Immersion Liquid Cooling Cabinet Cooling System and Control Method

Abstract

The present invention provides an immersion liquid-cooled cabinet cooling system and a control method. The cooling system includes: a liquid-cooling cycle, which includes a liquid-cooling terminal, a first liquid pump, a first intermediate heat exchanger, and a second intermediate heat exchanger, and has a first secondary coolant; a compression refrigeration cycle, which includes a compressor, a throttling element, and a condensation heat exchanger connected by pipelines, and the refrigerant therein forms a heat exchange with the first secondary coolant in the second intermediate heat exchanger; a waste heat recovery cycle, and the second secondary coolant therein can form a heat exchange with the first secondary coolant in the first intermediate heat exchanger, and the second secondary coolant can also form a heat exchange with the refrigerant in the condensation heat exchanger. The present invention can control at least one of the two cold sources to cool the liquid-cooling cycle according to the temperature of the second secondary coolant, make greater use of natural cold sources, reduce the energy consumption of the unit in high-temperature seasons; realize waste heat utilization, avoid meaningless dissipation of energy, and reduce thermal pollution to the environment.

Description

Technical Field

[0001] The present invention belongs to the technical field of cabinet cooling, and particularly relates to an immersion liquid cooling cabinet cooling system and a control method thereof. Background Art

[0002] With the increase in the data processing capacity and data transmission speed of data centers, which leads to an increase in the chip power density, the heat dissipation requirements of data centers have been further improved. For traditional air cooling of components such as servers, it is necessary to equip fans with higher speeds and larger diameters, as well as larger-volume heat dissipation channels to meet the requirements, which results in an increase in noise in the corresponding space, an exacerbation of environmental heat effects, and an increase in construction costs and operating costs. To meet the development needs of data centers, the development of immersion liquid cooling technology has become the most ideal data center refrigeration solution.

[0003] Existing immersion liquid cooling technologies are mainly divided into direct cooling and indirect cooling. Among them, indirect cooling is mainly cold plate liquid cooling, and direct cooling includes single-phase immersion liquid cooling, two-phase immersion liquid cooling, and single-phase spray liquid cooling. Single-phase immersion liquid cooling is to directly immerse the server in electronic fluorinated liquid, enabling heat exchange of each electronic component thereon. After the electronic fluorinated liquid absorbs heat from it, it releases heat through an external circulation cold source, thereby realizing the overall cooling cycle of the server. Among them, single-phase immersion liquid cooling is simpler and has a relatively lower price compared with two-phase immersion liquid cooling, and there is no need to consider the problems of vapor escape during the phase change of the cooling liquid and the selection of the cooling liquid.

[0004] The inventor found that most of the immersion liquid cooling cabinet cooling systems in the related art adopt a single external circulation cold source, such as one of the cooling water circulation of a cooling tower or the refrigerant circulation of a compressor. When the external environment is in a high-temperature or low-temperature working condition, a single external circulation cold source is difficult to have high energy efficiency, which further leads to a relatively high overall annual energy consumption and low energy efficiency of the unit cooling system. In addition, the heat absorbed by the circulating cooling in the related art cannot be recycled, which causes meaningless energy dissipation. Currently, the liquid cooling cabinet cooling system will cause a certain degree of heat pollution to the environment to some extent. Summary of the Invention

[0005] Therefore, the present invention provides an immersion liquid cooling cabinet cooling system and a control method thereof, which can solve the technical problems in the prior art that the cabinet cooling system adopting a single external circulation cold source cannot have high energy efficiency, the overall annual energy consumption of the unit cooling system is relatively high and the energy efficiency is low, and at the same time, the cooling system cannot effectively recycle the heat of the heat dissipation equipment (such as servers in data centers), resulting in meaningless energy dissipation and causing a certain degree of heat pollution to the environment.

[0006] To solve the above problems, the present invention provides an immersion liquid cooling cabinet cooling system, including:

[0007] A liquid cooling cycle, including a liquid cooling terminal, a first liquid pump, a first intermediate heat exchanger and a second intermediate heat exchanger connected by pipelines. The first liquid pump is used to drive a first secondary refrigerant to circulate in the liquid cooling cycle, and the equipment to be cooled is immersed in the first secondary refrigerant in the liquid cooling terminal;

[0008] A compression refrigeration cycle, including a compressor, a throttling element and a condensation heat exchanger connected by pipelines. The refrigerant in the exhaust pipeline of the compressor exchanges heat with the first secondary refrigerant in the second intermediate heat exchanger;

[0009] A waste heat recovery cycle, including a second liquid pump and a waste heat recovery and utilization device, which is used to drive a second secondary refrigerant to circulate in the waste heat recovery cycle, and the second secondary refrigerant can exchange heat with the first secondary refrigerant in the first intermediate heat exchanger, and the second secondary refrigerant can also exchange heat with the refrigerant in the condensation heat exchanger.

[0010] In some embodiments,

[0011] The liquid cooling cycle further includes a first flow path control valve group connected to the first side of the first intermediate heat exchanger and a second flow path control valve group connected to the first side of the second intermediate heat exchanger. The compression refrigeration cycle further includes a third flow path control valve group connected to the second side of the condensation heat exchanger. The waste heat recovery cycle further includes a fourth flow path control valve group connected to the second side of the first intermediate heat exchanger. The first flow path control valve group, the second flow path control valve group, the third flow path control valve group and the fourth flow path control valve group can adjust the heat exchange occurrence positions among the first secondary refrigerant, the second secondary refrigerant and the refrigerant.

[0012] In some embodiments,

[0013] The first pipeline is connected to the first refrigerant carrier inlet on the first side of the first intermediate heat exchanger, and the second pipeline is connected to the first refrigerant carrier outlet on the first side of the first intermediate heat exchanger. The first flow path control valve group includes a first solenoid valve connected in series on the first pipeline and a second solenoid valve connected in series on the second pipeline; the third pipeline is connected to the first refrigerant carrier inlet on the first side of the second intermediate heat exchanger, and the fourth pipeline is connected to the first refrigerant carrier outlet on the first side of the second intermediate heat exchanger. The second flow path control valve group includes a third solenoid valve connected in series on the third pipeline and a fourth solenoid valve connected in series on the fourth pipeline. The ends of the first pipeline and the second pipeline far from the first intermediate heat exchanger and the ends of the third pipeline and the fourth pipeline far from the second intermediate heat exchanger are connected in parallel to the fifth pipeline. The first flow path control valve group further includes a fifth solenoid valve connected in series on the fifth pipeline and located between the first pipeline and the second pipeline. The second flow path control valve group further includes a sixth solenoid valve connected in series on the fifth pipeline and located between the third pipeline and the fourth pipeline.

[0014] In some embodiments,

[0015] The sixth pipeline is connected to the second refrigerant carrier inlet on the second side of the condensation heat exchanger, and the seventh pipeline is connected to the second refrigerant carrier outlet on the second side of the condensation heat exchanger. The third flow path control valve group includes a seventh solenoid valve connected in series on the sixth pipeline and an eighth solenoid valve connected in series on the seventh pipeline; the eighth pipeline is connected to the second refrigerant carrier inlet on the second side of the first intermediate heat exchanger, and the ninth pipeline is connected to the second refrigerant carrier outlet on the second side of the first intermediate heat exchanger. The fourth flow path control valve group includes a ninth solenoid valve connected in series on the eighth pipeline and a tenth solenoid valve connected in series on the ninth pipeline; the ends of the sixth pipeline and the seventh pipeline far from the condensation heat exchanger and the ends of the eighth pipeline and the ninth pipeline far from the first intermediate heat exchanger are connected in parallel to the tenth pipeline. The third flow path control valve group further includes an eleventh solenoid valve connected in series on the tenth pipeline and located between the sixth pipeline and the seventh pipeline. The fourth flow path control valve group further includes a twelfth solenoid valve connected in series on the tenth pipeline and located between the eighth pipeline and the ninth pipeline.

[0016] In some embodiments,

[0017] The waste heat recovery cycle further includes a heat recovery liquid supply pipe and a heat recovery liquid return pipe. Among them, the outlet of the heat recovery liquid supply pipe communicates with one end of the eighth pipeline away from the first intermediate heat exchanger, and a thirteenth solenoid valve is connected in series on the heat recovery liquid supply pipe. The heat recovery liquid return pipe communicates with one end of the seventh pipeline away from the condensation heat exchanger, and a fourteenth solenoid valve is connected in series on the heat recovery liquid return pipe; and / or, a first liquid treatment device is connected in series on the heat recovery liquid return pipe, and / or, a second liquid treatment device is connected in series on the pipeline between the first liquid pump and the first pipeline.

[0018] In some embodiments, it further includes:

[0019] A cooling tower liquid supply pipeline and a cooling tower liquid return pipeline. One end of the cooling tower liquid supply pipeline is connected to the cooling tower, and the other end is connected to one end of the eighth pipeline away from the first intermediate heat exchanger through a nineteenth solenoid valve. One end of the cooling tower liquid return pipeline is connected to the cooling tower, and the other end is connected to one end of the heat recovery liquid return pipe away from the condensation heat exchanger through a twentieth solenoid valve, and the twentieth solenoid valve is connected in parallel with the fourteenth solenoid valve. A twenty-first solenoid valve is connected in series on the flow pipeline between the second liquid pump and the twelfth solenoid valve and the twenty-first solenoid valve is connected in series on the ninth pipeline. The secondary coolant for the internal circulation of the cooling tower is the second secondary coolant.

[0020] In some embodiments,

[0021] A fifteenth solenoid valve is connected in series on one of the liquid inlet pipe and the liquid outlet pipe of the liquid cooling terminal, and a flow regulating valve is connected in series on the other; and / or, there are multiple liquid cooling terminals, and multiple said liquid cooling terminals are connected in parallel within the liquid cooling cycle.

[0022] In some embodiments,

[0023] The liquid cooling cycle further includes a cold storage device. The cold storage device is connected to the liquid inlet pipe of the liquid cooling terminal through a fifth flow path control valve group, and the fifth flow path control valve group can control whether the first secondary coolant in the liquid inlet pipe flows through the cold storage device or not.

[0024] In some embodiments,

[0025] The fifth flow path control valve group includes a sixteenth solenoid valve connected in series on the inlet pipe of the cold storage device, a seventeenth solenoid valve connected in series on the outlet pipe of the cold storage device, and an eighteenth solenoid valve connected in series on the liquid inlet pipe and located between the inlet pipe and the outlet pipe.

[0026] The present invention also provides a control method for the immersion liquid cooling cabinet cooling system as described above, which is characterized by including the following steps:

[0027] Obtain the system operation instructions;

[0028] When the system operation instruction is a heat recovery instruction, obtain the real-time temperature Tr of the second coolant in the heat recovery liquid supply pipe of the waste heat recovery cycle;

[0029] According to the temperature range where the Tr is located, control and adjust the heat exchange occurrence positions of the first coolant in the liquid cooling cycle, the refrigerant in the compression refrigeration cycle, and the second coolant in the waste heat recovery cycle.

[0030] In some embodiments, according to the temperature range where the Tr is located, controlling and adjusting the heat exchange occurrence positions of the first coolant in the liquid cooling cycle, the refrigerant in the compression refrigeration cycle, and the second coolant in the waste heat recovery cycle includes:

[0031] When Tr < Tr1, control the first coolant and the second coolant to exchange heat at the first intermediate heat exchanger; or,

[0032] When Tr1 ≤ Tr < Tr2, control the first coolant and the second coolant to exchange heat at the first intermediate heat exchanger, control the first coolant and the refrigerant to exchange heat at the second intermediate heat exchanger, and control the second coolant after exchanging heat with the first coolant to exchange heat with the refrigerant again at the condensation heat exchanger; or,

[0033] When Tr2 ≤ Tr < Tr3, control the first coolant and the refrigerant to exchange heat at the second intermediate heat exchanger, and control the second coolant and the refrigerant to exchange heat at the condensation heat exchanger;

[0034] The first preset water inlet temperature Tr1 < the second preset water inlet temperature Tr2 < the third preset water inlet temperature Tr3.

[0035] In some embodiments, when the immersion liquid cooling cabinet cooling system includes a cooling tower liquid supply pipeline and a cooling tower liquid return pipeline,

[0036] When Tr ≥ Tr3, control the cooling tower liquid supply pipeline to be connected to the heat recovery liquid supply pipe, control the cooling tower liquid return pipeline to be connected to the heat recovery liquid return pipe, and according to the temperature range of the real-time temperature Tr after the cooling tower liquid supply pipeline and the heat recovery liquid supply pipe are connected and mixed, control and adjust the heat exchange occurrence positions of the first coolant in the liquid cooling cycle, the refrigerant in the compression refrigeration cycle, and the second coolant in the waste heat recovery cycle.

[0037] In some embodiments,

[0038] When the system operation instruction is the normal operation instruction of the unit, obtain the outdoor ambient temperature Tout;

[0039] According to the temperature range where the Tout is located, control and adjust the heat exchange occurrence positions of the first secondary refrigerant in the liquid cooling cycle, the refrigerant in the compression refrigeration cycle, and the second secondary refrigerant in the cooling tower.

[0040] In some embodiments, according to the temperature range where the Tout is located, controlling and adjusting the heat exchange occurrence positions of the first secondary refrigerant in the liquid cooling cycle, the refrigerant in the compression refrigeration cycle, and the second secondary refrigerant in the cooling tower includes:

[0041] When Tout > T3, control the first secondary refrigerant and the refrigerant to exchange heat at the second intermediate heat exchanger 52, and control the second secondary refrigerant and the refrigerant to exchange heat at the condensation heat exchanger 51; or,

[0042] When T3 ≥ Tout > T2, control the first secondary refrigerant and the second secondary refrigerant to exchange heat at the first intermediate heat exchanger, the first secondary refrigerant and the refrigerant to exchange heat at the second intermediate heat exchanger, and control the second secondary refrigerant after exchanging heat with the first secondary refrigerant to exchange heat with the refrigerant again at the condensation heat exchanger; or,

[0043] When T2 ≥ Tout > T1, control the first secondary refrigerant and the second secondary refrigerant to exchange heat at the first intermediate heat exchanger; or,

[0044] When T1 ≥ Tout, control the first secondary refrigerant and the refrigerant to exchange heat at the second intermediate heat exchanger, and the refrigerant exchanges heat with the external ambient air at the condensation heat exchanger;

[0045] The first preset ambient temperature T1 < the second preset ambient temperature T2 < the third preset ambient temperature T3.

[0046] In some embodiments, when a cold storage device is included, the control method further includes:

[0047] Judge whether the power grid reaches the low valley period or the peak period;

[0048] When the power grid reaches the low valley period, control the first secondary refrigerant in the inlet pipe to enter the cold storage device for cold storage, and cut off the first secondary refrigerant from entering the cold storage device after the cold storage is completed; or,

[0049] When the cold storage device has completed cold storage and the power grid reaches the peak period, control the first secondary refrigerant in the liquid inlet pipe to enter the cold storage device so that the cold storage device releases cold to the first secondary refrigerant, and cut off the entry of the first secondary refrigerant into the cold storage device after the cold release is completed.

[0050] An immersion liquid-cooled cabinet cooling system and a control method provided by the present invention have the following beneficial effects:

[0051] It has both a compression refrigeration cycle and a waste heat recovery cycle as two cold sources. In this way, according to the temperature of the second secondary refrigerant in the waste heat recovery cycle, at least one of the foregoing two cold sources can be controlled to cool the liquid cooling cycle, which can make greater use of natural cold sources, reduce the energy consumption of the unit in high-temperature seasons, improve the utilization rate of natural cold sources in transitional seasons, and thus can improve the annual energy efficiency of the refrigeration unit (cooling system) and reduce the overall annual energy consumption of the refrigeration unit; at the same time, the heat in the liquid cooling cycle is transferred to the waste heat recovery and utilization equipment through the second secondary refrigerant in the waste heat recovery cycle to realize waste heat utilization, avoid meaningless dissipation of energy, and reduce the thermal pollution to the environment;

[0052] By controlling the opening and closing of the fifth flow path control valve group, the first secondary refrigerant can flow through or not flow through the cold storage device. In this way, it can be started during the low valley period of the power grid and the stored cold quantity can be released during the peak period of the power grid, so as to achieve the effects of energy conservation and consumption reduction and peak load shifting, and reduce the operation and maintenance costs of the data center to a certain extent. BRIEF DESCRIPTION OF THE DRAWINGS

[0053] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the following will briefly introduce the drawings required for use in the description of the embodiments or the prior art. Obviously, the drawings in the following description are only exemplary, and for those of ordinary skill in the art, without creative efforts, other implementation drawings can also be obtained according to the provided drawings.

[0054] The structures, ratios, sizes, etc. illustrated in this specification are only used to cooperate with the content disclosed in the specification for those who are familiar with this technology to understand and read, and are not used to limit the limited conditions that the present invention can be implemented. Therefore, they do not have technical essence. Any modification of the structure, change of the proportional relationship, or adjustment of the size, without affecting the effects that the present invention can produce and the purposes that can be achieved, should still fall within the scope that can be covered by the technical content disclosed by the present invention.

[0055] Figure 1 It is a schematic diagram of the principle of the immersion liquid-cooled cabinet cooling system according to an embodiment of the present invention, and the arrows in the figure show the flow directions of the liquids in the relevant pipelines;

[0056] Figure 2Schematic diagram of the operation of the natural cooling mode for waste heat recovery of the immersion liquid-cooled cabinet cooling system of the present invention;

[0057] Figure 3 Schematic diagram of the operation of the conventional refrigeration mode for waste heat recovery of the immersion liquid-cooled cabinet cooling system of the present invention;

[0058] Figure 4 Schematic diagram of the operation of the high-temperature refrigeration mode for waste heat recovery of the immersion liquid-cooled cabinet cooling system of the present invention;

[0059] Figure 5 Schematic diagram of the operation of the natural cooling mode with hybrid cold sources for the immersion liquid-cooled cabinet cooling system of the present invention;

[0060] Figure 6 Schematic diagram of the operation of the conventional refrigeration mode with hybrid cold sources for the immersion liquid-cooled cabinet cooling system of the present invention;

[0061] Figure 7 Schematic diagram of the operation of the high-temperature refrigeration mode with hybrid cold sources for the immersion liquid-cooled cabinet cooling system of the present invention;

[0062] Figure 8 Schematic diagram of the operation of the high-temperature refrigeration mode for the immersion liquid-cooled cabinet cooling system of the present invention;

[0063] Figure 9 Schematic diagram of the operation of the conventional refrigeration mode for the immersion liquid-cooled cabinet cooling system of the present invention;

[0064] Figure 10 Schematic diagram of the operation of the natural cooling mode for the immersion liquid-cooled cabinet cooling system of the present invention;

[0065] Figure 11 Schematic diagram of the operation of the low-temperature refrigeration mode for the immersion liquid-cooled cabinet cooling system of the present invention;

[0066] Figure 12 Schematic diagram of the system operation control method for the immersion liquid-cooled cabinet cooling system of another embodiment of the present invention.

[0067] The reference numerals are represented as:

[0068] 1. Liquid cooling terminal;

[0069] 21. First liquid pump; 22. Second liquid pump;

[0070] 31. Second liquid treatment device; 32. First liquid treatment device;

[0071] 4. First intermediate heat exchanger;

[0072] 51. Condensation heat exchanger; 52. Second intermediate heat exchanger;

[0073] 6. Throttle element;

[0074] 7. Compressor;

[0075] 8. Cold storage device;

[0076] 9. Flow regulating valve;

[0077] 101. Fifteenth solenoid valve; 102. Fifth solenoid valve; 103. Second solenoid valve; 104. First solenoid valve; 105. Ninth solenoid valve; 106. Tenth solenoid valve; 107. Twenty - first solenoid valve; 108. Twelfth solenoid valve; 109. Nineteenth solenoid valve; 110. Thirteenth solenoid valve; 111. Fourteenth solenoid valve; 112. Twentieth solenoid valve; 113. Eleventh solenoid valve; 114. Seventh solenoid valve; 115. Eighth solenoid valve; 116. Fourth solenoid valve; 117. Third solenoid valve; 118. Sixth solenoid valve; 119. Sixteenth solenoid valve; 120. Eighteenth solenoid valve; 121. Seventeenth solenoid valve. Detailed implementation manners

[0078] Next, the technical solutions in the embodiments of the present invention will be clearly and completely described in conjunction with the accompanying drawings in the embodiments of the present invention. Obviously, the described embodiments are only a part of the embodiments of the present invention, rather than all the embodiments. The following description of at least one exemplary embodiment is actually only illustrative and in no way restrictive of the present invention and its application or use. Based on the embodiments of the present invention, all other embodiments obtained by those of ordinary skill in the art without creative efforts belong to the scope of protection of the present invention.

[0079] It should be noted that the terms used herein are only for describing the specific implementation manners and are not intended to limit the exemplary embodiments according to the present application. As used herein, unless the context clearly indicates otherwise, the singular form is also intended to include the plural form. In addition, it should be understood that when the terms "comprise" and / or "include" are used in this specification, they indicate the presence of features, steps, operations, devices, components, and / or their combinations.

[0080] It should be understood that the term " / " used herein is generally used to indicate that the associated objects before and after are in an "or" relationship. The term "and / or" used herein is only a description of the associated relationship of the associated objects, indicating that three relationships may exist. For example, A and / or B may represent: A exists alone, A and B exist simultaneously, and B exists alone.

[0081] Unless otherwise specifically stated, the relative arrangement of components and steps, numerical expressions, and values set forth in these embodiments do not limit the scope of the present invention. At the same time, it should be understood that, for the sake of convenience of description, the dimensions of the various parts shown in the drawings are not drawn in actual proportional relationships. Technologies, methods, and devices known to those of ordinary skill in the relevant art may not be discussed in detail, but where appropriate, such technologies, methods, and devices should be regarded as part of the authorization specification. In all the examples shown and discussed here, any specific value should be construed as merely exemplary and not as a limitation. Therefore, other examples of the exemplary embodiments may have different values. It should be noted that like reference numerals and letters denote like items in the following drawings, and thus, once an item is defined in one drawing, further discussion thereof in subsequent drawings is not required.

[0082] In the description of the present invention, it should be understood that the orientation or positional relationship indicated by orientation words such as "front, rear, upper, lower, left, right", "lateral, vertical, perpendicular, horizontal", and "top, bottom", etc. is usually based on the orientation or positional relationship shown in the drawings. It is only for the convenience of describing the present invention and simplifying the description. Without contrary description, these orientation words do not indicate and imply that the device or element referred to must have a specific orientation or be constructed and operated in a specific orientation. Therefore, it should not be construed as limiting the protection scope of the present invention; the orientation words "inside, outside" refer to the inside and outside relative to the contour of each component itself.

[0083] For the convenience of description, spatial relative terms such as "above...", "over...", "on the upper surface of...", "above" can be used here to describe the spatial positional relationship of a device or feature shown in the drawings with other devices or features. It should be understood that the spatial relative terms are intended to include different orientations in use or operation in addition to the orientation described in the drawings for the device. For example, if the device in the drawing is inverted, the device described as "above other devices or structures" or "over other devices or structures" will then be positioned "below other devices or structures" or "under other devices or structures". Thus, the exemplary term "above..." can include both the orientations of "above..." and "below...". The device can also be positioned in other different ways (rotated 90 degrees or in other orientations), and corresponding interpretations are made for the spatial relative descriptions used here.

[0084] In addition, it should be noted that the use of words such as "first", "second" to limit components is only for the convenience of distinguishing the corresponding components. Without otherwise stating, the above words have no special meanings. Therefore, it should not be construed as limiting the protection scope of the present invention.

[0085] See in combination Figure 1and Figure 12 As shown, according to an embodiment of the present invention, an immersion liquid-cooled cabinet cooling system is provided. Specifically, refer to Figure 1 shown. The cooling system includes:

[0086] A liquid-cooling cycle, including a liquid-cooling terminal 1, a first liquid pump 21, a first intermediate heat exchanger 4, and a second intermediate heat exchanger 52 connected by pipelines. The first liquid pump 21 is used to drive the first secondary refrigerant to circulate in the liquid-cooling cycle. The equipment to be cooled is immersed in the first secondary refrigerant in the liquid-cooling terminal 1, so as to realize the cooling and heat dissipation of the equipment to be cooled through the phase change of the first secondary refrigerant. The aforementioned equipment to be cooled can specifically be a server in a data center, etc. The aforementioned first secondary refrigerant can adopt working media such as electronic fluorinated liquid or mineral oil that can realize immersion liquid-cooling cycles;

[0087] A compression refrigeration cycle, including a compressor 7, a throttling element 6, and a condensation heat exchanger 51 connected by pipelines. The refrigerant in the exhaust pipeline of the compressor 7 forms a heat exchange with the first secondary refrigerant in the second intermediate heat exchanger 52. That is, the second intermediate heat exchanger 52 is shared by the compression refrigeration cycle and the liquid-cooling cycle. The working media in the corresponding pipelines of the two cycles can form a heat exchange in the second intermediate heat exchanger 52. The aforementioned refrigerant is specifically the refrigerant in the current compression refrigeration cycle system. Specifically, the second intermediate heat exchanger 52 serves as the evaporation side of the compression refrigeration cycle, while the condensation heat exchanger 51 serves as the condensation side of the compression refrigeration cycle;

[0088] A waste heat recovery cycle, including a waste heat recovery and utilization device (not shown in the figure), a second liquid pump 22, which is used to drive the second secondary refrigerant to circulate in the waste heat recovery cycle, and the second secondary refrigerant can form a heat exchange with the first secondary refrigerant in the first intermediate heat exchanger 4, and the second secondary refrigerant can also form a heat exchange with the refrigerant in the condensation heat exchanger 51. In a specific embodiment, the second secondary refrigerant can specifically adopt cooling water.

[0089] In the immersion liquid cooling cabinet cooling system of this technical solution, there are two cold sources, namely the compression refrigeration cycle and the waste heat recovery cycle. In this way, according to the temperature of the second secondary coolant in the waste heat recovery cycle, at least one of the two cold sources can be controlled to cool the liquid cooling cycle, which can make greater use of natural cold sources, reduce the energy consumption of the unit in high-temperature seasons, improve the utilization rate of natural cold sources in transitional seasons, and thus improve the annual energy efficiency of the refrigeration unit (cooling system) and reduce the overall annual energy consumption of the refrigeration unit. At the same time, through the second secondary coolant in the waste heat recovery cycle, the heat in the liquid cooling cycle is transferred to the waste heat utilization equipment to realize waste heat utilization, avoid meaningless dissipation of energy, and reduce the thermal pollution to the environment. It should be noted that the liquid cooling cycle in this application is an immersion liquid cooling cycle. By using this immersion liquid cooling cycle to dissipate heat from the equipment to be cooled in the liquid cooling terminal 1, the heat dissipation energy consumption of the data center can be greatly reduced, the heat dissipation capacity of the terminal can be enhanced, and at the same time, the control difficulty and operating noise of the data center cooling system can be reduced.

[0090] The aforementioned waste heat recovery cycle can extract low-grade heat sources for use in heating nearby residents or industries, saving heating costs and reducing the power consumption of the cold source system. At this time, the waste heat utilization equipment is specifically a heat dissipation terminal such as a radiator on the indoor side of the user. In some other feasible operating conditions, the waste heat utilization equipment can also be other components, such as a domestic hot water tank, which will not be elaborated here. It should be noted that compared with traditional air-cooled data centers, the return liquid temperature of the immersion liquid cooling coolant (i.e., the temperature at which the waste heat recovery cycle delivers liquid to the waste heat utilization equipment) can reach 45°C, which is 15 - 25°C higher than the return air temperature of air-cooled data centers, and has greater advantages in terms of higher and more stable waste heat recovery efficiency.

[0091] In some embodiments,

[0092] The liquid cooling cycle further includes a first flow path control valve group (not labeled in the figure) connected to the first side of the first intermediate heat exchanger 4 and a second flow path control valve group (not labeled in the figure) connected to the first side of the second intermediate heat exchanger 52. The compression refrigeration cycle further includes a third flow path control valve group (not labeled in the figure) connected to the second side of the condensation heat exchanger 51. The waste heat recovery cycle further includes a fourth flow path control valve group (not labeled in the figure) connected to the second side of the first intermediate heat exchanger 4. The first flow path control valve group, the second flow path control valve group, the third flow path control valve group, and the fourth flow path control valve group can adjust the heat exchange positions among the first secondary coolant, the second secondary coolant, and the refrigerant.

[0093] In this technical solution, the flow directions of the first secondary refrigerant, the second secondary refrigerant, and the refrigerant are adjusted through the first flow path control valve group, the second flow path control valve group, the third control valve group, and the fourth control valve group, thereby adjusting the heat exchange occurrence positions of the three heat exchange media, making the pipeline layout of the cooling system of the architecture reasonable and the structure relatively compact.

[0094] As a specific implementation manner, the first pipeline is connected to the first secondary refrigerant inlet at the first side of the first intermediate heat exchanger 4, the second pipeline is connected to the first secondary refrigerant outlet at the first side of the first intermediate heat exchanger 4, the first flow path control valve group includes a first solenoid valve 104 connected in series on the first pipeline and a second solenoid valve 103 connected in series on the second pipeline; the third pipeline is connected to the first secondary refrigerant inlet at the first side of the second intermediate heat exchanger 52, the fourth pipeline is connected to the first secondary refrigerant outlet at the first side of the second intermediate heat exchanger 52, the second flow path control valve group includes a third solenoid valve 117 connected in series on the third pipeline and a fourth solenoid valve 116 connected in series on the fourth pipeline, one ends of the first pipeline and the second pipeline far from the first intermediate heat exchanger 4 and one ends of the third pipeline and the fourth pipeline far from the second intermediate heat exchanger 52 are connected in parallel to the fifth pipeline, the first flow path control valve group further includes a fifth solenoid valve 102 connected in series on the fifth pipeline and located between the first pipeline and the second pipeline, and the second flow path control valve group further includes a sixth solenoid valve 118 connected in series on the fifth pipeline and located between the third pipeline and the fourth pipeline.

[0095] The sixth pipeline is connected to the second secondary refrigerant inlet on the second side of the condensation heat exchanger 51, and the seventh pipeline is connected to the second secondary refrigerant outlet on the second side of the condensation heat exchanger 51. The third flow path control valve group includes a seventh solenoid valve 114 connected in series on the sixth pipeline and an eighth solenoid valve 115 connected in series on the seventh pipeline; the eighth pipeline is connected to the second secondary refrigerant inlet on the second side of the first intermediate heat exchanger 4, and the ninth pipeline is connected to the second secondary refrigerant outlet on the second side of the first intermediate heat exchanger 4. The fourth flow path control valve group includes a ninth solenoid valve 105 connected in series on the eighth pipeline and a tenth solenoid valve 106 connected in series on the ninth pipeline; one end of the sixth pipeline and the seventh pipeline away from the condensation heat exchanger 51 and one end of the eighth pipeline and the ninth pipeline away from the first intermediate heat exchanger 4 are connected in parallel to the tenth pipeline. The third flow path control valve group further includes an eleventh solenoid valve 113 connected in series on the tenth pipeline and between the sixth pipeline and the seventh pipeline, and the fourth flow path control valve group further includes a twelfth solenoid valve 108 connected in series on the tenth pipeline and between the eighth pipeline and the ninth pipeline. In this technical solution, by controlling the on-off of the solenoid valves on each pipeline, the flow direction of each refrigeration medium is adjusted. The on-off of the solenoid valve is used to achieve flow control, and the control is simple and reliable.

[0096] In some embodiments, the waste heat recovery cycle further includes a heat recovery liquid supply pipe (not labeled in the figure) and a heat recovery liquid return pipe (not labeled in the figure). Among them, the outlet of the liquid supply pipe is communicated with one end of the eighth pipeline away from the first intermediate heat exchanger 4, and a thirteenth solenoid valve 110 is connected in series on the liquid supply pipe. The liquid return pipe is communicated with one end of the seventh pipeline away from the condensation heat exchanger 51, and a fourteenth solenoid valve 111 is connected in series on the heat recovery liquid return pipe. By controlling the on-off of the thirteenth solenoid valve 110 and the fourteenth solenoid valve 111, the flow of the second secondary refrigerant can be completely cut off under the condition that the waste heat recovery cycle does not participate in cooling and heat dissipation. At the same time, this design also facilitates the maintenance of the waste heat recovery cycle on the pipeline side of the first intermediate heat exchanger 4 and the condensation heat exchanger 51.

[0097] In a preferred embodiment, a first liquid treatment device 32 is connected in series on the liquid return pipe, and / or a second liquid treatment device 31 is connected in series on the pipeline between the first liquid pump 21 and the first pipeline, for filtering and cleaning the first secondary refrigerant and the second secondary refrigerant.

[0098] In a preferred embodiment, the cooling system further includes: a cooling tower liquid supply pipeline and a cooling tower liquid return pipeline. One end of the cooling tower liquid supply pipeline is communicated with a cooling tower (not shown in the figure), and the other end is communicated with the end of the eighth pipeline far from the first intermediate heat exchanger 4 through a nineteenth solenoid valve 109. One end of the cooling tower liquid return pipeline is communicated with the cooling tower, and the other end is communicated with the end of the heat recovery liquid return pipe far from the condensation heat exchanger 51 through a twentieth solenoid valve 112. The twentieth solenoid valve 112 is connected in parallel with the fourteenth solenoid valve 111. A twenty-first solenoid valve 107 is connected in series on the pipeline between the second liquid pump 22 and the twelfth solenoid valve 108, and the twenty-first solenoid valve 107 is connected in series on the ninth pipeline. The secondary coolant circulating in the cooling tower is the second secondary coolant.

[0099] In this technical solution, by arranging the cooling tower, a mixed flow can be formed with the waste heat recovery cycle. Thus, when the temperature of the second secondary coolant in the waste heat recovery cycle is too high, resulting in a low heat dissipation efficiency (low energy efficiency and high energy consumption) for the liquid cooling cycle, the secondary coolant in the cooling tower can be controlled to mix and flow into the waste heat recovery cycle, thereby improving the cooling efficiency. In a preferred embodiment, the second secondary coolant can be water. It can be understood that some pipelines and solenoid valves of the cooling tower and the waste heat recovery cycle are shared, enabling the cooling system of the present invention to have a three-cooling-source system including a compression refrigeration cycle, a waste heat recovery cycle, and a cooling tower water cycle. Since most of the pipelines and solenoid valves of the waste heat recovery cycle and the cooling tower water cycle are shared, while improving the energy efficiency of the system (unit), the system structure is greatly simplified and the system construction cost is reduced.

[0100] In some embodiments, a fifteenth solenoid valve 101 is connected in series on one of the liquid inlet pipe (not labeled in the figure) and the liquid outlet pipe (not labeled in the figure) of the liquid cooling terminal 1, and a flow regulating valve 9 is connected in series on the other one; and / or, there are multiple liquid cooling terminals 1, and the multiple liquid cooling terminals 1 are connected in parallel in the liquid cooling cycle.

[0101] In this technical solution, the flow regulating valve 9 is located inside the liquid cooling terminal 1, and can adjust the coolant flow according to the real-time load change of the liquid cooling terminal 1 to achieve a reasonable distribution of cooling capacity.

[0102] In another feasible embodiment, the liquid cooling cycle further includes a cold storage device 8, and the cold storage device 8 is connected to the liquid inlet pipe of the liquid cooling terminal 1 through a fifth flow path control valve group (not labeled in the figure). The fifth flow path control valve group can control whether the first secondary refrigerant in the liquid inlet pipe flows through the cold storage device 8 or not. Specifically, the fifth flow path control valve group includes a sixteenth solenoid valve 119 connected in series on the inlet pipe of the cold storage device 8, a seventeenth solenoid valve 121 connected in series on the outlet pipe of the cold storage device 8, and an eighteenth solenoid valve 120 connected in series on the liquid inlet pipe and between the inlet pipe and the outlet pipe.

[0103] In this technical solution, by controlling the on-off of the fifth flow path control valve group, the first secondary refrigerant can be made to flow through or not flow through the cold storage device 8. In this way, it can be turned on during the low grid period and the stored cold can be released during the high grid period, so as to achieve the effects of energy conservation and consumption reduction and peak-shifting power consumption, and to a certain extent reduce the operation and maintenance costs of the data center.

[0104] According to an embodiment of the present invention, there is also provided a control method for an immersion liquid cooling cabinet cooling system as described above, including the following steps:

[0105] Obtain the system operation instruction;

[0106] When the system operation instruction is a heat recovery instruction, obtain the real-time temperature Tr of the second secondary refrigerant in the heat recovery liquid supply pipe of the waste heat recovery cycle;

[0107] According to the temperature range where the Tr is located, control and adjust the heat exchange occurrence positions of the first secondary refrigerant in the liquid cooling cycle, the refrigerant in the compression refrigeration cycle, and the second secondary refrigerant in the waste heat recovery cycle.

[0108] In this technical solution, there are two cold sources, namely the compression refrigeration cycle and the waste heat recovery cycle. In this way, according to the temperature of the second secondary refrigerant in the waste heat recovery cycle, at least one of the foregoing two cold sources can be controlled to cool the liquid cooling cycle, so that the natural cold source can be utilized to a large extent, the energy consumption of the unit in the high temperature season can be reduced, the utilization rate of the natural cold source in the transitional season can be improved, and thus the annual energy efficiency of the refrigeration unit (cooling system) can be improved and the overall annual energy consumption of the refrigeration unit can be reduced; at the same time, the heat in the liquid cooling cycle is transferred to the waste heat recovery and utilization equipment through the second secondary refrigerant in the waste heat recovery cycle to realize waste heat utilization, avoid meaningless dissipation of energy, and reduce the thermal pollution to the environment.

[0109] In some embodiments, according to the temperature range where the Tr is located, controlling and adjusting the heat exchange occurrence positions of the first secondary refrigerant in the liquid cooling cycle, the refrigerant in the compression refrigeration cycle, and the second secondary refrigerant in the waste heat recovery cycle includes:

[0110] When Tr < Tr1, control the heat exchange between the first secondary refrigerant and the second secondary refrigerant at the first intermediate heat exchanger 4. At this time, the temperature of the second secondary refrigerant in the waste heat recovery cycle is relatively low, which can meet the cooling capacity required for the heat exchange of the first secondary refrigerant in the liquid cooling cycle. Therefore, at this time, the cooling system operates in the waste heat recovery natural cooling mode. As Figure 2 shown, in this mode: the liquid cooling terminal 1, the first liquid pump 21, the second liquid pump 22, the second liquid treatment device 31, the first liquid treatment device 32, the first intermediate heat exchanger 4, the cold storage device 8, the flow regulating valve 9, the fifteenth solenoid valve 101, the second solenoid valve 103, the first solenoid valve 104, the ninth solenoid valve 105, the tenth solenoid valve 106, the twelfth solenoid valve 108, the thirteenth solenoid valve 110, the fourteenth solenoid valve 111, the eleventh solenoid valve 113, the sixth solenoid valve 118, and the eighteenth solenoid valve 120 are opened (i.e., conducted), and the rest of the components are closed (i.e., cut off). At this time, the refrigeration unit (i.e., the compression refrigeration cycle) of the system is turned off, and the cold source system side provides cold by the heat recovery return water. The coolant (i.e., the first secondary refrigerant) is cooled through the first intermediate heat exchanger 4 and then pumped to the heat recovery water use end by the second liquid pump 22; in the coolant system, the coolant exchanges heat with the heat recovery water at the first intermediate heat exchanger 4 to complete cooling, reaches the liquid cooling terminal 1 to cool the servers in the liquid cooling cabinet, and then is pumped to the first intermediate heat exchanger 4 by the first liquid pump 21 to complete heat dissipation for one cycle.

[0111] Or,

[0112] When Tr1 ≤ Tr < Tr2, control the heat exchange between the first secondary refrigerant and the second secondary refrigerant at the first intermediate heat exchanger 4, and control the heat exchange between the first secondary refrigerant and the refrigerant at the second intermediate heat exchanger 52. And control the second secondary refrigerant after heat exchange with the first secondary refrigerant to exchange heat with the refrigerant again at the condensation heat exchanger 51. At this time, the temperature of the second secondary refrigerant in the waste heat recovery cycle is relatively high and cannot fully meet the cooling capacity requirement of the first secondary refrigerant in the liquid cooling cycle. Therefore, at this time, control the compression refrigeration cycle to operate, and at the same time use the second secondary refrigerant to dissipate heat from the condensation heat exchanger of the compression refrigeration cycle. The cold quantity of the refrigerant in the compression refrigeration cycle is provided to the liquid cooling cycle at the second intermediate heat exchanger 52, improving the cooling energy efficiency of the unit. Therefore, at this time, the cooling system operates in the waste heat recovery conventional refrigeration mode, as Figure 3As shown, in this mode: the liquid cooling terminal 1, the first liquid pump 21, the second liquid pump 22, the second liquid treatment device 31, the first liquid treatment device 32, the first intermediate heat exchanger 4, the condensation heat exchanger 51, the second intermediate heat exchanger 52, the throttling element 6, the compressor 7, the cold storage device 8, the flow regulating valve 9, the fifteenth solenoid valve 101, the second solenoid valve 103, the first solenoid valve 104, the ninth solenoid valve 105, the tenth solenoid valve 106, the twelfth solenoid valve 108, the thirteenth solenoid valve 110, the fourteenth solenoid valve 111, the seventh solenoid valve 114, the eighth solenoid valve 115, the fourth solenoid valve 116, the third solenoid valve 117, and the eighteenth solenoid valve 120 are opened, and the rest of the components are closed. At this time, the refrigeration unit of the system is started, and the cold source system side provides cold energy by the heat recovery return water. First, the coolant is pre-cooled through the first intermediate heat exchanger 4, and then pumped by the second liquid pump 22 to the condensation heat exchanger 51 to cool the condensation end of the refrigeration unit, and finally pumped to the heat recovery water use end; in the refrigeration unit system, the refrigerant dissipates heat in the condensation heat exchanger 51, throttles through the throttling element 6, exchanges heat with the coolant system in the second intermediate heat exchanger 52, is compressed by the compressor 7, and exchanges heat with the cold source system in the condensation heat exchanger 51; in the coolant system (i.e., the liquid cooling cycle), the coolant first exchanges heat with the heat recovery water in the first intermediate heat exchanger 4 to complete pre-cooling, exchanges heat through the second intermediate heat exchanger 52 to complete re-cooling, then reaches the liquid cooling terminal 1 to cool the servers in the liquid cooling cabinet, and is then pumped by the first liquid pump 21 to the first intermediate heat exchanger 4 to dissipate heat to complete one cycle.

[0113] Or,

[0114] When Tr2 ≤ Tr < Tr3, control the heat exchange between the first secondary refrigerant and the refrigerant at the second intermediate heat exchanger 52, and control the heat exchange between the second secondary refrigerant and the refrigerant at the condensation heat exchanger 51. At this time, the temperature of the second secondary refrigerant in the waste heat recovery cycle is too high, and the energy efficiency of directly using it to provide cold energy for cooling in the liquid cooling cycle is relatively low. Therefore, at this time, the second secondary refrigerant in the waste heat recovery cycle is used to cool and dissipate heat the refrigerant in the compression refrigeration cycle. Therefore, at this time, the cooling system operates in the waste heat recovery high-temperature refrigeration mode, as Figure 4As shown, in this mode: the liquid cooling terminal 1, the first liquid pump 21, the second liquid pump 22, the second liquid treatment device 31, the first liquid treatment device 32, the condensation heat exchanger 51, the second intermediate heat exchanger 52, the throttling element 6, the compressor 7, the cold storage device 8, the flow regulating valve 9, the fifteenth solenoid valve 101, the fifth solenoid valve 102, the twenty-first solenoid valve 107, the thirteenth solenoid valve 110, the fourteenth solenoid valve 111, the seventh solenoid valve 114, the eighth solenoid valve 115, the fourth solenoid valve 116, the third solenoid valve 117, and the eighteenth solenoid valve 120 are opened, and the rest of the components are closed. At this time, the refrigeration unit of the system is started. On the cold source system side, the cold energy is provided by the heat recovery return water, and the heat recovery return water is pumped by the second liquid pump 22 to the condensation heat exchanger 51 to cool the condensation end of the refrigeration unit, and finally pumped to the heat recovery water use end; in the refrigeration unit system, the refrigerant dissipates heat in the condensation heat exchanger 51, is throttled by the throttling element 6, exchanges heat with the coolant system in the second intermediate heat exchanger 52, is compressed by the compressor 7, and exchanges heat with the heat recovery return water in the condensation heat exchanger 51; in the coolant system, the coolant exchanges heat in the second intermediate heat exchanger 52 and then reaches the liquid cooling terminal 1 to cool the servers in the liquid cooling cabinet, and then is pumped by the first liquid pump 21 to the second intermediate heat exchanger 52 to dissipate heat to complete a cycle.

[0115] The foregoing first preset water inlet temperature Tr1 < the second preset water inlet temperature Tr2 < the third preset water inlet temperature Tr3. In a specific embodiment, Tr1 = 15°C, Tr2 = 25°C, and Tr3 = 35°C.

[0116] In some embodiments, when the immersion liquid cooling cabinet cooling system includes a cooling tower liquid supply pipeline and a cooling tower liquid return pipeline,

[0117] When Tr ≥ Tr3, control the cooling tower liquid supply pipeline to communicate with the heat recovery liquid supply pipe, and control the cooling tower liquid return pipeline to communicate with the heat recovery liquid return pipe, and control and adjust the heat exchange occurrence positions of the first secondary refrigerant in the liquid cooling cycle, the refrigerant in the compression refrigeration cycle, and the second secondary refrigerant in the waste heat recovery cycle according to the temperature range of the real-time temperature Tr after the mixing of the cooling tower liquid supply pipeline and the heat recovery liquid supply pipe. That is, in this technical solution, when Tr ≥ Tr3, the waste heat recovery cycle and the second secondary refrigerant in the cooling tower are simultaneously used to provide cold energy for the unit to dissipate heat. Since the secondary refrigerants in the cooling tower and the waste heat recovery cycle are mixed, the specific value of the foregoing real-time temperature Tr can be reduced. At this time, the operation control strategy of the hybrid cold source is different from the control strategy of a single waste heat recovery cycle.

[0118] Specifically, when the waste heat recovery function is enabled (for example, actively selected by the user), it can be divided into the aforementioned waste heat recovery mode and the hybrid cold source mode according to the type of cold source. Among them, the waste heat recovery mode is mainly an operation mode that only uses the heat recovery return water as the cold source, and it is further divided into the waste heat recovery natural cooling mode, the waste heat recovery conventional refrigeration mode, and the waste heat recovery high-temperature refrigeration mode (as described above); while the hybrid cold source mode is mainly an operation mode that uses the mixture of heat recovery return water and cooling tower supply water as the cold source, and it is further divided into the hybrid cold source natural cooling mode, the hybrid cold source conventional refrigeration mode, and the hybrid cold source high-temperature refrigeration mode. Specifically,

[0119] When Tr < Tr1, the cooling system operates in the hybrid cold source natural cooling mode, as Figure 5 shown. In this mode: the liquid cooling terminal 1, the first liquid pump 21, the second liquid pump 22, the second liquid treatment device 31, the first liquid treatment device 32, the first intermediate heat exchanger 4, the cold storage device 8, the flow regulating valve 9, the fifteenth solenoid valve 101, the second solenoid valve 103, the first solenoid valve 104, the ninth solenoid valve 105, the tenth solenoid valve 106, the twelfth solenoid valve 108, the nineteenth solenoid valve 109, the thirteenth solenoid valve 110, the fourteenth solenoid valve 111, the twentieth solenoid valve 112, the eleventh solenoid valve 113, the sixth solenoid valve 118, and the eighteenth solenoid valve 120 are opened, and the rest of the components are closed. At this time, the cooling tower is turned on and the refrigeration unit is turned off in the cold source system side. The cold quantity is provided by the mixture of heat recovery return water and cooling tower supply water (hereinafter referred to as the hybrid cold source). The coolant is cooled by the first intermediate heat exchanger 4 and then pumped to the heat recovery water use end and the cooling tower return water by the second liquid pump 22; in the coolant system, the coolant exchanges heat with the hybrid cold source in the first intermediate heat exchanger 4 to complete the cooling, reaches the liquid cooling terminal 1 to cool the servers in the liquid cooling cabinet, and then is pumped to the first intermediate heat exchanger 4 by the first liquid pump 21 for heat dissipation to complete a cycle.

[0120] When Tr1 ≤ Tr < Tr2, the cooling system operates in the hybrid cold source conventional refrigeration mode, as Figure 6As shown in the figure, in this mode: the liquid cooling terminal 1, the first liquid pump 21, the second liquid pump 22, the second liquid treatment device 31, the first liquid treatment device 32, the first intermediate heat exchanger 4, the condensation heat exchanger 51, the second intermediate heat exchanger 52, the throttling element 6, the compressor 7, the cold storage device 8, the flow regulating valve 9, the fifteenth solenoid valve 101, the second solenoid valve 103, the first solenoid valve 104, the ninth solenoid valve 105, the tenth solenoid valve 106, the twelfth solenoid valve 108, the nineteenth solenoid valve 109, the thirteenth solenoid valve 110, the fourteenth solenoid valve 111, the twentieth solenoid valve 112, the seventh solenoid valve 114, the eighth solenoid valve 115, the fourth solenoid valve 116, the third solenoid valve 117, and the eighteenth solenoid valve 120 are opened, and the rest of the components are closed. At this time, the cooling tower and the refrigeration unit are started in the cold source system, and the cold source is provided by the mixed cold source. First, the coolant is pre-cooled by the first intermediate heat exchanger 4, then pumped to the condensation heat exchanger 51 by the second liquid pump 22 to cool the condensation end of the refrigeration unit, and finally pumped to the heat recovery water use end and the cooling tower return water; in the refrigeration unit system, the refrigerant dissipates heat in the condensation heat exchanger 51, exchanges heat with the coolant system in the second intermediate heat exchanger 52 after throttling through the throttling element 6, and exchanges heat with the cold source system in the condensation heat exchanger 51 after being compressed by the compressor 7; in the coolant system, the coolant first exchanges heat with the mixed cold source in the first intermediate heat exchanger 4 to complete pre-cooling, exchanges heat in the second intermediate heat exchanger 52 to complete re-cooling, then reaches the liquid cooling terminal 1 to cool the servers in the liquid cooling cabinet, and is then pumped to the first intermediate heat exchanger 4 by the first liquid pump 21 to dissipate heat to complete a cycle.

[0121] When Tr2 ≤ Tr < Tr3, the cooling system operates in the mixed cold source high-temperature refrigeration mode, as Figure 7As shown, in this mode: the liquid cooling terminal 1, the first liquid pump 21, the second liquid pump 22, the second liquid treatment device 31, the first liquid treatment device 32, the condensation heat exchanger 51, the second intermediate heat exchanger 52, the throttling element 6, the compressor 7, the cold storage device 8, the flow regulating valve 9, the fifteenth solenoid valve 101, the fifth solenoid valve 102, the twenty-first solenoid valve 107, the twelfth solenoid valve 108, the nineteenth solenoid valve 109, the thirteenth solenoid valve 110, the fourteenth solenoid valve 111, the twentieth solenoid valve 112, the seventh solenoid valve 114, the eighth solenoid valve 115, the fourth solenoid valve 116, the third solenoid valve 117, and the eighteenth solenoid valve 120 are opened, and the remaining components are closed. At this time, the cooling tower and the refrigeration unit are started. On the cold source system side, the cooling capacity is provided by the hybrid cold source, and the heat recovery return water is pumped by the second liquid pump 22 to the condensation heat exchanger 51 to cool the condensation end of the refrigeration unit, and finally pumped to the heat recovery water use end and the cooling tower return water; in the refrigeration unit system, the refrigerant dissipates heat in the condensation heat exchanger 51, is throttled by the throttling element 6, exchanges heat with the coolant system in the second intermediate heat exchanger 52, is compressed by the compressor 7, and exchanges heat with the hybrid cold source in the condensation heat exchanger 51; in the coolant system, the coolant exchanges heat in the second intermediate heat exchanger 52 and then reaches the liquid cooling terminal 1 to cool the servers in the liquid cooling cabinet, and is then pumped by the first liquid pump 21 to the second intermediate heat exchanger 52 for heat dissipation to complete a cycle.

[0122] In some embodiments,

[0123] When the system operation instruction is the unit normal operation instruction (for example, issued by manual control, and the waste heat recovery function is turned off at this time), obtain the outdoor ambient temperature Tout;

[0124] According to the temperature range in which the Tout is located, control and adjust the heat exchange occurrence positions of the first secondary refrigerant in the liquid cooling cycle, the refrigerant in the compression refrigeration cycle, and the second secondary refrigerant in the cooling tower (that is, in the cooling tower water cycle).

[0125] In this technical solution, according to the level of the outdoor ambient temperature, controlling at least one of the aforementioned two cold sources to cool the liquid cooling cycle can make greater use of the natural cold source, reduce the energy consumption of the unit in high-temperature seasons, improve the utilization rate of the natural cold source in transitional seasons, thereby being able to improve the annual energy efficiency of the refrigeration unit (cooling system) and reduce the overall annual energy consumption of the refrigeration unit.

[0126] Combined with reference to Figure 6 As shown, according to the temperature range in which the Tout is located, controlling and adjusting the heat exchange occurrence positions of the first secondary refrigerant in the liquid cooling cycle, the refrigerant in the compression refrigeration cycle, and the second secondary refrigerant in the cooling tower includes:

[0127] When Tout > T3, control the heat exchange between the first secondary refrigerant and the refrigerant at the second intermediate heat exchanger 52, and control the heat exchange between the second secondary refrigerant and the refrigerant at the condensation heat exchanger 51. At this time, the outdoor temperature is in a high temperature state, and the cooling system operates in the high temperature cooling mode. Refer to Figure 8 as shown. In this mode: the liquid cooling terminal 1, the first liquid pump 21, the second liquid pump 22, the second liquid treatment device 31, the first liquid treatment device 32, the condensation heat exchanger 51, the second intermediate heat exchanger 52, the throttling element 6, the compressor 7, the cold storage device 8, the flow regulating valve 9, the fifteenth solenoid valve 101, the fifth solenoid valve 102, the twenty-first solenoid valve 107, the twelfth solenoid valve 108, the nineteenth solenoid valve 109, the twentieth solenoid valve 112, the seventh solenoid valve 114, the eighth solenoid valve 115, the fourth solenoid valve 116, the third solenoid valve 117, and the eighteenth solenoid valve 120 are opened, and the rest of the components are closed. At this time, the cooling tower and the refrigeration unit are started. On the cooling water system side, heat exchange is carried out between the cooling tower and the outside air to provide cooling water, and the cooling water is pumped to the condensation heat exchanger 51 by the second liquid pump 22 to cool the condensation end of the refrigeration unit; in the refrigeration unit system, the refrigerant dissipates heat at the condensation heat exchanger 51, is throttled by the throttling element 6, and then exchanges heat with the coolant system at the second intermediate heat exchanger 52, and after being compressed by the compressor 7, exchanges heat with the cooling water at the condensation heat exchanger 51; in the coolant system, the coolant exchanges heat at the second intermediate heat exchanger 52 and then reaches the liquid cooling terminal 1 to cool the servers in the liquid cooling cabinet, and then is pumped to the second intermediate heat exchanger 52 by the first liquid pump 21 for heat dissipation to complete one cycle.

[0128] When T3 ≥ Tout > T2, control the heat exchange between the first secondary refrigerant and the second secondary refrigerant at the first intermediate heat exchanger 4, control the heat exchange between the first secondary refrigerant and the refrigerant at the second intermediate heat exchanger 52, and control the second secondary refrigerant after heat exchange with the first secondary refrigerant to exchange heat with the refrigerant again at the condensation heat exchanger 51. At this time, the outdoor temperature is relatively high, and the cooling system operates in the conventional cooling mode. Refer to Figure 9As shown, in this mode: the liquid cooling terminal 1, the first liquid pump 21, the second liquid pump 22, the second liquid treatment device 31, the first liquid treatment device 32, the first intermediate heat exchanger 4, the condensation heat exchanger 51, the second intermediate heat exchanger 52, the throttling element 6, the compressor 7, the cold storage device 8, the flow regulating valve 9, the fifteenth solenoid valve 101, the second solenoid valve 103, the first solenoid valve 104, the ninth solenoid valve 105, the tenth solenoid valve 106, the nineteenth solenoid valve 109, the twentieth solenoid valve 112, the seventh solenoid valve 114, the eighth solenoid valve 115, the fourth solenoid valve 116, the third solenoid valve 117, and the eighteenth solenoid valve 120 are opened, and the rest of the components are closed. At this time, the system starts the cooling tower and the refrigeration unit. On the cooling water system side, the cooling tower exchanges heat with the outside air to provide cooling water. First, the coolant is precooled by the first intermediate heat exchanger 4, and then the cooling water is pumped by the second liquid pump 22 to the condensation heat exchanger 51 to cool the condensation end of the refrigeration unit; in the refrigeration unit system, the refrigerant dissipates heat in the condensation heat exchanger 51, is throttled by the throttling element 6, and then exchanges heat with the coolant system in the second intermediate heat exchanger 52, is compressed by the compressor 7, and then exchanges heat with the cooling water in the condensation heat exchanger 51; in the coolant system, the coolant first exchanges heat with the cooling water in the first intermediate heat exchanger 4 to complete precooling, exchanges heat in the second intermediate heat exchanger 52 to complete rechilling, then reaches the liquid cooling terminal 1 to cool the servers in the liquid cooling cabinet, and is then pumped by the first liquid pump 21 to the first intermediate heat exchanger 4 to dissipate heat to complete one cycle.

[0129] When T2≥Tout>T1, control the heat exchange between the first secondary coolant and the second secondary coolant at the first intermediate heat exchanger 4. At this time, the outdoor temperature is relatively low, and the cooling system operates in the natural cooling mode. See Figure 10 As shown, in this mode: the liquid cooling terminal 1, the first liquid pump 21, the second liquid pump 22, the second liquid treatment device 31, the first liquid treatment device 32, the first intermediate heat exchanger 4, the cold storage device 8, the flow regulating valve 9, the fifteenth solenoid valve 101, the second solenoid valve 103, the first solenoid valve 104, the ninth solenoid valve 105, the tenth solenoid valve 106, the nineteenth solenoid valve 109, the twentieth solenoid valve 112, the eleventh solenoid valve 113, the sixth solenoid valve 118, and the eighteenth solenoid valve 120 are opened, and the rest of the components are closed. At this time, the system starts the cooling tower and shuts down the refrigeration unit. On the cooling water system side, the cooling tower exchanges heat with the outside air to provide cooling water. The coolant is cooled by the first intermediate heat exchanger 4 and then pumped by the second liquid pump 22 to the cooling tower for heat dissipation; in the coolant system, the coolant exchanges heat with the cooling water in the first intermediate heat exchanger 4 to complete cooling, reaches the liquid cooling terminal 1 to cool the servers in the liquid cooling cabinet, and is then pumped by the first liquid pump 21 to the first intermediate heat exchanger 4 to dissipate heat to complete one cycle.

[0130] When T1≥Tout, control the heat exchange between the first secondary refrigerant and the refrigerant at the second intermediate heat exchanger 52, and the refrigerant exchanges heat with the external ambient air at the condensation heat exchanger 51. At this time, the outdoor temperature is in a low temperature state, and there is a risk of freezing of the second secondary refrigerant in the cooling tower under this low temperature state. The cooling system operates in the low temperature cooling mode. Refer to Figure 11 As shown, in this mode: the liquid cooling terminal 1, the first liquid pump 21, the second liquid treatment device 31, the condensation heat exchanger 51, the second intermediate heat exchanger 52, the throttling element 6, the compressor 7, the cold storage device 8, the flow regulating valve 9, the fifteenth solenoid valve 101, the fifth solenoid valve 102, the fourth solenoid valve 116, the third solenoid valve 117, and the eighteenth solenoid valve 120 are opened, and the rest of the components are closed. At this time, the cooling tower of the system is closed and the refrigeration unit is started. In the refrigeration unit system, the refrigerant dissipates heat at the condensation heat exchanger 51, is throttled by the throttling element 6, exchanges heat with the coolant system at the second intermediate heat exchanger 52, and exchanges heat at the condensation heat exchanger 51 after being compressed by the compressor 7; in the coolant system, the coolant exchanges heat at the second intermediate heat exchanger 52, reaches the liquid cooling terminal 1 to cool the servers in the liquid cooling cabinet, and is then pumped by the first liquid pump 21 to the second intermediate heat exchanger 52 for heat dissipation to complete one cycle.

[0131] The aforementioned first preset ambient temperature T1 < the second preset ambient temperature T2 < the third preset ambient temperature T3, and the values of T1, T2, and T3 are determined according to the local climate temperature and humidity distribution.

[0132] In some embodiments, when including the cold storage device 8, the control method further includes:

[0133] Judge whether the power grid reaches the low valley period or the peak period;

[0134] When the power grid reaches the low valley period, control the first secondary refrigerant in the liquid inlet pipe to enter the cold storage device 8 for cold storage, and cut off the entry of the first secondary refrigerant into the cold storage device 8 after the cold storage is completed; or,

[0135] When the cold storage device 8 has completed cold storage and the power grid reaches the peak period, control the first secondary refrigerant in the liquid inlet pipe to enter the cold storage device 8 to enable the cold storage device 8 to release cold to the first secondary refrigerant, and cut off the entry of the first secondary refrigerant into the cold storage device 8 after the cold release is completed.

[0136] That is to say, during the operation of the unit, it is possible to choose whether to activate the cold storage mode. When the cold storage mode is activated, the cold storage device 8, the sixteenth solenoid valve 119, and the seventeenth solenoid valve 121 are opened, and the eighteenth solenoid valve 120 is closed, and the unit enters the cold storage mode. When the cold storage mode is deactivated, the cold storage device 8, the sixteenth solenoid valve 119, and the seventeenth solenoid valve 121 are closed, and the eighteenth solenoid valve 120 is opened. When the unit activates the cold storage mode, it is possible to choose to store or release cold in the cold storage device 8 according to whether the power grid is in a peak period or a valley period. When the power grid reaches the valley period, the unit activates the cold storage mode. When the power grid reaches the peak period, the unit activates the cold release mode. Through the cold storage technology, the energy conservation and consumption reduction, and peak load shifting of the data center can be achieved. It can be understood that when the cold storage device 8 neither stores nor releases cold, the sixteenth solenoid valve 119 and the seventeenth solenoid valve 121 are closed, and the eighteenth solenoid valve 120 is opened.

[0137] The above are only the preferred embodiments of the present invention, and are not intended to limit the present invention. Any modifications, equivalent replacements, and improvements made within the spirit and principles of the present invention shall be included in the protection scope of the present invention. The above is only the preferred implementation manner of the present invention. It should be noted that for those of ordinary skill in the art, without departing from the technical principle of the present invention, several improvements and modifications can be made, and these improvements and modifications should also be regarded as the protection scope of the present invention.

Claims

1. An immersion liquid cooling cabinet cooling system, characterized in that, Comprising: A liquid cooling cycle, including a liquid cooling terminal (1), a first liquid pump (21), a first intermediate heat exchanger (4), and a second intermediate heat exchanger (52) connected by pipelines. The first liquid pump (21) is used to drive a first secondary refrigerant to circulate within the liquid cooling cycle, and the equipment to be cooled is immersed in the first secondary refrigerant within the liquid cooling terminal (1). A compression refrigeration cycle, including a compressor (7), a throttling element (6), and a condensation heat exchanger (51) connected by pipelines. The refrigerant in the exhaust pipeline of the compressor (7) exchanges heat with the first secondary refrigerant within the second intermediate heat exchanger (52). A waste heat recovery cycle, including a second liquid pump (22) and a waste heat recovery and utilization device, which is used to drive a second secondary refrigerant to circulate within the waste heat recovery cycle, and the second secondary refrigerant can exchange heat with the first secondary refrigerant within the first intermediate heat exchanger (4), and the second secondary refrigerant can also exchange heat with the refrigerant within the condensation heat exchanger (51). According to the temperature range of the real-time temperature Tr of the second secondary refrigerant in the heat recovery liquid supply pipe of the waste heat recovery cycle, control and adjust the heat exchange occurrence positions of the first secondary refrigerant in the liquid cooling cycle, the refrigerant in the compression refrigeration cycle, and the second secondary refrigerant in the waste heat recovery cycle; when Tr1 ≤ Tr < Tr2, control the first secondary refrigerant and the second secondary refrigerant to exchange heat at the first intermediate heat exchanger (4), control the first secondary refrigerant and the refrigerant to exchange heat at the second intermediate heat exchanger (52), and control the second secondary refrigerant after exchanging heat with the first secondary refrigerant to exchange heat with the refrigerant again at the condensation heat exchanger (51); wherein, Tr1 is the first preset water inlet temperature, and Tr2 is the second preset water inlet temperature.

2. The immersion liquid cooling cabinet cooling system according to claim 1, wherein The liquid cooling cycle further includes a first flow path control valve group connected to the first side of the first intermediate heat exchanger (4) and a second flow path control valve group connected to the first side of the second intermediate heat exchanger (52). The compression refrigeration cycle further includes a third flow path control valve group connected to the second side of the condensation heat exchanger (51). The waste heat recovery cycle further includes a fourth flow path control valve group connected to the second side of the first intermediate heat exchanger (4). The first flow path control valve group, the second flow path control valve group, the third flow path control valve group, and the fourth flow path control valve group can adjust the heat exchange occurrence positions among the first secondary refrigerant, the second secondary refrigerant, and the refrigerant.

3. The immersion liquid cooling cabinet cooling system according to claim 2, wherein The first pipeline is connected to the first refrigerant carrier inlet on the first side of the first intermediate heat exchanger (4), and the second pipeline is connected to the first refrigerant carrier outlet on the first side of the first intermediate heat exchanger (4). The first flow path control valve group includes a first solenoid valve (104) connected in series on the first pipeline and a second solenoid valve (103) connected in series on the second pipeline; the third pipeline is connected to the first refrigerant carrier inlet on the first side of the second intermediate heat exchanger (52), and the fourth pipeline is connected to the first refrigerant carrier outlet on the first side of the second intermediate heat exchanger (52). The second flow path control valve group includes a third solenoid valve (117) connected in series on the third pipeline and a fourth solenoid valve (116) connected in series on the fourth pipeline. The ends of the first pipeline and the second pipeline far from the first intermediate heat exchanger (4) and the ends of the third pipeline and the fourth pipeline far from the second intermediate heat exchanger (52) are connected in parallel to the fifth pipeline. The first flow path control valve group further includes a fifth solenoid valve (102) connected in series on the fifth pipeline and located between the first pipeline and the second pipeline. The second flow path control valve group further includes a sixth solenoid valve (118) connected in series on the fifth pipeline and located between the third pipeline and the fourth pipeline.

4. The immersion liquid cooling cabinet cooling system according to claim 3, wherein The sixth pipeline is connected to the second refrigerant carrier inlet on the second side of the condensation heat exchanger (51), and the seventh pipeline is connected to the second refrigerant carrier outlet on the second side of the condensation heat exchanger (51). The third flow path control valve group includes a seventh solenoid valve (114) connected in series on the sixth pipeline and an eighth solenoid valve (115) connected in series on the seventh pipeline; the eighth pipeline is connected to the second refrigerant carrier inlet on the second side of the first intermediate heat exchanger (4), and the ninth pipeline is connected to the second refrigerant carrier outlet on the second side of the first intermediate heat exchanger (4). The fourth flow path control valve group includes a ninth solenoid valve (105) connected in series on the eighth pipeline and a tenth solenoid valve (106) connected in series on the ninth pipeline; the ends of the sixth pipeline and the seventh pipeline far from the condensation heat exchanger (51) and the ends of the eighth pipeline and the ninth pipeline far from the first intermediate heat exchanger (4) are connected in parallel to the tenth pipeline. The third flow path control valve group further includes an eleventh solenoid valve (113) connected in series on the tenth pipeline and located between the sixth pipeline and the seventh pipeline. The fourth flow path control valve group further includes a twelfth solenoid valve (108) connected in series on the tenth pipeline and located between the eighth pipeline and the ninth pipeline.

5. The immersion liquid cooling cabinet cooling system according to claim 4, wherein The waste heat recovery cycle further includes a heat recovery liquid supply pipe and a heat recovery liquid return pipe. Among them, the outlet of the heat recovery liquid supply pipe is communicated with one end of the eighth pipeline far from the first intermediate heat exchanger (4), and a thirteenth solenoid valve (110) is connected in series on the heat recovery liquid supply pipe. The heat recovery liquid return pipe is communicated with one end of the seventh pipeline far from the condensation heat exchanger (51), and a fourteenth solenoid valve (111) is connected in series on the heat recovery liquid return pipe; and / or, a first liquid treatment device (32) is connected in series on the heat recovery liquid return pipe, and / or, a second liquid treatment device (31) is connected in series on the pipeline between the first liquid pump (21) and the first pipeline.

6. The immersion liquid cooling cabinet cooling system according to claim 5, characterized in that It further includes: A cooling tower liquid supply pipeline and a cooling tower liquid return pipeline. One end of the cooling tower liquid supply pipeline is communicated with the cooling tower, and the other end is communicated with one end of the eighth pipeline far from the first intermediate heat exchanger (4) through a nineteenth solenoid valve (109). One end of the cooling tower liquid return pipeline is communicated with the cooling tower, and the other end is communicated with one end of the heat recovery liquid return pipe far from the condensation heat exchanger (51) through a twentieth solenoid valve (112). And the twentieth solenoid valve (112) is in parallel with the fourteenth solenoid valve (111). A twenty-first solenoid valve (107) is connected in series on the flow pipeline between the second liquid pump (22) and the twelfth solenoid valve (108), and the twenty-first solenoid valve (107) is connected in series on the ninth pipeline. The secondary coolant for the internal circulation in the cooling tower is the second coolant.

7. The immersed liquid-cooled cabinet cooling system according to claim 1, wherein A fifteenth solenoid valve (101) is connected in series on one of the liquid inlet pipe and the liquid outlet pipe of the liquid-cooled terminal (1), and a flow regulating valve (9) is connected in series on the other; and / or, there are multiple liquid-cooled terminals (1), and multiple liquid-cooled terminals (1) are connected in parallel in the liquid-cooling cycle.

8. The immersed liquid-cooled cabinet cooling system according to claim 1, wherein The liquid-cooling cycle further includes a cold storage device (8). The cold storage device (8) is connected to the liquid inlet pipe of the liquid-cooled terminal (1) through a fifth flow path control valve group. The fifth flow path control valve group can control the first coolant in the liquid inlet pipe to flow through or not flow through the cold storage device (8).

9. The immersed liquid-cooled cabinet cooling system according to claim 8, wherein The fifth flow path control valve group includes a sixteenth solenoid valve (119) connected in series on the inlet pipe of the cold storage device (8), a seventeenth solenoid valve (121) connected in series on the outlet pipe of the cold storage device (8), and an eighteenth solenoid valve (120) connected in series on the liquid inlet pipe and between the inlet pipe and the outlet pipe.

10. A control method for an immersion liquid cooling cabinet cooling system according to any one of claims 1 to 9, characterized in that, It includes the following steps: Obtain a system operation instruction; When the system operation instruction is a waste heat recovery instruction, obtain the real-time temperature Tr of the second coolant in the heat recovery liquid supply pipe of the waste heat recovery cycle; According to the temperature range where Tr is located, control and adjust the heat exchange occurrence positions of the first secondary refrigerant in the liquid cooling cycle, the refrigerant in the compression refrigeration cycle, and the second secondary refrigerant in the waste heat recovery cycle.

11. The control method according to claim 10, characterized in that, According to the temperature range where Tr is located, controlling and adjusting the heat exchange occurrence positions of the first secondary refrigerant in the liquid cooling cycle, the refrigerant in the compression refrigeration cycle, and the second secondary refrigerant in the waste heat recovery cycle includes: When Tr < Tr1, control the first secondary refrigerant and the second secondary refrigerant to exchange heat at the first intermediate heat exchanger (4); or, When Tr1 ≤ Tr < Tr2, control the first secondary refrigerant and the second secondary refrigerant to exchange heat at the first intermediate heat exchanger (4), control the first secondary refrigerant and the refrigerant to exchange heat at the second intermediate heat exchanger (52), and control the second secondary refrigerant after exchanging heat with the first secondary refrigerant to exchange heat with the refrigerant again at the condensation heat exchanger (51); or, When Tr2 ≤ Tr < Tr3, control the first secondary refrigerant and the refrigerant to exchange heat at the second intermediate heat exchanger (52), and control the second secondary refrigerant and the refrigerant to exchange heat at the condensation heat exchanger (51); The first preset inlet water temperature Tr1 < the second preset inlet water temperature Tr2 < the third preset inlet water temperature Tr3.

12. The control method according to claim 11, wherein When the immersion liquid cooling cabinet cooling system includes a cooling tower liquid supply pipeline and a cooling tower liquid return pipeline, When Tr ≥ Tr3, control the cooling tower liquid supply pipeline to be connected to the heat recovery liquid supply pipe, control the cooling tower liquid return pipeline to be connected to the heat recovery liquid return pipe, and according to the temperature range of the real-time temperature Tr after the mixing of the connected cooling tower liquid supply pipeline and the heat recovery liquid supply pipe, control and adjust the heat exchange occurrence positions of the first secondary refrigerant in the liquid cooling cycle, the refrigerant in the compression refrigeration cycle, and the second secondary refrigerant in the waste heat recovery cycle.

13. The control method according to claim 10, wherein When the system operation instruction is a unit normal operation instruction, obtain the outdoor ambient temperature Tout; According to the temperature range where Tout is located, control and adjust the heat exchange occurrence positions of the first secondary refrigerant in the liquid cooling cycle, the refrigerant in the compression refrigeration cycle, and the second secondary refrigerant in the cooling tower.

14. The control method according to claim 13, characterized in that According to the temperature range where Tout is located, controlling and adjusting the heat exchange occurrence positions of the first secondary refrigerant in the liquid cooling cycle, the refrigerant in the compression refrigeration cycle, and the second secondary refrigerant in the cooling tower includes: When Tout > T3, control the first secondary refrigerant and the refrigerant to exchange heat at the second intermediate heat exchanger (52), and control the second secondary refrigerant and the refrigerant to exchange heat at the condensation heat exchanger (51); or, When T3≥Tout>T2, control the first secondary refrigerant and the second secondary refrigerant to exchange heat at the first intermediate heat exchanger (4), the first secondary refrigerant and the refrigerant to exchange heat at the second intermediate heat exchanger (52), and control the second secondary refrigerant after exchanging heat with the first secondary refrigerant to exchange heat with the refrigerant again at the condensation heat exchanger (51); or, When T2≥Tout>T1, control the first secondary refrigerant and the second secondary refrigerant to exchange heat at the first intermediate heat exchanger (4); or, When T1≥Tout, control the first secondary refrigerant and the refrigerant to exchange heat at the second intermediate heat exchanger (52), and the refrigerant to exchange heat with the external ambient air at the condensation heat exchanger (51); The first preset ambient temperature T1<the second preset ambient temperature T2<the third preset ambient temperature T3.

15. The control method according to claim 10, wherein When a cold storage device (8) is included, the control method further includes: Judge whether the power grid reaches the low valley period or the peak period; When the power grid reaches the low valley period, control the first secondary refrigerant in the liquid inlet pipe to enter the cold storage device (8) for cold storage, and cut off the first secondary refrigerant from entering the cold storage device (8) after the cold storage is completed; or, When the cold storage device (8) has completed cold storage and the power grid reaches the peak period, control the first secondary refrigerant in the liquid inlet pipe to enter the cold storage device (8) so that the cold storage device (8) releases cold to the first secondary refrigerant, and cut off the first secondary refrigerant from entering the cold storage device (8) after the cold release is completed.

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