Cold source utilization systems, methods, apparatuses, devices, and computer program products

Abstract

The application provides a cold source utilization system, method, device, equipment and computer program product. The cold source utilization system comprises at least two levels of heat exchange systems and a control device. The evaporation temperature of the evaporator of different levels of heat exchange systems is different. The condensation temperature of the condenser of different levels of heat exchange systems is different. Compared with a single-level cold source utilization system, the cold source utilization system composed of multiple levels of heat exchange systems can have a flexible control mode. The switching of the cold source utilization system in different control modes is realized by determining the driving device through a refrigerating capacity influencing parameter. Therefore, the power consumption of the cold source utilization system is reduced, and the system energy efficiency is improved.

Description

Technical Field

[0001] This application belongs to the field of infrastructure technology, specifically relating to a cold source utilization system, method, apparatus, equipment, and computer program product. Background Technology

[0002] In recent years, with the rapid development of cloud computing and big data, the amount of data processing in data centers has also exploded. The high heat emissions from servers caused by the massive data processing have placed higher cooling requirements on the new generation of air conditioning units for data centers. However, in many cities where data centers are located, outdoor temperatures drop in winter, and there is more time to utilize outdoor cold sources. Therefore, how to make full, reasonable and efficient use of this heat is the key to improving the energy efficiency of data center air conditioning.

[0003] Currently, refrigerant pump air conditioning units mainly operate in compressor mode, gas pump mode, and liquid pump mode under different ambient temperature conditions throughout the year. The compressor has a high power, and the system efficiency is not high when the outdoor temperature is high. As the outdoor temperature decreases, the gas pump mode and liquid pump mode can be gradually adopted, reducing system power consumption and increasing energy efficiency. When the outdoor temperature is below 5°C, the liquid pump mode can be used. The refrigerant pump has a lower power and can make full use of the low outdoor temperature for heat exchange to achieve cooling inside the data center and meet the cooling needs.

[0004] Existing cold source utilization technologies mainly adopt single-stage cold source utilization systems, resulting in a one-size-fits-all control approach. This leads to low cold source utilization rates in some cold source utilization control modes, resulting in high energy efficiency of the cold source utilization system. Summary of the Invention

[0005] This application proposes a cold source utilization system, method, apparatus, equipment, and computer program product, which can alleviate the problem in related technologies where the use of a single-stage cold source utilization system leads to a one-size-fits-all control approach, resulting in low cold source utilization rate in some cold source utilization control modes.

[0006] The first aspect of this application provides a cold source utilization system, comprising:

[0007] At least two stages of heat exchange system and control equipment;

[0008] Each stage of the heat exchange system includes an evaporator, a condenser, a refrigerant drive unit, and delivery pipelines;

[0009] The delivery pipeline passes through the evaporator and the condenser, and is connected to the refrigerant driving device; each of the refrigerant driving devices includes at least one driving device.

[0010] The refrigerant drive device is also connected to the control device;

[0011] The evaporator of the heat exchange system in different stages has a different evaporation temperature, and the condenser of the heat exchange system in different stages has a different condensation temperature.

[0012] The control device is used to determine the target mode of the refrigerant drive device in each stage of the heat exchange system based on the cooling capacity influence parameters. The target mode is used to indicate the drive device that needs to be started in the refrigerant drive device; and to control the refrigerant drive device to operate according to the target mode.

[0013] In one or more embodiments, the supply air of the condenser with a low condensing temperature in two adjacent stages of the heat exchange system is the return air of the condenser with a high condensing temperature.

[0014] In one or more embodiments, the return air of the condensers included in each stage of the heat exchange system is outdoor return air.

[0015] In one or more embodiments, the refrigerant driving device includes at least one of the following driving means:

[0016] compressor;

[0017] air pump;

[0018] Liquid pump.

[0019] A second aspect of this application provides a control method for a cold source utilization system, applied to the cold source utilization system described in the first aspect, the method comprising:

[0020] Based on the cooling capacity influence parameters of the cold source utilization system, the target mode of the refrigerant drive device in each stage of the heat exchange system is determined. The target mode is used to indicate the drive device that needs to be activated in the refrigerant drive device.

[0021] Control the refrigerant drive device to operate according to the target mode.

[0022] In one or more embodiments, the refrigerant driving device includes a compressor, a gas pump, and a liquid pump; the energy consumption of the compressor is greater than the energy consumption of the gas pump, and the energy consumption of the gas pump is greater than the energy consumption of the liquid pump.

[0023] Based on the cooling capacity influence parameters of the cold source utilization system, the target modes of the refrigerant drive equipment that need to be activated in each stage of the heat exchange system are determined, including:

[0024] Based on the outdoor ambient temperature, which is included in the parameters affecting the cooling capacity, the indoor and outdoor heat exchange temperature difference corresponding to each stage of the heat exchange system is predicted.

[0025] If the indoor and outdoor heat exchange temperature difference is less than a first temperature threshold, the target mode is determined to be the mode of starting the compressor;

[0026] If the indoor-outdoor heat exchange temperature difference is greater than or equal to a first temperature threshold and less than a second temperature threshold, the target mode is determined to be the mode of starting the air pump; the second temperature threshold is greater than the first temperature threshold.

[0027] If the indoor and outdoor heat exchange temperature difference is greater than or equal to the second temperature threshold, the target mode is determined to be the mode of starting the liquid pump.

[0028] In one or more embodiments, the refrigerant driving device includes any two of a compressor, a gas pump, and a liquid pump; the energy consumption of the compressor is greater than the energy consumption of the gas pump, and the energy consumption of the gas pump is greater than the energy consumption of the liquid pump.

[0029] Based on the cooling capacity influence parameters, determine the target modes of the refrigerant drive equipment that needs to be activated in each stage of the heat exchange system, including:

[0030] Based on the outdoor ambient temperature, which is included in the parameters affecting the cooling capacity, the indoor and outdoor heat exchange temperature difference corresponding to each stage of the heat exchange system is predicted.

[0031] When the indoor and outdoor heat exchange temperature difference is less than the third temperature threshold, the target mode is determined to be the mode of starting the first drive device;

[0032] If the indoor-outdoor heat exchange temperature difference is greater than or equal to the third temperature threshold, the target mode is determined to be the mode of starting the second drive device;

[0033] The first driving device is the one with higher energy consumption among the two devices, and the second driving device is the one with lower energy consumption among the two devices.

[0034] In one or more embodiments, based on the outdoor ambient temperature, which is included in the cooling capacity influence parameters, the indoor-outdoor heat exchange temperature difference corresponding to each stage of the heat exchange system is predicted, including:

[0035] Based on the outdoor ambient temperature, the first condensing return air temperature of the condenser included in each stage of the heat exchange system is predicted, and the temperature difference between the first condensing return air temperature and the condensing temperature of the condenser included in each stage of the heat exchange system is calculated to obtain the indoor and outdoor heat exchange temperature difference.

[0036] or,

[0037] Based on the outdoor ambient temperature, the evaporation return air temperature of the evaporator and the second condensation return air temperature of the condenser, which are included in each stage of the heat exchange system, are predicted. The temperature difference between the evaporation return air temperature and the second condensation return air temperature is calculated to obtain the indoor and outdoor heat exchange temperature difference.

[0038] In one or more embodiments, the refrigerant driving device includes any one of a compressor, a gas pump, and a liquid pump;

[0039] Based on the cooling capacity influence parameters, determine the target modes of the refrigerant drive equipment that needs to be activated in each stage of the heat exchange system, including:

[0040] Obtain the driving strategy corresponding to the current load of the cold source utilization system, which is included in the cooling capacity influence parameters;

[0041] According to the driving strategy, the operation of any one of the devices included in each level of the heat exchange system is controlled.

[0042] A third aspect of this application provides a control device for a cold source utilization system, applied to the cold source utilization system described in the first aspect, the device comprising:

[0043] The determination module is used to determine the target mode of the refrigerant drive device in each stage of the heat exchange system based on the refrigeration capacity influence parameters of the cold source utilization system. The target mode is used to indicate the drive device that needs to be activated in the refrigerant drive device.

[0044] The control module is used to control the refrigerant drive device to operate according to the target mode.

[0045] A fourth aspect of this application provides an electronic device including a memory, a processor, and a computer program stored in the memory and executable on the processor, the processor running the computer program to implement the method as described in the first aspect.

[0046] A fifth aspect of this application provides a computer-readable storage medium having a computer program stored thereon, the program being executed by a processor to implement the method described in the first aspect.

[0047] A sixth aspect of this application provides a computer program product including computer-readable code, or a non-volatile computer-readable storage medium carrying computer-readable code, wherein when the computer-readable code is run in a processor of an electronic device, the processor in the electronic device performs the method as described in the first aspect.

[0048] The technical solutions provided in this application embodiment have at least the following technical effects or advantages:

[0049] In this embodiment, the cold source utilization system includes at least two stages of heat exchange systems and control equipment. The evaporator of the different stages of heat exchange systems has a different evaporation temperature, and the condenser of the different stages of heat exchange systems has a different condensation temperature. Compared with a single-stage cold source utilization system, the cold source utilization system composed of a multi-stage heat exchange system in this application can have flexible and varied control modes. Furthermore, the switching of the cold source utilization system in different control modes is realized by determining the driving device through the cooling capacity influence parameter, thereby reducing the power consumption of the cold source utilization system and improving the system energy efficiency.

[0050] Additional aspects and advantages of this application will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of this application. Attached Figure Description

[0051] Various other advantages and benefits will become apparent to those skilled in the art upon reading the following detailed description of preferred embodiments. The accompanying drawings are for illustrative purposes only and are not intended to limit the scope of this application. Furthermore, the same reference numerals denote the same parts throughout the drawings. In the drawings:

[0052] Figure 1 This invention provides a schematic diagram of a cold source utilization system according to an embodiment of the present application.

[0053] Figure 2 This invention provides a schematic diagram of yet another structural embodiment of a cold source utilization system.

[0054] Figure 3 This invention provides a schematic diagram of yet another structural embodiment of a cold source utilization system.

[0055] Figure 4 This invention provides a schematic diagram of yet another structural embodiment of a cold source utilization system.

[0056] Figure 5 This invention provides a schematic diagram of yet another structural embodiment of a cold source utilization system.

[0057] Figure 6 This invention provides a schematic diagram of yet another structural embodiment of a cold source utilization system.

[0058] Figure 7 This invention provides a schematic diagram of yet another structural embodiment of a cold source utilization system.

[0059] Figure 8 This invention provides a schematic diagram of yet another structural embodiment of a cold source utilization system.

[0060] Figure 9A schematic flowchart of a control method for a cold source utilization system provided in an embodiment of this application is shown;

[0061] Figure 10 A schematic flowchart of a control method for a cold source utilization system provided in an embodiment of this application is shown;

[0062] Figure 11 This invention provides a schematic diagram of the control device for a cold source utilization system according to an embodiment of the present application.

[0063] Figure 12 This illustration shows a schematic diagram of the structure of an electronic device according to an embodiment of this application;

[0064] Figure 13 A schematic diagram of a storage medium provided in one embodiment of this application is shown. Detailed Implementation

[0065] To make the objectives, technical solutions, and advantages of the embodiments of this application clearer, the technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this application, and not all embodiments. The components of the embodiments of this application described and shown in the accompanying drawings can generally be arranged and designed in various different configurations. Therefore, the following detailed description of the embodiments of this application provided in the accompanying drawings is not intended to limit the scope of the claimed application, but merely represents selected embodiments of this application. All other embodiments obtained by those skilled in the art based on the embodiments of this application without inventive effort are within the scope of protection of this application.

[0066] It should be noted that similar labels and letters in the following figures indicate similar items. Therefore, once an item is defined in one figure, it does not need to be further defined and explained in subsequent figures.

[0067] In this document, the term "and / or" merely describes a relationship, indicating that three relationships can exist. For example, A and / or B can represent three cases: A alone, A and B simultaneously, and B alone. Furthermore, the term "at least one" in this document means any combination of at least two of any one or more elements. For example, including at least one of A, B, and C can mean including any one or more elements selected from the set consisting of A, B, and C.

[0068] With the rapid development of the data center industry, the performance improvement of air conditioning products for data centers and the efficient utilization of liquid pump sources have attracted increasing attention. Existing technologies for improving the performance of refrigerant pump air conditioners for data centers, besides enhancing the performance of the air conditioning units themselves, also focus on the efficient utilization of outdoor cold sources. However, current refrigerant pump air conditioning technology uses a single-stage cold source utilization system, resulting in a one-size-fits-all control logic and low cold source utilization rates in some control modes.

[0069] Specifically, when the ambient temperature is high, such as above 25°C, the compressor mode is used. When the temperature gradually drops below 25°C, the air pump mode is used. In the air pump mode, the outdoor liquid pump source is utilized, the system pressure ratio is reduced, and the power consumption is reduced. Only when the outdoor temperature is below 5°C is the liquid pump mode, which has the highest energy utilization efficiency, used. Because the indoor and outdoor evaporation and condensation temperatures are affected, the liquid pump mode cannot be partially turned on in advance, so the energy cannot be used more efficiently in the temperature range of 25-5°C. In most parts of the country, this temperature range occupies a large part of the year, and the existing single cold source utilization technology cannot effectively utilize this temperature range, resulting in low cold source utilization rate.

[0070] To alleviate the problems existing in related technologies, embodiments of this application provide a cold source utilization system, method, apparatus, device, and computer program product. This cold source utilization system includes at least two stages of heat exchange systems and control equipment. The evaporator temperatures of the evaporators in different stages of the heat exchange systems are different, and the condenser temperatures of the condensers in different stages of the heat exchange systems are different. Compared to a single-stage cold source utilization system, the cold source utilization system of this application, composed of multi-stage heat exchange systems, can have flexible and varied control modes. Furthermore, the switching between different control modes of the cold source utilization system is achieved by determining the drive device through parameters affecting the cooling capacity, thereby reducing the power consumption of the cold source utilization system and improving system energy efficiency.

[0071] To facilitate understanding of this embodiment, a detailed description of a cold source utilization system disclosed in this application embodiment will be provided first, such as... Figure 1 As shown, the cold source utilization system may include:

[0072] At least two-stage heat exchange systems and control equipment (not shown in the figure);

[0073] Each stage of the heat exchange system 00 includes an evaporator 111, a condenser 112, a refrigerant drive device 113, and a delivery pipeline 114;

[0074] The delivery pipeline 114 passes through the evaporator 111 and the condenser 112, and is connected to the refrigerant drive device 113; each refrigerant drive device 113 includes at least one drive device.

[0075] The refrigerant drive unit 113 is also connected to a control unit;

[0076] The evaporator 111 of different stages of heat exchange system 00 has different evaporation temperatures, and the condenser 112 of different stages of heat exchange system 00 has different condensation temperatures.

[0077] The control device is used to determine the target mode of the refrigerant drive device 113 in each stage of the heat exchange system 00 based on the cooling capacity influence parameters. The target mode is used to indicate the drive device that needs to be started in the refrigerant drive device 113; and to control the refrigerant drive device 113 to operate according to the target mode.

[0078] The refrigerant drive device, based on the control of the control equipment, drives the refrigerant to be transferred between the evaporator and the condenser through the delivery pipeline.

[0079] In at least two heat exchange systems 00, the evaporation temperature of the Nth evaporator in the Nth heat exchange system is greater than the evaporation temperature of the N+1th evaporator in the N+1th heat exchange system, the air supply port of the Nth evaporator is connected to the air return port of the N+1th evaporator, the condensation temperature of the Nth condenser in the Nth heat exchange system is less than the condensation temperature of the N+1th condenser in the N+1th heat exchange system, and N≥1.

[0080] It should be understood that the Nth stage heat exchange system and the N+1th stage heat exchange system are two adjacent heat exchange systems in at least two-stage heat exchange systems. The Nth evaporator is closer to the indoor environment than the N+1th evaporator. If the return air of the Nth evaporator is the indoor return air, then the return air of the N+1th evaporator is the supply air of the Nth evaporator. Here, return air refers to the air flowing into the evaporator, and supply air refers to the air flowing out of the evaporator.

[0081] It should be understood that when the evaporation temperature of the Nth evaporator is greater than that of the (N+1)th evaporator, and the condensation temperature of the Nth condenser is less than that of the (N+1)th condenser, the evaporation-condensation temperature difference of the Nth stage heat exchange system is less than that of the (N+1)th stage heat exchange system. Here, the evaporation-condensation temperature difference refers to the temperature difference between the evaporation temperature of the evaporator and the condensation temperature of the condenser belonging to the same stage heat exchange system.

[0082] It should be understood that the evaporation temperature refers to the saturation temperature at which the refrigerant changes from a liquid to a gas in the evaporator, while the condensation temperature refers to the temperature at which the refrigerant condenses from a gaseous state to a liquid state in the condenser. The temperature of the liquid refrigerant flowing through the evaporator is lower than the evaporation temperature. The liquid refrigerant absorbs heat at the evaporator, and after its temperature rises to the evaporation temperature, it becomes a gaseous refrigerant. Similarly, the temperature of the gaseous refrigerant flowing through the condenser is higher than the condensation temperature. The gaseous refrigerant dissipates heat at the condenser, and after its temperature drops to the condensation temperature, it becomes a liquid refrigerant.

[0083] It should be noted that the Nth condenser refers to the condenser included in the Nth stage heat exchange system, and does not represent the Nth heat exchanger in the Nth stage heat exchange system. Similarly, the N+1th condenser refers to the condenser included in the N+1th stage heat exchange system, and does not represent the N+1th heat exchanger in the N+1th stage heat exchange system.

[0084] It should be understood that at least two heat exchange systems can share a single control device, or each can have its own control device. If each heat exchange system has its own control device, the control device can be integrated into the refrigerant drive unit.

[0085] In one or more embodiments, such as Figure 1 As shown, the refrigerant drive device includes at least one of the following drive units:

[0086] compressor;

[0087] air pump;

[0088] Liquid pump.

[0089] It should be understood that when the refrigerant-driven equipment includes at least two of the following: a compressor, a gas pump, and a liquid pump, the power of the compressor is greater than that of the gas pump, and the power of the gas pump is greater than that of the liquid pump. When the refrigerant-driven equipment includes one of the following: a compressor, a gas pump, and a liquid pump, the power of the refrigerant-driven equipment included in each stage of the heat exchange system varies, and the heat exchange system with a larger evaporation-condensation temperature difference has a higher power refrigerant-driven equipment.

[0090] In some embodiments, the types of refrigerant drive devices in different stages of the heat exchange system can be completely identical (i.e., a proportional structure). For example, each stage of the heat exchange system may include a compressor, a gas pump, and a liquid pump; another example is that each stage of the heat exchange system includes a gas pump and a liquid pump; yet another example is that each stage of the heat exchange system includes a compressor, and so on. In other embodiments, the types of refrigerant drive devices in different stages of the heat exchange system may not be completely identical (i.e., a non-proportional structure). In this case, the types of refrigerant drive devices in the multi-stage heat exchange system need to meet the following principles:

[0091] For ease of explanation, let's take a three-stage heat exchange system with at least two stages as an example. In this three-stage heat exchange system, the condenser temperature of the condenser in the first stage is higher than that of the condenser in the second stage, and the condenser temperature of the condenser in the second stage is higher than that of the condenser in the third stage. Then, when the refrigerant drive device in the first stage heat exchange system is a compressor, the refrigerant drive devices in the second and third stage heat exchange systems can be liquid pumps and / or gas pumps. When the first stage heat exchange system is a gas pump, the refrigerant drive devices in the second and third stage heat exchange systems can be liquid pumps and / or gas pumps. When the refrigerant drive device in the first stage heat exchange system is a liquid pump, the refrigerant drive devices in the second and third stage heat exchange systems can only be liquid pumps.

[0092] Also, please refer to the application instructions for future reference. Figures 2-8 The examples used in this application all illustrate the same type of refrigerant drive device in a multi-stage heat exchange system, but this does not mean that the refrigerant drive device in the multi-stage heat exchange system of the cold source utilization system in this application cannot be implemented in a non-uniform structure.

[0093] In one or more embodiments, the supply air of the condenser with a low condensing temperature in two adjacent heat exchange systems is the return air of the condenser with a high condensing temperature.

[0094] It should be understood that when the Nth condenser is connected in series with the N+1th condenser, the air outlet of the Nth condenser is connected to the air return outlet of the N+1th condenser. The N+1th condenser further exchanges heat and cools the air flowing out of the Nth condenser, thereby improving the heat exchange efficiency of the cold source utilization system.

[0095] As an example, please refer to Figure 2 , Figure 2 A schematic diagram of a cold source utilization system consisting of three heat exchange systems is shown. Figure 2 As shown, the cold source utilization system includes a primary system consisting of a primary compressor 01, a primary air pump 02, a primary evaporator 15, a primary condenser 07, and a primary liquid pump 09; a secondary system consisting of a secondary compressor 06, a secondary air pump 04, a secondary evaporator 14, a secondary condenser 08, and a secondary liquid pump 11; and a tertiary system consisting of a tertiary compressor 05, a tertiary air pump 03, a tertiary evaporator 13, a tertiary condenser 10, and a tertiary liquid pump 12. The primary condenser 07, secondary condenser 08, and tertiary condenser 10 are connected in series. The supply air to the tertiary condenser 10 is the return air to the secondary condenser 08, and the supply air to the secondary condenser 08 is the return air to the primary condenser 07. The condensing temperature of the primary condenser 07 is higher than that of the secondary condenser 08, and the condensing temperature of the secondary condenser 08 is higher than that of the tertiary condenser 10.

[0096] As an example, still refer to Figure 2Assume the evaporation temperature of the first-stage system is 20℃ and the condensation temperature is 50℃, the evaporation temperature of the second-stage system is 24℃ and the condensation temperature is 46℃, and the evaporation temperature of the third-stage system is 28℃ and the condensation temperature is 42℃. The outdoor return air temperature is 35℃, the supply air temperature is 47℃, the indoor return air temperature is 35℃, and the supply air temperature is 23℃.

[0097] The working principle of this cold source utilization system is as follows: outdoor return air at 35°C passes through a three-stage condenser on the outdoor side, where it is heated to 39°C. After heat exchange, it passes through a second-stage condenser to reach 43°C, and finally passes through the outermost first-stage condenser to reach 47°C before being discharged. The same principle applies to the indoor side. Indoor return air at 35°C is cooled to 31°C and 27°C respectively through three layers of heat exchange, and finally discharged at a supply air temperature of 23°C.

[0098] Compared to the three cooling modes of traditional refrigerant pump air conditioning units, Figure 2 The cold source utilization system shown has six different cold source utilization modes. It is assumed that the condensing temperature of the third-stage heat exchange system is T1, the condensing temperature of the second-stage heat exchange system is T2, and the condensing temperature of the first-stage heat exchange system is T3, where T1 < T2 < T3. As shown in Table 1, when the outdoor ambient temperature is greater than T1, all three stages of the heat exchange system operate in compressor mode. As the outdoor ambient temperature gradually decreases, when the outdoor ambient temperature drops to T1, the third-stage system activates the air pump mode, and the cold source utilization system enters 1 / 3 air pump mode. When the outdoor ambient temperature drops to T2, the third-stage system activates the liquid pump mode, and the system enters 1 / 3 liquid pump mode. When the outdoor ambient temperature drops to T3, the second-stage system activates the air pump mode, and the system enters 1 / 3 air pump mode + 1 / 3 liquid pump mode. When the temperature drops to T4, the second-stage system also activates the liquid pump mode, and the system enters 2 / 3 liquid pump mode. When the temperature drops to T5, the first-stage system activates the air pump mode, and the system enters 2 / 3 liquid pump mode + 1 / 3 air pump mode. When the temperature drops to T6, the first-stage system activates the liquid pump mode, and the system enters full liquid pump mode. Compared to the three cooling modes of traditional refrigerant pump air conditioning units, the cold source utilization system in this embodiment provides a more detailed division of time and temperature for cold source utilization, shortening the operating time of the higher-power compressor and extending the operating time of the lower-power air pump and liquid pump, reducing system power consumption and further improving energy efficiency.

[0099] Table 1

[0100]

[0101] As an example, a specific value is given for further analysis. Figure 2The mode switching of the cold source utilization system is shown in Table 2. The air pump mode is set to start when the indoor and outdoor heat exchange temperature difference is 4°C, and the liquid pump mode is set to start when the temperature difference is 7°C. It can be seen that when the outdoor temperature is above 23°C, both the traditional refrigerant pump air conditioner and the cold source utilization system in this embodiment start the compressor mode. When the outdoor temperature drops to 23°C, the condensing temperature of the third-stage condenser is 28°C. According to the condition that the air pump mode is started when the condensing temperature is 5°C different from the outdoor temperature, the third-stage system starts the air pump mode, the first and second-stage systems start the compressor mode, and the 1 / 3 air pump mode is started.

[0102] When the outdoor temperature drops to 21℃, the condensing temperature of the condenser in the third-stage system is 28℃. Based on a 7℃ temperature difference, the return air temperature of the third stage reaches 21℃. The third-stage system then enters liquid pump mode and starts 1 / 3 liquid pump mode.

[0103] When the outdoor temperature drops further to 15℃, the condensing temperature of the second-stage system condenser is 24℃. Because the return air temperature has passed through the three-stage heat exchange system, the temperature increases by 4℃ with each stage of the heat exchange system, while the temperature difference is reduced by 4℃. Therefore, when the outdoor ambient temperature is 15℃, the second-stage system starts the air pump mode. At this time, the third-stage system is in liquid pump mode, and the first-stage system is still in compressor mode. That is, the system starts 1 / 3 air pump mode + 1 / 3 liquid pump mode.

[0104] When the outdoor temperature drops further to 13℃, the condensing temperature of the second-stage system condenser is 24℃. Because the return air temperature has passed through the three-stage heat exchange system, the temperature increases by 4℃ with each stage of the heat exchange system, while the temperature difference of 7℃ is subtracted. Therefore, when the outdoor ambient temperature is 13℃, the second-stage system also starts the liquid pump mode, that is, the system starts the 2 / 3 liquid pump mode.

[0105] When the outdoor temperature drops further to 7℃, the condensing temperature of the first-stage system is 20℃. Because the return air temperature passes through the second-stage and third-stage heat exchange systems, the temperature increases by 4℃ with each stage of heat exchange, while the temperature difference is reduced by 4℃. Therefore, when the outdoor ambient temperature is 7℃, the first-stage system starts in air pump mode, while the second and third-stage systems are in liquid pump mode. The system operates in 1 / 3 air pump mode + 2 / 3 liquid pump mode.

[0106] When the outdoor temperature drops further to 5℃, the third-level system switches to liquid pump mode, that is, the system starts full liquid pump mode. Compared with traditional refrigerant pump air conditioners that only start liquid pump mode at 5℃, this new multi-gradient cold source technology can enter liquid pump mode more quickly, greatly improving the utilization capacity of liquid pump source.

[0107] Table 2

[0108]

[0109] In one or more embodiments, the return air of the condensers included in each stage of the heat exchange system is outdoor return air.

[0110] It should be understood that when the Nth condenser and the N+1th condenser are connected in parallel, the return air of the Nth condenser and the N+1th condenser are both indoor air. This parallel connection can still ensure the heat exchange effect of the cold source utilization system as much as possible even if one or more condensers in the multi-stage heat exchange system fail.

[0111] As an example, please refer to Figure 3 , Figure 3 A schematic diagram of a cold source utilization system consisting of three heat exchange systems is shown. Figure 3 As shown, the cold source utilization system includes a primary system consisting of a primary compressor 01, a primary air pump 02, a primary evaporator 15, a primary condenser 07, and a primary liquid pump 09; a secondary system consisting of a secondary compressor 06, a secondary air pump 04, a secondary evaporator 14, a secondary condenser 08, and a secondary liquid pump 11; and a tertiary system consisting of a tertiary compressor 05, a tertiary air pump 03, a tertiary evaporator 13, a tertiary condenser 10, and a tertiary liquid pump 12. The primary condenser 07, secondary condenser 08, and tertiary condenser 10 are connected in parallel, and their return air is all outdoor return air. The condensing temperature of the primary condenser 07 is higher than that of the secondary condenser 08, and the condensing temperature of the secondary condenser 08 is higher than that of the tertiary condenser 10.

[0112] The working principle of this cold source utilization system and the switching of cold source utilization modes can be found in the aforementioned... Figure 2 The cold source utilization system shown is omitted here to avoid redundancy.

[0113] The foregoing Figure 2 and Figure 3 The cold source utilization system is introduced using refrigerant-driven equipment including compressors, liquid pumps, and gas pumps as examples. The following section will introduce the cold source utilization system of this application using refrigerant-driven equipment including compressors and liquid pumps, compressors and gas pumps, gas pumps and liquid pumps, compressors, or gas pumps.

[0114] Please refer to Figure 4 , Figure 4 A schematic diagram of a cold source utilization system when the refrigerant-driven equipment includes a compressor and a liquid pump. (Example) Figure 4 As shown, when the temperature reaches the air pump mode activation temperature, the air pump mode is activated step by step. As the temperature continues to decrease, the liquid pump mode is activated step by step, further improving energy utilization efficiency based on this cold source utilization system. Figure 4As shown, taking the cold source utilization system comprising three heat exchange systems as an example, the first-stage heat exchange system includes a first-stage compressor 01, a first-stage liquid pump 09, a first-stage evaporator 15, and a first-stage condenser 07, where the evaporator temperature of the first-stage system is 20℃ and the condensation temperature is 50℃. The second-stage heat exchange system includes a second-stage compressor 06, a second-stage evaporator 14, a second-stage condenser 08, and a second-stage liquid pump 11, where the evaporator temperature of the second-stage system is 24℃ and the condensation temperature is 46℃. The third-stage system includes a third-stage compressor 05, a third-stage evaporator 13, a third-stage liquid pump 12, and a third-stage condenser 10, where the evaporator temperature of the third-stage system is 28℃ and the condensation temperature is 42℃. The outdoor return air temperature is 35℃, the supply air temperature is 47℃, the indoor return air temperature is 35℃, and the supply air temperature is 23℃.

[0115] The mode switching of the cold source utilization system is shown in Table 3. It can be seen that when the outdoor temperature is above T1℃, both the traditional refrigerant pump air conditioner and the cold source utilization system operate in compressor mode. When the outdoor temperature drops to T1℃, the third-stage system activates liquid pump mode, while the first and second-stage systems activate compressor mode, initiating 1 / 3 natural cooling mode. When the outdoor temperature drops to T2℃, the second and third-stage systems also activate liquid pump mode, and the first-stage system activates compressor mode, operating in 2 / 3 natural cooling mode. When the outdoor temperature drops to T3℃, the outdoor return air, after heat exchange through the three-stage system, meets the conditions for the third-stage system to activate natural cooling mode, and all three stages activate liquid pump mode, at which point the system enters full natural cooling mode. Compared to the traditional liquid pump mode, which only activates compressor mode above 5℃ and full natural cooling mode below 5℃, this significantly improves the utilization capacity of the natural cold source.

[0116] Table 3

[0117]

[0118] Please refer to Figure 5 , Figure 5 This diagram illustrates a cold source utilization system when the refrigerant-driven equipment includes a compressor and an air pump. When the temperature reaches the air pump mode activation temperature, the system first activates the air pump at 1 / 3 capacity. As the temperature continues to decrease, it then gradually activates the full air pump mode. Based on this multi-gradient cold source utilization system, the system progressively utilizes low-temperature outdoor cold sources, replacing the higher-power compressor with a lower-power air pump to complete the refrigeration process, further improving energy efficiency.

[0119] like Figure 5As shown, taking the cold source utilization system comprising three heat exchange systems as an example, the first-stage system includes a primary compressor 01, a primary air pump 02, a primary evaporator 15, and a primary condenser 07, where the evaporator temperature of the primary system is 20℃ and the condensation temperature is 50℃. The second-stage system includes a secondary compressor 06, a secondary evaporator 14, a secondary condenser 08, and a secondary air pump 04, where the evaporator temperature of the secondary system is 24℃ and the condensation temperature is 46℃. The third-stage system includes a tertiary compressor 05, a tertiary evaporator 13, a tertiary air pump 03, and a tertiary condenser 10, where the evaporator temperature of the tertiary system is 28℃ and the condensation temperature is 42℃. The outdoor return air temperature is 35℃, the supply air temperature is 47℃, the indoor return air temperature is 35℃, and the supply air temperature is 23℃.

[0120] The three systems utilize the natural cooling source by switching compressor and air pump modes in batches. The heat exchange of this multi-stage system is analyzed according to temperature symbols T1, T2, and T3. Table 4 shows the different natural cooling switching temperatures of this cooling source utilization system. It can be seen that when the outdoor temperature is above T1, both the traditional refrigerant pump air conditioner and the cooling source utilization system operate in compressor mode. When the outdoor temperature drops to T1℃, the innermost third-stage system activates air pump mode, while the first and second-stage systems activate compressor mode and operate at 1 / 3 air pump mode. When the outdoor temperature drops to T2℃, the second-stage system activates air pump mode, and the second and third-stage systems also activate air pump mode. The outermost first-stage system activates compressor mode and operates at 2 / 3 air pump mode. In contrast, the traditional refrigerant pump air conditioner still operates in compressor mode. This cooling source utilization system can efficiently utilize the natural cooling source from T1 to T3, effectively improving air conditioning energy efficiency. When the temperature drops below T3℃, the outermost system also activates air pump mode, at which point the system operates in full air pump mode, achieving efficient energy utilization.

[0121] Table 4

[0122]

[0123] Please refer to Figure 6 , Figure 6 A schematic diagram of a cold source utilization system when the refrigerant-driven equipment includes a gas pump and a liquid pump. (Example) Figure 6 As shown, when the temperature reaches the activation temperature of the air pump mode, the air pump mode is activated at 1 / 3 level first. As the temperature continues to decrease, the full air pump mode is activated step by step. As the temperature continues to decrease, the natural cooling mode is activated step by step. Based on this multi-gradient cold source utilization system, the low-temperature cold source outdoors is gradually utilized, and the lower-power air pump and liquid pump are used to replace the higher-power compressor to complete the cooling, thereby further improving energy utilization efficiency.

[0124] like Figure 6As shown, taking the cold source utilization system comprising three heat exchange systems as an example, the first-stage system includes a primary liquid pump 09, a primary air pump 02, a primary evaporator 15, and a primary condenser 07, where the evaporator temperature of the primary system is 20℃ and the condensation temperature is 50℃; the second-stage system includes a secondary liquid pump 11, a secondary evaporator 14, a secondary condenser 08, and a secondary air pump 04, where the evaporator temperature of the secondary system is 24℃ and the condensation temperature is 46℃; the third-stage system includes a tertiary liquid pump 12, a tertiary evaporator 13, a tertiary air pump 03, and a tertiary condenser 10, where the evaporator temperature of the tertiary system is 28℃ and the condensation temperature is 42℃. The outdoor return air temperature is 35℃, the supply air temperature is 47℃, the indoor return air temperature is 35℃, and the supply air temperature is 23℃.

[0125] Three heat exchange systems switch between liquid pump and gas pump modes in batches to achieve optimal utilization of the natural cold source. The heat exchange of this multi-stage system is analyzed according to temperature symbols T1, T2, and T3. Table 5 shows the different natural cooling switching temperatures of this cold source utilization system. It can be seen that when the outdoor temperature is above T1℃, a traditional refrigerant pump air conditioner operates in compressor mode, while the cold source utilization system in this embodiment operates in gas pump mode. When the outdoor temperature drops to T1℃, the innermost third-stage system operates in natural cooling mode, while the first and second-stage systems operate in gas mode, activating 1 / 3 of the natural cooling mode. When the outdoor temperature drops to T2℃, the second-stage system operates in natural cooling mode, and the third-stage system also operates in natural cooling mode. The outermost first-stage system operates in gas pump mode, activating 2 / 3 of the natural cooling mode. In contrast, a traditional refrigerant pump air conditioner still operates in compressor mode. The cold source utilization system in this embodiment can efficiently utilize the natural cold source from T1 to T3, effectively improving the air conditioner's energy efficiency. When the temperature drops below T3℃, the outermost system also activates liquid pump mode, at which point the system operates in full natural cooling mode, achieving efficient energy utilization.

[0126] Table 5

[0127]

[0128] Please refer to Figure 7 , Figure 7 A schematic diagram of a cold source utilization system when the refrigerant-driven equipment includes a compressor. (Example) Figure 7 As shown, the system consists of three compressors with different power ratings, which can be matched to air conditioning cooling modes applied to different cooling needs, and can effectively reduce the power consumption of the air conditioner's internal compressor.

[0129] like Figure 7As shown, taking the cold source utilization system comprising three heat exchange systems as an example, the first-stage system includes a primary compressor 01, a primary evaporator 15, and a primary condenser 07, where the evaporator temperature of the primary system is 20℃ and the condensation temperature is 50℃; the second-stage system includes a secondary evaporator 14, a secondary condenser 08, and a secondary compressor 06, where the evaporator temperature of the secondary system is 24℃ and the condensation temperature is 46℃; the third-stage system includes a tertiary condenser 10, a tertiary evaporator 13, and a tertiary compressor 05, where the evaporator temperature of the tertiary system is 28℃ and the condensation temperature is 42℃. The outdoor return air temperature is 35℃, the supply air temperature is 47℃, the indoor return air temperature is 35℃, and the supply air temperature is 23℃.

[0130] The three systems, each with different evaporation and condensation temperatures, can be applied to cooling needs in various environments while minimizing power consumption to meet those needs. In full-compressor mode, the reduced pressure ratio between the second and third stages allows the system to meet low-temperature cooling or dehumidification requirements. Low-temperature cooling is defined as cooling when the outdoor ambient temperature is lower than the indoor evaporation temperature. Because the evaporation temperature of the second and third stages is higher, this system is more suitable for low-temperature cooling, providing another application possibility for this multi-gradient cold source system in various scenarios. In full-compressor mode, when applied to dehumidification, the higher the evaporation temperature, the lower the condensation temperature, resulting in stronger system cooling capacity and better dehumidification. Furthermore, in areas with high outdoor ambient temperatures, compared to traditional refrigerant pump air conditioning units, this multi-gradient system has a smaller temperature difference between the second and third stages of evaporation and condensation, resulting in lower compressor power consumption and thus saving power during compressor operation. The system has higher energy efficiency.

[0131] In applications, compressors can be flexibly activated according to cooling needs. For example, at 100% load, three compressors can be activated; at 75% load, level 1 and level 2 systems can be activated; at 50% load, level 1 and level 3 systems can be activated; and at 25% load, level 2 and level 3 systems can be activated. When cooling demand decreases, one of the level systems can be flexibly shut down to avoid redundant cooling capacity, thereby reducing power consumption and increasing energy efficiency. It should be understood that the control equipment is pre-configured with corresponding drive strategies for different load conditions, and the drive strategies include the operating status of the compressors in each level of the heat exchange system under a certain load.

[0132] Please refer to Figure 8 , Figure 8 This is a schematic diagram of a cold source utilization system when the refrigerant-driven equipment includes an air pump. The system consists of three air pumps of different power ratings. Compared to a full compressor mode, the full air pump mode is more suitable for air conditioning cooling needs during transitional seasons while still meeting cooling requirements. Compared to a compressor, air pumps consume less power and can better utilize outdoor natural cold sources, reducing compressor power consumption.

[0133] like Figure 8 As shown, taking the cold source utilization system comprising three heat exchange systems as an example, the first-stage system includes a primary air pump 02, a primary evaporator 15, and a primary condenser 07, where the evaporator temperature of the primary system is 20℃ and the condensation temperature is 50℃; the second-stage system includes a secondary evaporator 14, a secondary condenser 08, and a secondary air pump 04, where the evaporator temperature of the secondary system is 24℃ and the condensation temperature is 46℃; the third-stage system includes a tertiary condenser 10, a tertiary evaporator 13, and a tertiary air pump 03, where the evaporator temperature of the tertiary system is 28℃ and the condensation temperature is 42℃. The outdoor return air temperature is 35℃, the supply air temperature is 47℃, the indoor return air temperature is 35℃, and the supply air temperature is 23℃.

[0134] The three systems are three sets of devices with different evaporation and condensation temperatures, which can be applied to cooling needs in different environments while achieving minimal power consumption to meet cooling requirements. In full-pump mode, the system is suitable for cooling needs of 5~25℃ during transitional seasons, providing another possibility for the multi-scenario application of this multi-gradient cold source system. Compared with compressor mode, the air conditioning unit in pump mode is more energy efficient and suitable for areas during transitional seasons, saving more power than the traditional compressor mode, resulting in higher system energy efficiency.

[0135] For compressor mode under high pressure ratio and large temperature difference conditions, the cold source utilization system in this embodiment adopts a gradient setting of evaporation and condensation temperatures. The evaporation and condensation temperatures differ by 30°C in the first-stage system, 22°C in the second-stage system, and 14°C in the third-stage system, with the temperature difference decreasing progressively. Compared to the 30°C difference between the evaporation and condensation temperatures of a single system in a traditional refrigerant pump air conditioning unit, the temperature difference is significantly reduced, and the pressure difference is also reduced, resulting in lower compressor power consumption and higher energy efficiency. In the pump mode under low pressure ratio and small temperature difference conditions, compared to the 20°C evaporation-condensation temperature difference in the pump mode of a traditional refrigerant pump air conditioning unit, this multi-gradient cold source technology has a 20°C evaporation-condensation temperature difference in the first stage, a 12°C difference in the second stage, and a 4°C difference in the third stage. Compared to traditional refrigerant pump air conditioning systems, this saves on the pump power consumption of the second and third stages, and further improves the system's energy efficiency in the low-pressure pump mode.

[0136] It should be understood that the aforementioned Figures 4-8 In the diagram, the condensers of each stage of the heat exchange system can be connected in series or in parallel. It should be understood that this is for ease of demonstration purposes. Figures 4-8 In the diagrams, the connections between the condensers in each stage of the heat exchange system are shown in series.

[0137] It should be understood that refrigerant-driven equipment may also include only a liquid pump. When only a liquid pump is included, the principle of the cold source utilization system is the same as that of the aforementioned system that only includes a gas pump or compressor, which will not be elaborated here.

[0138] In one or more embodiments, the cold source utilization system in this application can also effectively optimize the cost of the air conditioning system.

[0139] For air conditioning units used in data centers, the system typically needs to be equipped with a backup air conditioning unit to meet the cooling needs during actual operation and maintenance. For traditional refrigerant pump air conditioning units, in a data center, if the heat load demand is 720KW, for 180KW air conditioning units, according to the backup principle, traditional refrigerant pump air conditioning units need 4 units to meet the heat load, with 1 unit as a backup, for a total of 5 units totaling 900KW.

[0140] When using the cold source utilization system of this application, taking the refrigerant-driven equipment including compressor + liquid pump + gas pump as an example, one air conditioning unit includes a three-stage heat exchange system with a total of 9 units, that is, a combination of three compressors + gas pump + liquid pump, plus a spare heat exchange system, for a total of 12 units. According to the principle of one spare, the 11 units equally complete the 720KW heat load, with each unit receiving 66KW, which is equivalent to the cooling capacity of each heat exchange system being 198KW. The four heat exchange systems together provide 792KW. Compared with the traditional refrigerant pump air conditioning unit, which requires a total cooling capacity of 900KW, a total of 108KW is saved, achieving backup reduction and saving backup costs. Based on the price of 242,831 yuan for a 180KW air conditioning unit and 267,115 yuan for a 198KW air conditioning unit, the cost of a traditional refrigerant pump air conditioner is 1,214,159 yuan, while the cost of a multi-gradient cooling source technology is 1,068,460 yuan. In comparison, to meet the same cooling capacity requirements, the cost is reduced by approximately 145,699 yuan, which greatly optimizes the cost.

[0141] In one or more embodiments, the cold source utilization system can also realize different directions of supply and return air, thereby adjusting the evaporation temperature and condensation temperature of the multi-stage system. That is, it can realize three-stage system return air and one-stage system supply air, or one-stage system return air and three-stage system intake air. The intake air direction and evaporation and condensation temperature can be adjusted as needed, which helps the cold source utilization system to self-clean.

[0142] Based on the same inventive concept, this application also provides a control method for a cold source utilization system, which can be applied to the cold source utilization system described in the foregoing embodiments, such as... Figure 9 As shown, the method may include the following steps:

[0143] Step 901: Based on the cooling capacity influence parameters of the cold source utilization system, determine the target mode of the refrigerant drive device in each stage of the heat exchange system. The target mode is used to indicate the drive device that needs to be activated in the refrigerant drive device.

[0144] Step 902: Control the refrigerant drive device to operate according to the target mode.

[0145] Among them, the cooling capacity impact parameter is used to reflect the cooling capacity that the heat exchange systems at all levels included in the cold source utilization system need to output.

[0146] In this embodiment, the parameters affecting cooling capacity include, but are not limited to, outdoor ambient temperature or the current load of the cold source utilization system. Specifically, when the refrigerant driving device includes at least two of a compressor, a liquid pump, and a gas pump, the target mode of the refrigerant driving device is determined based on the outdoor ambient temperature. When the refrigerant driving device includes any one of a compressor, a liquid pump, and a gas pump, the target mode of the refrigerant driving device is determined based on the current load of the cold source utilization system.

[0147] The following explanations will cover two scenarios: when the types of refrigerant drive devices in each stage of the heat exchange system are the same, and when the types of refrigerant drive devices in each stage of the heat exchange system are not completely the same.

[0148] First, the types of refrigerant-driven devices are the same in all levels of heat exchange systems:

[0149] First, the refrigerant drive equipment for each stage of the heat exchange system includes a compressor, a gas pump, and a liquid pump.

[0150] Based on the refrigeration capacity influence parameters of the cold source utilization system, the target mode of the refrigerant drive equipment that needs to be activated in each stage of the heat exchange system can be determined, which may include the following steps:

[0151] Based on the outdoor ambient temperature, which is included as a parameter affecting cooling capacity, the indoor and outdoor heat exchange temperature difference corresponding to each level of heat exchange system is predicted.

[0152] If the temperature difference between indoor and outdoor heat exchange is less than the first temperature threshold, the target mode is determined to be the mode of starting the compressor;

[0153] If the temperature difference between indoor and outdoor heat exchange is greater than or equal to the first temperature threshold and less than the second temperature threshold, the target mode is determined to be the mode of starting the air pump; the second temperature threshold is greater than the first temperature threshold.

[0154] If the temperature difference between indoor and outdoor heat exchange is greater than or equal to the second temperature threshold, the target mode is determined to be the mode of starting the liquid pump.

[0155] In this embodiment, both the first temperature threshold and the second temperature threshold can be preset according to requirements, for example, the first temperature threshold can be set to 4°C and the second temperature threshold can be set to 7°C.

[0156] It should be understood that among compressors, air pumps, and liquid pumps belonging to the same heat exchange system, the power of the compressor is greater than that of the air pump, and the power of the air pump is greater than that of the liquid pump.

[0157] In this embodiment, the indoor-outdoor heat exchange temperature difference corresponding to each stage of the heat exchange system is used to characterize the temperature difference between the air flowing into and out of that stage of the heat exchange system. In application, this embodiment provides at least two methods for calculating the indoor-outdoor heat exchange temperature difference:

[0158] Based on the outdoor ambient temperature, the first condensing return air temperature of the condensers included in each stage of the heat exchange system is predicted, and the temperature difference between the first condensing return air temperature and the condensing temperature of the condensers included in each stage of the heat exchange system is calculated to obtain the indoor and outdoor heat exchange temperature difference.

[0159] or,

[0160] Based on the outdoor ambient temperature, the evaporation return air temperature of the evaporator and the second condensation return air temperature of the condenser, which are included in each stage of the heat exchange system, are predicted. The temperature difference between the evaporation return air temperature and the second condensation return air temperature is calculated to obtain the indoor and outdoor heat exchange temperature difference.

[0161] In a heat exchange system where condensers are connected in series at each level, if each level of the heat exchange system has an adjacent upstream heat exchange system, then the condenser return air temperature of the condenser in that level of the heat exchange system equals the supply air temperature of the condenser in the upstream heat exchange system. If each level of the heat exchange system does not have an adjacent upstream heat exchange system, then the condenser return air temperature of the condenser in that level of the heat exchange system equals the outdoor ambient temperature. The upstream heat exchange system refers to the heat exchange system that supplies air to each level of the heat exchange system.

[0162] When the condensers in each stage of the heat exchange system are connected in parallel, the condensing return air temperature of the condensers in that stage of the heat exchange system is equal to the outdoor ambient temperature.

[0163] Since the evaporators in the multi-stage heat exchange system are connected in series, the return air temperature of the evaporator in each stage of the heat exchange system is equal to the supply air temperature of the evaporator in the previous stage of the heat exchange system.

[0164] It should be understood that in at least two-stage heat exchange systems, the condenser temperatures of the condensers in different stages of the heat exchange system are different. This allows multiple heat exchange systems to switch target modes in a gradient, such as as shown in Table 1 or Table 2, where multiple heat exchange systems sequentially activate gas pump mode, liquid pump mode, etc. Compared to related technologies where refrigerant pump air conditioners only use the most energy-efficient liquid pump mode when the outdoor temperature is below 5°C, resulting in insufficient energy utilization in the 25-5°C temperature range, this embodiment provides a more detailed division of time and temperature for cold source utilization. This shortens the operating time of the higher-power compressor and extends the operating time of the lower-power gas pump and liquid pump, reducing system power consumption and further improving energy efficiency.

[0165] As an example, refer to Tables 1 and 2 above to understand the target mode of the cold source utilization system.

[0166] Secondly, the refrigerant drive equipment for each stage of the heat exchange system includes any two of the following: a compressor, a gas pump, and a liquid pump.

[0167] Based on the parameters affecting cooling capacity, the target mode for refrigerant-driven equipment that needs to be activated in each stage of the heat exchange system can be determined, which may include the following steps:

[0168] Based on the outdoor ambient temperature, which is included as a parameter affecting cooling capacity, the indoor and outdoor heat exchange temperature difference corresponding to each level of heat exchange system is predicted.

[0169] When the temperature difference between indoor and outdoor heat exchange is less than the third temperature threshold, the target mode is determined to be the mode of starting the first drive device;

[0170] When the temperature difference between indoor and outdoor heat exchange is greater than or equal to the third temperature threshold, the target mode is determined to be the mode of starting the second drive device;

[0171] The first driving device is the one with higher energy consumption among any two devices, and the second driving device is the one with lower energy consumption among any two devices.

[0172] It should be noted that the refrigerant driving devices included in each stage of the heat exchange system are the same. For example, if the refrigerant driving devices included in one stage of the heat exchange system in at least two stages are compressors and air pumps, then the refrigerant driving devices included in the other stages of the heat exchange system in at least two stages are also compressors and air pumps.

[0173] In this embodiment, the third temperature threshold can also be preset manually according to requirements.

[0174] The calculation process for the indoor-outdoor heat exchange temperature difference here is the same as that in the previous embodiment, and will not be described further here to avoid redundancy.

[0175] Finally, the refrigerant drive equipment for each stage of the heat exchange system includes any one of a compressor, a gas pump, and a liquid pump.

[0176] Based on the cooling capacity influence parameters, determine the target modes of the refrigerant drive equipment that needs to be activated in each stage of the heat exchange system, including:

[0177] The driving strategy corresponding to the current load of the cold source utilization system is obtained, including parameters that affect the cooling capacity.

[0178] According to the driving strategy, including the operating status of any device in each level of the heat exchange system, control the operation of any device.

[0179] In this embodiment, the control device is pre-configured with drive strategies corresponding to different loads. For example, at 100% load, all refrigerant drive devices in the three-stage heat exchange system are activated; at 75% load, the refrigerant drive devices in the first and second-stage heat exchange systems are activated; at 50% load, the refrigerant drive devices in the first and third-stage heat exchange systems are activated; and at 25% load, the refrigerant drive devices in the second and third-stage systems are activated. Thus, when the current load of the cold source utilization system is obtained, the pre-configured correspondence between load and drive strategy can be queried to obtain the drive strategy corresponding to the current load, and the refrigerant drive devices in the cold source utilization system can be controlled according to the obtained drive strategy.

[0180] Second, the types of refrigerant-driven devices in each stage of the heat exchange system are not entirely the same:

[0181] The following example uses a three-stage heat exchange system as an illustration.

[0182] like Figure 10 As shown, taking the cold source utilization system comprising three heat exchange systems as an example, the first-stage system includes a primary air pump 02, a primary compressor 01, a primary evaporator 15, and a primary condenser 07, where the evaporator temperature of the primary system is 20℃ and the condensation temperature is 50℃; the second-stage system includes a secondary evaporator 14, a secondary condenser 08, a secondary air pump 04, and a secondary liquid pump 11, where the evaporator temperature of the secondary system is 24℃ and the condensation temperature is 46℃; the third-stage system includes a tertiary condenser 10, a tertiary evaporator 13, and a tertiary liquid pump 12, where the evaporator temperature of the tertiary system is 28℃ and the condensation temperature is 42℃. The outdoor return air temperature is 35℃, the supply air temperature is 47℃, the indoor return air temperature is 35℃, and the supply air temperature is 23℃.

[0183] Compared to the three cooling modes of traditional refrigerant pump air conditioning units, Figure 10The cold source utilization heat exchange system shown has 6 different cold source utilization modes, as shown in Table 6. When the temperature is above T1, the compressor mode is activated. As the temperature gradually decreases, the three-stage heat exchange system activates the liquid pump mode to meet the cooling demand, and the cold source utilization system enters 1 / 3 natural cooling mode. When the temperature drops to T2, the two-stage heat exchange system activates the air pump mode, and the cold source utilization system enters 1 / 3 air pump mode + 1 / 3 natural cooling mode. When the temperature drops to T3, the two-stage heat exchange system activates the liquid pump mode, and the cold source utilization system enters 2 / 3 natural cooling mode. When the temperature drops to T4, the primary heat exchange system activates the air pump mode, and the cold source utilization system enters a 1 / 3 air pump mode + 2 / 3 natural cooling mode; when the temperature drops to T5, the primary heat exchange system also activates the liquid pump mode, and the cold source utilization system enters a completely natural cooling mode. The multi-gradient cold source technology heat exchange system of compressor + air pump + liquid pump provides more detailed division of time and temperature for cold source utilization, shortens the usage time of the higher-power compressor, and extends the usage time of the lower-power air pump and liquid pump, thereby reducing the power consumption of the heat exchange system and further improving energy efficiency.

[0184] Table 6. Natural cooling source switching temperature under compressor + air pump + liquid pump mode

[0185]

[0186] This application also provides a control device for a cold source utilization system. This device is applied to the cold source utilization system described in the foregoing embodiments and is used to execute the control method for the cold source utilization system provided in any of the above embodiments. For example... Figure 11 As shown, the device includes:

[0187] The determination module 110 is used to determine the target mode of the refrigerant drive device in each stage of the heat exchange system based on the refrigeration capacity influence parameters of the cold source utilization system. The target mode is used to indicate the drive device that needs to be started in the refrigerant drive device.

[0188] The control module 120 is used to control the refrigerant drive device to operate according to the target mode.

[0189] In one or more embodiments, the refrigerant driving device includes a compressor, a gas pump, and a liquid pump; the energy consumption of the compressor is greater than the energy consumption of the gas pump, and the energy consumption of the gas pump is greater than the energy consumption of the liquid pump.

[0190] The determination module 110 is used for:

[0191] Based on the outdoor ambient temperature, which is included in the parameters affecting the cooling capacity, the indoor and outdoor heat exchange temperature difference corresponding to each stage of the heat exchange system is predicted.

[0192] If the indoor and outdoor heat exchange temperature difference is less than a first temperature threshold, the target mode is determined to be the mode of starting the compressor;

[0193] If the indoor-outdoor heat exchange temperature difference is greater than or equal to a first temperature threshold and less than a second temperature threshold, the target mode is determined to be the mode of starting the air pump; the second temperature threshold is greater than the first temperature threshold.

[0194] If the indoor and outdoor heat exchange temperature difference is greater than or equal to the second temperature threshold, the target mode is determined to be the mode of starting the liquid pump.

[0195] In one or more embodiments, the refrigerant driving device includes any two of a compressor, a gas pump, and a liquid pump; the energy consumption of the compressor is greater than the energy consumption of the gas pump, and the energy consumption of the gas pump is greater than the energy consumption of the liquid pump.

[0196] The determination module 110 is used for:

[0197] Based on the outdoor ambient temperature, which is included in the parameters affecting the cooling capacity, the indoor and outdoor heat exchange temperature difference corresponding to each stage of the heat exchange system is predicted.

[0198] When the indoor and outdoor heat exchange temperature difference is less than the third temperature threshold, the target mode is determined to be the mode of starting the first drive device;

[0199] If the indoor-outdoor heat exchange temperature difference is greater than or equal to the third temperature threshold, the target mode is determined to be the mode of starting the second drive device;

[0200] The first driving device is the one with higher energy consumption among the two devices, and the second driving device is the one with lower energy consumption among the two devices.

[0201] In one or more embodiments, the determining module 110 is configured to:

[0202] Based on the outdoor ambient temperature, the first condensing return air temperature of the condenser included in each stage of the heat exchange system is predicted, and the temperature difference between the first condensing return air temperature and the condensing temperature of the condenser included in each stage of the heat exchange system is calculated to obtain the indoor and outdoor heat exchange temperature difference.

[0203] or,

[0204] Based on the outdoor ambient temperature, the evaporation return air temperature of the evaporator and the second condensation return air temperature of the condenser, which are included in each stage of the heat exchange system, are predicted. The temperature difference between the evaporation return air temperature and the second condensation return air temperature is calculated to obtain the indoor and outdoor heat exchange temperature difference.

[0205] In one or more embodiments, the refrigerant driving device includes any one of a compressor, a gas pump, and a liquid pump;

[0206] The determination module 110 is used for:

[0207] Obtain the driving strategy corresponding to the current load of the cold source utilization system, which is included in the cooling capacity influence parameters;

[0208] According to the driving strategy, the operation of any one of the devices included in each level of the heat exchange system is controlled.

[0209] The control device for the cold source utilization system provided in this application embodiment and the control method for the cold source utilization system provided in this application embodiment are based on the same inventive concept and have the same beneficial effects as the methods they adopt, operate or implement.

[0210] This application also provides an electronic device for executing the control method of the above-described cold source utilization system. Please refer to... Figure 12 It illustrates a schematic diagram of an electronic device provided by some embodiments of this application. For example... Figure 12 As shown, the electronic device 8 includes: a processor 800, a memory 801, a bus 802, and a communication interface 803. The processor 800, the communication interface 803, and the memory 801 are connected via the bus 802. The memory 801 stores a computer program that can run on the processor 800. When the processor 800 runs the computer program, it executes the control method of the cold source utilization system provided in any of the foregoing embodiments of this application.

[0211] The memory 801 may include high-speed random access memory (RAM) or non-volatile memory, such as at least one disk storage device. Communication between this device network element and at least one other network element is achieved through at least one communication interface 803 (which can be wired or wireless), such as the Internet, wide area network, local area network, metropolitan area network, etc.

[0212] Bus 802 can be an ISA bus, PCI bus, or EISA bus, etc. The bus can be divided into an address bus, a data bus, a control bus, etc. The memory 801 is used to store programs. After receiving an execution instruction, the processor 800 executes the program. The control method of the cold source utilization system disclosed in any of the foregoing embodiments of this application can be applied to the processor 800, or implemented by the processor 800.

[0213] The processor 800 may be an integrated circuit chip with signal processing capabilities. In implementation, each step of the above method can be completed by the integrated logic circuitry in the hardware of the processor 800 or by instructions in software form. The processor 800 may be a general-purpose processor, including a central processing unit (CPU), a network processor (NP), etc.; it may also be a digital signal processor (DSP), an application-specific integrated circuit (ASIC), an off-the-shelf programmable gate array (FPGA), or other programmable logic devices, discrete gate or transistor logic devices, or discrete hardware components. It can implement or execute the methods, steps, and logic block diagrams disclosed in the embodiments of this application. The general-purpose processor may be a microprocessor or any conventional processor. The steps of the methods disclosed in the embodiments of this application can be directly embodied in the execution of a hardware decoding processor, or executed by a combination of hardware and software modules in the decoding processor. The software modules may reside in random access memory, flash memory, read-only memory, programmable read-only memory, electrically erasable programmable memory, registers, or other mature storage media in the art. The storage medium is located in memory 801. Processor 800 reads the information in memory 801 and, in conjunction with its hardware, completes the steps of the above method.

[0214] The electronic device provided in this application embodiment and the control method of the cold source utilization system provided in this application embodiment are based on the same inventive concept and have the same beneficial effects as the methods they adopt, operate or implement.

[0215] This application also provides a computer-readable storage medium corresponding to the control method of the cold source utilization system provided in the foregoing embodiments. Please refer to... Figure 13 The computer-readable storage medium shown is an optical disc 30, on which a computer program (i.e., a program product) is stored. When the computer program is run by a processor, it executes the control method of the cold source utilization system provided in any of the foregoing embodiments.

[0216] It should be noted that examples of the computer-readable storage medium may also include, but are not limited to, phase-change memory (PRAM), static random access memory (SRAM), dynamic random access memory (DRAM), other types of random access memory (RAM), read-only memory (ROM), electrically erasable programmable read-only memory (EEPROM), flash memory or other optical and magnetic storage media, which will not be elaborated here.

[0217] The computer-readable storage medium provided in the above embodiments of this application and the control method of the cold source utilization system provided in the embodiments of this application are based on the same inventive concept and have the same beneficial effects as the methods adopted, run or implemented by the application programs stored therein.

[0218] It should be noted that:

[0219] Numerous specific details are set forth in the specification provided herein. However, it will be understood that embodiments of this application may be practiced without these specific details. In some instances, well-known structures and techniques have not been shown in detail so as not to obscure the understanding of this specification.

[0220] Similarly, it should be understood that, for the sake of brevity and to aid in understanding one or more of the various inventive aspects, in the above description of exemplary embodiments of this application, various features of this application are sometimes grouped together in a single embodiment, figure, or description thereof. However, this disclosure should not be construed as reflecting a schematic diagram in which the claimed application requires more features than expressly recited in each claim. Rather, as reflected in the following claims, inventive aspects lie in fewer than all features of a single foregoing disclosed embodiment. Therefore, the claims following the detailed description are hereby expressly incorporated into that detailed description, wherein each claim itself is a separate embodiment of this application.

[0221] Furthermore, those skilled in the art will understand that although some embodiments described herein include certain features but not others included in other embodiments, combinations of features from different embodiments are intended to be within the scope of this application and form different embodiments. For example, in the following claims, any of the claimed embodiments can be used in any combination.

[0222] The above description is merely a preferred embodiment of this application, but the scope of protection of this application is not limited thereto. Any variations or substitutions that can be easily conceived by those skilled in the art within the technical scope disclosed in this application should be included within the scope of protection of this application. Therefore, the scope of protection of this application should be determined by the scope of the claims.

Claims

1. A cold source utilization system, characterized in that, include: At least two stages of heat exchange system and control equipment; Each stage of the heat exchange system includes an evaporator, a condenser, a refrigerant drive unit, and delivery pipelines; The delivery pipeline passes through the evaporator and the condenser, and is connected to the refrigerant driving device; each of the refrigerant driving devices includes a driving unit: a compressor, a gas pump, and a liquid pump. The refrigerant drive device is also connected to the control device; The evaporator of the heat exchange system in different stages has a different evaporation temperature, and the condenser of the heat exchange system in different stages has a different condensation temperature; wherein, the evaporation temperature refers to the saturation temperature at which the refrigerant changes from liquid to gas in the evaporator, and the condensation temperature refers to the temperature at which the refrigerant condenses from a gaseous state to a liquid state in the condenser. The control device is used to determine the target mode of the refrigerant drive device in each stage of the heat exchange system based on the cooling capacity influence parameters. The target mode is used to indicate the drive device that needs to be activated in the refrigerant drive device. Control the refrigerant drive device to operate according to the target mode.

2. The cold source utilization system according to claim 1, characterized in that, In the heat exchange systems of adjacent stages, the supply air of the condenser with the low condensing temperature is the return air of the condenser with the high condensing temperature.

3. The cold source utilization system according to claim 1, characterized in that, The return air of the condensers in each stage of the heat exchange system is outdoor return air.

4. A control method for a cold source utilization system, characterized in that, The method, applied to the cold source utilization system according to any one of claims 1-3, comprises: Based on the cooling capacity influence parameters of the cold source utilization system, the target mode of the refrigerant drive device in each stage of the heat exchange system is determined. The target mode is used to indicate the drive device that needs to be activated in the refrigerant drive device. Control the refrigerant drive device to operate according to the target mode.

5. The method according to claim 4, characterized in that, The refrigerant driving device includes a compressor, an air pump, and a liquid pump; the energy consumption of the compressor is greater than that of the air pump, and the energy consumption of the air pump is greater than that of the liquid pump. Based on the cooling capacity influence parameters of the cold source utilization system, the target modes of the refrigerant drive equipment that need to be activated in each stage of the heat exchange system are determined, including: Based on the outdoor ambient temperature, which is included in the parameters affecting the cooling capacity, the indoor and outdoor heat exchange temperature difference corresponding to each stage of the heat exchange system is predicted. If the indoor and outdoor heat exchange temperature difference is less than a first temperature threshold, the target mode is determined to be the mode of starting the compressor; If the indoor-outdoor heat exchange temperature difference is greater than or equal to a first temperature threshold and less than a second temperature threshold, the target mode is determined to be the mode of starting the air pump; the second temperature threshold is greater than the first temperature threshold. If the indoor and outdoor heat exchange temperature difference is greater than or equal to the second temperature threshold, the target mode is determined to be the mode of starting the liquid pump.

6. The method according to claim 4, characterized in that, The refrigerant driving device includes any two of the following: a compressor, a gas pump, and a liquid pump; the energy consumption of the compressor is greater than that of the gas pump, and the energy consumption of the gas pump is greater than that of the liquid pump. Based on the cooling capacity influence parameters, determine the target modes of the refrigerant drive equipment that needs to be activated in each stage of the heat exchange system, including: Based on the outdoor ambient temperature, which is included in the parameters affecting the cooling capacity, the indoor and outdoor heat exchange temperature difference corresponding to each stage of the heat exchange system is predicted. When the indoor and outdoor heat exchange temperature difference is less than the third temperature threshold, the target mode is determined to be the mode of starting the first drive device; If the indoor-outdoor heat exchange temperature difference is greater than or equal to the third temperature threshold, the target mode is determined to be the mode of starting the second drive device; The first driving device is the one with higher energy consumption among the two devices, and the second driving device is the one with lower energy consumption among the two devices.

7. The method according to claim 5 or 6, characterized in that, Based on the outdoor ambient temperature, which is included in the parameters affecting the cooling capacity, the indoor and outdoor heat exchange temperature difference corresponding to each stage of the heat exchange system is predicted, including: Based on the outdoor ambient temperature, the first condensing return air temperature of the condenser included in each stage of the heat exchange system is predicted, and the temperature difference between the first condensing return air temperature and the condensing temperature of the condenser included in each stage of the heat exchange system is calculated to obtain the indoor and outdoor heat exchange temperature difference. or, Based on the outdoor ambient temperature, the evaporation return air temperature of the evaporator and the second condensation return air temperature of the condenser, which are included in each stage of the heat exchange system, are predicted. The temperature difference between the evaporation return air temperature and the second condensation return air temperature is calculated to obtain the indoor and outdoor heat exchange temperature difference.

8. The method according to claim 4, characterized in that, The refrigerant driving device includes any one of a compressor, a gas pump, and a liquid pump; Based on the cooling capacity influence parameters, determine the target modes of the refrigerant drive equipment that needs to be activated in each stage of the heat exchange system, including: Obtain the driving strategy corresponding to the current load of the cold source utilization system, which is included in the cooling capacity influence parameters; According to the driving strategy, the operation of any one of the devices included in each level of the heat exchange system is controlled.

9. A control device for a cold source utilization system, characterized in that, The device is applied to the cold source utilization system according to any one of claims 1-3, the device comprising: The determination module is used to determine the target mode of the refrigerant drive device in each stage of the heat exchange system based on the refrigeration capacity influence parameters of the cold source utilization system. The target mode is used to indicate the drive device that needs to be activated in the refrigerant drive device. The control module is used to control the refrigerant drive device to operate according to the target mode.

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