regenerator 6 to achieve water preheating.

[0065] Among them, the flow direction of the first heat return flow channel 61 is from the ice storage tank 31 to the refrigerant supercooler 4, and the flow direction of the second heat return flow channel 62 is from the refrigerant supercooler 4 to the ice storage tank 31. In this way, the water flowing out of the ice storage tank 31 enters the first heat return flow channel 61 to realize water preheating. At this time, the water temperature is 0.2-0.5°C. The water continues to enter the first cold water flow channel 42 and passes through the refrigerant supercooler 4. It is heated again. At this time, the water temperature is 0.5-1°C. The heated water flows back into the second heat return flow channel 62 to exchange heat with the low-temperature water in the first heat return flow channel 61, which can reduce the water temperature so that the water temperature can be maintained in the range of 0.3-0.5°C. In this way, the smoothness of the water transportation process can be improved and the stability of ice making can be improved.

[0066] Therefore, through the above-mentioned arrangement, after the heat exchange between the refrigerant and the cold water in the refrigerant subcooler 4, the water with increased temperature can flow to the regenerator 6 again, and the water in the first heat recovery flow channel 61 of the regenerator 6 can be preheated continuously and stably, thereby reducing the heat exchange energy consumption of the regenerator 6, and the reverse flow prevents the water temperature from being too high, which is conducive to improving the subsequent ice-making efficiency.

[0067] Furthermore, the direct expansion dynamic ice slurry unit 100 may not be provided with the regenerator 6. Figure 2 and Figure 4 As shown, such an arrangement allows the low-temperature water in the ice storage tank 31 to directly exchange heat with the refrigerant in the refrigerant subcooler 4, preheating the low-temperature water to 0.2-0.5°C and obtaining a very high degree of subcooling.

[0068] In some embodiments, the direct expansion dynamic ice slurry unit 100 further includes a gas-liquid separator 7 , which is provided with a first inlet 71 and a first outlet 72 . The first inlet 71 is connected to the outlet end of the first refrigerant flow channel 41 , and the first outlet 72 is connected to the inlet end of the compressor 1 .

[0069] Among them, the gas-liquid separator 7 is used for separation of gas and liquid. Figure 1As shown, the gas-liquid separator 7 can be arranged between the subcooled water heat exchanger 5 and the compressor 1. The gas-liquid separator 7 is provided with a first inlet 71 and a first outlet 72. The first inlet 71 and the first outlet 72 are used for the inflow and outflow of the refrigerant, respectively. The first refrigerant flow channel 41 is connected to the gas-liquid separator 7 through the first inlet 71, so that the refrigerant in the first refrigerant flow channel 41 can enter the gas-liquid separator 7 from the first inlet 71. The gas-liquid separator 7 is connected to the compressor 1 through the first outlet 72, so that the refrigerant entering the gas-liquid separator 7 from the first inlet 71 can be separated into gas and liquid, and the gaseous refrigerant can flow into the compressor 1 from the first outlet 72 to realize the reflux of the refrigerant.

[0070] Therefore, during the operation of the direct expansion dynamic ice slurry unit 100, the refrigerant absorbs heat in the subcooled water heat exchanger 5 and becomes gaseous, and releases heat in the condenser 2 and becomes liquid. During this cycle, a gas-liquid mixture may form due to various factors (such as changes in pipeline pressure and uneven refrigerant flow). Liquid refrigerant is incompressible. If it enters the compressor 1, it will cause the internal pressure of the compressor 1 to rise sharply, resulting in a "liquid hammer" phenomenon, which will damage the compressor 1. The gas-liquid separator 7 ensures that only pure gaseous refrigerant enters the compressor 1, protecting the compressor 1 from damage. The gas-liquid separator 7 also allows the liquid refrigerant to be retained in the gas-liquid separator 7, and only the gaseous refrigerant enters the compressor 1 for compression. This can reduce the power consumption of the compressor 1 and improve the efficiency and stability of the entire refrigeration system.

[0071] In some embodiments, the gas-liquid separator 7 is further provided with a second inlet 73 and a second outlet 74 . The second outlet 74 is communicated with the inlet end of the second refrigerant flow channel 51 , and the second inlet 73 is communicated with the outlet end of the second refrigerant flow channel 51 .

[0072] like Figure 1 As shown, the gas-liquid separator 7 can be arranged between the supercooled water heat exchanger 5 and the compressor 1. The gas-liquid separator 7 is provided with a second inlet 73 and a second outlet 74. The second inlet 73 and the second outlet 74 are respectively used for the inflow and outflow of refrigerant. The gas-liquid separator 7 is connected with the second refrigerant flow channel 51 through the second outlet 74, and the outlet end of the second refrigerant flow channel 51 is connected with the gas-liquid separator 7 through the second inlet 73, so that the gas-liquid separator 7 and the supercooled water heat exchanger 5 can be connected. In this way, after the refrigerant in the gas-liquid separator 7 is separated into gas and liquid, the liquid refrigerant flows into the supercooled water heat exchanger 5 from the second outlet 74, and the refrigerant and water absorb heat and become gaseous when exchanging heat in the supercooled water heat exchanger 5. The gaseous refrigerant can enter the gas-liquid separator 7 from the second inlet 73, and after separation in the gas-liquid separator 7, the gaseous refrigerant flows into the compressor 1 from the first outlet 72 to realize the reflux of the refrigerant, thereby realizing the circulation of the refrigerant.

[0073] Therefore, through the above-mentioned arrangement, the refrigerant can be first separated into gas and liquid in the gas-liquid separator 7, and then the liquid refrigerant is transported to the supercooled water heat exchanger 5, thereby improving the heat exchange efficiency in the supercooled water heat exchanger 5, and the refrigerant that has undergone heat exchange in the supercooled water heat exchanger 5 enters the gas-liquid separator 7 again for separation, which can prevent the mixed liquid in the refrigerant from entering the compressor 1, thereby ensuring the stable operation of the compressor 1, so as to improve the stability and reliability of the ice-making process.

[0074] In some embodiments, the first inlet 71 and the second outlet 74 are disposed at the lower portion of the gas-liquid separator 7 , and the second inlet 73 and the first outlet 72 are disposed at the upper portion of the gas-liquid separator 7 .

[0075] In this way, the first inlet 71 and the second outlet 74 are located at the lower part of the gas-liquid separator 7, so that the outlet end of the first refrigerant flow channel 41 and the inlet end of the second refrigerant flow channel 51 can be connected to the lower part of the gas-liquid separator 7 respectively, so that the refrigerant in the first refrigerant flow channel 41 flows into the gas-liquid separator 7 from the lower part of the gas-liquid separator 7, and the second inlet 73 and the first outlet 72 are arranged at the upper part of the gas-liquid separator 7, so that the outlet end of the second refrigerant flow channel 51 can be connected to the upper part of the gas-liquid separator 7.

[0076] The liquid refrigerant enters the gas-liquid separator 7 from the lower part of the gas-liquid separator 7, and through the separation action of the gas-liquid separator 7, the gaseous refrigerant mixed in the liquid refrigerant can be separated out, and the gaseous refrigerant will flow upward, and the liquid refrigerant will flow downward, and the liquid refrigerant relies on its gravity to flow out from the lower part of the gas-liquid separator 7, thereby improving the flow efficiency of the liquid refrigerant, and the liquid refrigerant absorbs heat and becomes gaseous refrigerant during heat exchange in the supercooled water heat exchanger 5, and the gaseous refrigerant flows into the gas-liquid separator 7 from the upper part of the gas-liquid separator 7, and through the separation action of the gas-liquid separator 7, the liquid refrigerant mixed in the gaseous refrigerant can be separated out, and the formed pure gaseous refrigerant flows into the compressor 1 from the upper part of the gas-liquid separator 7, and the gas-liquid separation effect of the whole process is good, thereby improving the overall ice-making efficiency.

[0077] Among them, Figure 1 As shown, the first inlet 71 and the second outlet 74 are spaced apart and distributed in the lower part of the gas-liquid separator 7, and the second inlet 73 and the first outlet 72 are spaced apart and distributed in the upper part of the gas-liquid separator 7, so that the refrigerant flowing into and out of the gas-liquid separator 7 can be separated, and the connection between the first refrigerant flow channel 41 and the second refrigerant flow channel 51 and the gas-liquid separator 7 is clearer and more convenient.

[0078] In some embodiments, the direct expansion dynamic ice slurry unit 100 also includes an ice melting branch 8, the condenser 2 is provided with a first condenser interface 21, the inlet end of the ice melting branch 8 is connected to the first condenser interface 21, and the outlet end of the ice melting branch 8 is connected between the second outlet 74 and the inlet end of the second refrigerant flow channel 51.

[0079] That is to say, an ice melting branch 8 can be set to connect between the condenser 2 and the second refrigerant flow channel 51, and the refrigerant flows in the ice melting branch 8. The first interface 21 of the condenser is used to discharge the refrigerant. The refrigerant in the condenser 2 flows into the second refrigerant flow channel 51 through the ice melting branch 8, and the temperature of the refrigerant flowing out of the condenser 2 is relatively high, so that the second refrigerant flow channel 51 contains high-temperature refrigerant, which can heat the interior of the second refrigerant flow channel 51 and the subcooled water heat exchanger 5.

[0080] Therefore, during actual operation, when the subcooled water heat exchanger 5 becomes clogged with ice, the ice-melting branch 8 can be connected to the second refrigerant flow channel 51, and the high-temperature refrigerant can be used to heat the subcooled water heat exchanger 5 to melt the ice in the subcooled water heat exchanger 5. By providing the ice-melting branch 8, ice blockage in the subcooled water heat exchanger 5 can be avoided, and the flow rate of the second cold water flow channel 52 and / or the second refrigerant flow channel 51 in the subcooled water heat exchanger 5 can be maintained at a normal level, thereby achieving high ice-making efficiency and a more stable ice-making process.

[0081] In some embodiments, the ice melting branch 8 is provided with a first expansion valve 81. The first expansion valve 81 serves as an on-off valve of the ice melting branch 8, which can realize the connection and closing of the ice melting branch 8 and the second refrigerant flow channel 51. In this way, after the subcooled water heat exchanger 5 is blocked by ice, the first expansion valve 81 is opened to pass the refrigerant into the second refrigerant flow channel 51 and the subcooled water heat exchanger 5. When the ice melting of the subcooled water heat exchanger 5 is completed, the first expansion valve 81 is closed to stop supplying refrigerant to the second refrigerant flow channel 51 and the subcooled water heat exchanger 5. The switching is flexible and can be selectively connected according to actual needs, which is more convenient to use.

[0082] The first expansion valve 81 also functions as a throttling and pressure-reducing device, reducing the high-pressure refrigerant to a low-pressure mist or wet vapor state. This low-pressure refrigerant then enters the second refrigerant flow channel 51 and the subcooled water heat exchanger 5, absorbing surrounding heat to melt the ice in the subcooled water heat exchanger 5. The opening of the first expansion valve 81 is adjustable, controlling the refrigerant flow and pressure entering the subcooled water heat exchanger 5. Appropriate refrigerant flow and pressure ensure uniform and rapid melting of the ice layer.

[0083] The first expansion valve 81 can be arranged at any position of the ice melting branch 8 .

[0084] In some embodiments, the direct expansion dynamic ice slurry unit 100 also includes a diffusion preventer 9, a first branch 43 is provided between the first inlet 71 and the outlet end of the first refrigerant flow channel 41, and the flow path between the outlet end of the second cold water flow channel 52 and the inlet end of the ice storage tank 31 exchanges heat with the first branch 43 through the diffusion preventer 9.

[0085] Thus, the flow path between the outlet of the second cold water flow channel 52 and the inlet of the ice storage tank 31 is cold water, which is relatively low in temperature and prone to freezing. The flow path between the first branch 43 is refrigerant, which is at a higher temperature than the cold water. This allows the cold water and refrigerant to exchange heat at the diffusion barrier 9, raising the temperature of the cold water. Using the heat of the refrigerant to heat the cold water, rather than external or electrical heating, maximizes energy savings, maximizes profits, and reduces costs.

[0086] Therefore, by heating the outlet end of the second cold water channel 52 through the anti-propagation device 9, the ice crystals can be blocked from propagating between the flow path between the outlet end of the second cold water channel 52 and the inlet end of the ice storage tank 31 and the supercooled water heat exchanger 5, thereby preventing the supercooled water heat exchanger 5 from being blocked by ice, and reducing the risk of ice cracking the pipeline, so as to ensure the safety of the pipeline and the supercooled water heat exchanger 5, and improve the stability and reliability of ice making.

[0087] Among them, such as Figure 1 As shown, the propagation preventer 9 is provided at the outlet end of the subcooled water heat exchanger 5. At least a portion of the first branch 43 is located within the propagation preventer 9 and is connected to the first inlet 71. The inlet end of the first branch 43 is connected to the outlet end of the first refrigerant flow channel 41, allowing the refrigerant in the first branch 43 to flow from the first inlet 71 into the gas-liquid separator 7. Thus, by providing the first branch 43 between the first refrigerant flow channel 41 and the first inlet 71, the reverse propagation of ice crystals is prevented. It has a simple structure, a reasonable layout, and convenient pipe connection.

[0088] In some embodiments, a second branch 44 is further provided between the first inlet 71 and the outlet end of the first refrigerant flow channel 41 , and the second branch 44 is distributed in parallel with the first branch 43 .

[0089] like Figure 1As shown, the inlet end of the second branch 44 is connected to the outlet end of the first refrigerant flow channel 41, and the outlet end of the second branch 44 is connected to the first inlet 71. The first refrigerant flow channel 41 and the gas-liquid separator 7 can be connected through the second branch 44. The second branch 44 and the first branch 43 are arranged in parallel between the first refrigerant flow channel 41 and the gas-liquid separator 7, so that the refrigerant in the first refrigerant flow channel 41 can be divided into two paths, one path flows into the first branch 43, and the other path flows into the second branch 44. The refrigerant in the first branch 43 exchanges heat with the cold water flowing out of the supercooled water heat exchanger 5 at the anti-propagation device 9 to block the reverse propagation of ice crystals. The refrigerant in the second branch 44 directly enters the gas-liquid separator 7 from the first inlet 71 to realize subsequent work.

[0090] Therefore, by setting the first branch 43 and the second branch 44 in parallel and distributing them between the first refrigerant flow channel 41 and the gas-liquid separator 7, different functions can be achieved respectively, and the refrigerants in the first branch 43 and the second branch 44 do not affect each other. The refrigerant transportation of the anti-spreader 9 can be achieved through the first branch 43, and the refrigerant transportation speed of the gas-liquid separator 7 can be met through the second branch 44, thereby improving the efficiency and reliability of ice making, and being compatible with multiple heat exchange requirements of the direct expansion dynamic ice slurry unit 100, and the pipeline distribution is clear and reasonable, and maintenance is more convenient.

[0091] In some embodiments, an economizer 441 is further included, and an air supply branch 13 is provided between the outlet end of the first refrigerant flow channel 41 and the first interface 12 of the compressor; wherein, an economizer 441 is provided in the second branch 44, and the compressor 1 is provided with a first compressor interface 12, and the air supply branch 13 exchanges heat with the second branch 44 through the economizer 441, or the air supply branch 13 exchanges heat with the part of the refrigerant flow channel 11 located between the condenser 2 and the first refrigerant flow channel 41 through the economizer 441.

[0092] Among them, the second branch 44 and the air supply branch 13 are respectively circulated with refrigerant, such as Figure 1 As shown, economizer 441 is located at the outlet of refrigerant subcooler 4, which is divided into an air supply branch 13 and a second branch 44. During operation, the refrigerant entering refrigerant subcooler 4 exchanges heat with low-temperature water from ice storage tank 31, significantly increasing the subcooling degree of the refrigerant circuit. The refrigerant exiting refrigerant subcooler 4 flows into air supply branch 13 and second branch 44 respectively. The refrigerants in these two branches exchange heat in economizer 441, further increasing the subcooling degree. Based on the principles of refrigeration, the cooling capacity and energy efficiency of the refrigeration system can be significantly improved. The economizer 441 can be configured in a variety of ways, allowing for flexible selection.

[0093] The first interface 12 of the compressor is used for the inflow of refrigerant. After the air supply branch 13 exchanges heat with the second branch 44 in the economizer 441, the refrigerant in the second branch 44 flows backward to the subcooled water heat exchanger 5 for heat exchange. The refrigerant in the air supply branch 13 flows into the compressor 1 from the first interface 12 of the compressor, realizing air supply to the compressor 1, thereby increasing the refrigerant flow of the compressor 1 and improving the cooling capacity.

[0094] Among them, such as Figure 2 As shown, the economizer 441 is arranged at the refrigerant outlet end of the condenser 2. The refrigerant outlet end of the condenser 2 is divided into an air supply branch 13 and a second branch 44. During actual operation, after the compressor 1 compresses the refrigerant, the exhaust gas refrigerant passes through the condenser 2 and is condensed into liquid refrigerant. The liquid refrigerant flows into the air supply branch 13 and the second branch 44 respectively, and the refrigerants in the two branches exchange heat in the economizer 441 to further obtain subcooling. The refrigerant enters the refrigerant subcooler 4 and exchanges heat with the low-temperature water from the ice storage tank 31, which greatly increases the subcooling of the refrigerant circuit again, thereby improving the energy efficiency of the refrigeration system.

[0095] The refrigerant after heat exchange in the economizer 441 enters the refrigerant subcooler 4 to exchange heat with the low-temperature water from the ice storage tank 31, greatly increasing the subcooling degree of the refrigerant circuit. According to the refrigeration principle, the cooling capacity and energy efficiency of the refrigeration system can be greatly improved.

[0096] Furthermore, the second branch 44 may not be provided with the economizer 441, such as Figure 3 and Figure 4 As shown, the compressor 1 is not provided with an air supply branch 13, so that after the refrigerant is condensed into liquid refrigerant in the condenser 2, it only exchanges heat with the low-temperature water from the ice storage tank 31 through the refrigerant subcooler 4 to obtain a large degree of subcooling, thereby improving the system refrigeration performance.

[0097] In some embodiments, a second expansion valve 131 and / or a solenoid valve 132 is provided in the air supply branch 13. Only the second expansion valve 131 can be provided in the air supply branch 13. The air supply branch 13 can also be provided with a second expansion valve 131 and a solenoid valve 132. The setting method is not limited and can be flexibly selected.

[0098] Among them, the solenoid valve 132 can control the opening and closing of the air supply branch 13, automatically opening or closing according to system requirements, realizing automated control of the refrigeration system and improving the system's operating efficiency and stability. The solenoid valve 132 can precisely control the flow of refrigerant, ensuring the correct path of the refrigerant in the refrigeration cycle. By controlling the refrigerant flow and pressure, the solenoid valve 132 can prevent the refrigeration system from overloading or low pressure anomalies, thereby protecting the refrigeration equipment from damage. The second expansion valve 131 also has a throttling and pressure-reducing function, which can reduce the high-pressure refrigerant to a low-pressure mist or wet vapor state, creating conditions for the evaporation of the refrigerant. By controlling the refrigerant flow, the refrigerant entering the compressor 1 is ensured to be completely gaseous refrigerant, preventing refrigerant liquid hammer on the compressor 1, and enhancing the safety of the compressor 1.

[0099] like Figure 1 As shown, the air supply branch 13 is provided with a second expansion valve 131 and a solenoid valve 132. The coordinated action of the second expansion valve 131 and the solenoid valve 132 allows for precise control of the refrigerant flow and pressure, ensuring optimal operation of the refrigeration system and improving the cooling effect. The automated control function of the solenoid valve 132 ensures stable operation of the refrigeration system under various operating conditions, avoiding system failures caused by abnormal refrigerant flow or pressure. Furthermore, the simultaneous use of the second expansion valve 131 and the solenoid valve 132 increases the flexibility of the refrigeration system, enabling it to adapt to different operating environments and requirements.

[0100] The refrigerant in the air supply branch 13 is converted into gaseous refrigerant after heat exchange with the refrigerant in the second branch 44, and then enters the compressor 1 to supply air, thereby increasing the cooling capacity.

[0101] In some embodiments, a third expansion valve 431 is provided in the first branch 43. The third expansion valve 431 serves as an on-off valve of the first branch 43, which can realize the connection and closing of the first branch 43 and the first refrigerant flow channel 41. In this way, during actual operation, the third expansion valve 431 is opened, and the refrigerant in the first refrigerant flow channel 41 flows into the first branch 43, and exchanges heat with the cold water in the flow path between the outlet end of the second cold water flow channel 52 and the inlet end of the ice storage tank 31 at the anti-transmission device 9. After ice making is completed, the third expansion valve 431 is closed to stop supplying refrigerant to the first branch 43.

[0102] Third expansion valve 431 also functions as a throttling and pressure-reducing device, reducing the high-pressure refrigerant to a low-pressure mist or wet vapor state. This low-pressure refrigerant then enters propagation preventer 9 to achieve heat exchange with the chilled water. The opening of first expansion valve 81 is adjustable, controlling the flow rate and pressure of the refrigerant entering propagation preventer 9 to ensure heat exchange within the preventer.

[0103] The third expansion valve 431 can be set at any position of the first branch 43 .

[0104] In other embodiments, Figure 1 As shown, a fourth expansion valve 432 is provided between the outlet end of the first branch 43 and the first inlet 71. The fourth expansion valve 432 serves as a switching valve between the first branch 43 and the gas-liquid separator 7, and can realize the connection and closing of the first branch 43 and the gas-liquid separator 7. In this way, during actual operation, the fourth expansion valve 432 is opened, and the refrigerant of the first branch 43 and / or the second branch 44 flows to the first inlet 71 and enters the gas-liquid separator 7 through the first inlet 71. After ice making is completed, the fourth expansion valve 432 is closed to stop supplying refrigerant to the gas-liquid separator 7.

[0105] The fourth expansion valve 432 has the function of throttling and reducing pressure, which can reduce the high-pressure refrigerant to a low-pressure refrigerant in a mist or wet steam state. In this way, the low-pressure refrigerant enters the gas-liquid separator 7 to separate the gas and liquid.

[0106] The fourth expansion valve 432 may be disposed at any position between the first branch 43 and / or the second branch 44 and the first inlet 71 .

[0107] In some embodiments, the direct expansion dynamic ice slurry unit 100 also includes a compressor cooling circuit 101, the condenser 2 is provided with a condenser second interface 22, the compressor 1 is provided with a compressor second interface 14, and the compressor cooling circuit 101 is connected between the condenser second interface 22 and the compressor second interface 14.

[0108] like Figure 1 As shown, the inlet end of the compressor cooling circuit 101 is connected to the second interface 22 of the condenser, and the outlet end of the compressor cooling circuit 101 is connected to the second interface 14 of the compressor, so as to realize the connection between the cooling circuits of the compressor 1 and the condenser 2, wherein the second interface 14 of the compressor is used for the inflow of refrigerant, and the second interface 22 of the condenser is used for the outflow of refrigerant.

[0109] During actual operation, the refrigerant or cooling medium in the condenser 2 flows into the compressor cooling circuit 101 from the condenser second interface 22, and flows to the compressor second interface 14 through the compressor cooling circuit 101, and flows into the compressor 1 through the compressor second interface 14, which can cool and reduce the temperature of the compressor 1 to keep the temperature of the compressor 1 stable.

[0110] In some embodiments, a first filter 1011 is provided in the compressor cooling circuit 101. The first filter 1011 has a filtering function, filtering and intercepting impurities such as solid particles, metal debris, and rust contained in the cooling medium in the compressor cooling circuit 101. This ensures the cleanliness of the cooling medium flowing into the compressor 1, ensuring smooth flow of the cooling medium in the system, reducing the risk of pipe blockage and heat exchanger scaling, and thereby improving cooling efficiency and ice-making efficiency. Furthermore, the filtering function purifies the cooling medium, reducing the content of oil, water, and other contaminants therein, thereby ensuring the quality and performance of the cooling medium. Furthermore, clean cooling medium can reduce wear and corrosion of equipment components, thereby extending the service life of the entire ice-making system and its related equipment.

[0111] In some embodiments, an ice-making pump 32 and a second filter 33 are provided between the inlet end of the first cold water channel 42 and the outlet end of the ice storage tank 31. The main function of the ice-making pump 32 is to extract the ice slurry stored in the ice storage tank 31 and transport it to the inlet end of the first cold water channel 42 through a pipeline, and then enter the ice-making system for ice making.

[0112] Therefore, by installing an ice pump 32 at the outlet of the ice storage tank 31, the ice pump 32 acts as a power source, driving the circulation of ice slurry within the system, enabling delivery from the ice storage tank 31 to the ice-making system. The ice pump 32 can quickly extract the ice slurry from the ice storage tank 31 and deliver it to the ice-making system, accelerating the ice slurry preparation process and improving ice-making efficiency. Furthermore, precise control of the ice pump 32 ensures that parameters such as the flow rate, pressure, and temperature of the ice slurry in the system remain within set ranges, thereby ensuring stable system operation.

[0113] An ice melting pump 102 and an ice melting heat exchanger 103 are provided between the outlet end of the second cold water channel 52 and the inlet end of the ice storage tank 31. The ice melting heat exchanger 103 is connected to the equipment on the user side. The ice melting pump 102 is used to extract the ice slurry stored in the ice storage tank 31 and transport it to the ice melting heat exchanger 103 through a pipeline for use on the user side.

[0114] In actual production, when ice slurry needs to be made, the ice melting pump 102 is turned off, and the compressor 1, condenser 2 and ice making pump 32 are turned on to make ice. When used on the user side, the ice melting pump 102 is turned on. After ice making is completed, the compressor 1, condenser 2 and ice making pump 32 are turned off, and the low-temperature water of about 0°C at the bottom of the ice storage tank 31 is exchanged with the high-temperature water from the user side in the ice melting heat exchanger 103 to produce water of 7°C or lower. In this way, the low-temperature water in the ice storage tank 31 is recycled for recycling on the user side.

[0115] The second filter 33 has a filtering function. It is installed in the pipeline between the inlet end of the first cold water flow channel 42 and the outlet end of the ice storage tank 31. The second filter 33 can filter and intercept impurities such as solid particles, metal debris, and rust contained in the low-temperature water in the ice storage tank 31 to maintain the cleanliness of the water flowing into the first cold water flow channel 42. This ensures the smooth flow of cold water in the system, reduces the risk of pipe blockage and heat exchanger scaling, and thus improves cooling efficiency and ice making efficiency. The filtering effect can also purify the cold water, reducing the content of oil, water, and other contaminants. Clean cold water helps form more uniform and purer ice crystals during the ice making process, thereby improving the quality and stability of the ice slurry. Clean cold water can also reduce wear and corrosion of equipment components, thereby extending the service life of the entire ice making system and its related equipment.

[0116] In some embodiments, a first check valve 34 connected in series with the ice making pump 32 is further provided between the inlet end of the first cold water flow channel 42 and the outlet end of the ice storage tank 31 .

[0117] The first check valve 34 has the function of opening and closing the pipeline. The first check valve 34 is set in the pipeline between the inlet end of the first cold water flow channel 42 and the outlet end of the ice storage tank 31. In the ice-making system, the first check valve allows the cold water in the ice storage tank 31 to flow into the first cold water flow channel 42, and ensures that when the ice-making pump 32 stops working or the system fails, the cold water or ice slurry will not flow back into the ice storage tank 31, avoiding system confusion or damage, thereby maintaining the stability and safety of the system. The first check valve 34 helps maintain pressure stability in the system and prevents pressure fluctuations caused by backflow.

[0118] Thus, through the coordinated action of the second filter 33 and / or the first check valve 34, the cold water or ice slurry entering the first cold water flow channel 42 is ensured to be clean and free of impurities, and the cold water backflow is prevented and the system pressure is maintained stable, thereby improving the quality and stability of the ice slurry.

[0119] In some embodiments, a third filter 23 is provided between the inlet end of the first refrigerant flow channel 41 and the refrigerant outlet end of the condenser 2. The third filter 23 has a filtering function and can filter and intercept impurities such as solid particles, metal debris, and rust contained in the refrigerant flowing out of the condenser 2 to keep the refrigerant flowing into the refrigerant subcooler 4 and the subcooled water heat exchanger 5 clean. This can ensure the smooth flow of refrigerant in the system, reduce the risk of pipe blockage and heat exchanger scaling, and thus improve cooling efficiency and ice-making efficiency. The filtering function can also purify the refrigerant, reduce the content of oil, water, and other contaminants therein, and ensure the quality and performance of the refrigerant. Clean refrigerant can also reduce wear and corrosion of equipment components, thereby extending the service life of the entire ice-making system and its related equipment.

[0120] In some embodiments, the cold water flow path 3 is further provided with a pressure difference switch 35 connected in parallel with the second cold water flow path 52. Figure 1 As shown, the pressure differential switch 35 is connected to the inlet and outlet ends of the second cold water flow channel 52 of the supercooled water heat exchanger 5, so that the pressure differential switch 35 can be connected in parallel to the outside of the supercooled water heat exchanger 5. The pressure differential switch 35 can detect the pressure difference at both ends of the second cold water flow channel 52 in the cold water flow path 3 to determine the water flow rate.

[0121] In actual applications, when the water flow rate is lower than the set threshold, the water side pressure difference will become smaller, and the pressure differential switch 35 will be triggered. When the water flow rate is insufficient, the water in the supercooled water heat exchanger 5 may cool down rapidly due to insufficient heat exchange. By stopping the operation of the direct expansion dynamic ice slurry unit 100 in time through the pressure differential switch 35, the water temperature in the supercooled water heat exchanger 5 can be prevented from being too low, and the water freezing and expansion can be avoided to cause damage to the supercooled water heat exchanger 5.

[0122] Therefore, through the monitoring and control of the pressure difference switch 35, timely measures can be taken when the water flow is insufficient to prevent the water in the supercooled water heat exchanger 5 from freezing, thereby better preventing the heat exchanger from freezing and cracking, and more effectively protecting the supercooled water heat exchanger 5.

[0123] In some embodiments, a second check valve 15 is provided between the refrigerant inlet of the condenser 2 and the outlet of the compressor 1. The second check valve 15 has the function of opening and closing the pipeline. That is, the second check valve 15 can connect the compressor 1 to the condenser 2 and disconnect the compressor 1 from the condenser 2. In the direct expansion dynamic ice slurry unit 100, the second check valve 15 allows the refrigerant compressed by the compressor 1 to flow into the condenser 2. In addition, the second check valve 15 prevents the refrigerant from flowing back into the compressor 1 if the direct expansion dynamic ice slurry unit 100 stops operating or a system failure occurs.

[0124] Therefore, through the one-way flow of the second check valve 15, when the compressor 1 stops running, the second check valve 15 can prevent the high-pressure refrigerant in the condenser 2 from flowing back to the compressor 1, thereby avoiding the abnormal increase in pressure inside the compressor 1 due to the refrigerant flowing back to the compressor 1, and even damaging the compressor 1, and can prevent the liquid hammer phenomenon caused by the backflow of refrigerant, thereby maintaining the stability and safety of the system. The second check valve 15 helps to maintain the pressure stability in the system and prevent pressure fluctuations caused by backflow.

[0125] In other embodiments, a crystal promoter 36 is provided between the outlet of the second cold water channel 52 and the inlet of the ice storage tank 31, such as Figure 1As shown, the crystal promoter 36 is located between the propagation preventer 9 and the inlet of the ice storage tank 31. The function of the crystal promoter 36 is to promote the formation of ice crystals in the supercooled water. In this way, the supercooled water flowing out of the outlet of the second cold water flow channel 52 can flow into the crystal promoter 36, quickly forming ice crystals from the supercooled water, and then transporting the formed ice crystals to the ice storage tank 31 for storage.

[0126] Therefore, through the efficient operation of the crystal promoter 36, the entire direct expansion dynamic ice slurry unit 100 can operate more stably. The crystal promoter 36 not only improves the efficiency of ice crystal generation, but also prevents ice crystal backflow and blockage through the anti-propagation device 9, ensuring the long-term stable operation of the system.

[0127] In other embodiments, a flow meter 37 is provided between the outlet end of the first cold water channel 42 and the inlet end of the second cold water channel 52. The flow meter 37 is used to detect the cold water flow in the pipeline. By setting the flow meter 37 between the first cold water channel 42 and the second cold water channel 52, the cold water flow can be measured in real time, helping the operator to understand the flow of water in the system.

[0128] Flow meter 37 prevents damage to the equipment caused by insufficient or excessive flow. For example, insufficient flow could cause ice to form in the subcooled water heat exchanger 5, while excessive flow could increase the load on the equipment. Flow meter 37 can also be used for fault diagnosis. Sudden or abnormal flow rates could indicate a blockage, leak, or other problem in the system. Monitoring with flow meter 37 allows for timely detection and resolution of these issues.

[0129] Therefore, the direct expansion dynamic ice slurry unit 100 can be equipped with a pressure differential switch 35 and a flow meter 37 at the same time, or only a pressure differential switch 35 can be equipped, both of which can realize the judgment of ice blockage in the subcooled water heat exchanger 5, save costs, and have high reliability in judging ice blockage.

[0130] In some embodiments, the condenser 2 is constructed as a water-cooled condenser, an air-cooled condenser or an evaporative cooling condenser. That is, the condenser 2 can be constructed as a water-cooled condenser, or the condenser 2 can be constructed as an air-cooled condenser, or the condenser 2 can be constructed as an evaporative cooling condenser. These three different condensers 2 can all achieve condensation and cooling of the refrigerant, and the type of the compressor 1 is not limited to whether it is multi-stage compression, and its setting methods are diverse and can be flexibly selected.

[0131] Among them, the water-cooled condenser uses cooling water to cool and reduce the temperature of the refrigerant to achieve water cooling of the refrigerant, the air-cooled condenser uses air to cool and reduce the temperature of the refrigerant to achieve air cooling of the refrigerant, and the evaporative cooling condenser uses the evaporation of water to achieve cooling and reducing the temperature of the refrigerant.

[0132] The present invention also proposes a dynamic ice slurry system.

[0133] The dynamic ice slurry system according to an embodiment of the present invention includes the direct expansion dynamic ice slurry unit 100 in any of the above embodiments. The direct expansion dynamic ice slurry unit 100 is connected to the dynamic ice slurry system to meet the demand for producing ice slurry, and the direct expansion dynamic ice slurry unit 100 can realize the production of ice slurry by setting up a compressor 1, a condenser 2, a refrigerant supercooler 4 and a supercooled water heat exchanger 5. The ice slurry is stored in the ice storage tank 31 for users to use at any time, which reduces the energy consumption of producing ice slurry during the day to improve the production efficiency of users during the day, and the compressor 1 is an oil-free compressor, which reduces the setting of complex oil return system components in the direct expansion dynamic ice slurry unit 100, fundamentally eliminates oil enrichment in the heat exchanger, and reduces heat exchange temperature difference fluctuations, thereby improving the efficiency and stability of ice slurry production.

[0134] Throughout this specification, reference to terms such as "one embodiment," "some embodiments," "illustrative embodiments," "examples," "specific examples," or "some examples" means that a specific feature, structure, material, or characteristic described in conjunction with that embodiment or example is included in at least one embodiment or example of the present invention. In this specification, illustrative uses of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples.

[0135] While embodiments of the present invention have been shown and described, it will be appreciated by those skilled in the art that various changes, modifications, substitutions, and variations may be made to the embodiments without departing from the principles and spirit of the invention, and that the scope of the invention is defined by the claims and their equivalents.

Claims

1. A direct expansion dynamic ice slurry unit, characterized in that: include: refrigerant flow path; a compressor, the compressor being disposed in the refrigerant flow path; a condenser, the condenser being arranged in the refrigerant flow path, the refrigerant inlet end of the condenser being in communication with the outlet end of the compressor; a cold water flow path, the cold water flow path being adapted to be connected to the ice storage tank; A refrigerant subcooler, the refrigerant subcooler comprising a first refrigerant flow channel and a first cold water flow channel for mutual heat exchange; A supercooled water heat exchanger, the supercooled water heat exchanger comprising a second refrigerant flow channel and a second cold water flow channel for mutual heat exchange; Among them, the first refrigerant flow channel and the second refrigerant flow channel are connected in series in the refrigerant flow path, the inlet end of the first refrigerant flow channel is connected to the refrigerant outlet end of the condenser, and the outlet end of the second refrigerant flow channel is connected to the inlet end of the compressor, the first cold water flow channel and the second cold water flow channel are connected in series in the cold water flow path, the inlet end of the first cold water flow channel is connected to the outlet end of the ice storage tank, and the outlet end of the second cold water flow channel is connected to the inlet end of the ice storage tank.

2. The direct expansion dynamic ice slurry unit according to claim 1, characterized in that: The compressor is configured as an oil-free compressor.

3. The direct expansion dynamic ice slurry unit according to claim 1, characterized in that: It also includes a heat regenerator, which includes a first heat regeneration channel and a second heat regeneration channel for exchanging heat with each other, the first heat regeneration channel is connected between the inlet end of the first cold water channel and the outlet end of the ice storage tank, and the second heat regeneration channel is connected between the outlet end of the first cold water channel and the inlet end of the second cold water channel.

4. The direct expansion dynamic ice slurry unit according to claim 3, characterized in that: A preheater is provided between the outlet end of the first cold water flow channel and the inlet end of the second heat recovery flow channel, and the preheater is suitable for being connected to an external heat source.

5. The direct expansion dynamic ice slurry unit according to claim 1, characterized in that: It also includes a gas-liquid separator, which is provided with a first inlet and a first outlet, wherein the first inlet is connected to the outlet end of the first refrigerant flow channel, and the first outlet is connected to the inlet end of the compressor.

6. The direct expansion dynamic ice slurry unit according to claim 5, characterized in that: The gas-liquid separator is further provided with a second inlet and a second outlet, wherein the second outlet is communicated with the inlet end of the second refrigerant flow channel, and the second inlet is communicated with the outlet end of the second refrigerant flow channel.

7. The direct expansion dynamic ice slurry unit according to claim 6, characterized in that: It also includes an ice melting branch, the condenser is provided with a first condenser interface, the inlet end of the ice melting branch is connected to the first condenser interface, and the outlet end of the ice melting branch is connected between the second outlet and the inlet end of the second refrigerant flow channel.

8. The direct expansion dynamic ice slurry unit according to claim 5, characterized in that: It also includes a diffusion preventer, a first branch is provided between the first inlet and the outlet end of the first refrigerant flow channel, and the flow path between the outlet end of the second cold water flow channel and the inlet end of the ice storage tank exchanges heat with the first branch through the diffusion preventer.

9. The direct expansion dynamic ice slurry unit according to claim 8, characterized in that: A second branch is further provided between the first inlet and the outlet end of the first refrigerant flow channel, and the second branch is distributed in parallel with the first branch.

10. The direct expansion dynamic ice slurry unit according to claim 9, characterized in that: An economizer is also included, and an air supply branch is provided between the outlet end of the first refrigerant flow channel and the first interface of the compressor.

11. The direct expansion dynamic ice slurry unit according to claim 10, characterized in that: The economizer is provided in the second branch, and the compressor is provided with a compressor first interface. The air supply branch and the second branch exchange heat through the economizer, or the air supply branch exchanges heat with the part of the refrigerant flow path located between the condenser and the first refrigerant flow path through the economizer.

12. The direct expansion dynamic ice slurry unit according to claim 2, characterized in that: The compressor further comprises a compressor cooling circuit, wherein the condenser is provided with a condenser second interface, the compressor is provided with a compressor second interface, and the compressor cooling circuit is connected between the condenser second interface and the compressor second interface; And / or, a pressure differential switch connected in parallel with the second cold water flow channel is further provided in the cold water flow channel.

13. The direct expansion dynamic ice slurry unit according to claim 1, characterized in that: An ice making pump and a second filter are provided between the inlet end of the first cold water flow channel and the outlet end of the ice storage tank. A first check valve connected in series with the ice making pump is also provided between the inlet end of the first cold water flow channel and the outlet end of the ice storage tank.

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