Liquid supply mechanism, cooling system and liquid supply control method

Abstract

The invention relates to the technical field of cooling systems, in particular to a liquid supply mechanism, a cooling system and a liquid supply control method.The liquid supply mechanism is applied to the cooling system, the cooling system comprises a refrigeration host, the liquid supply mechanism comprises a cooling pipe network and a gas-liquid separator, and the cooling pipe network comprises a liquid inlet header pipe, cooling branch pipes and a liquid return header pipe which communicate with one another; the cooling branch pipe is used for cooling the heating unit; the liquid return header pipe is connected with the liquid inlet end of the refrigeration host; the gas-liquid separator is arranged at the liquid outlet end of the refrigeration main machine, and a liquid state area located at the bottom and a gas state area located above the liquid state area are arranged in the gas-liquid separator. Wherein the input end of the liquid inlet header pipe is communicated with the liquid state area of the gas-liquid separator, the liquid supply mechanism improves the uniformity of refrigerant distribution to all the heating units, and then the cooling effect on the heating units is improved.

Description

Technical Field

[0001] The present application relates to the technical field of cooling systems, and in particular to a liquid supply mechanism, a cooling system and a liquid supply control method. Background Art

[0002] Liquid refrigerant evaporates into gas, and the heat absorption of phase change is more than ten times that of single-phase heat exchange with the same mass flow rate, which is an efficient cooling solution for high-power heating equipment. Since high-power heating equipment may have large and fast changes in heat load, the traditional compressor refrigeration cycle solution may have liquid in the return air, resulting in liquid shock damage to the compressor. The fluorine pump refrigeration solution is a new two-phase refrigeration method.

[0003] In the fluorine pump refrigeration system, after the refrigerant is condensed into liquid in the heat exchanger, it is transported to the heating unit through the refrigerant pump (fluorine pump). The refrigerant absorbs heat and evaporates in the internal flow channel of the heating unit. The evaporated refrigerant flows into the heat exchanger under the action of pressure difference and condenses into liquid refrigerant in the heat exchanger. This reciprocating process realizes cyclic refrigeration.

[0004] Two-phase cooling systems are usually high-power systems that use modular combinations. The refrigerant needs to be evenly distributed to the heating units that need to be cooled. If the distribution is uneven, some heating units may have too much liquid distribution, resulting in waste, and some heating units may not be cooled enough, resulting in overheating and burning. Summary of the invention

[0005] The purpose of the present application is to provide a liquid supply mechanism, a cooling system and a liquid supply control method, wherein the liquid supply mechanism improves the uniformity of distributing refrigerant to each heating unit, thereby improving the cooling effect on the heating unit.

[0006] To this end, an embodiment of the present application provides a liquid supply mechanism, which is applied to a cooling system. The cooling system includes a refrigeration main unit, and the liquid supply mechanism includes: a cooling pipe network, the cooling pipe network includes a connected liquid inlet main pipe, a cooling branch pipe and a liquid return main pipe, the cooling branch pipe is used to cool the heating unit, and the liquid return main pipe is connected to the liquid inlet end of the refrigeration main unit; and a gas-liquid separator, which is arranged at the liquid outlet end of the refrigeration main unit, and the gas-liquid separator is provided with a liquid area located at the bottom and a gas area located above the liquid area; wherein the input end of the liquid inlet main pipe is connected to the liquid area of ​​the gas-liquid separator.

[0007] In a possible implementation, an exhaust pipeline communicating with the gaseous region is disposed on the gas-liquid separator, and a first valve body is disposed on the exhaust pipeline.

[0008] In one possible implementation, a first liquid level sensor for detecting the liquid level is disposed inside the gas-liquid separator, and the first liquid level sensor is electrically connected to the first valve body; wherein when the liquid level in the liquid area drops to the detection end of the first liquid level sensor, the first valve body opens.

[0009] In one possible implementation, a second liquid level sensor for detecting the liquid level is disposed inside the gas-liquid separator, the second liquid level sensor is electrically connected to the first valve body, and the second liquid level sensor is located above the first liquid level sensor; wherein, when the liquid level in the liquid area rises to the detection end of the second liquid level sensor, the first valve body is closed.

[0010] In a possible implementation, one end of the exhaust pipeline away from the gaseous region is connected to the liquid return main pipe; and / or one end of the exhaust pipeline away from the gaseous region is connected to the refrigeration host.

[0011] In a possible implementation, the cooling branch pipe includes a plurality of cooling branches arranged in parallel, and the plurality of cooling branches are respectively used to cool a plurality of groups of heating units.

[0012] In one possible implementation, the cooling branch includes an input pipeline located at the front end of the heating unit and an output pipeline located at the rear end of the heating unit; the resistance in the input pipeline is a, and the resistance in the output pipeline is b, where cd≤a+b≤c+d, where c is the standard resistance value in the cooling branch and d is the error value.

[0013] In a possible implementation, the inner diameters of the input pipeline and the output pipeline are equal, the effective length of the cooling branch is equal to the sum of the length of the input pipeline and the length of the output pipeline, and the effective lengths of the plurality of cooling branches are equal.

[0014] In a possible implementation, multiple cooling branches are arranged in parallel, the input ends of the multiple cooling branches are connected to the liquid inlet main pipe, the output ends of the multiple cooling branches are connected to the liquid return main pipe, and the input ends of the multiple cooling branches are respectively provided with stop valves.

[0015] In a possible implementation, the cooling branch pipe further includes a pressure sensor, and the pressure sensor is used to detect the pressure at the output end of the cooling branch pipe.

[0016] In a possible implementation, the cooling branch pipe further includes a temperature sensor, and the temperature sensor is used to detect the temperature of the output end of the cooling branch pipe.

[0017] In a possible implementation, the cooling branch pipe has two output ends, and two adjacent cooling branch pipes share one output end.

[0018] In a second aspect, an embodiment of the present application provides a cooling system, comprising: a refrigeration host, the refrigeration host comprising a delivery pump; and the above-mentioned liquid supply mechanism.

[0019] In the third aspect, an embodiment of the present application provides a liquid supply control method for the above-mentioned liquid supply mechanism, comprising the following steps: controlling the liquid level of the liquid area in the gas-liquid separator based on a preset range so that the liquid refrigerant in the liquid area is transmitted to the liquid inlet main pipe of the cooling network.

[0020] In one possible implementation, an exhaust pipeline connected to the gaseous area is provided on the gas-liquid separator, and a first valve body is provided on the exhaust pipeline; a first liquid level sensor for detecting the liquid level is provided inside the gas-liquid separator, and the first liquid level sensor is electrically connected to the first valve body; the liquid level of the liquid area in the gas-liquid separator is controlled based on a preset range, including: detecting by the first liquid level sensor whether the liquid level in the liquid area reaches the lower limit of the preset range; if it is detected that the liquid level in the liquid area reaches the lower limit of the preset range, controlling the first valve body to open, so that the gaseous refrigerant in the gaseous area is discharged through the exhaust pipeline, so that the liquid level in the liquid area rises.

[0021] In one possible implementation, a second liquid level sensor for detecting the liquid level is provided inside the gas-liquid separator, the second liquid level sensor is electrically connected to the first valve body, and the second liquid level sensor is located above the first liquid level sensor; the liquid level of the liquid area in the gas-liquid separator is controlled based on a preset range, including: detecting by the second liquid level sensor whether the liquid level in the liquid area reaches the upper limit of the preset range; if it is detected that the liquid level in the liquid area reaches the upper limit of the preset range, controlling the first valve body to close.

[0022] In one possible implementation, the liquid supply mechanism is applied to a cooling system, and the liquid supply control method further includes: when the heat generating unit in the cooling system is operating at a maximum heat load, adjusting the liquid supply amount of the refrigeration host in the cooling system to a first liquid supply amount so that the heat generating unit in the cooling system is effectively cooled.

[0023] In one possible implementation, a stop valve is provided at each input end of the cooling branch pipe, and the liquid supply control method further includes: adjusting the opening of the stop valve to adjust the flow in each cooling branch pipe in the liquid supply mechanism so that the heating unit corresponding to each cooling branch pipe can be effectively cooled.

[0024] In a possible implementation, it also includes: after each heating unit of the cooling system operates normally, obtaining the temperature of the output end of each cooling branch pipe in the liquid supply mechanism, and comparing it with the saturation temperature of the output end of the cooling branch pipe to determine the temperature difference; adjusting the liquid supply amount of the refrigeration host to the second liquid supply amount so that the heating unit in the cooling branch pipe with the largest temperature difference can be effectively cooled.

[0025] According to the liquid supply mechanism, cooling system and liquid supply control method provided in the embodiments of the present application, the liquid supply mechanism separates the refrigerant output by the refrigeration main unit into gas and liquid through a gas-liquid separator, and allows the liquid refrigerant in the liquid area to enter the cooling branch through the liquid inlet main pipe. After the cooling branch completes cooling the heating unit, the refrigerant returns to the refrigeration main unit through the liquid return main pipe. Compared with the prior art in which each cooling branch cools the heating unit with a two-phase refrigerant and it is difficult to control the uniform distribution of the two-phase refrigerant, the present application ensures that the refrigerant in the liquid inlet main pipe is in liquid state, thereby ensuring the uniform distribution of the refrigerant in each cooling branch, improving the uniformity of distributing the refrigerant to each heating unit, and thereby improving the cooling effect on the heating unit. BRIEF DESCRIPTION OF THE DRAWINGS

[0026] The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate embodiments consistent with the invention and, together with the description, serve to explain the principles of the invention.

[0027] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings required for use in the embodiments or the description of the prior art will be briefly introduced below. Obviously, for ordinary technicians in this field, other drawings can be obtained based on these drawings without paying any creative labor.

[0028] One or more embodiments are exemplarily described by pictures in the corresponding drawings, and these exemplified descriptions do not constitute limitations on the embodiments. Elements with the same reference numerals in the drawings represent similar elements, and unless otherwise stated, the figures in the drawings do not constitute proportional limitations.

[0029] Figure 1 A schematic diagram of the structure of a cooling system provided in an embodiment of the present application is shown;

[0030] Figure 2 A schematic structural diagram of a cooling system provided by an embodiment of the present application when there is only one cooling branch pipe is shown;

[0031] Figure 3 A schematic diagram showing the structure of a gas-liquid separator provided in an embodiment of the present application connected to a liquid inlet main pipe and a liquid return main pipe;

[0032] Figure 4 A schematic diagram of the structure of a cooling branch pipe provided in an embodiment of the present application is shown;

[0033] Figure 5 A schematic diagram of the structure of a cooling branch provided in an embodiment of the present application is shown;

[0034] Figure 6 A flow chart of a liquid supply control method provided in an embodiment of the present application is shown.

[0035] Description of reference numerals:

[0036] h. Heating unit;

[0037] 1. Refrigeration main unit; 11. Delivery pump; 12. Heat exchanger; 13. Fan; 14. Liquid storage tank; 15. Filter;

[0038] 2. Cooling pipe network; 21. Liquid inlet main pipe; 22. Cooling branch pipe; 221. Cooling branch; 2211. Input pipeline; 2212. Output pipeline; 222. Stop valve; 223. Pressure sensor; 224. Temperature sensor; 23. Liquid return main pipe;

[0039] 3. Gas-liquid separator; 31. Exhaust pipeline; 32. First valve body; 33. First liquid level sensor; 34. Second liquid level sensor; 35. Liquid area; 36. Gas area. DETAILED DESCRIPTION

[0040] In order to make the purpose, technical solution and advantages of the embodiments of the present application clearer, the technical solution in the embodiments of the present application will be clearly and completely described below in conjunction with the drawings in the embodiments of the present application. Obviously, the described embodiments are part of the embodiments of the present application, not all of the embodiments. Based on the embodiments in the present application, all other embodiments obtained by ordinary technicians in this field without making creative work are within the scope of protection of this application.

[0041] The disclosure below provides many different embodiments or examples to realize the different structures of the embodiments of the present application. In order to simplify the disclosure of the embodiments of the present application, the parts and settings of specific examples are described below. Of course, they are only examples, and the purpose is not to limit the embodiments of the present application. In addition, the embodiments of the present application can repeat reference numbers and / or letters in different examples. This repetition is for the purpose of simplification and clarity, and does not itself indicate the relationship between the various embodiments and / or settings discussed.

[0042] For ease of description, spatial relative terms may be used herein to describe the relative positional relationship or movement of one element or feature relative to another element or feature as shown in the figure, such as "inside", "outside", "inner side", "outer side", "below", "below", "above", "above", "front", "back", etc. Such spatial relative terms are intended to include different orientations of the device in use or operation in addition to the orientation depicted in the figure. For example, if the device in the figure undergoes a position flip or a posture change or a motion state change, then these directional indications also change accordingly, for example: an element described as "below other elements or features" or "below other elements or features" will subsequently be oriented as "above other elements or features" or "above other elements or features". Therefore, the example term "below..." may include both upper and lower orientations. The device may be otherwise oriented (rotated 90 degrees or in other directions) and the spatial relative descriptors used herein are interpreted accordingly.

[0043] In order to solve the problems in the prior art, the present application provides a liquid supply mechanism, a cooling system and a liquid supply control method, wherein the liquid supply mechanism improves the uniformity of distributing refrigerant to each heating unit, thereby improving the cooling effect on the heating unit.

[0044] Figure 1 A schematic diagram of the structure of a cooling system provided in an embodiment of the present application is shown; Figure 2 A schematic structural diagram of a cooling system provided by an embodiment of the present application when there is only one cooling branch pipe is shown; Figure 3 A schematic diagram showing the structure of a gas-liquid separator provided in an embodiment of the present application connected to a liquid inlet main pipe and a liquid return main pipe; Figure 4 A schematic diagram of the structure of a cooling branch pipe provided in an embodiment of the present application is shown; Figure 5 A schematic structural diagram of a cooling branch provided in an embodiment of the present application is shown.

[0045] like Figure 1-5 As shown, the embodiment of the present application provides a liquid supply mechanism, which is applied to a cooling system, and the cooling system includes a refrigeration main unit 1, and the liquid supply mechanism includes: a cooling pipe network 2 and a gas-liquid separator 3. Specifically, the refrigeration main unit 1 is used to cool the refrigerant, and the cooled refrigerant cools the heating unit h in the system through the liquid supply mechanism, and the refrigerant returns to the refrigeration main unit 1 after heating, and the cooling of the refrigerant is completed again, so that the refrigerant reaches a temperature that can cool the heating unit h, and then the heating unit h is cooled again through the liquid supply mechanism to achieve circulation.

[0046] The cooling pipe network 2 includes a liquid inlet main pipe 21, a cooling branch pipe 22 and a liquid return main pipe 23 which are connected to each other. The cooling branch pipe 22 is used to cool the heating unit h, and the liquid return main pipe 23 is connected to the liquid inlet end of the refrigeration host 1.

[0047] The gas-liquid separator 3 is arranged at the liquid outlet end of the refrigeration main unit 1, and the interior of the gas-liquid separator 3 is provided with a liquid area 35 located at the bottom and a gas area 36 located above the liquid area 35; wherein, the input end of the liquid inlet main pipe 21 is connected to the liquid area 35 of the gas-liquid separator 3.

[0048] In the present application, the refrigerant output from the refrigeration main unit 1 is separated into gas and liquid by the gas-liquid separator 3, and the liquid refrigerant in the liquid area 35 enters the cooling branch 22 through the liquid inlet main pipe 21, and returns to the refrigeration main unit 1 through the liquid return main pipe 23 after the cooling branch 22 completes the cooling of the heating unit h. Compared with the prior art in which each cooling branch 22 cools the heating unit h through a two-phase refrigerant, it is difficult to control the uniform distribution of the two-phase refrigerant. The present application ensures that the refrigerant in the liquid inlet main pipe 21 is in liquid state, thereby ensuring the uniform distribution of the refrigerant in each cooling branch 22, improving the uniformity of the refrigerant distribution to each heating unit h, and thereby improving the cooling effect on the heating unit h.

[0049] In the related art, in the fluorine pump refrigeration system, after the refrigerant is condensed into liquid in the heat exchanger 12, it is transported to the heating unit h through the refrigerant pump (fluorine pump), and the refrigerant absorbs heat and evaporates in the internal flow channel of the heating unit h. Under the action of the pressure difference, the evaporated refrigerant flows into the heat exchanger 12 and condenses into liquid refrigerant in the heat exchanger 12. This reciprocating process is used to achieve cyclic refrigeration. Two-phase cooling systems are usually high-power systems, which adopt modular combinations. The refrigerant needs to be evenly distributed to the heating units h that need to be cooled. If the distribution is uneven, some heating units h may have too much liquid distribution, and some heating units h may not be cooled enough, resulting in overheating and burning. In the current technology, the refrigerant output by the refrigeration host 1 includes gaseous refrigerant and liquid refrigerant. The heat absorption of liquid refrigerant during phase change is more than ten times that of gaseous refrigerant with the same mass flow rate. Therefore, it is very difficult to evenly distribute the two-phase refrigerant.

[0050] In the embodiment of the present application, a gas-liquid separator 3 is arranged between the refrigeration main unit 1 and the cooling pipe network 2. After the refrigerant enters the gas-liquid separator 3, the gas-liquid separation is completed, wherein the liquid refrigerant is located in the liquid area 35 at the bottom, and the gaseous refrigerant is located in the gaseous area above. The input end of the liquid inlet main pipe 21 is connected with the liquid area 35 at the bottom, thereby ensuring that the refrigerant entering the liquid inlet main pipe 21 is liquid refrigerant. When the liquid refrigerant enters the cooling branch pipe 22 to cool the heating unit h, the amount of heat absorbed is fixed, so that the refrigerant in each cooling branch pipe 22 can be evenly distributed. Avoid the phenomenon that the heating unit h is always insufficient due to insufficient refrigerant distribution and overheating and burning, and avoid the waste caused by excessive refrigerant distribution, thereby improving the cooling effect on the heating unit h.

[0051] Moreover, the heating units h in the system are all cooled by liquid refrigerant, and the liquid refrigerant has a higher heat absorption ratio. Compared with the prior art in which the heating units h are cooled by two-phase refrigerant, the cooling effect on the heating units h can be improved.

[0052] Specifically, the gas-liquid separator 3 is a tank body. After the two-phase refrigerant is delivered into the gas-liquid separator 3 by the delivery pump 11 of the refrigeration host 1, the liquid refrigerant is located in the liquid area 35 at the bottom due to its larger density, while the gaseous refrigerant is located in the gaseous area 36 above due to its smaller density than the liquid refrigerant. The liquid level of the liquid refrigerant is located at the junction of the liquid area 35 and the gaseous area 36.

[0053] In some embodiments, the gas-liquid separator 3 is provided with an exhaust pipeline 31 communicating with the gaseous region 36 , and the exhaust pipeline 31 is provided with a first valve body 32 .

[0054] In the present application, an exhaust pipeline 31 is provided on the gas-liquid separator 3, and the opening and closing of the exhaust pipeline 31 is controlled by the opening and closing of the first valve body 32. After the pressurized refrigerant is delivered into the gas-liquid separator 3 by the delivery pump 11 of the refrigeration host 1, it itself has a certain pressure, so that when the gaseous refrigerant and the liquid refrigerant exist at the same time, there is sufficient pressure so that the liquid refrigerant can enter the cooling network 2. When the liquid area 35 in the gas-liquid separator 3 is small, that is, the liquid level of the liquid refrigerant in the gas-liquid separator 3 is low, the first valve body 32 can be opened so that the gaseous refrigerant in the gas-liquid separator 3 can be discharged through the exhaust pipe 31, thereby causing the liquid refrigerant level in the gas-liquid separator 3 to rise, thereby ensuring the amount of liquid refrigerant retained in the gas-liquid separator 3, and further ensuring that the refrigerant entering the cooling network 2 is all liquid refrigerant; when the liquid refrigerant level in the gas-liquid separator 3 rises to a certain level, the first valve body 32 is controlled to close, and the pressure inside the gas-liquid separator 3 is maintained to ensure that the refrigerant can be effectively transported into the cooling network 2.

[0055] Optionally, a pump body may be provided between the gas-liquid separator 3 and the cooling network 2, and the liquid refrigerant in the gas-liquid separator 3 may be transported into the cooling network 2 through the pump body. Similarly, the refrigerant entering the cooling network 2 may be controlled to be a liquid refrigerant, and the pumping of the liquid refrigerant is not affected by the pressure in the gas-liquid separator 3, so the delivery of the refrigerant may be controlled more accurately.

[0056] In some embodiments, a first liquid level sensor 33 for detecting the liquid level is disposed inside the gas-liquid separator 3, and the first liquid level sensor 33 is electrically connected to the first valve body 32; wherein, when the liquid level of the liquid region 35 drops to the detection end of the first liquid level sensor 33, the first valve body 32 is opened. Specifically, the input end of the liquid inlet manifold 21 is lower than the height of the detection end of the first liquid level sensor 33, so as to ensure that the liquid level of the liquid refrigerant in the liquid region 35 is always higher than the input end of the liquid inlet manifold 21.

[0057] In the present application, the height of the detection end of the first liquid level sensor 33 is higher than the height of the input end of the liquid inlet main pipe 21. When the liquid level of the liquid refrigerant in the gas-liquid separator 3 drops to the detection end of the first liquid level sensor 33, the first liquid level sensor 33 is triggered, and the first liquid level sensor 33 controls the first valve body 32 to open through the controller. At this time, exhaust is performed through the exhaust pipe 31 to achieve the rise of the liquid refrigerant level in the gas-liquid separator 3, thereby ensuring that the liquid level of the liquid refrigerant in the gas-liquid separator 3 is always higher than the height of the input end of the liquid inlet main pipe 21. There is no need to manually control the opening and closing of the first valve body 32, so as to ensure that the refrigerant entering the cooling pipe network 2 is all liquid refrigerant.

[0058] Specifically, the closing of the first valve body 32 can be done manually, or when the liquid level of the liquid refrigerant in the gas-liquid separator 3 is higher than a certain height, the first valve body 32 can be controlled to close automatically, or when the weight of the gas-liquid separator 3 rises to a certain value, the first valve body 32 can be controlled to close automatically. In a specific embodiment, a weighing platform is provided at the bottom of the gas-liquid separator 3, and the overall weight of the gas-liquid separator 3 can be monitored in real time. As the amount of liquid refrigerant in the gas-liquid separator 3 increases, the weight of the entire gas-liquid separator 3 continues to increase. When the overall weight of the gas-liquid separator 3 reaches a preset value, the first valve body 32 is controlled to close, and the pressure inside the gas-liquid separator 3 is maintained, thereby ensuring the pumping of the refrigerant.

[0059] like Figure 3 As shown, in a specific embodiment, a second liquid level sensor 34 for detecting the liquid level is provided inside the gas-liquid separator 3, the second liquid level sensor 34 is electrically connected to the first valve body 32, and the second liquid level sensor 34 is located above the first liquid level sensor 33; wherein, when the liquid level in the liquid area 35 rises to the detection end of the second liquid level sensor 34, the first valve body 32 is closed.

[0060] In the present application, the second liquid level sensor 34 is electrically connected to the first valve body 32 and is used to control the closing of the first valve body 32. The detection end of the second liquid level sensor 34 is located above the detection end of the first liquid level sensor 33. When the first liquid level sensor 33 controls the first valve body 32 to open, the liquid level of the liquid refrigerant in the gas-liquid separator 3 continues to rise. When the liquid level of the liquid refrigerant rises to the detection end of the second liquid level sensor 34, the second liquid level sensor 34 is triggered. At this time, the second liquid level sensor 34 controls the closing of the first valve body 32 through the controller to maintain the pressure in the gas-liquid separator 3 to ensure the effective pumping of the liquid refrigerant.

[0061] Specifically, in the present application, a first liquid level sensor 33 and a second liquid level sensor 34 are provided. The first liquid level sensor 33 is used to control the opening of the first valve body 32, and the second liquid level sensor 34 is used to control the closing of the first valve body 32, so that the liquid level of the liquid refrigerant in the gas-liquid separator 3 can be maintained between the detection end of the first liquid level sensor 33 and the detection end of the second liquid level sensor 34, thereby ensuring that the refrigerant entering the cooling pipe network 2 is all liquid refrigerant, thereby ensuring the uniform distribution of the refrigerant in each cooling branch pipe 22, and thereby improving the cooling effect of the heat generating unit h in the system.

[0062] In some embodiments, one end of the exhaust pipe 31 away from the gaseous region 36 is connected to the liquid return main pipe 23; and / or one end of the exhaust pipe 31 away from the gaseous region 36 is connected to the refrigeration host 1.

[0063] like Figure 1-3 As shown, in a specific embodiment, one end of the exhaust pipe 31 away from the gaseous area 36 is connected to the liquid return main pipe 23, and the exhausted gaseous refrigerant is returned to the liquid return main pipe 23, and then returned to the refrigeration host 1 through the liquid return main pipe 23, so as to avoid waste of refrigerant.

[0064] In another specific embodiment, one end of the exhaust pipe 31 away from the gaseous region 36 is connected to the refrigeration host 1, and the exhausted gaseous refrigerant is directly returned to the refrigeration host 1, so as to realize the recycling of the refrigerant and avoid the waste of the refrigerant.

[0065] In another specific embodiment, two branches are provided at one end of the exhaust pipe 31 away from the gaseous area 36, ​​one of which is connected to the liquid return main pipe 23 to return the discharged gaseous refrigerant to the liquid return main pipe 23, and the other is connected to the refrigeration main unit 1 to return the discharged gaseous refrigerant to the refrigeration main unit 1, which can also realize the circulation of the refrigerant and avoid the waste of the refrigerant.

[0066] Optionally, the end of the exhaust pipe 31 away from the gaseous region 36 can also be used to refrigerate some heating units h inside or outside the system. Since the heating units h are cooled by pure gaseous refrigerant, the distribution amount of the gaseous refrigerant can be controlled, thereby ensuring the cooling effect on the heating units h. After the cooling of the heating units h is completed, the gaseous refrigerant is merged into the return liquid main pipe 23 or the refrigeration main unit 1, which can improve the effective utilization rate of the refrigerant and avoid the low-temperature gaseous refrigerant returning to the refrigeration main unit 1 without passing through the heating units h. For example, the above-mentioned heating units h are some heating units h outside the system that do not require a high amount of cooling. By cooling the above-mentioned heating units h with gaseous refrigerant during the exhaust process, the heating units h are within the required operating temperature range. When there is no exhaust, this part of the heating units h will not be cooled, but the temperature of this part of the heating units h will not be too high and exceed the operating temperature range.

[0067] In some embodiments, the cooling branch pipe 22 includes a plurality of cooling branches 221 arranged in parallel, and the plurality of cooling branches 221 are respectively used to cool a plurality of groups of heating units h.

[0068] In the present application, the cooling system is a high-power system, which adopts a modular combination, and the number of heating units h is also multiple. The cooling branch pipe 22 adopts multiple cooling branches 221, each cooling branch 221 cools down a heating unit h, or each cooling branch 221 cools down a group of heating units h. For multiple heating units h with relatively small heat generation, they can be combined into a group of heating units h. Moreover, multiple cooling branches 221 are arranged in parallel without interfering with each other, so as to ensure the cooling effect of the heating unit h at each cooling branch 221.

[0069] Specifically, the heating units h in the present application are arranged in parallel in a secondary grouping manner to shorten the process length of a single flow path while controlling the complexity of the system, thereby ensuring that the inlet of each heating unit h is pure liquid refrigerant, thereby avoiding local overheating due to liquid supply.

[0070] In the related art, there is a certain resistance when the refrigerant passes through the heat exchanger 12 at the heating unit h. Since the pipe path is relatively long, there is still a certain resistance during the transportation of the refrigerant in the pipe path. Although the cooling branches 221 are arranged in parallel, there are still different resistances of the refrigerant in the entire cooling branch 221. Finally, the temperature and pressure of the refrigerant at the output end of the cooling branch 221 are different, so that the cooling capacity of some refrigerants is fully utilized, while the cooling capacity of some refrigerants is not fully utilized, which will also affect the uniformity of the refrigerant distribution.

[0071] In order to solve the above problems, the present application further provides the following embodiments:

[0072] like Figure 5 As shown, in one embodiment, the cooling branch 221 includes an input pipe 2211 located at the front end of the heating unit h and an output pipe 2212 located at the rear end of the heating unit h; the resistance in the input pipe 2211 is a, and the resistance in the output pipe 2212 is b, where cd≤a+b≤c+d, where c is the standard resistance value in the cooling branch 221, and d is the error value.

[0073] In the present application, the pipe resistance a+b of multiple cooling branches 221 arranged in parallel is set near the standard value, that is, the standard resistance value c±error value d in the cooling branch 221, and the pipe resistance in the cooling branch 221 is controlled near the standard value, so that the pipe resistance values ​​in each cooling branch 221 are close, and then the pressure and temperature parameters of the refrigerant at the output end of the cooling branch are close, thereby ensuring the effective utilization rate of the refrigerant in each cooling branch 221.

[0074] Specifically, the cooling pipe network 2 adopts a two-level distribution method of a main pipe (liquid inlet main pipe 21 and liquid return main pipe 23) and a secondary branch pipe (cooling branch pipe 22). According to the position relationship of the heating units h, adjacent heating units h are placed in the same group to form a cooling branch pipe 22. All heating units h are divided into m cooling branches 22 and connected to the main pipe. For the convenience of layout, it is recommended to arrange the cooling branches 22 in rows or columns, such as Figure 1 The branching method shown is that the upper and lower lines form a cooling branch 22. According to the power load scale and characteristics, one line can also be a branch or one column can be a cooling branch 22. A stop valve 222 for adjusting flow balance is installed at the inlet of each cooling branch 22, which is used to compensate for the flow resistance difference between different branches and realize uniform liquid separation between each branch. Each cooling branch 22 is connected to n heating units h. The input pipeline 2211 and the output pipeline 2212 of the heating unit h on the same cooling branch 22 are connected in different distances, that is, the liquid inlet position of the cooling branch 221 is closest to the first unit and farthest from the nth unit, and the liquid outlet position of the cooling branch 221 is farthest from the first unit and closest to the nth unit, so as to ensure that the refrigerant flow resistance of each heating unit h in the same cooling branch 221 is close. In addition, the total resistance of the refrigerant in a cooling branch 221 is equal or close, and the pressure and temperature of the refrigerant at the output end of multiple cooling branches 221 are close, so as to improve the effective utilization rate of the refrigerant in the cooling branch 221.

[0075] In some embodiments, the inner diameters of the input pipeline 2211 and the output pipeline 2212 are equal, the effective length of the cooling branch 221 is equal to the sum of the length of the input pipeline 2211 and the length of the output pipeline 2212, and the effective lengths of multiple cooling branches 221 are equal.

[0076] like Figure 4-5 As shown, in the present application, the inner diameters of the input pipeline 2211 and the output pipeline 2212 are equal. By controlling the sum of the length of the input pipeline 2211 and the length of the output pipeline 2212 in the cooling branch 221, the effective lengths of multiple cooling branches 221 are ultimately equal, and the total resistances in the multiple cooling branches 221 can be controlled to be equal or close, which facilitates the arrangement of the pipelines to achieve equal total resistances in multiple cooling branches 221.

[0077] Specifically, when arranging the pipelines, multiple heating units h in a cooling branch 22 are generally located in one area or in the same row or column. The longest pipeline length required for arranging the heating units h in the multiple cooling branches 221 of the cooling branch 22 is selected as the standard, and the lengths of the multiple cooling branches 221 in the cooling branch 22 are arranged according to the above standard, that is, the lengths of the multiple cooling branches 221 are arranged according to the above standard, and finally the effective lengths of the multiple cooling branches 221 in the cooling branch 22 are equal.

[0078] Optionally, for some heating units h that have different demands and speeds for coolant, the input pipelines 2211 and output pipelines 2212 in different cooling branches 221 may be set to different inner diameters, and the lengths of the input pipelines 2211 and output pipelines 2212 may be adjusted accordingly to achieve equal or close total resistances in multiple cooling branches. Specifically, for input pipelines 2211 or output pipelines 2212 with larger inner diameters, the lengths of the input pipelines 2211 and / or output pipelines 2212 may be shortened accordingly; for input pipelines 2211 or output pipelines 2212 with smaller inner diameters, the lengths of the input pipelines 2211 and / or output pipelines 2212 may be increased accordingly.

[0079] In some embodiments, multiple cooling branches 22 are arranged in parallel, the input ends of the multiple cooling branches 22 are connected to the liquid inlet main pipe 21, the output ends of the multiple cooling branches 22 are connected to the liquid return main pipe 23, and the input ends of the multiple cooling branches 22 are respectively provided with stop valves 222.

[0080] like Figure 1 As shown, in a specific embodiment, for the case where there are relatively many heat generating units h in the cooling system, multiple cooling branches 22 can be provided, and the multiple cooling branches 22 are provided in parallel without affecting each other, and a stop valve 222 is provided at the input end of the cooling branch 22. The stop valve 222 adjusts the flow rate of the refrigerant entering each cooling branch 22, and is used to compensate for the flow resistance difference between different cooling branches 22, to achieve uniform liquid separation between the cooling branches 22, and to ensure that the refrigerant flow rate entering each cooling branch 22 can meet the cooling and temperature reduction of the multiple heat generating units h corresponding to the cooling branch 22.

[0081] like Figure 2As shown, in another specific embodiment, for the case where there are relatively few heat generating units h in the cooling system, only one cooling branch pipe 22 can be provided, and the refrigerant in the liquid inlet main pipe 21 enters the cooling branch pipe 22, and after completing the cooling of multiple heat generating units h corresponding to the cooling branch pipe 22, returns to the refrigeration host 1 through the liquid return main pipe 23.

[0082] In some embodiments, the cooling branch pipe 22 further includes a pressure sensor 223 , and the pressure sensor 223 is used to detect the pressure at the output end of the cooling branch pipe 22 .

[0083] In the present application, the pressure at the output end of the cooling branch 22 is detected by the pressure sensor 223, and the opening of the stop valve 222 at the input end of each cooling branch 22 is adjusted to keep the pressure at the output end of each cooling branch 22 equal or close, thereby ensuring the effective utilization rate of the coolant in each cooling branch 22, and reducing the waste of refrigerant while ensuring the cooling effect on the heating unit h.

[0084] In some embodiments, the cooling branch pipe 22 further includes a temperature sensor 224 , and the temperature sensor 224 is used to detect the temperature of the output end of the cooling branch pipe 22 .

[0085] In the present application, the temperature of the output end of the cooling branch pipe 22 is detected by the temperature sensor 224, and the temperature is compared with the saturation temperature corresponding to the output end of the cooling branch pipe 22 at the pressure, and then the refrigerant supply of the refrigeration main unit 1 or the refrigerant supply of a single cooling branch pipe 22 is adjusted according to the difference between the two temperatures to maximize the utilization of the cooling capacity in the refrigerant.

[0086] Specifically, according to the refrigerant characteristics, when the refrigerant is in a saturated state of gas-liquid mixture, its temperature is equal to the saturation temperature corresponding to its pressure. When the refrigerant supply is reduced, all the liquid refrigerant evaporates into gaseous refrigerant, and the gaseous refrigerant continues to be heated, the temperature of the refrigerant will be higher than the saturation temperature corresponding to its pressure. This difference can be controlled at 1-2°C. It can ensure that all the supplied liquid is used up without waste, and the refrigerant temperature is not too high to ensure the cooling effect. This can optimize the refrigerant supply amount and reduce the amount of refrigerant used while ensuring the cooling effect.

[0087] Optionally, a temperature sensor 224 can also be set at the output end of each cooling branch 221 to detect the outlet liquid temperature of each cooling branch 221 and compare the outlet liquid temperature with the saturation temperature. When the outlet liquid temperature rises to 1°C-2°C higher than the saturation temperature, it proves that the refrigerant at the output end of the cooling branch 221 is completely vaporized, thereby ensuring the cooling effect of the heating unit h corresponding to the cooling branch 221 and improving the effective utilization rate of the refrigerant, and the cooling effect of the heating unit h will not be affected by excessively high temperature.

[0088] In some embodiments, the cooling branch pipe 22 has two output ends, and two adjacent cooling branch pipes 22 share one output end.

[0089] In the present application, by adjusting the refrigerant supply amount through the above pressure detection, the pressure at the output end of each cooling branch 22 can be kept consistent or close, ensuring that the parameters of the corresponding heating unit h on each cooling branch 22 are close, and then two adjacent cooling branches 22 can share one output end, that is, a temperature sensor 224 is used to detect the temperature of the output ends of the two cooling branches 22, and a pressure sensor 223 is used to detect the pressure at the output ends of the two cooling branches 22, thereby simplifying the layout of the pipe circuit.

[0090] Optionally, three or more cooling branches 22 may share one output end, that is, one temperature sensor 224 may detect the temperature of the output ends of multiple cooling branches 22, and one pressure sensor 223 may detect the pressure of the output ends of multiple cooling branches 22. Adjustments may be made according to the actual arrangement of the heating unit h.

[0091] The liquid supply mechanism separates the gas and liquid of the refrigerant output by the refrigeration main unit 1 through the gas-liquid separator 3, and allows the liquid refrigerant in the liquid area 35 to enter the cooling branch 22 through the liquid inlet main pipe 21, and return to the refrigeration main unit 1 through the liquid return main pipe 23 after the cooling branch 22 completes cooling the heating unit h. Compared with the prior art, each cooling branch 22 cools the heating unit h through a two-phase refrigerant, which makes it difficult to control the uniform distribution of the two-phase refrigerant. The present application ensures that the refrigerant in the liquid inlet main pipe 21 is in liquid state, thereby ensuring the uniform distribution of the refrigerant in each cooling branch 22, improving the uniformity of distributing the refrigerant to each heating unit h, and thereby improving the cooling effect on the heating unit h.

[0092] The embodiment of the present application provides a cooling system, comprising: a refrigeration host 1, the refrigeration host 1 comprising a delivery pump 11; and the above-mentioned liquid supply mechanism.

[0093] The refrigeration host 1 in the present application is used to prepare low-temperature refrigerant, and the refrigerant is delivered to the liquid supply mechanism through the delivery pump 11. The liquid supply mechanism completes the distribution of the refrigerant and cools down the heating unit h in the system. The gas-liquid separation of the refrigerant is completed by the gas-liquid separator 3 in the liquid supply mechanism, thereby ensuring that the refrigerant entering the cooling network 2 is all liquid refrigerant. Compared with the situation in which the two-phase refrigerant in the prior art cools the heating unit h, the uniform distribution of the refrigerant can be achieved, thereby ensuring the cooling effect of the heating unit h.

[0094] Specifically, the refrigeration unit also includes a heat exchanger 12, a fan 13, a liquid storage tank 14, a filter 15, and sensors such as pressure and temperature. The heat exchanger 12 and the fan 13 are used in combination to realize the cooling function of the refrigerant. The refrigerant entering the heat exchanger 12 is condensed into a cold liquid in the heat exchanger 12. The function of the liquid storage tank 14 is to prevent the heat of the heating unit h from changing sharply (the heat production increases, which can be the increase in the number of heating units h turned on, or the increase in the power of the heating unit h) and the situation where all the refrigerants cannot be condensed into liquid. When the gas-liquid two-phase situation occurs, the delivery pump 11 can still absorb the liquid refrigerant in the liquid storage tank to avoid cavitation damage to the delivery pump 11. The filter 15 filters the impurities in the system to ensure the reliable operation of the delivery pump 11. The delivery pump 11 is the power source of the system, which increases the pressure of the liquid refrigerant and provides power for the flow of the refrigerant.

[0095] Figure 6 A flow chart of a liquid supply control method provided in an embodiment of the present application is shown.

[0096] like Figure 6 As shown, the embodiment of the present application provides a liquid supply control method of the above-mentioned liquid supply mechanism, comprising the following steps:

[0097] S1. Control the liquid level of the liquid region 35 in the gas-liquid separator 3 based on a preset range, so that the liquid refrigerant in the liquid region 35 is transmitted to the liquid inlet main pipe 21 of the cooling pipe network 2.

[0098] In the present application, the refrigeration host 1 pumps the refrigerant into the gas-liquid separator 3, and controls the liquid level of the liquid area 35 in the liquid level separator within a preset range to ensure that the refrigerant pumped into the cooling network 2 is all liquid refrigerant. Compared with the prior art in which the heating unit h is cooled by a gas-liquid two-phase refrigerant, the present application cools the heating unit h by a pure liquid refrigerant, thereby ensuring the uniformity of the distribution of the refrigerant to each heating unit h. At the same time, because the heat absorption of the liquid phase change is higher than the single-phase heat absorption of the same mass flow rate, the cooling effect on the heating unit h can also be improved, saving the amount of refrigerant.

[0099] Specifically, the refrigeration host 1 includes a delivery pump 11, through which the refrigerant is delivered to the gas-liquid separator 3. The bottom of the gas-liquid separator 3 is liquid refrigerant, and the top is gaseous refrigerant. The liquid refrigerant is pumped to the cooling network 2. As the gaseous refrigerant in the gas-liquid separator 3 increases, the liquid level of the liquid refrigerant will continue to decrease under the action of pressure. In order to ensure that the liquid level of the liquid refrigerant in the gas-liquid separator 3 is within a preset range, the following embodiments are provided in the present application:

[0100] In some embodiments, the gas-liquid separator 3 is provided with an exhaust pipeline 31 connected to the gaseous region 36, and the exhaust pipeline 31 is provided with a first valve body 32; the gas-liquid separator 3 is provided with a first liquid level sensor 33 for detecting the liquid level, and the first liquid level sensor 33 is electrically connected to the first valve body 32; the liquid level of the liquid region 35 in the gas-liquid separator 3 is controlled based on a preset range, including:

[0101] S11. Detect whether the liquid level in the liquid area 35 reaches the lower limit of the preset range through the first liquid level sensor 33; if it is detected that the liquid level in the liquid area 35 reaches the lower limit of the preset range, control the first valve body 32 to open, so that the gaseous refrigerant in the gas area 36 is discharged through the exhaust pipe 31, so that the liquid level in the liquid area 35 rises.

[0102] In the present application, when the liquid level in the liquid area 35 drops to the lower limit of the preset range, the first liquid level sensor 33 is triggered. The first liquid level sensor 33 controls the first valve body 32 to open through the controller, so that the gaseous refrigerant in the gas area 36 is discharged through the exhaust pipe, thereby achieving an increase in the liquid level in the liquid area 35, thereby ensuring that the liquid level in the liquid area 35 will not be lower than the lower limit of the preset range, ensuring that the refrigerant entering the cooling network 2 is all liquid refrigerant.

[0103] In some embodiments, a second liquid level sensor 34 for detecting the liquid level is disposed inside the gas-liquid separator 3, the second liquid level sensor 34 is electrically connected to the first valve body 32, and the second liquid level sensor 34 is located above the first liquid level sensor 33; the liquid level of the liquid area 35 in the gas-liquid separator 3 is controlled based on a preset range, including:

[0104] S12, detecting whether the liquid level in the liquid area 35 reaches the upper limit of the preset range through the second liquid level sensor 34; if it is detected that the liquid level in the liquid area 35 reaches the upper limit of the preset range, controlling the first valve body 32 to close.

[0105] In the present application, after the first valve body 32 is opened, as the gaseous refrigerant is continuously discharged, the liquid level of the liquid refrigerant continues to rise. When the liquid level in the liquid area 35 rises to the upper limit of the preset range, the first valve body 32 is controlled to close, and the discharge of the gaseous refrigerant is suspended to prevent the liquid refrigerant from being discharged through the exhaust pipe 31 and causing waste of refrigerant.

[0106] In some embodiments, the liquid supply mechanism is applied to a cooling system, and the liquid supply control method further includes:

[0107] S2. When the heat generating unit h in the cooling system is running at the maximum heat load, the liquid supply amount of the refrigeration host 1 in the cooling system is adjusted to a first liquid supply amount, so that the heat generating unit h in the cooling system is effectively cooled.

[0108] The refrigeration system in the present application is a fluorine pump refrigeration system. Since the fluorine pump refrigeration system can allow liquid refrigerant to flow back to the two-phase refrigeration main unit 1, the maximum liquid supply set at the maximum heat load can be used to control the refrigerant supply. The specific method is: turn on all the heating units h in the system at full power, and adjust the flow of the delivery pump 11 by comparing the temperature at the output end of the cooling branch pipe 22 and the saturation temperature under the pressure, so that all heating units h are effectively cooled. After the flow of the delivery pump 11 is set, you can choose not to change it with the number of heating units h turned on and the power adjustment.

[0109] Specifically, in the present application, effective cooling of the heating unit h refers to: cooling the heating unit h to a desired temperature. For example, the operating temperature of the heating unit h is 15°C-40°C, and the heating unit h can be cooled to a temperature within the range of 15°C-40°C. Generally, the heating unit h is cooled to the highest value of the operating temperature, which can both ensure the operating temperature of the heating unit h and save refrigerant.

[0110] In some embodiments, a stop valve 222 is respectively provided at the input end of the cooling branch pipe 22, and the liquid supply control method further includes:

[0111] S3. Adjust the opening of the stop valve 222 to adjust the flow rate in each cooling branch pipe 22 in the liquid supply mechanism, so that the heating unit h corresponding to each cooling branch pipe 22 can be effectively cooled.

[0112] In the present application, by comparing the temperature at the output end of each cooling branch 22 with the saturation temperature under the pressure, the stop valve 222 at the input end of each cooling branch 22 is adjusted to adjust the refrigerant flow in the cooling branch 22, so as to ensure that the heating unit h corresponding to each cooling branch 22 can just complete effective cooling. That is, the refrigerant flow in each cooling branch 22 is just enough to make the multiple heating units h corresponding to the cooling branch 22 just complete effective cooling, and the refrigerant flow in different cooling branches 22 may be different.

[0113] Specifically, the first liquid supply amount in the present application corresponds to the maximum heating value of the heating unit h in the system. After preliminarily adjusting the liquid supply amount of the delivery pump 11, effective cooling of each heating unit h can be guaranteed. After some heating units h are turned off or the power is lowered, that is, when the heating value of the heat load is not the maximum, this first liquid supply amount is still selected to supply the refrigerant, which will cause some refrigerants to fail to achieve the maximum cooling effect.

[0114] In some embodiments, the liquid supply control method further comprises:

[0115] S4. After each heating unit h of the cooling system operates normally, the temperature of the output end of each cooling branch pipe 22 in the liquid supply mechanism is obtained, and compared with the saturation temperature of the output end of the cooling branch pipe 22 to determine the temperature difference;

[0116] S5. Adjust the liquid supply of the refrigeration host 1 to the second liquid supply so that the heat generating unit h in the cooling branch pipe 22 with the largest temperature difference can be effectively cooled.

[0117] In the present application, after each heating unit h in the system operates normally, some of the heating units h will be shut down or the operating power will be lowered. At this time, the temperature of the output end of each cooling branch 22 is detected, and the detected temperature is compared with the saturation temperature under the pressure to obtain the temperature difference. The liquid supply of the delivery pump 11 is adjusted to the second liquid supply according to the temperature difference, so that the heating unit h corresponding to the cooling branch 22 with the largest temperature difference is just cooled, and the heating unit h corresponding to the cooling branch 22 with a temperature difference less than the above maximum temperature difference can also be cooled, thereby ensuring the cooling effect of each heating unit h after the system operates normally, and at the same time reducing the waste of refrigerant.

[0118] Specifically, the maximum temperature difference between the temperature at the output end of the cooling branch pipe 22 and the saturation temperature at the pressure is selected to be 1°C-2°C, that is, the temperature at the output end of the cooling branch pipe 22 is 1°C-2°C higher than the saturation temperature at the pressure, which proves that the refrigerant in the cooling branch pipe 22 rises by 1°C-2°C after reaching the saturation temperature, which can ensure that all the supplied refrigerant is used up without waste, and the refrigerant temperature is not too high to ensure the cooling effect. The temperature difference between the output end of other cooling branches 22 and the saturation temperature at the pressure is less than or equal to the maximum temperature difference, which can also ensure the cooling effect of the heating unit h.

[0119] In the present application, by selecting the temperature difference between the temperature at the output end of the cooling branch pipe 22 and the saturation temperature under the pressure to be between 1°C and 2°C, it is convenient to monitor the maximum temperature difference, because the temperature of the refrigerant at the output end of the cooling branch pipe 22 will only rise after it is completely converted into gas, and the temperature of this critical point is not easy to control, and by selecting the maximum temperature difference to be 1°C-2°C higher than the saturation temperature, the saturation temperature (i.e., the target temperature) can be obtained according to the pressure at the output end of the cooling branch pipe 22, which is 1°C-2°C higher than the above saturation temperature for easy detection, and can avoid the influence of the temperature fluctuation of the refrigerant in the saturated state of gas-liquid mixture, and further improve the control accuracy of the liquid supply of the delivery pump 11. For example, when the pressure at the output end of the cooling branch pipe 22 rises slightly, it will cause a slight increase in the saturation temperature, and the increase is less than 1°C. Because the pressure fluctuation will not be too large, the fluctuation of the saturation temperature can also be maintained within 1°C. If the temperature at the output end of the cooling branch pipe 22 at this time is taken as the maximum temperature difference with the saturation temperature, it is possible that the refrigerant is not completely gasified, and the temperature rise is only caused by the pressure fluctuation.

[0120] Specifically, in the present application, the maximum liquid supply amount, i.e., the first liquid supply amount, is selected to ensure the cooling effect of the heating unit h, and the liquid supply amount is reduced based on the first liquid supply amount, thereby ensuring the cooling effect of each heating unit h and reducing the waste of refrigerant.

[0121] Example 1

[0122] The present invention provides a method for controlling the liquid supply of a cooling system, comprising the following steps:

[0123] S1, controlling the liquid level of the liquid region 35: controlling the liquid level of the liquid region 35 in the gas-liquid separator 3 to be within a preset range, so that the liquid refrigerant in the liquid region 35 is pumped to the cooling pipe network 2;

[0124] S2. Roughly adjust the liquid supply amount: operate the heat generating unit h in the system at the maximum heat load, and adjust the liquid supply amount of the refrigeration host 1 to the first liquid supply amount, so that the heat generating unit h in the system can be effectively cooled.

[0125] S3. Regulating the flow of the cooling branch pipe 22: Regulating the opening of the stop valve 222 to regulate the flow in each cooling branch pipe 22 in the liquid supply mechanism, so that the heating unit h corresponding to each cooling branch pipe 22 can be effectively cooled.

[0126] In the present application, all the heating units h in the system are turned on at full power, that is, the theoretical maximum heating value of the heating unit h, and the temperature difference between the temperature at the output end of the cooling branch 22 and the target temperature (the saturation temperature of the refrigerant at the output end of the cooling branch 22 at the current pressure) is compared, and the liquid supply of the delivery pump 11 is adjusted to the first liquid supply and the opening of the stop valve 222 at the input end of each cooling branch 22 is adjusted, so that all the heating units h can be effectively cooled, that is, the refrigerant at the output end of each cooling branch 22 just reaches the saturation temperature or just exceeds the saturation temperature by 1°C-2°C, which proves that all cooling branches 22 can complete the effective cooling of the corresponding heating units h.

[0127] Example 2

[0128] S1, controlling the liquid level of the liquid region 35: controlling the liquid level of the liquid region 35 in the gas-liquid separator 3 to be within a preset range, so that the liquid refrigerant in the liquid region 35 is pumped to the cooling pipe network 2;

[0129] S2. Roughly adjust the liquid supply amount: operate the heat generating unit h in the system at the maximum heat load, and adjust the liquid supply amount of the refrigeration host 1 to the first liquid supply amount, so that the heat generating unit h in the system can be effectively cooled.

[0130] S3. Regulating the flow of the cooling branch pipe 22: Regulating the opening of the stop valve 222 to regulate the flow in each cooling branch pipe 22 in the liquid supply mechanism, so that the heating unit h corresponding to each cooling branch pipe 22 can be effectively cooled.

[0131] S4, temperature comparison: after each heating unit h of the system operates normally, the temperature of the output end of each cooling branch pipe 22 in the liquid supply mechanism is obtained, and compared with the saturation temperature of the output end of the cooling branch pipe 22 to obtain the temperature difference;

[0132] S5. Fine-tuning the liquid supply amount: adjusting the liquid supply amount of the refrigeration host 1 to the second liquid supply amount, so that the heat generating unit h in the cooling branch pipe 22 with the largest temperature difference can be effectively cooled.

[0133] In the present application, after the heating units h of the system operate normally, some of the heating units h are shut down or the operating power is lowered, and the amount of refrigerant required is reduced accordingly. At this time, the temperature at the output end of each cooling branch pipe 22 can be compared with the target temperature (the saturation temperature under the pressure at the output end of the cooling branch pipe 22) to obtain the temperature difference at the output end of each cooling branch pipe 22. The maximum temperature difference is selected as the control target, and the liquid supply of the delivery pump 11 and the opening of the stop valve 222 at the input end of each cooling branch pipe 22 are adjusted to control the overall delivery amount of the refrigerant and the refrigerant entering each cooling branch. The flow rate of tube 22 is adjusted so that the cooling branch 22 of the above-mentioned control target (i.e., the cooling branch 22 with the largest temperature difference and the most unfavorable cooling) is in a slightly hot state, which proves that the refrigerant in this cooling branch 22 has been completely vaporized, and the vaporization degree of the refrigerant at the output end of other cooling branches 22 is less than or equal to that of the above-mentioned cooling branch 22, while the temperature and pressure at the output ends of multiple cooling branches 22 are close, and the refrigerant at the output ends of other cooling branches 22 is also close to complete vaporization, thereby ensuring effective cooling of the heating unit h and minimizing the waste of refrigerant.

[0134] It should be understood that the terms used herein are only for the purpose of describing specific example embodiments and are not intended to be limiting. Unless the context clearly indicates otherwise, the singular forms "one", "an" and "" as used herein may also be meant to include plural forms. The terms "include", "comprise", "contain", and "have" are inclusive and therefore specify the presence of stated features, steps, operations, elements and / or parts, but do not exclude the presence or addition of one or more other features, steps, operations, elements, parts, and / or combinations thereof. The method steps, processes, and operations described herein are not interpreted as necessarily requiring them to be performed in the specific order described or illustrated, unless the execution order is clearly indicated. It should also be understood that additional or alternative steps may be used.

[0135] Although the terms first, second, third, etc. can be used in the text to describe multiple elements, components, regions, layers and / or sections, these elements, components, regions, layers and / or sections should not be limited by these terms. These terms can only be used to distinguish an element, component, region, layer or section from another region, layer or section. Unless the context clearly indicates, terms such as "first", "second" and other numerical terms do not imply order or sequence when used in the text. Therefore, the first element, component, region, layer or section discussed below can be referred to as the second element, component, region, layer or section without departing from the teaching of the example embodiments.

[0136] The above is only a specific implementation of the present application, so that those skilled in the art can understand or implement the present application. Various modifications to these embodiments will be apparent to those skilled in the art, and the general principles defined herein can be implemented in other embodiments without departing from the spirit or scope of the present application. Therefore, the present application will not be limited to the embodiments shown herein, but will conform to the widest range consistent with the principles and novel features applied for herein.

Claims

1. A liquid supply mechanism, applied to a cooling system, the cooling system comprising a refrigeration host (1), characterized in that: The liquid supply mechanism comprises: A cooling pipe network (2), the cooling pipe network (2) comprising a liquid inlet main pipe (21), a cooling branch pipe (22) and a liquid return main pipe (23) which are connected to each other, the cooling branch pipe (22) being used for cooling the heating unit, and the liquid return main pipe (23) being connected to the liquid inlet end of the refrigeration main unit (1); and A gas-liquid separator (3) is arranged at the liquid outlet end of the refrigeration main unit (1), wherein the gas-liquid separator (3) is provided with a liquid region (35) at the bottom and a gas region (36) above the liquid region (35); Wherein, the input end of the liquid inlet main pipe (21) is in communication with the liquid region (35) of the gas-liquid separator (3).

2. The liquid supply mechanism according to claim 1, characterized in that: The gas-liquid separator (3) is provided with an exhaust pipeline (31) which is in communication with the gaseous region (36), and the exhaust pipeline (31) is provided with a first valve body (32).

3. The liquid supply mechanism according to claim 2, characterized in that: A first liquid level sensor (33) for detecting the liquid level is disposed inside the gas-liquid separator (3), and the first liquid level sensor (33) is electrically connected to the first valve body (32); When the liquid level of the liquid area (35) drops to the detection end of the first liquid level sensor (33), the first valve body (32) opens.

4. The liquid supply mechanism according to claim 3, characterized in that: A second liquid level sensor (34) for detecting the liquid level is disposed inside the gas-liquid separator (3), the second liquid level sensor (34) is electrically connected to the first valve body (32), and the second liquid level sensor (34) is located above the first liquid level sensor (33); When the liquid level of the liquid area (35) rises to the detection end of the second liquid level sensor (34), the first valve body (32) is closed.

5. The liquid supply mechanism according to claim 2, characterized in that: One end of the exhaust pipe (31) away from the gaseous region (36) is connected to the liquid return main pipe (23); and / or, One end of the exhaust pipe (31) away from the gaseous region (36) is connected to the refrigeration main unit (1).

6. The liquid supply mechanism according to claim 1, characterized in that: The cooling branch pipe (22) comprises a plurality of cooling branches (221) arranged in parallel, and the plurality of cooling branches (221) are respectively used to cool a plurality of groups of heating units.

7. The liquid supply mechanism according to claim 6, characterized in that: The cooling branch (221) comprises an input pipeline (2211) located at the front end of the heating unit and an output pipeline (2212) located at the rear end of the heating unit; The resistance in the input pipeline (2211) is a, and the resistance in the output pipeline (2212) is b, wherein cd≤a+b≤c+d, wherein c is the standard resistance value in the cooling branch (221), and d is the error value.

8. The liquid supply mechanism according to claim 7, characterized in that: The inner diameters of the input pipeline (2211) and the output pipeline (2212) are equal, the effective length of the cooling branch (221) is equal to the sum of the length of the input pipeline (2211) and the length of the output pipeline (2212), and the effective lengths of multiple cooling branches (221) are equal.

9. The liquid supply mechanism according to claim 1, characterized in that: A plurality of cooling branch pipes (22) are arranged in parallel, the input ends of the plurality of cooling branch pipes (22) are connected to the liquid inlet main pipe (21), the output ends of the plurality of cooling branch pipes (22) are connected to the liquid return main pipe (23), and stop valves (222) are respectively arranged at the input ends of the plurality of cooling branch pipes (22).

10. The liquid supply mechanism according to claim 9, characterized in that: The cooling branch pipe (22) further comprises a pressure sensor (223), wherein the pressure sensor (223) is used to detect the pressure at the output end of the cooling branch pipe (22).

11. The liquid supply mechanism according to claim 9, characterized in that: The cooling branch pipe (22) also includes a temperature sensor (224), and the temperature sensor (224) is used to detect the temperature of the output end of the cooling branch pipe (22).

12. The liquid supply mechanism according to any one of claims 9 to 11, characterized in that: The cooling branch pipe (22) has two output ends, and two adjacent cooling branch pipes (22) share one output end.

13. A cooling system, characterized in that: include: A refrigeration main unit (1), the refrigeration main unit (1) comprising a delivery pump (11); as well as A liquid supply mechanism as claimed in any one of claims 1 to 12.

14. A method for controlling liquid supply of a liquid supply mechanism according to any one of claims 1 to 12, characterized in that: The steps include: The liquid level of the liquid region (35) in the gas-liquid separator (3) is controlled based on a preset range so that the liquid refrigerant in the liquid region (35) is transmitted to the liquid inlet main pipe (21) of the cooling pipe network (2).

15. The liquid supply control method according to claim 14, characterized in that: The gas-liquid separator (3) is provided with an exhaust pipeline (31) connected to the gaseous region (36), and the exhaust pipeline (31) is provided with a first valve body (32); a first liquid level sensor (33) for detecting the liquid level is provided inside the gas-liquid separator (3), and the first liquid level sensor (33) is electrically connected to the first valve body (32); the liquid level of the liquid region (35) in the gas-liquid separator (3) is controlled based on a preset range, comprising: Detecting, by means of a first liquid level sensor (33), whether the liquid level of the liquid area (35) reaches the lower limit of the preset range; If it is detected that the liquid level of the liquid region (35) reaches the lower limit of the preset range, the first valve body (32) is controlled to open so that the gaseous refrigerant in the gas region (36) is discharged through the exhaust pipe (31), so that the liquid level of the liquid region (35) rises.

16. The liquid supply control method according to claim 15, characterized in that: A second liquid level sensor (34) for detecting the liquid level is disposed inside the gas-liquid separator (3), the second liquid level sensor (34) is electrically connected to the first valve body (32), and the second liquid level sensor (34) is located above the first liquid level sensor (33); the liquid level of the liquid area (35) in the gas-liquid separator (3) is controlled based on a preset range, comprising: detecting, by means of a second liquid level sensor (34), whether the liquid level of the liquid area (35) reaches an upper limit of the preset range; If it is detected that the liquid level of the liquid area (35) reaches the upper limit of the preset range, the first valve body (32) is controlled to close.

17. The liquid supply control method according to claim 14, characterized in that: The liquid supply mechanism is applied to a cooling system, and the liquid supply control method further comprises: When the heat generating unit in the cooling system is running at the maximum heat load, the liquid supply amount of the refrigeration host (1) in the cooling system is adjusted to a first liquid supply amount so that the heat generating unit in the cooling system is effectively cooled.

18. The liquid supply control method according to claim 17, characterized in that: The input ends of the cooling branches (22) are respectively provided with stop valves (222), and the liquid supply control method further comprises: The opening of the stop valve (222) is adjusted to adjust the flow rate in each cooling branch pipe (22) in the liquid supply mechanism, so that the heating unit corresponding to each cooling branch pipe (22) can be effectively cooled.

19. The liquid supply control method according to claim 17 or 18, characterized in that: Also includes: After each heating unit of the cooling system operates normally, the temperature of the output end of each cooling branch pipe (22) in the liquid supply mechanism is obtained, and compared with the saturation temperature of the output end of the cooling branch pipe (22) to determine the temperature difference; The liquid supply amount of the refrigeration main unit (1) is adjusted to a second liquid supply amount so that the heat generating unit in the cooling branch pipe (22) with the largest temperature difference can be effectively cooled.

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