Direct expansion type dynamic ice slurry unit

Abstract

The utility model 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; an ice storage tank is arranged in the cold water flow path; 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 first refrigerant flow channel is connected to the refrigerant outlet end of the condenser, the outlet end of the second refrigerant flow channel communicates with the inlet end of the compressor, 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 communicates with the inlet end of the ice storage tank; and the air supply branch is connected between the condenser and the compressor. According to the direct expansion type dynamic ice slurry unit, cold water from the ice storage tank is heated through the refrigerant subcooler, the great subcooling degree can be obtained, the air supply branch is arranged to supply air to the compressor, the compression amount of the compressor can be increased, and the system refrigerating capacity and the system energy efficiency are effectively improved.

Description

TECHNICAL FIELD

[0001] The utility model relates to air conditioning refrigeration technical field especially relates to a direct expansion type dynamic ice slurry unit. BACKGROUND

[0002] The direct expansion type dynamic ice slurry unit is used for continuously preparing ice slurry, and the prior art usually adopts electric heating, cooling water flowing through a condenser or condenser heat recovery to preheat and eliminate ice crystals in the direct expansion type dynamic ice slurry unit. Among them, the scheme of using electric heating is very energy inefficient, and the scheme of using cooling water flowing through a condenser or condenser heat recovery has the problem of cold and heat offset, that is, the reduced heat is released to the outside world, which is not conducive to the improvement of system energy efficiency, and there is room for improvement. SUMMARY

[0003] The utility model discloses at least one of the technical problems in the prior art. To this end, the utility model provides a direct expansion type dynamic ice slurry unit, which can realize peak load shifting refrigeration function, can heat the cold water from the ice storage tank through the refrigerant supercooler, save energy consumption, obtain great supercooling degree, and set up the air supplement branch to supplement the air to the compressor, improve the compression amount of the compressor, and effectively improve the system refrigeration capacity and system energy efficiency.

[0004] The direct expansion type dynamic ice slurry unit according to the utility model embodiment comprises: a refrigerant flow path; a compressor, which is arranged in the refrigerant flow path and is provided with a first compressor interface; a condenser, which is arranged in the refrigerant flow path and has a refrigerant inlet end in communication with an outlet end of the compressor; a cold water flow path, which is provided with an ice storage tank; a refrigerant supercooler, which comprises a first refrigerant flow channel and a first cold water flow channel in heat exchange with each other; a supercooled water heat exchanger, which comprises a second refrigerant flow channel and a second cold water flow channel in heat exchange with each other, 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 in communication with the refrigerant outlet end of the condenser, the outlet end of the second refrigerant flow channel is in communication with 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 in communication with the outlet end of the ice storage tank, and the outlet end of the second cold water flow channel is in communication with the inlet end of the ice storage tank; and an air supplement branch, which has an inlet end in communication with the refrigerant outlet end of the condenser and an outlet end in communication with the first compressor interface.

[0005] The direct expansion type dynamic ice slurry unit can make the refrigerant at the outlet end of the condenser flow into the compressor through the air supplement branch, air supplement to the compressor is realized, the refrigerant flow in the compressor is improved, the compression amount of the compressor is improved, the air supplement path is shortened, and the efficiency of the refrigerant flowing back to the compressor is improved, so that the overall refrigerating capacity of the system is effectively improved.

[0006] The direct expansion type dynamic ice slurry unit further comprises an economizer, the economizer has first and second inner side flow channels that exchange heat with each other, the first inner side flow channel is connected in series in the air supplement branch, and the second inner side flow channel is connected in series between the refrigerant outlet end of the condenser and the first refrigerant flow channel.

[0007] The flow direction of the first inner side flow channel is the same as that of the second inner side flow channel.

[0008] The inlet end of the air supplement branch is communicated between the refrigerant outlet end of the condenser and the second inner side flow channel.

[0009] The direct expansion type dynamic ice slurry unit further comprises a gas-liquid separator, the gas-liquid separator is provided with a first inlet, a first outlet, a second inlet and a second outlet, the first inlet is communicated with the outlet end of the first refrigerant flow channel, the first outlet is communicated with the inlet end of the compressor, 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.

[0010] The direct expansion type dynamic ice slurry unit further comprises a propagation prevention device, a first branch is arranged between the first inlet and the outlet end of the first refrigerant flow channel, and a 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 propagation prevention device.

[0011] The first inlet and the outlet end of the first refrigerant flow channel are further provided with a second branch, and the second branch and the first branch are distributed in parallel.

[0012] According to some embodiments of the present invention, the direct expansion dynamic ice slurry unit further includes an economizer, which has a first inner flow channel and a second inner flow channel that exchange heat with each other. The first inner flow channel is connected in series in the gas supply branch, and the second inner flow channel is connected in series between the outlet end of the first refrigerant flow channel and the first inlet.

[0013] 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.

[0014] According to some embodiments of the present invention, the direct expansion dynamic ice slurry unit is provided with a second expansion valve and / or a solenoid valve in the air replenishment branch.

[0015] According to some embodiments of the present invention, the direct expansion dynamic ice slurry unit further includes a regenerator, which includes a first regenerator channel and a second regenerator channel that exchange heat with each other. The first regenerator 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 regenerator channel is connected between the outlet end of the first cold water channel and the inlet end of the ice storage tank.

[0016] According to some embodiments of the present invention, in the direct expansion dynamic ice slurry unit, the flow direction of the first regenerating channel is opposite to that of the second regenerating channel.

[0017] 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 second condenser interface, the compressor is provided with a second compressor interface, and the compressor cooling circuit is connected between the second condenser interface and the second compressor interface.

[0018] According to some embodiments of the present invention, in the direct expansion dynamic ice slurry unit, a first filter is provided in the compressor cooling circuit.

[0019] According to some embodiments of the present invention, the compressor of the direct expansion dynamic ice slurry unit is configured as an oil-free compressor.

[0020] Additional aspects and advantages of this invention will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention. Attached Figure Description

[0021] The above and / or additional aspects and advantages of this utility model will become apparent and readily understood from the description of the embodiments taken in conjunction with the following drawings, in which:

[0022] Figure 1 This is a structural schematic diagram of a direct expansion dynamic ice slurry unit according to some embodiments of this utility model;

[0023] Figure 2 This is a structural schematic diagram of a direct expansion dynamic ice slurry unit according to other embodiments of this utility model;

[0024] Figure 3 This is a structural schematic diagram of a direct expansion dynamic ice slurry unit according to some embodiments of the present invention;

[0025] Figure 4 This is a structural schematic diagram of a direct expansion dynamic ice slurry unit according to some embodiments of the present invention.

[0026] Figure label:

[0027] 100 direct expansion dynamic ice slurry unit

[0028] Compressor 1, refrigerant flow path 11, compressor first interface 12, gas supply branch 13, second expansion valve 131, solenoid valve 132, compressor second interface 14, second check valve 15.

[0029] Condenser 2, condenser first inlet 21, condenser second inlet 22, third filter 23,

[0030] Cold water flow path 3, ice storage tank 31, ice pump 32, second filter 33, first check valve 34, differential pressure switch 35, crystallizer 36, flow meter 37.

[0031] Refrigerant subcooler 4, first refrigerant flow channel 41, first chilled water flow channel 42, first branch 43, third expansion valve 431, fourth expansion valve 432, second branch 44, economizer 441, first inner flow channel 4411, second inner flow channel 4412.

[0032] Subcooled water heat exchanger 5, second refrigerant flow channel 51, second cold water flow channel 52

[0033] Regenerator 6, first regenerating flow channel 61, second regenerating flow channel 62,

[0034] Gas-liquid separator 7, first inlet 71, first outlet 72, second inlet 73, second outlet 74.

[0035] De-icing branch 8, first expansion valve 81,

[0036] Anti-propagation device 9,

[0037] Compressor cooling circuit 101, first filter 1011, ice-melting pump 102, ice-melting heat exchanger 103.

[0038] Preheater 200. Detailed Implementation

[0039] The embodiments of this utility model are described in detail below. Examples of these embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain this utility model, and should not be construed as limiting this utility model.

[0040] In the description of this utility model, it should be understood that the terms "center," "longitudinal," "transverse," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," "counterclockwise," "axial," "radial," and "circumferential," etc., indicating the orientation or positional relationship shown in the accompanying drawings, are only for the convenience of describing this utility model and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this utility model. Furthermore, features defined with "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this utility model, unless otherwise stated, "a plurality of" means two or more.

[0041] In the description of this utility model, it should be noted that, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "joining" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection of two components. Those skilled in the art can understand the specific meaning of the above terms in this utility model based on the specific circumstances.

[0042] The following is for reference. Figure 1The direct expansion dynamic ice slurry unit 100 according to an embodiment of the present invention includes a refrigerant flow path 11, a compressor 1, and a condenser 2. The refrigerant flow path 11 is used for the flow of refrigerant, wherein the refrigerant can achieve the transfer of cooling and heating through the switching of its gaseous and liquid states during its flow within the refrigerant flow path 11. The compressor 1 is located in the refrigerant flow path 11 and can compress and transport the refrigerant in the refrigerant flow path 11. The compressor 1 has a first compressor interface 12 for the inflow of refrigerant. The condenser 2 is located in the refrigerant flow path 11, and its refrigerant inlet is connected to the outlet of the compressor 1. That is, the condenser 2 is connected to the outlet of the compressor 1, and the refrigerant compressed in the compressor 1 can enter the condenser 2 for cooling, thereby converting the compressed gaseous refrigerant into a liquid refrigerant.

[0043] like Figure 1 As shown, the direct expansion dynamic ice slurry unit 100 also includes a cold water flow path 3, in which cold water flows. The cold water flow path 3 is adapted to be connected 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. That is, cold water can enter the ice storage tank 31 from the cold water flow path 3, or it can enter the cold water flow path 3 from the ice storage tank 31 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.

[0044] like Figure 1 As shown, the direct expansion dynamic ice slurry unit 100 also includes a refrigerant subcooler 4. The refrigerant subcooler 4 includes a first refrigerant flow channel 41 and a first cold water flow channel 42 that exchange heat with each other. The first refrigerant flow channel 41 carries refrigerant, and the first cold water flow channel 42 carries cold water. The refrigerant and cold water exchange heat in the refrigerant subcooler 4. The temperature of the cold water is lower than the temperature of the refrigerant. The heating of the cold water and the cooling of the refrigerant are achieved through the heat exchange between the cold water and the refrigerant.

[0045] like Figure 1 As shown, the direct expansion dynamic ice slurry unit 100 also includes a subcooling water heat exchanger 5. The subcooling water heat exchanger 5 includes a second refrigerant flow channel 51 and a second cold water flow channel 52 that exchange heat with each other. The second refrigerant flow channel 51 carries refrigerant, and the second cold water flow channel 52 carries cold water. The refrigerant and cold water exchange heat in the subcooling water heat exchanger 5. The temperature of the cold water is higher than that of the refrigerant. The cooling of the cold water and the heating of the refrigerant are achieved through the heat exchange between the cold water and the refrigerant.

[0046] 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 channel 41 and a second refrigerant flow channel 51 connected in series. The first refrigerant flow channel 41 is connected to the refrigerant outlet end of the condenser 2, and the second refrigerant flow channel 51 is connected to the inlet end of the compressor 1. The compressor 1 and the condenser 2 are connected, forming a complete refrigerant flow path 11, realizing the connection between the compressor 1 and the condenser 2. In this way, through the cooperative use of the compressor 1 and the condenser 2, the refrigerant can circulate, and the pressure and temperature of the refrigerant can change during the flow.

[0047] The first cold water channel 42 and the second cold water channel 52 are connected in series in the cold water flow path 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 1 As shown, the cold water flow path 3 includes a first cold water flow channel 42 and a second cold water flow channel 52 connected in series. The first cold water flow channel 42 and the second cold water flow channel 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, which can complete the production of ice slurry in the circulation of cold water.

[0048] And such as Figure 1 As shown, compressor 1, condenser 2, refrigerant subcooler 4 and subcooled water heat exchanger 5 are connected in sequence through the first refrigerant flow channel 41 and the second refrigerant flow channel 51, respectively. Ice storage tank 31, refrigerant subcooler 4 and 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, which can form a direct expansion dynamic ice slurry unit 100.

[0049] like Figure 1 As shown, the direct expansion dynamic ice slurry unit 100 also includes a gas replenishment branch 13, in which refrigerant flows. The inlet end of the gas replenishment branch 13 is connected to the refrigerant outlet end of the condenser 2, and the outlet end of the gas replenishment branch 13 is connected to the first interface 12 of the compressor. That is to say, the gas replenishment branch 13 is connected between the condenser 2 and the compressor 1. The refrigerant produced by compression in the compressor 1 can enter the condenser 2 for cooling, so that the compressed gaseous refrigerant is converted into liquid refrigerant. After the refrigerant flows out of the condenser 2, part of the gaseous refrigerant formed enters the gas replenishment branch 13 and flows into the compressor 1 through the gas replenishment branch 13.

[0050] The direct expansion dynamic ice slurry chiller unit 100 is used to produce ice slurry and is connected to the user end to achieve cooling for the user. In actual application, after compression by the compressor 1, the gaseous refrigerant discharged by the compressor 1 is condensed into liquid refrigerant in the condenser 2. The refrigerant enters the refrigerant subcooler 4. At this time, the chilled water in the ice storage tank 31 enters the refrigerant subcooler 4 from the first chilled water flow channel 42. In the refrigerant subcooler 4, the refrigerant and chilled water exchange heat to heat the chilled water and further cool the condensed refrigerant. The refrigerant and chilled water exchange heat at the subcooled water heat exchanger 5 to cool the chilled water. In this way, the temperature of the refrigerant can be lower than the saturation temperature under the condensation pressure through the refrigerant subcooler 4, which greatly increases 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.

[0051] 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 needs to 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 through the condenser 2, and then send it into the subcooled water heat exchanger 5; or they draw 0°C water from the bottom of the ice storage tank 31, heat it electrically, and then send it into the subcooled water heat exchanger 5. Another method uses spray water onto the air-cooled condenser 2, first using the heat dissipated by the air-cooled condenser 2 to heat the spray water, and then using the spray water to preheat the water in the ice storage tank 31. While some of these methods consider the possibility of system energy recovery and lower the condensing temperature, they result in lower energy efficiency, and the use of electric heating to heat the cold water leads to energy waste. In this embodiment, the cold water is directly heated through the refrigerant subcooler 4, saving energy and achieving a high degree of subcooling, thus improving ice-making efficiency.

[0052] Furthermore, during production, power consumption is high during the day and low at night. The direct expansion dynamic ice slurry unit 100 produces ice slurry during off-peak electricity price periods at night, and concentrates the ice slurry in the ice storage tank 31. During peak-valley electricity price periods during the day, the direct expansion dynamic ice slurry unit 100 is shut down, and the ice stored in the ice storage tank 31 is used solely for supplying the user side. The direct expansion dynamic ice slurry unit 100 consumes the most power in the system. By producing ice at night, it can effectively alleviate the peak power demand during the daytime, playing a role in peak shifting and valley filling. This plays an important role in matching user demand with grid supply, and improves the economic efficiency of grid operation.

[0053] According to an embodiment of this utility model, 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 the chilled water from the ice storage tank 31, saving energy and achieving a high degree of subcooling, thus significantly improving cooling capacity and system energy efficiency. Furthermore, the produced ice slurry is stored in the ice storage tank 31 for immediate use by the user, reducing energy consumption during daytime ice slurry production and improving daytime user productivity. Furthermore, the gas replenishment branch 13 is connected between the refrigerant outlet end of the condenser 2 and the first interface 12 of the compressor, which allows the refrigerant at the outlet end of the condenser 2 to flow into the compressor 1, thereby replenishing the compressor 1 with gas, increasing the refrigerant flow rate in the compressor 1, and increasing the compression capacity of the compressor 1. In addition, the gas replenishment branch 13 between the condenser 2 and the compressor 1 can shorten the gas replenishment path and improve the efficiency of refrigerant flowing back to the compressor 1, so as to effectively improve the overall cooling capacity of the system.

[0054] In some embodiments, the direct expansion dynamic ice slurry chiller unit 100 further includes an economizer 441. The economizer 441 has a first inner flow channel 4411 and a second inner flow channel 4412 that exchange heat with each other. The first inner flow channel 4411 is connected in series in the make-up gas branch 13, and the second inner flow channel 4412 is connected in series between the refrigerant outlet end of the condenser 2 and the first refrigerant flow channel 41. The refrigerant subcooler 4 includes the first refrigerant flow channel 41, that is, as... Figure 2 As shown, the gas supply branch 13 is located between the condenser 2 and the refrigerant subcooler 4. Refrigerant flows through both the first inner flow channel 4411 and the second inner flow channel 4412. The liquid refrigerant flowing out from the refrigerant outlet end of the condenser 2 enters the first inner flow channel 4411 and the second inner flow channel 4412 respectively to exchange heat in the economizer 441.

[0055] The refrigerant in the first inner flow channel 4411 after heat exchange in the economizer 441 enters the gas replenishment branch 13, and the refrigerant in the gas replenishment branch 13 flows into the compressor 1 from the compressor's first interface 12, thereby replenishing the compressor 1 with gas to increase the refrigerant flow rate of the compressor 1 and thus increase the cooling capacity. Furthermore, the short path of the gas replenishment branch 13 can improve the gas replenishment efficiency of the compressor 1, thereby increasing the compression capacity of the compressor 1.

[0056] Furthermore, the refrigerant in the second inner channel 4412 after heat exchange in the economizer 441 enters the first refrigerant channel 41, which allows the refrigerant to exchange heat with the low-temperature water from the ice storage tank 31 in the refrigerant subcooler 4, greatly increasing the subcooling degree of the refrigerant circuit. Based on the refrigeration principle, the cooling capacity and energy efficiency of the refrigeration system can be significantly improved.

[0057] In some embodiments, the flow direction of the first inner channel 4411 is the same as that of the second inner channel 4412, so that the refrigerant in the first inner channel 4411 and the second inner channel 4412 flows in the same direction, and the refrigerant in the first inner channel 4411 and the second inner channel 4412 exchanges heat in the economizer 441.

[0058] The first inner flow channel 4411 and the second inner flow channel 4412 both flow from the condenser 2 to the refrigerant subcooler 4. However, the flow directions at the outlet ends of the first inner flow channel 4411 and the second inner flow channel 4412 are different. The refrigerant flowing out from the outlet end of the second inner flow channel 4412 flows to the refrigerant subcooler 4 to realize the circulation of refrigerant between the refrigerant subcooler 4, the subcooled water heat exchanger 5 and the compressor 1. The refrigerant flowing out from the outlet end of the first inner flow channel 4411 flows to the gas supply branch 13 and then directly flows to the compressor 1 to realize the gas supply to the compressor 1.

[0059] Therefore, by setting an economizer 441 in the refrigerant flow path 11 between the condenser 2 and the refrigerant subcooler, the subcooling degree of the refrigerant can be improved, and the gaseous refrigerant after heat exchange can be introduced into the gas supply branch 13. Its structure is reasonable and its function is clear.

[0060] In some embodiments, the inlet end of the supplementary gas branch 13 is connected between the refrigerant outlet end of the condenser 2 and the second inner flow channel 4412, that is, as Figure 2 As shown, the inlet end of the gas supply branch 13 is located between the condenser 2 and the economizer 441, and the first inner flow channel 4411 is connected in series with the gas supply branch 13. In this way, the gas supply branch 13 and the second inner flow channel 4412 can be distributed in parallel.

[0061] In this way, the refrigerant flowing out of the refrigerant outlet of the condenser 2 can be split, with one path flowing into the make-up gas branch 13 and the first inner flow channel 4411, and the other path flowing into the second inner flow channel 4412, so as to exchange heat in the economizer 441.

[0062] Therefore, by splitting the refrigerant flow path 11 at the outlet end of the condenser 3, the refrigerant in the two split paths exchanges heat in the economizer 441, which can improve the subcooling of the refrigerant and allow the gaseous refrigerant after heat exchange to be introduced into the gas supply branch 13. Its structure is reasonable and will not add too many branch settings, which can make the overall layout of the direct expansion dynamic ice slurry unit 100 simpler and the function clearer.

[0063] In some embodiments, the direct expansion dynamic ice slurry unit 100 further includes a gas-liquid separator 7, which has a first inlet 71, a first outlet 72, a second inlet 73 and a second outlet 74. 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.

[0064] Among them, the gas-liquid separator 7 is used for the separation of gas and liquid. For example... Figure 1 As shown, the gas-liquid separator 7 can be installed between the subcooled water heat exchanger 5 and the compressor 1. The gas-liquid separator 7 has 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 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 refrigerant reflux.

[0065] Therefore, during the operation of the direct expansion dynamic slurry chiller unit 100, the refrigerant absorbs heat in the subcooled water heat exchanger 5 and becomes gaseous, while releasing heat in the condenser 2 and becoming liquid. During this cycle, various factors (such as changes in pipeline pressure and uneven refrigerant flow) may cause the formation of a gas-liquid mixture. Liquid refrigerant is incompressible; if it enters the compressor 1, it will cause a sharp increase in internal pressure, resulting in "liquid slugging" and damaging the compressor 1. The gas-liquid separator 7 ensures that only pure gaseous refrigerant enters the compressor 1, protecting it from damage. Furthermore, the gas-liquid separator 7 retains liquid refrigerant, allowing only gaseous refrigerant to enter the compressor 1 for compression. This reduces the power consumption of the compressor 1 and improves the efficiency and stability of the entire refrigeration system.

[0066] Furthermore, the gas-liquid separator 7 is also provided with a second inlet 73 and a second outlet 74. The second outlet 74 is connected to the inlet end of the second refrigerant flow channel 51, and the second inlet 73 is connected to the outlet end of the second refrigerant flow channel 51.

[0067] like Figure 1As shown, the gas-liquid separator 7 can be installed between the subcooled water heat exchanger 5 and the compressor 1. The gas-liquid separator 7 has a second inlet 73 and a second outlet 74. The second inlet 73 and the second outlet 74 are used for the inflow and outflow of refrigerant, respectively. The gas-liquid separator 7 is connected to the second refrigerant flow channel 51 through the second outlet 74, and the outlet end of the second refrigerant flow channel 51 is connected to the gas-liquid separator 7 through the second inlet 73. This allows the gas-liquid separator 7 to be connected to the subcooled water heat exchanger 5. In this way, after the refrigerant in the gas-liquid separator 7 is separated into gas and liquid, the liquid refrigerant flows into the subcooled water heat exchanger 5 from the second outlet 74. When the refrigerant and water exchange heat in the subcooled water heat exchanger 5, the refrigerant absorbs heat and becomes gaseous. The gaseous refrigerant can enter the gas-liquid separator 7 from the second inlet 73. After separation by the gas-liquid separator 7, the gaseous refrigerant flows into the compressor 1 from the first outlet 72 to realize the refrigerant return and thus realize the circulation of refrigerant.

[0068] Therefore, through the above configuration, the refrigerant can first be separated into gas and liquid in the gas-liquid separator 7, and then the liquid refrigerant can be transported to the subcooling water heat exchanger 5 to improve the heat exchange efficiency in the subcooling water heat exchanger 5. Furthermore, the refrigerant that has undergone heat exchange in the subcooling water heat exchanger 5 can re-enter the gas-liquid separator 7 for separation, which can prevent the liquid mixed in the refrigerant from entering the compressor 1, thereby ensuring the stable operation of the compressor 1 and improving the stability and reliability of the ice-making process.

[0069] In some embodiments, the first inlet 71 and the second outlet 74 are located at the lower part of the gas-liquid separator 7, and the second inlet 73 and the first outlet 72 are located at the upper part of the gas-liquid separator 7.

[0070] Thus, the first inlet 71 and the second outlet 74 are located at the lower part of the gas-liquid separator 7, which allows the outlet end of the first refrigerant flow channel 41 and the inlet end of the second refrigerant flow channel 51 to be connected to the lower part of the gas-liquid separator 7 respectively, thereby allowing the refrigerant in the first refrigerant flow channel 41 to flow into the gas-liquid separator 7 from the lower part of the gas-liquid separator 7. The second inlet 73 and the first outlet 72 are located at the upper part of the gas-liquid separator 7, which allows the outlet end of the second refrigerant flow channel 51 to be connected to the upper part of the gas-liquid separator 7.

[0071] The liquid refrigerant enters the gas-liquid separator 7 from the bottom. Through the separation action of the gas-liquid separator 7, the gaseous refrigerant mixed in with the liquid refrigerant is separated out. The gaseous refrigerant flows upwards, while the liquid refrigerant flows downwards. The liquid refrigerant flows out from the bottom of the gas-liquid separator 7 due to gravity, improving the flow efficiency of the liquid refrigerant. During heat exchange in the subcooling water heat exchanger 5, the liquid refrigerant absorbs heat and becomes gaseous. The gaseous refrigerant flows into the gas-liquid separator 7 from the top. Through the separation action of the gas-liquid separator 7, the liquid refrigerant mixed in with the gaseous refrigerant is separated out, and the resulting pure gaseous refrigerant flows into the compressor 1 from the top of the gas-liquid separator 7. The entire process has a good gas-liquid separation effect, thus improving the overall ice-making efficiency.

[0072] Among them, such as Figure 1 As shown, the first inlet 71 and the second outlet 74 are spaced apart and distributed at the lower part of the gas-liquid separator 7, and the second inlet 73 and the first outlet 72 are spaced apart and distributed at the upper part of the gas-liquid separator 7. This allows the refrigerant flowing into and out of the gas-liquid separator 7 to 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.

[0073] In some embodiments, the direct expansion dynamic ice slurry unit 100 further includes an anti-propagation device 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 anti-propagation device 9.

[0074] In this way, the flow path between the outlet end of the second cold water channel 52 and the inlet end of the ice storage tank 31 is filled with cold water. The cold water has a low temperature and is prone to freezing. The first branch 43 carries refrigerant, whose temperature is higher than that of the cold water. This allows the cold water and refrigerant to exchange heat at the anti-propagation device 9, thereby raising the temperature of the cold water. By using the heat of the refrigerant to heat the cold water, rather than external electric heating, energy savings are maximized, resulting in maximum benefits and lower costs.

[0075] Therefore, by heating the outlet end of the second cold water channel 52 through the anti-propagation device 9, the propagation of ice crystals between the outlet end of the second cold water channel 52 and the inlet end of the ice storage tank 31 and the subcooled water heat exchanger 5 can be blocked, thereby preventing the subcooled water heat exchanger 5 from freezing and blocking, and reducing the risk of freezing and cracking the pipeline, so as to ensure the safety of the pipeline and the subcooled water heat exchanger 5, and improve the stability and reliability of ice making.

[0076] Among them, such as Figure 1As shown, the anti-propagation device 9 is located at the outlet end of the subcooled water heat exchanger 5. At least a portion of the first branch 43 is located within the anti-propagation device 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 setting the first branch 43 between the first refrigerant flow channel 41 and the first inlet 71, the reverse propagation of ice crystals is prevented. Its structure is simple, its layout is reasonable, and its pipe connections are convenient.

[0077] In some embodiments, a second branch 44 is provided between the first inlet 71 and the outlet end of the first refrigerant channel 41, and the second branch 44 is distributed in parallel with the first branch 43.

[0078] like Figure 1 As shown, the inlet end of the second branch 44 is connected to the outlet end of the first refrigerant channel 41, and the outlet end of the second branch 44 is connected to the first inlet 71. The first refrigerant 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 connected in parallel between the first refrigerant channel 41 and the gas-liquid separator 7, which can divide the refrigerant in the first refrigerant channel 41 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 subcooled 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.

[0079] Therefore, by setting the first branch 43 and the second branch 44 in parallel between the first refrigerant flow channel 41 and the gas-liquid separator 7, different functions can be achieved respectively. Moreover, the refrigerants of the first branch 43 and the second branch 44 do not affect each other. The refrigerant delivery of the anti-propagation device 9 can be achieved through the first branch 43, and the refrigerant delivery speed of the gas-liquid separator 7 can be met through the second branch 44, which improves the efficiency and reliability of ice making. It can also be compatible with multiple heat exchange requirements of the direct expansion dynamic ice slurry unit 100, and the pipeline distribution is clear and reasonable, making maintenance more convenient.

[0080] The first branch 43 is equipped with a third expansion valve 431, which acts as the on / off valve for the first branch 43. It can connect and close the first branch 43 with the first refrigerant channel 41. In actual operation, when the third expansion valve 431 is opened, the refrigerant in the first refrigerant 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 channel 52 and the inlet end of the ice storage tank 31 at the anti-propagation device 9. After ice making is completed, the third expansion valve 431 is closed to stop the supply of refrigerant to the first branch 43.

[0081] Furthermore, the third expansion valve 431 has a throttling and pressure-reducing function, which can reduce the high-pressure refrigerant to a low-pressure mist or wet vapor state. In this way, the low-pressure refrigerant enters the anti-propagation device 9 to meet the heat exchange requirements with the chilled water. Moreover, the opening degree of the first expansion valve 81 is adjustable, which can control the flow rate and pressure of the refrigerant entering the anti-propagation device 9 to ensure the heat exchange within the anti-propagation device 9.

[0082] The third expansion valve 431 can be located at any position in the first branch 43.

[0083] In other embodiments, such as 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 the on / off valve between the first branch 43 and the gas-liquid separator 7, enabling the connection and closure of the first branch 43 and the gas-liquid separator 7. Thus, during actual operation, when the fourth expansion valve 432 is opened, the refrigerant from 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 the supply of refrigerant to the gas-liquid separator 7.

[0084] Furthermore, the fourth expansion valve 432 has a throttling and pressure-reducing function, which can reduce the high-pressure refrigerant to a low-pressure mist or wet vapor state. In this way, the low-pressure refrigerant enters the gas-liquid separator 7 for gas and liquid separation.

[0085] The fourth expansion valve 432 can be located at any position between the first branch 43 and / or the second branch 44 and the first inlet 71.

[0086] In some embodiments, the direct expansion dynamic ice slurry chiller 100 further includes an economizer 441, which has a first inner flow channel 4411 and a second inner flow channel 4412 that exchange heat with each other. The first inner flow channel 4411 is connected in series in the gas supply branch 13, and the second inner flow channel 4412 is connected in series between the outlet end of the first refrigerant flow channel 41 and the first inlet 71. The refrigerant subcooler 4 includes the first refrigerant flow channel 41, that is, as... Figure 1 As shown, the economizer 441 is located at the outlet end of the refrigerant subcooler 4, and the gas supply branch 13 is located at the outlet end of the refrigerant subcooler 4. Refrigerant flows through both the first inner flow channel 4411 and the second inner flow channel 4412. The liquid refrigerant flowing out from the outlet end of the refrigerant subcooler 4 enters the first inner flow channel 4411 and the second inner flow channel 4412 respectively to exchange heat in the economizer 441.

[0087] The refrigerant in the first inner flow channel 4411 after heat exchange in the economizer 441 enters the gas replenishment branch 13, and the refrigerant in the gas replenishment branch 13 flows into the compressor 1 from the compressor's first interface 12, thereby replenishing the compressor 1 with gas to increase the refrigerant flow rate of the compressor 1 and thus increase the cooling capacity. Furthermore, the short path of the gas replenishment branch 13 can improve the gas replenishment efficiency of the compressor 1, thereby increasing the compression capacity of the compressor 1.

[0088] Furthermore, the refrigerant in the second inner channel 4412 after heat exchange in the economizer 441 flows to the first inlet 71 and then into the gas-liquid separator 7 to complete the subsequent work.

[0089] Therefore, by setting an economizer 441 at the outlet of the refrigerant subcooler 4, the refrigerant after heat exchange in the refrigerant subcooler 4 can be split into two paths to exchange heat again in the economizer 441, which greatly increases the subcooling of the refrigerant circuit. According to the refrigeration principle, the cooling capacity and energy efficiency of the refrigeration system can be significantly improved.

[0090] Furthermore, the economizer 441 may not be installed in the refrigerant flow path 11, such as... Figure 3 and Figure 4 As shown, compressor 1 does not have a gas supply branch 13, so that after the refrigerant is condensed into liquid refrigerant in condenser 2, it only exchanges heat with low temperature water from ice storage tank 31 through refrigerant subcooler 4 to obtain a large degree of subcooling, which can also improve the system's cooling performance.

[0091] In some embodiments, the direct expansion dynamic ice slurry unit 100 further 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.

[0092] In other words, an ice-melting branch 8 can be set up to connect the condenser 2 and the second refrigerant channel 51. Refrigerant flows through the ice-melting branch 8, and the first interface 21 of the condenser is used for the discharge of refrigerant. The refrigerant in the condenser 2 flows into the second refrigerant channel 51 through the ice-melting branch 8. The temperature of the refrigerant flowing out of the condenser 2 is relatively high, which can make the second refrigerant channel 51 contain high-temperature refrigerant, which can heat the interior of the second refrigerant channel 51 and the subcooled water heat exchanger 5.

[0093] Therefore, in actual operation, when the subcooled water heat exchanger 5 becomes blocked by ice, the ice-melting branch 8 can be connected to the second refrigerant channel 51. The high-temperature refrigerant can then heat the subcooled water heat exchanger 5, thus melting the ice. By setting up the ice-melting branch 8, ice blockage in the subcooled water heat exchanger 5 can be avoided, maintaining the normal flow rate of the second cold water channel 52 and / or the second refrigerant channel 51 within the subcooled water heat exchanger 5, resulting in high ice-making efficiency and a more stable ice-making process.

[0094] In some embodiments, the ice-melting branch 8 is provided with a first expansion valve 81. The first expansion valve 81 serves as the on / off valve of the ice-melting branch 8, enabling the connection and closure of the ice-melting branch 8 and the second refrigerant flow channel 51. Thus, after the subcooling water heat exchanger 5 becomes blocked by ice, the first expansion valve 81 is opened to allow refrigerant to flow into the second refrigerant flow channel 51 and the subcooling water heat exchanger 5. After the ice-melting of the subcooling water heat exchanger 5 is completed, the first expansion valve 81 is closed to stop the supply of refrigerant to the second refrigerant flow channel 51 and the subcooling water heat exchanger 5. The switching is flexible and can be selectively connected according to actual needs, making it more convenient to use.

[0095] Furthermore, the first expansion valve 81 has a throttling and pressure-reducing function, which can reduce the high-pressure refrigerant to a low-pressure mist or wet vapor state. This low-pressure refrigerant then enters the second refrigerant channel 51 and the subcooling water heat exchanger 5, absorbing heat from the surroundings to melt the ice in the subcooling water heat exchanger 5. The opening degree of the first expansion valve 81 is adjustable, allowing control of the refrigerant flow rate and pressure entering the subcooling water heat exchanger 5. Appropriate refrigerant flow rate and pressure ensure uniform and rapid melting of the ice layer.

[0096] The first expansion valve 81 can be located at any position in the ice melting branch 8.

[0097] In some embodiments, the air supply branch 13 is provided with a second expansion valve 131 and / or a solenoid valve 132. The air supply branch 13 may be provided with only the second expansion valve 131, or it may be provided with both the second expansion valve 131 and the solenoid valve 132. The arrangement is not limited and can be flexibly selected.

[0098] The solenoid valve 132 controls the opening and closing of the gas supply branch 13, automatically opening or closing according to system needs to achieve automated control of the refrigeration system and improve system operating efficiency and stability. The solenoid valve 132 precisely controls the refrigerant flow, ensuring the correct path of the refrigerant in the refrigeration cycle. By controlling the refrigerant flow and pressure, the solenoid valve 132 prevents overload operation or low-pressure abnormalities in the refrigeration system, thus protecting the refrigeration equipment from damage. Furthermore, the second expansion valve 131 has a throttling and pressure-reducing function, lowering the high-pressure refrigerant to a low-pressure mist or wet vapor state, creating conditions for refrigerant evaporation. By controlling the refrigerant flow, it ensures that the refrigerant entering the compressor 1 is entirely gaseous, avoiding liquid slugging of the compressor 1 and ensuring high safety for the compressor 1.

[0099] like Figure 1 and Figure 2 As shown, the refrigerant supply branch 13 is equipped with a second expansion valve 131 and a solenoid valve 132. Through the coordinated action of the second expansion valve 131 and the solenoid valve 132, the flow rate and pressure of the refrigerant can be precisely controlled, ensuring that the refrigeration system can operate in optimal condition, thereby improving the refrigeration effect. The automatic control function of the solenoid valve 132 can ensure that the refrigeration system can operate stably 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 can increase the flexibility of the refrigeration system, enabling it to adapt to different working environments and needs.

[0100] The refrigerant in the gas replenishment branch 13 and the refrigerant in the second branch 44 exchange heat in the economizer 441 and are converted into gaseous refrigerant, which then enters the compressor 1 to replenish gas and increase the cooling capacity.

[0101] In some embodiments, the direct expansion dynamic ice slurry unit 100 further includes a regenerator 6, which includes a first regenerator channel 61 and a second regenerator channel 62 that exchange heat with each other. The first regenerator 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 regenerator 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.

[0102] The regenerator 6 is located between the ice storage tank 31 and the refrigerant subcooler 4. The regenerator 6 includes a first regenerating channel 61 and a second regenerating channel 62 that exchange heat with each other. The first regenerating channel 61, the first cold water channel 42 and the second regenerating channel 62 are connected sequentially between the outlet end and the inlet end of the ice storage tank 31.

[0103] The regenerator 6 is used for reheating cold water. In practical applications, the water in the ice storage tank 31 can be preheated to 0.2-0.5℃ through the regenerator 6, and then further heated to 0.5-1℃ by exchanging heat with the refrigerant from the condenser 2. This can completely eliminate ice crystals (ice crystals are an important medium for the transformation of subcooled water into ice, and eliminating ice crystals can make subcooled water less likely to freeze). Then it enters the subcooled water heat exchanger 5, and exchanges heat with the refrigerant in the second refrigerant flow channel 51 of the subcooled water heat exchanger 5 to obtain subcooled water at 0.2-0℃. Finally, it flows into the ice storage tank 31 from the inlet end of the ice storage tank 31 for storage.

[0104] 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 system ice blockage, thus improving the system's ice-making stability. Furthermore, using a separate regenerator 6 for heat exchange with the refrigerant from the refrigeration system can improve the system's subcooling degree. The regenerator 6 and the refrigeration system can form a self-contained design, resulting in greater energy savings and eliminating the need to consume or control external heat sources. This also leads to a simpler structure and lower cost.

[0105] And, in some embodiments, such as Figure 3 As shown, a preheater 200 is provided between the outlet end of the first cold water flow channel 42 and the inlet end of the second regenerated flow channel 62. The preheater 200 is suitable for connection to an external heat source. The external heat source includes high-temperature cold water, unit cooling water, and other external heating sources.

[0106] This allows the cooling water entering the second heat return channel 62 to be heated, thereby increasing the temperature of the cooling water in the second heat return channel 62, which further helps to eliminate ice crystals and improve the subcooling of the system.

[0107] In some embodiments, the flow direction of the first reheating channel 61 is opposite to that of the second reheating channel 62. This allows the water in the first reheating channel 61 and the second reheating channel 62 to flow in opposite directions, and the water in the first reheating channel 61 and the second reheating channel 62 exchanges heat within the regenerator 6, thereby achieving water preheating.

[0108] The first reheating channel 61 flows from the ice storage tank 31 to the refrigerant subcooler 4, while the second reheating channel 62 flows from the refrigerant subcooler 4 to the ice storage tank 31. Water flowing out of the ice storage tank 31 enters the first reheating channel 61 for preheating, at which point the water temperature is 0.2-0.5℃. The water then enters the first cold water channel 42 and passes through the refrigerant subcooler 4, where it is heated again to 0.5-1℃. The heated water then flows back into the second reheating channel 62 to exchange heat with the low-temperature water in the first reheating channel 61, thus lowering the water temperature and maintaining it within the range of 0.3-0.5℃. This improves the smoothness of the water transport process and enhances the stability of ice making.

[0109] Therefore, through the above settings, the water that has been heated after exchanging heat with the refrigerant in the refrigerant subcooler 4 can flow back to the regenerator 6 after its temperature has risen. This allows for continuous and stable preheating of the water in the first regenerating channel 61 of the regenerator 6, reducing the heat exchange energy consumption of the regenerator 6. Furthermore, the reverse flow ensures that the water temperature will not be too high, which is beneficial for improving the subsequent ice-making efficiency.

[0110] Furthermore, the direct expansion dynamic ice slurry unit 100 may not require the regenerator 6, such as... Figure 2 and Figure 4 As shown, this configuration 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℃ and achieving a very high degree of subcooling.

[0111] In some embodiments, the direct expansion dynamic ice slurry unit 100 further 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.

[0112] like Figure 1 and Figure 2 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, which can realize the connection of the cooling circuits of the compressor 1 and the condenser 2. 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.

[0113] In actual operation, the refrigerant or cooling medium in the condenser 2 flows from the second interface 22 of the condenser into the compressor cooling circuit 101, and then flows through the compressor cooling circuit 101 to the second interface 14 of the compressor, and then flows into the compressor 1 through the second interface 14 of the compressor, which can cool and lower the temperature of the space of the compressor 1 to maintain the temperature stability of the compressor 1.

[0114] Furthermore, the direct expansion dynamic ice slurry unit 100 may not require a compressor cooling circuit 101, such as... Figure 3 and Figure 4 As shown, this method is applicable to situations where the compressor 1 has a small compression capacity and the temperature of the compressor 1 is within a relatively stable range, so the compressor cooling circuit 101 is not required to cool the compressor 1.

[0115] In some embodiments, a first filter 1011 is provided in the compressor cooling circuit 101. The first filter 1011 has a filtering function, which can filter and intercept impurities such as solid particles, metal shavings, and rust contained in the cooling medium in the compressor cooling circuit 101, so as to keep the cooling medium flowing into the compressor 1 clean. This ensures the smooth flow of the cooling medium in the system, maintains continuous and stable cooling of the compressor 1, and reduces the risk of pipe blockage and heat exchanger scaling, thereby improving cooling efficiency and ice-making efficiency. Furthermore, through filtration, the cooling medium can be purified, reducing the content of oil, water, and other contaminants, ensuring the quality and performance of the cooling medium. Clean cooling medium 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, the compressor is configured as an oil-free compressor. The oil-free compressor does not contain lubricating oil, which can prevent oil-mixed refrigerant from flowing into the condenser and prevent oil from seeping into the condenser, thus reducing energy loss and improving the heat exchange efficiency of the unit. Moreover, the absence of lubricating oil saves on the installation of oil circuits, fundamentally eliminating oil accumulation in the condenser, reducing maintenance costs and workload. Furthermore, without oil interference, temperature control is more stable and the production of ice slurry is smoother.

[0117] In this system, compressor 1 is typically a screw compressor or scroll compressor. To maintain stable operation, lubricating oil is unavoidable. On one hand, oil affects heat exchange in the heat exchanger; on the other hand, the formation of dynamic ice requires stable temperature control, and oil accumulation leads to changes in the heat exchange temperature difference, thus affecting the continuous and stable production of dynamic ice slurry. Generally, complex oil return devices, such as oil separators and return circuits, are required in the system. Because the heat exchanger operates under complex variable conditions, flow rates and pressures are often not constant. These oil return devices cannot maintain a consistently good oil return state, further exacerbating the increase in heat exchange temperature difference, affecting stable ice slurry production, and in more severe cases, causing compressor 1 to be damaged due to oil shortage. In this embodiment, compressor 1 is an oil-free compressor, eliminating the need for complex oil return system components in the refrigeration system and preventing oil accumulation in the heat exchanger. This fundamentally eliminates the problem of oil accumulation in the condenser or pipelines, which causes fluctuations in heat exchange temperature and hinders continuous ice slurry production, thereby improving the efficiency and stability of ice slurry production.

[0118] In some embodiments, the hydraulic system is a magnetic levitation variable frequency centrifuge, an air suspension variable frequency centrifuge, or a liquid suspension variable frequency centrifuge.

[0119] Among them, magnetic levitation variable frequency centrifuges, air-suspended variable frequency centrifuges, and liquid-suspended variable frequency centrifuges all have gas compression capabilities. They work on the refrigerant gas through a high-speed rotating impeller, increasing the gas's pressure and flow rate. Then, the flow rate is reduced in the diffuser, the pressure continues to increase, and the gas is discharged from the volute and enters the condenser 2. Magnetic levitation variable frequency centrifuges utilize magnetic levitation technology, eliminating mechanical contact and friction during compressor 1 operation, thus improving energy efficiency and reducing maintenance costs. Air-suspended variable frequency centrifuges utilize air suspension technology, enabling compressor 1 to operate without friction, reducing energy loss. Liquid-suspended variable frequency centrifuges (or positive pressure liquid-float variable frequency centrifuges) are mainly used for material classification and purification, but in some designs, they can also be used for refrigerant compression. Furthermore, combined with variable frequency technology, the compressor 1's speed can be automatically adjusted according to actual refrigeration or compression requirements.

[0120] Therefore, the oil-free compressor setup can utilize any one of the following: magnetic levitation variable frequency centrifuge, air-suspended variable frequency centrifuge, or liquid-suspended variable frequency centrifuge. All three types can achieve refrigerant compression and delivery, offering diverse setup options for flexible selection. Furthermore, the magnetic levitation bearings in all three types of oil-free compressors require no lubrication, preventing oil seepage into the heat exchanger, reducing energy loss, and improving unit efficiency. The elimination of lubrication saves on oil circuitry, reducing maintenance costs and workload. Moreover, the absence of oil interference results in more stable temperature control and smoother ice slurry production.

[0121] In some embodiments, an ice-making pump 32 is 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 through a pipeline to the inlet end of the first cold water channel 42, so that it can enter the ice-making system for ice making.

[0122] Therefore, by installing an ice-making pump 32 at the outlet of the ice storage tank 31, the ice-making pump 32, as a power source, can drive the ice slurry to circulate in the system, realizing the transportation from the ice storage tank 31 to the ice-making system. The ice-making pump 32 can quickly extract the ice slurry from the ice storage tank 31 and transport it to the ice-making system, accelerating the ice slurry preparation process and improving ice-making efficiency. Furthermore, through precise control of the ice-making pump 32, it can be ensured that parameters such as the flow rate, pressure, and temperature of the ice slurry in the system are maintained within the set range, thereby guaranteeing the stable operation of the system.

[0123] Furthermore, 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.

[0124] In actual production, when ice slurry is needed, the ice melting pump 102 is turned off, and the compressor 1, condenser 2, and ice pump 32 are turned on to make ice. When used by the user, the ice melting pump 102 is turned on. After ice making is completed, the compressor 1, condenser 2, and ice pump 32 are turned off. The low-temperature water at 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 at 7°C or lower. In this way, the low-temperature water in the ice storage tank 31 is recycled for use by the user side.

[0125] In some embodiments, a second filter 33 and / or a first check valve 34 connected in series with the ice pump 32 are provided between the inlet end of the first cold water channel 42 and the outlet end of the ice storage tank 31.

[0126] The second filter 33, installed in the pipeline between the inlet of the first cold water channel 42 and the outlet of the ice storage tank 31, filters and intercepts impurities such as solid particles, metal fragments, and rust in the low-temperature water of the ice storage tank 31. This maintains the cleanliness of the water flowing into the first cold water channel 42, ensuring smooth flow of cold water in the system, reducing the risk of pipe blockage and heat exchanger scaling, thereby improving cooling and ice-making efficiency. Furthermore, the filtration process purifies 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, thus improving the quality and stability of the ice slurry. Clean cold water also reduces wear and corrosion of equipment components, extending the service life of the entire ice-making system and its related equipment.

[0127] Furthermore, the first check valve 34 has the function of opening and closing the pipeline. The first check valve 34 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. 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 pump 32 stops working or the system malfunctions, the cold water or ice slurry will not flow back into the ice storage tank 31, avoiding system chaos or damage, thereby maintaining the stability and safety of the system. The first check valve 34 helps to maintain the pressure stability in the system and prevent pressure fluctuations caused by backflow.

[0128] Thus, through the synergistic action of the second filter 33 and / or the first check valve 34, the cold water or ice slurry entering the first cold water channel 42 is ensured to be clean and free of impurities, and backflow of cold water is prevented and system pressure is maintained, thereby improving the quality and stability of the ice slurry.

[0129] 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, which can filter and intercept impurities such as solid particles, metal shavings, and rust contained in the refrigerant flowing out of the condenser 2, so as 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, thereby improving cooling efficiency and ice-making efficiency. Moreover, through the filtering function, the refrigerant can be purified, reducing the content of oil, water and other contaminants, ensuring the quality and performance of the refrigerant. Furthermore, clean refrigerant can reduce the wear and corrosion of equipment components, thereby extending the service life of the entire ice-making system and its related equipment.

[0130] In some embodiments, the cold water flow path 3 is further provided with a differential pressure switch 35 connected in parallel with the second cold water flow path 52, such as Figure 1 As shown, the differential pressure switch 35 is connected to the inlet and outlet ends of the second cold water flow channel 52 of the subcooled water heat exchanger 5, so that the differential pressure switch 35 can be connected in parallel to the outside of the subcooled water heat exchanger 5. The differential pressure switch 35 can detect the pressure difference between the two ends of the second cold water flow channel 52 in the cold water flow path 3 to determine the water flow rate.

[0131] In practical applications, when the water flow rate is lower than the set threshold, the water-side pressure difference will decrease, and the differential pressure switch 35 will be triggered. When the water flow rate is insufficient, the water in the subcooled 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 differential pressure switch 35, the water temperature in the subcooled water heat exchanger 5 can be prevented from being too low, thus avoiding damage to the subcooled water heat exchanger 5 caused by water freezing and expansion.

[0132] Therefore, through the monitoring and control of the differential pressure switch 35, measures can be taken in time when the water flow is insufficient to prevent the water inside the subcooled water heat exchanger 5 from freezing, thereby effectively preventing the heat exchanger from freezing and cracking, and thus more effectively protecting the subcooled water heat exchanger 5.

[0133] In some embodiments, a second check valve 15 is provided between the refrigerant inlet end of the condenser 2 and the outlet end of the compressor 1. The second check valve 15 has the function of opening and closing the pipeline, that is, through the action of the second check valve 15, the compressor 1 can be connected to the condenser 2, and the compressor 1 can be disconnected 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, and ensures that when the direct expansion dynamic ice slurry unit 100 stops working or the system malfunctions, the second check valve 15 will prevent the refrigerant from flowing back to the compressor 1.

[0134] Therefore, through the unidirectional 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 into the compressor 1. This can avoid abnormal pressure rise or even damage to the compressor 1 due to refrigerant flowing back into the compressor 1, and can also prevent liquid slugging caused by refrigerant backflow, 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.

[0135] In other embodiments, a crystal promoter 36 is provided between the outlet end of the second cold water channel 52 and the inlet end of the ice storage tank 31, such as... Figure 1 As shown, the crystal promoter 36 is located between the anti-propagation device 9 and the inlet end 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 end of the second cold water channel 52 can flow into the crystal promoter 36, which can quickly form ice crystals in the supercooled water, and the formed ice crystals are transported to the ice storage tank 31 for storage.

[0136] Thus, through the efficient operation of the crystallizer 36, the entire direct expansion dynamic ice slurry unit 100 can operate more stably. The crystallizer 36 not only improves the ice crystal generation efficiency, but also prevents ice crystal backflow and blockage through the anti-propagation device 9, ensuring the long-term stable operation of the system.

[0137] In some 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 flow rate of cold water in the pipe. By setting the flow meter 37 between the first cold water channel 42 and the second cold water channel 52, the flow rate of cold water can be measured in real time, which helps operators understand the flow of water in the system.

[0138] The flow meter 37 can prevent damage to the equipment caused by insufficient or excessive flow. For example, insufficient flow may cause the subcooled water heat exchanger 5 to freeze, while excessive flow may increase the load on the equipment. Furthermore, the flow meter 37 can be used for fault diagnosis. If the flow rate changes suddenly or abnormally, it may indicate a blockage, leak, or other problem in the system. Monitoring with the flow meter 37 allows these problems to be detected and resolved promptly.

[0139] Therefore, the direct expansion dynamic ice slurry unit 100 can be equipped with both differential pressure switch 35 and flow meter 37, or only differential pressure switch 35, to determine ice blockage in the subcooled water heat exchanger 5, saving costs and ensuring high reliability in determining ice blockage.

[0140] In some embodiments, the condenser 2 is configured as a water-cooled condenser, an air-cooled condenser, or an evaporative cooling condenser. That is, the condenser 2 can be configured as a water-cooled condenser, or the condenser 2 can be configured as an air-cooled condenser, or the condenser 2 can be configured as an evaporative cooling condenser. All three different condensers 2 can achieve condensation and cooling of the refrigerant. The type of compressor 1 is not limited to whether it is a multi-stage compressor or not. Its configuration is diverse and can be flexibly selected.

[0141] Among them, water-cooled condensers use cooling water to cool and lower the temperature of the refrigerant, achieving water cooling of the refrigerant; air-cooled condensers use air to cool and lower the temperature of the refrigerant, achieving air cooling of the refrigerant; and evaporative cooling condensers use the evaporation of water to cool and lower the temperature of the refrigerant.

[0142] This invention also proposes a dynamic ice slurry system.

[0143] The dynamic ice slurry system according to the embodiments of this utility model includes a direct expansion dynamic ice slurry unit 100 as described 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 needs of ice slurry production. The direct expansion dynamic ice slurry unit 100 can produce ice slurry by using a compressor 1, a condenser 2, a refrigerant subcooler 4, and a subcooled water heat exchanger 5 in cooperation. The ice slurry is stored in an ice storage tank 31 for users to use at any time. This reduces the energy consumption for ice slurry production during the day, thereby improving the production efficiency of users during the day. The compressor 1 is an oil-free compressor, which reduces the complex oil return system components in the direct expansion dynamic ice slurry unit 100 and fundamentally eliminates oil accumulation in the heat exchanger, thereby reducing heat exchange temperature fluctuations and improving the efficiency and stability of ice slurry production.

[0144] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "illustrative embodiment," "example," "specific example," or "some examples," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of the present invention. In this specification, the illustrative expressions 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 one or more embodiments or examples.

[0145] Although embodiments of the present invention have been shown and described, those skilled in the art will understand that various changes, modifications, substitutions and alterations can be made to these embodiments without departing from the principles and spirit of the present invention, the scope of which is defined by the claims and their equivalents.

Claims

1. A direct expansion dynamic ice slurry unit, characterized in that, include: refrigerant flow path; The compressor is located in the refrigerant flow path and has a first compressor interface; A condenser is provided in the refrigerant flow path, and the refrigerant inlet end of the condenser is connected to the outlet end of the compressor; A cold water flow path, wherein the cold water flow path is adapted to be connected to an ice storage tank; A refrigerant subcooler, the refrigerant subcooler comprising a first refrigerant flow channel and a first cold water flow channel that exchange heat with each other; A subcooled water heat exchanger includes a second refrigerant flow channel and a second cold water flow channel that exchange heat with each other. 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. The gas supply branch has its inlet end connected to the refrigerant outlet end of the condenser, and its outlet end connected to the first interface of the compressor.

2. The direct expansion dynamic ice slurry unit according to claim 1, characterized in that, It also includes an economizer, which has a first inner flow channel and a second inner flow channel that exchange heat with each other. The first inner flow channel is connected in series in the gas supply branch, and the second inner flow channel is connected in series between the refrigerant outlet end of the condenser and the first refrigerant flow channel.

3. The direct expansion dynamic ice slurry unit according to claim 2, characterized in that, The flow direction of the first inner channel is the same as that of the second inner channel.

4. The direct expansion dynamic ice slurry unit according to claim 2, characterized in that, The inlet end of the gas supply branch is connected between the refrigerant outlet end of the condenser and the second inner flow channel.

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

6. The direct expansion dynamic ice slurry unit according to claim 5, characterized in that, It also includes an anti-propagation device, and a first branch is provided between the first inlet and the outlet end of the first refrigerant flow channel. 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 anti-propagation device.

7. The direct expansion dynamic ice slurry unit according to claim 6, characterized in that, A second branch is provided between the first inlet and the outlet of the first refrigerant flow channel, and the second branch is distributed in parallel with the first branch.

8. The direct expansion dynamic ice slurry unit according to claim 7, characterized in that, It also includes an economizer, which has a first inner flow channel and a second inner flow channel that exchange heat with each other. The first inner flow channel is connected in series in the gas supply branch, and the second inner flow channel is connected in series between the outlet end of the first refrigerant flow channel and the first inlet.

9. 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.

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

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