Supercooled water dynamic ice slurry unit

Abstract

The utility model discloses a supercooled water dynamic ice slurry unit which comprises a main circulation loop, a water side loop and a bearing lubrication flow path, a compressor, a condenser and an evaporator are arranged in the main circulation loop, a driving motor is arranged in the compressor, and a motor bearing is installed on the driving motor; an anti-spreading device, a crystallization promoting device and an ice storage tank are arranged in the water side loop; the crystallization promoting device is used for generating ice slurry from cooling water and then introducing the ice slurry into the ice storage tank; the bearing lubricating flow path is communicated with the condenser, so that at least part of refrigerant in the condenser enters the bearing lubricating flow path, and the refrigerant in the bearing lubricating flow path is suitable for flowing back to a motor bearing in the compressor after heat exchange with the water side loop through the anti-spreading device. Refrigerant in the bearing lubrication flow path exchanges heat with cold water of the water side loop, the problem that the cold water spreads towards the evaporator after being crystallized is solved, the refrigerant in the bearing lubrication flow path can lubricate a motor bearing in the compressor, and cavitation caused by refrigerant gasification to the motor bearing can be prevented after the refrigerant is supercooled.

Description

Technical Field

[0001] This utility model relates to the field of cold storage system technology, and in particular to a subcooled water dynamic ice slurry unit. Background Technology

[0002] Currently, in the process of making ice slurry in the crystallizer, the cooling water of the subcooled water dynamic ice slurry unit is prone to ice crystal propagation in the subcooled water crystallization pipeline, which can block the pipeline or even freeze the evaporator. It is necessary to install corresponding pipeline equipment on the water supply pipe wall for heating and melting crystals, which consumes heat.

[0003] However, electric heating increases system power consumption, and when cooling water from the condenser is introduced for heating, the water quality is generally poor, which can easily cause blockages in the heating pipes. If refrigerant from the condenser is used for heating alone, it will cause a loss of cooling capacity in the system. Therefore, there is room for improvement in how to reduce ice crystal propagation and prevent the evaporator from freezing. Utility Model Content

[0004] This invention aims to solve at least one of the technical problems existing in the prior art. To this end, this invention proposes a subcooled water dynamic ice slurry unit. After flowing out of the condenser, the refrigerant flows into the bearing lubrication path. The refrigerant in the bearing lubrication path exchanges heat with the cold water in the water-side circuit, reducing the problem of cold water crystallization spreading towards the evaporator. Furthermore, the refrigerant in the bearing lubrication path lubricates the motor bearings in the compressor, preventing refrigerant vaporization and cavitation of the motor bearings after subcooling.

[0005] According to an embodiment of the present invention, a subcooled water dynamic ice slurry unit includes: a main circulation loop, a water-side loop, and a bearing lubrication flow path. The main circulation loop is provided with a compressor, a condenser, and an evaporator arranged in series. The compressor is equipped with a drive motor, and the drive motor is fitted with a motor bearing. The water-side loop is provided with an anti-propagation device, a crystallizer, and an ice storage tank arranged in series. The crystallizer is used to generate ice slurry from cooling water and then pass it into the ice storage tank. The bearing lubrication flow path is connected to the condenser, and at least a portion of the refrigerant in the condenser enters the bearing lubrication flow path. The refrigerant entering the bearing lubrication flow path is adapted to exchange heat with the water-side loop through the anti-propagation device and then flow back to the motor bearing in the compressor.

[0006] According to the subcooled water dynamic ice slurry unit of this utility model embodiment, when the refrigerant lubricates the motor bearings inside the compressor, the refrigerant needs to have a certain degree of subcooling to prevent refrigerant vaporization from causing cavitation on the motor bearings. Cavitation may corrode the surface of the motor bearings, leading to wear, scratches, or pitting. Simultaneously, heat exchange between the bearing lubrication flow path and the water-side circuit is achieved through an anti-propagation device, increasing the subcooling of the refrigerant in the bearing lubrication flow path and avoiding cavitation on the motor bearings. This provides better lubrication for the motor bearings. At the same time, the water-side circuit absorbs the heat from the refrigerant in the bearing lubrication flow path, thereby reducing the problem of cold water crystallization spreading towards the evaporator in the water-side circuit.

[0007] According to an embodiment of the present invention, a subcooled water dynamic ice slurry unit is provided with a first temperature sensor at the inlet of the anti-propagation device and a second temperature sensor at the outlet. The first temperature sensor is located between the anti-propagation device and the evaporator, and the second temperature sensor is located between the anti-propagation device and the crystallizer. A regulating valve is provided in the bearing lubrication flow path between the condenser and the anti-propagation device, and the regulating valve regulates the flow rate of the refrigerant according to the temperature difference between the first temperature sensor and the second temperature sensor.

[0008] According to the embodiment of the present invention, the subcooled water dynamic ice slurry unit has an ice storage tank with a water outlet and an ice slurry inlet, and the water outlet is lower than the height of the ice slurry inlet.

[0009] According to the embodiment of the present invention, the subcooled water dynamic ice slurry unit has a first side flow path and a second side flow path inside the evaporator that can exchange heat with each other. The first side flow path is connected to the water side circuit, and the second side flow path is connected to the main circulation circuit.

[0010] According to an embodiment of the present invention, a subcooled water dynamic ice slurry unit further includes a gas-liquid separator, which has at least two inlets and at least two outlets; the outlet of the condenser is connected to one inlet of the gas-liquid separator, and one outlet of the gas-liquid separator is connected to the inlet of the second side flow path of the evaporator, so that after the refrigerant exchanges heat with the water-side circuit, it flows through the outlet of the second side flow path to the other inlet of the gas-liquid separator, and the other outlet of the gas-liquid separator is connected to the inlet of the compressor.

[0011] According to the embodiment of the present invention, in the subcooled water dynamic ice slurry unit, the height of the gas-liquid separator is higher than the height of the evaporator, so that the liquid in the gas-liquid separator flows to the bottom of the evaporator, and the gas in the evaporator flows from the top to the gas-liquid separator, and from the gas-liquid separator to the compressor.

[0012] According to an embodiment of the present invention, the subcooled water dynamic ice slurry unit further includes a return pipeline, through which the refrigerant cooling the motor bearing in the compressor can flow to the gas-liquid separator.

[0013] According to an embodiment of the present invention, the subcooled water dynamic ice slurry unit includes a first pipeline and a second pipeline. The first pipeline and the second pipeline are connected in parallel, and the inlets of the first pipeline and the second pipeline are connected to the outlet of the condenser. After passing through the anti-propagation device, the flow is directed to the motor bearing inside the compressor. The first pipeline is equipped with a third check valve, and the second pipeline is equipped with a refrigerant pump.

[0014] According to the embodiment of the present invention, in the subcooled water dynamic ice slurry unit, a third pipeline is connected in parallel at both ends of the second pipeline, and the third pipeline is equipped with a pressure reducing valve.

[0015] According to an embodiment of the present invention, the subcooled water dynamic ice slurry unit is provided with a fourth filter and a fifth filter in the bearing lubrication flow path. The fifth filter is located between the outlet of the condenser and the anti-propagation device, and the fourth filter is located between the anti-propagation device and the compressor.

[0016] 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

[0017] 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:

[0018] Figure 1 This is a schematic diagram illustrating the basic principle of the subcooled water dynamic ice slurry unit according to an embodiment of this utility model;

[0019] Figure 2 This is a schematic diagram illustrating the principle of adding a temperature difference monitoring device at the anti-propagation device to the subcooled water dynamic ice slurry unit according to an embodiment of this utility model.

[0020] Figure label:

[0021] 100 subcooled water dynamic ice slurry unit

[0022] Water-side circuit 1, anti-propagation device 11, crystallizer 12, ice storage tank 13, ice slurry inlet 131, water outlet 132, first filter 14, ice pump 15, first check valve 16, second filter 17, first temperature sensor 18, second temperature sensor 19, main circulation circuit 2, compressor 21, condenser 22, first condensate outlet 221, second condensate outlet 222, water outlet 223, water inlet 224, gas-liquid separator 23, first outlet 231, first inlet 232, second outlet 233, and so on. Second inlet 234, third inlet 235, evaporator 24, first side flow path 241, second side flow path 242, return pipe 25, expansion valve 26, second check valve 27, third filter 28, bearing lubrication flow path 3, first pipe 31, third check valve 311, second pipe 32, fourth check valve 321, refrigerant pump 322, third pipe 33, pressure reducing valve 331, fourth filter 34, regulating valve 35, pressure sensor 36, third temperature sensor 37, flow sensor 38, fifth filter 39. Detailed Implementation

[0023] 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.

[0024] 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.

[0025] 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.

[0026] Before describing the embodiments of this utility model, it is necessary to understand that in the industrial field, electricity consumption often accounts for a large proportion of operating costs, and under the current situation of tight electricity supply during peak hours, there may also be power rationing problems. Making reasonable use of peak and off-peak electricity prices is a good solution, and ice storage chiller units have emerged under such circumstances.

[0027] In many industrial sectors, such as the food industry, clean chilled water is often required for production and processing. Compared with the traditional indirect refrigeration static ice solution, a new cold storage system for producing dynamic ice from subcooled water has emerged in recent years. This cold storage system differs from the traditional method of generating static ice. It utilizes the characteristic that clean water will not freeze at zero degrees Celsius. It first produces subcooled water and then generates dynamic ice slurry through a crystallizer 12 for cold storage. This cold storage method produces clean water, and the evaporation temperature of the chiller unit is higher than that of traditional ice storage units, resulting in higher energy efficiency and higher melting efficiency of dynamic ice. It can continuously supply constant-temperature chilled water for a long time, making it an energy-saving, efficient, and pollution-free new technology.

[0028] The following is for reference. Figures 1-2 According to the embodiment of the present invention, in the subcooled water dynamic ice slurry unit 100, the refrigerant flows from the condenser 22 to the bearing lubrication flow path 3. The refrigerant in the bearing lubrication flow path 3 exchanges heat with the cold water in the water-side circuit 1, which can avoid the problem of cold water crystallizing and spreading towards the evaporator 24. In addition, the refrigerant in the bearing lubrication flow path 3 can lubricate the motor bearing of the drive motor in the compressor 21, so that after the refrigerant is subcooled, it prevents the refrigerant from vaporizing and causing cavitation on the motor bearing.

[0029] like Figures 1-2 As shown, a subcooled water dynamic ice slurry unit 100 according to an embodiment of the present invention includes: a main circulation loop 2, a water-side loop 1, and a bearing lubrication flow path 3.

[0030] The main circulation loop 2 is equipped with a compressor 21, a condenser 22 and an evaporator 24 distributed in series. The compressor 21 is equipped with a drive motor and a motor bearing. The motor bearing can support the rotor of the drive motor in the compressor 21, so that the rotor of the drive motor can rotate relative to the stator, ensuring that the compressor 21 can operate normally, thereby realizing the cooling or heating function of the air conditioner.

[0031] The high-temperature, high-pressure gaseous refrigerant in the compressor 21 flows into the condenser 22, where it exchanges heat with the cooling water and condenses into liquid refrigerant. After passing through the third filter 28, it continues to pass through the throttling device, such as the second expansion valve 26, and flows towards the evaporator 24. In other words, the liquid refrigerant is delivered to the evaporator 24, either indirectly or directly. The evaporator 24 absorbs heat, thereby achieving a cooling effect.

[0032] In addition, the water-side circuit 1 is equipped with a series-distributed anti-propagation device 11, a crystallizer 12, and an ice storage tank 13. The crystallizer 12 is used to generate ice slurry from the cooling water and then pass it into the ice storage tank 13. The bearing lubrication flow path 3 is connected to the condenser 22, and at least part of the refrigerant in the condenser 22 enters the bearing lubrication flow path 3. The refrigerant entering the bearing lubrication flow path 3 is suitable to exchange heat with the water-side circuit 1 through the anti-propagation device 11 and then flow back to the motor bearing in the compressor 21.

[0033] Specifically, the crystallizer 12 is used to generate ice slurry from cooling water and then introduce it into the ice storage tank 13. (Refer to...) Figure 1 As shown, the cooling water in the water-side loop 1 flows to the first check valve 16 and the second filter 17 under the action of the ice pump 15. The first check valve 16 allows the cooling water to flow in one direction only, and after filtration, it flows to the anti-propagation device 11, the crystallizer 12, and the ice storage tank 13. The water in the ice storage tank 13 then flows to the first filter 14, and after filtration, it flows to the ice pump 15, realizing cyclic ice making. The anti-propagation device 11 in the water-side loop 1 is actually equivalent to a heat exchanger, and it can exchange heat with the bearing lubrication flow path 3. The crystallizer 12 in the water-side loop 1 can cause the cooling water to crystallize and generate a mixture of dynamic ice slurry and water, which enters the ice storage tank 13 for cold storage. That is, the refrigerant in the condenser 22 flows to the motor bearing of the drive motor in the compressor 21 through the bearing lubrication flow path 3, realizing the lubrication of the motor bearing by the refrigerant.

[0034] When the refrigerant lubricates the motor bearings inside the compressor 21, the refrigerant needs to have a certain degree of subcooling to prevent refrigerant vaporization from causing cavitation on the motor bearings. Cavitation may corrode the surface of the motor bearings, leading to wear, scratches, or pitting. The bearing lubrication flow path 3 and the water-side circuit 1 exchange heat through the anti-propagation device 11, which reduces the temperature of the refrigerant in the bearing lubrication flow path 3, thus providing better lubrication for the motor bearings and preventing cavitation. At the same time, the water-side circuit 1 also absorbs the heat of the refrigerant in the bearing lubrication flow path 3, thereby reducing the problem of cold water crystallization spreading towards the evaporator 24 in the water-side circuit 1. Compared with the traditional heating method for heating the water-side circuit 1, this saves system power consumption.

[0035] In some embodiments, a first temperature sensor 18 is provided at the inlet of the anti-propagation device 11, and a second temperature sensor 19 is provided at the outlet. The first temperature sensor 18 is located between the anti-propagation device 11 and the evaporator 24, and the second temperature sensor 19 is located between the anti-propagation device 11 and the crystallizer 12. The bearing lubrication flow path 3 is provided with a regulating valve 35 between the condenser 22 and the anti-propagation device 11. The regulating valve 35 regulates the refrigerant flow rate according to the temperature difference between the first temperature sensor 18 and the second temperature sensor 19.

[0036] Reference Figure 2 As shown, after the cooling water of the water-side circuit 1 flows out of the evaporator 24, before the cold water flows to the anti-propagation device 11, the temperature of the cold water flowing to the anti-propagation device 11 is measured by the first temperature sensor 18. After the refrigerant exchanges heat with the water-side circuit 1 at the anti-propagation device 11, before the cold water of the water-side circuit 1 flows out of the anti-propagation device 11 and flows to the crystallizer 12, the temperature of the cold water after heat exchange is measured by the second temperature sensor 19. By measuring the water temperature at the inlet and outlet of the anti-propagation device 11, if the temperature difference is too large, the regulating valve 3 of the bearing lubrication flow path 3 is opened. 5. The regulating valve 35 is an electric regulating valve. In addition, the bearing lubrication flow path 3 is also equipped with a pressure sensor 36, a third temperature sensor 37 and a flow sensor 38. The third temperature sensor 37 senses the temperature of the refrigerant that is about to enter the compressor 21. At this time, the opening of the regulating valve 35 can be controlled according to the temperature difference between the first temperature sensor 18 and the second temperature sensor 19 on both sides of the anti-propagation device 11 and the flow rate displayed by the flow sensor 38. Under the premise that the flow rate meets the requirements, if the water temperature difference is too large, the refrigerant flow rate will be reduced, and if the temperature difference is too small, the refrigerant flow rate will be increased.

[0037] In other words, when the temperature difference is too large, reducing the refrigerant flow rate can prevent the temperature of the cold water and refrigerant in the water-side circuit 1 from becoming too high after heat exchange, which could lead to the failure of cold storage or the loss of cold energy. At the same time, when the temperature difference is too small, the refrigerant flow rate can be appropriately increased to avoid insufficient heat exchange, so that the refrigerant can effectively cool down, reduce the cavitation problem of the refrigerant on the motor bearing, facilitate better lubrication of the motor bearing, and effectively prevent the spread of ice crystals.

[0038] Furthermore, by placing the first temperature sensor 18 between the anti-propagation device 11 and the evaporator 24, and the second temperature sensor 19 between the anti-propagation device 11 and the crystallizer 12, the temperature at both ends of the anti-propagation device 11 can be measured more accurately, avoiding the problem of poor temperature accuracy caused by the first temperature sensor 18 and the second temperature sensor 19 being too far away from the anti-propagation device 11.

[0039] In some embodiments, the ice storage tank 13 is provided with a water outlet 132 and an ice slurry inlet 131, with the water outlet 132 being lower than the height of the ice slurry inlet 131.

[0040] In practice, the water outlet 132 is located at the bottom of the ice storage tank 13, and the ice slurry inlet 131 is located at the top of the ice storage tank 13. The water outlet 132 is lower than the ice slurry inlet 131. The supercooled water passes through the anti-propagation device 11 and then enters the crystallizer 12. Under the action of the crystallizer 12, crystallization generates a mixture of dynamic ice slurry and water, which enters the ice storage tank 13. In the ice storage tank 13, the ice slurry floats on top of the ice storage tank 13 due to its low density. The water flows to the bottom of the ice storage tank 13 and flows out of the ice storage tank 13 through the water outlet 132. After passing through the first filter 14, it enters the ice-making pump 15 to form a cycle. Therefore, by setting the position of the water outlet 132 lower than the position of the ice slurry inlet 131, the circulation of the water-side loop 1 can be better realized, and the function of ice storage can be achieved.

[0041] In some embodiments, the evaporator 24 is provided with a first side flow path 241 and a second side flow path 242 that can exchange heat with each other. The first side flow path 241 is connected to the water side loop 1, and the second side flow path 242 is connected to the main circulation loop 2.

[0042] Combination Figure 1 and Figure 2As shown, the cold water in the water-side loop 1 flows through the first side flow path 241 in the evaporator 24 to the anti-propagation device 11 and the crystallizer 12. Under the action of the crystallizer 12, it forms ice water and flows to the ice storage tank 13. At the same time, the refrigerant in the main circulation loop 2 flows to the second side flow path 242 in the evaporator 24. After the refrigerant in the second side flow path 242 exchanges heat with the cold water in the first side flow path 241, the refrigerant absorbs the heat of the cold water, thereby further reducing the temperature of the cold water and turning it into subcooled water below zero degrees. The subcooled water enters the crystallizer 12 after passing through the anti-propagation device 11, which further promotes the formation of ice slurry in the subcooled water, which is beneficial for cold storage. At the same time, a refrigeration cycle is formed between the evaporator 24, the compressor 21 and the condenser 22.

[0043] Furthermore, both the first side flow path 241 and the second side flow path 242 can be curved S-shaped flow paths. The design of the S-shaped flow path can improve the fluid flow state, reduce vortices and backflow phenomena, thereby making the fluid flow more stable. This reduces the vortices and backflow that may occur in the fluid in the straight pipe, improving heat transfer efficiency. Moreover, the S-shaped flow path increases the length of the first side flow path 241 and the second side flow path in a limited space, thereby effectively expanding the heat exchange area in a limited space and improving heat exchange efficiency.

[0044] In some embodiments, the subcooled water dynamic ice slurry unit 100 further includes a gas-liquid separator 23, which has at least two inlets and at least two outlets; the outlet of the condenser 22 is connected to one inlet of the gas-liquid separator 23, and one outlet of the gas-liquid separator 23 is connected to the inlet of the second side flow path 242 of the evaporator 24, so that after the refrigerant exchanges heat with the water-side circuit 1, it flows through the outlet of the second side flow path 242 to the other inlet of the gas-liquid separator 23, and the other outlet of the gas-liquid separator 23 is connected to the inlet of the compressor 21.

[0045] Specifically, the gas-liquid separator 23 is located between the condenser 22 and the evaporator 24. The gas-liquid separator 23 has a first outlet 231, a first inlet 232, a second outlet 233, a second inlet 234, and a third inlet 235. The refrigerant outlets of the condenser 22 include a first condensation outlet 221 and a second condensation outlet 222. The refrigerant flowing out of the first condensation outlet 221 passes through the third filter 28 and the expansion valve 26 before entering the second inlet 234 of the gas-liquid separator 23. After flowing out of the first outlet 231, the refrigerant flows to the second side flow path 242 of the evaporator 24, and then flows out of the second side flow path 242 before entering the first inlet 232 of the gas-liquid separator 23. After gas and liquid separation, the gaseous refrigerant flows from the second outlet 233 of the gas-liquid separator 23 to the compressor 21, thus realizing the refrigeration cycle. A second check valve 27 is provided between the outlet of the compressor 21 and the inlet of the condenser 22 to achieve unidirectional flow of the refrigerant and prevent backflow or self-circulation.

[0046] In addition, the refrigerant flowing out of the first condensing outlet 221 of the condenser 22 can pass through the bearing lubrication flow path 3, and after heat exchange between the anti-propagation device 11 and the water-side circuit 1, the refrigerant flows to the motor bearing in the compressor 21 to lubricate the motor bearing.

[0047] In some embodiments, the height of the gas-liquid separator 23 is higher than the height of the evaporator 24, so that the liquid in the gas-liquid separator 23 flows to the bottom of the evaporator 24, and the gas in the evaporator 24 flows from the top to the gas-liquid separator 23 and from the gas-liquid separator 23 to the compressor 21.

[0048] In practice, after the refrigerant in the main circulation loop 2 flows to the gas-liquid separator 23, the gas and liquid are separated after passing through the gas-liquid separator 23. An expansion valve 26 is also provided between the second condensation outlet 222 of the condenser 22 in the main circulation loop 2 and the second inlet 234 of the gas-liquid separator 23. The expansion valve 26 controls the flow rate and pressure of the refrigerant according to the temperature change of the refrigerant. The refrigerant in the gas-liquid separator 23 flows through the first outlet 231 to the bottom of the second side flow path 242 of the evaporator 24. Since the height of the gas-liquid separator 23 is higher than the height of the evaporator 24, the liquid in the gas-liquid separator 23 flows to the bottom of the evaporator 24 by gravity and exchanges heat with the water from the ice storage tank 13. At least part of the refrigerant becomes a low-temperature and low-pressure refrigerant gas and returns to the upper part of the gas-liquid separator 23, and then enters the compressor 21 from the upper part of the gas-liquid separator 23, forming one cycle of the main circulation loop 2.

[0049] Therefore, by setting the height of the gas-liquid separator 23 higher than that of the evaporator 24, the liquid refrigerant can be made to flow from the gas-liquid separator 23 to the bottom of the evaporator 24 by gravity. This eliminates the need for a pump between the evaporator 24 and the gas-liquid separator 23 and facilitates the separation of gas and liquid.

[0050] In some embodiments, the subcooled water dynamic ice slurry unit 100 further includes a return line 25, through which the refrigerant cooling the motor bearing in the compressor 21 can flow to the gas-liquid separator 23.

[0051] In this process, the refrigerant in the bearing lubrication flow path 3 flows to the motor bearing in the compressor 21 to lubricate it. Some of the gas-liquid mixture of refrigerant then flows through the return pipe 25 to the third inlet 235 of the gas-liquid separator 23. After the gas is separated by the gas-liquid separator 23, the gas enters the compressor 21 for the next cycle. It should be noted that the refrigerant entering the compressor 21 and the refrigerant used to lubricate the motor bearing are two separate refrigerants. For example, the refrigerant used to lubricate the motor bearing may be liquid, while the refrigerant entering the compressor 21 for refrigeration circulation may be gaseous. Therefore, by returning the refrigerant used for bearing lubrication to the gas-liquid separator 23, the refrigerant can be effectively utilized and circulated.

[0052] In some embodiments, the bearing lubrication flow path 3 includes a first pipe 31 and a second pipe 32, which are connected in parallel. The inlets of the first pipe 31 and the second pipe 32 are connected to the outlet of the condenser 22, and after passing through the anti-propagation device 11, they flow to the motor bearing inside the compressor 21. The first pipe 31 is provided with a third check valve 311, and the second pipe 32 is provided with a refrigerant pump 322.

[0053] For example, condenser 22 has a first condenser outlet 221, a second condenser outlet 222, a water outlet 223, and a water inlet 224. Heat exchange occurs between the refrigerant in condenser 22 and the chilled water in the water tower (not shown). The flow direction of the cooling water at water outlet 223 and water inlet 224 is... Figure 1 and Figure 2 As shown by the two scissors on the right side of the condenser 22, the cold water from the water tower enters the condenser 22 from the inlet 224 and flows out of the condenser 22 from the outlet 223 back to the water tower, thus realizing heat exchange between the refrigerant and the cooling water.

[0054] In this system, the refrigerant flowing from the first condenser outlet 221 of the condenser 22 simultaneously flows to both the first pipe 31 and the second pipe 32. The first pipe 31 is equipped with a third check valve 311 to achieve unidirectional refrigerant flow. The second pipe 32 is connected in parallel with the first pipe 31, and is equipped with a refrigerant pump 322 and a fourth check valve 321. This allows the refrigerant to flow from the refrigerant pump 322 to the fourth check valve 321, achieving unidirectional refrigerant flow. Initially, the refrigerant can be powered by turning on the refrigerant pump 322 to allow the refrigerant to flow from the condenser 22 to the first pipe 31 and the second pipe 32. Pipeline 31 and pipeline 32 flow together to the anti-propagation device 11 and then to the motor bearing in the compressor 21 for lubrication. The refrigerant can also flow back from the motor bearing in the compressor 21 to the gas-liquid separator 23. After establishing a normal refrigerant flow path, since the pressure difference between the condenser 22 and the gas-liquid separator 23 has been established, the refrigerant pump 322 can be turned off, allowing the refrigerant to flow from the first pipeline 31. This reduces the working time of the refrigerant pump 322, reduces dependence on the refrigerant pump 322, and makes the refrigerant pump 322 less prone to failure. The pressure difference liquid supply is more reliable, saving electricity and energy.

[0055] In addition, it should be noted that when the aforementioned regulating valve 35 is adjusting the flow rate, it can cooperate with the refrigerant pump 322 to jointly regulate the flow rate in the bearing lubrication path 3.

[0056] In some embodiments, a third pipeline 33 is connected in parallel to both ends of the second pipeline 32, and the third pipeline 33 is provided with a pressure reducing valve 331.

[0057] Among them, the pressure reducing valve 331 of the third pipeline 33 can be understood as an unloading valve or a bypass valve. Its main function is to prevent the refrigerant pump 322 from burning out when the refrigerant pump 322 is stuck. The second pipeline 32 where the refrigerant pump 322 is located is connected in parallel with the third pipeline 33 where the pressure reducing valve 331 is located, so that the pressure reducing valve 331 is pushed open to form a passage and realize the self-circulation of the refrigerant pump 322.

[0058] In some embodiments, the bearing lubrication flow path 3 is provided with a fourth filter 34 and a fifth filter 39. The fifth filter 39 is located between the outlet of the condenser 22 and the anti-propagation device 11, and the fourth filter 34 is located between the anti-propagation device 11 and the compressor 21.

[0059] Specifically, after the refrigerant flows from the condenser 22 to the bearing lubrication path 3, it first passes through the fifth filter 39 to prevent impurities from entering the anti-propagation device 11. Impurities can wear down the pipe wall as they flow through the pipe, reducing the strength and service life of the pipe material. Impurities may also accumulate in the pipe, reducing the flow cross-sectional area and causing other problems. Therefore, the refrigerant is filtered first. After the refrigerant exchanges heat with the water-side circuit 1 through the anti-propagation device 11, the refrigerant flows out and passes through the fourth filter 34 for filtration again. This results in higher purity refrigerant entering the motor bearing of the compressor 21, preventing impurities from affecting the motor bearing of the compressor 21.

[0060] 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.

[0061] 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 supercooled water dynamic ice slurry machine characterized by, include: The main circulation loop includes a compressor, a condenser, and an evaporator connected in series. The compressor contains a drive motor, and the drive motor is equipped with a motor bearing. The water-side circuit includes a series-distributed anti-propagation device, a crystal promoter, and an ice storage tank. The crystal promoter is used to generate ice slurry from the cooling water and then introduce it into the ice storage tank. A bearing lubrication flow path is provided, which is connected to the condenser and allows at least a portion of the refrigerant in the condenser to enter the bearing lubrication flow path. The refrigerant entering the bearing lubrication flow path is adapted to exchange heat with the water-side circuit through the anti-propagation device and then flow back to the motor bearing in the compressor.

2. The subcooled water dynamic ice slurry machine set according to claim 1, characterized in that, The anti-propagation device is equipped with a first temperature sensor at its inlet and a second temperature sensor at its outlet. The first temperature sensor is located between the anti-propagation device and the evaporator, and the second temperature sensor is located between the anti-propagation device and the crystallizer. The bearing lubrication path is provided with a regulating valve between the condenser and the anti-propagation device. The regulating valve adjusts the flow rate of the refrigerant according to the temperature difference between the first temperature sensor and the second temperature sensor.

3. The subcooled water dynamic ice slurry machine set according to claim 1, characterized in that, The ice storage tank is provided with a water outlet and an ice slurry inlet, and the water outlet is lower than the height of the ice slurry inlet.

4. The subcooled water dynamic ice slurry machine set according to claim 1, characterized in that, The evaporator is equipped with a first side flow path and a second side flow path that can exchange heat with each other. The first side flow path is connected to the water side loop, and the second side flow path is connected to the main circulation loop.

5. The subcooled water dynamic ice slurry machine set according to claim 4, characterized in that, It also includes a gas-liquid separator, which has at least two inlets and at least two outlets; The outlet of the condenser is connected to one inlet of the gas-liquid separator, and one outlet of the gas-liquid separator is connected to the inlet of the second side flow path of the evaporator, so that after the refrigerant exchanges heat with the water-side circuit, it flows through the outlet of the second side flow path to the other inlet of the gas-liquid separator, and the other outlet of the gas-liquid separator is connected to the inlet of the compressor.

6. The subcooled water dynamic ice slurry machine set according to claim 5, characterized in that, The height of the gas-liquid separator is higher than the height of the evaporator, so that the liquid in the gas-liquid separator flows to the bottom of the evaporator, and the gas in the evaporator flows from the top to the gas-liquid separator and from the gas-liquid separator to the compressor.

7. The subcooled water dynamic ice slurry machine set according to claim 5, characterized in that, It also includes a return pipeline, through which the refrigerant cooling the motor bearing in the compressor can flow to the gas-liquid separator.

8. The subcooled water dynamic ice slurry machine set according to claim 1, characterized in that, The bearing lubrication flow path includes a first pipeline and a second pipeline, which are connected in parallel. The inlets of the first pipeline and the second pipeline are connected to the outlet of the condenser, and after passing through the anti-propagation device, the flow is directed to the motor bearing inside the compressor. The first pipeline is equipped with a third check valve, and the second pipeline is equipped with a refrigerant pump.

9. The subcooled water dynamic ice slurry machine set according to claim 8, characterized in that, A third pipeline is connected in parallel to both ends of the second pipeline, and the third pipeline is equipped with a pressure reducing valve.

10. The subcooled water dynamic ice slurry machine set according to claim 1, characterized in that, The bearing lubrication flow path is provided with a fourth filter and a fifth filter. The fifth filter is located between the outlet of the condenser and the anti-propagation device, and the fourth filter is located between the anti-propagation device and the compressor.

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