Cooling unit, cooling control method, device, apparatus, medium and cooling system

Abstract

The present disclosure provides a cooling unit, a cooling control method, a device, equipment, a medium and a cooling system, and relates to the technical field of heat dissipation. The cooling unit comprises: a first evaporator comprising a plurality of first heat exchange pipelines, a first compressor in fluid communication with the first evaporator, a second evaporator comprising a plurality of second heat exchange pipelines arranged in parallel and at intervals with the plurality of first heat exchange pipelines, and a second compressor in fluid communication with the second evaporator, the plurality of first heat exchange pipelines are arranged in parallel in an inner circulating air supply channel, and are used for cooling an air flow flowing through the first evaporator in the inner circulating air supply channel by using a first refrigerant flow circulating in the first heat exchange pipeline; the plurality of second heat exchange pipelines are arranged in parallel in the inner circulating air supply channel, and are used for cooling an air flow flowing through the second evaporator in the inner circulating air supply channel by using a second refrigerant flow circulating in the second heat exchange pipeline, thereby improving air supply uniformity.

Description

Technical Field

[0001] This disclosure relates to the field of heat dissipation technology, and more specifically, to a cooling unit, a cooling control method, a cooling control device, an electronic device, a computer-readable storage medium, a computer program product, and a cooling system. Background Technology

[0002] In applications that utilize compressor cooling for heat dissipation, such as data centers and server rooms, the amount of heat generated is substantial, leading to significant cooling demands. Therefore, multiple compressor systems are typically employed, with each system's compressors starting sequentially until the cooling requirements are met. Improving the energy efficiency of multi-compressor systems has become a pressing issue. Summary of the Invention

[0003] The purpose of this disclosure is to provide a cooling unit, cooling control method, cooling control device, electronic device, computer-readable storage medium, computer program product, and cooling system that improves the energy efficiency of multiple compressor systems to at least a certain extent.

[0004] Other features and advantages of this disclosure will become apparent from the following detailed description, or may be learned in part from practice of this disclosure.

[0005] This disclosure provides a cooling unit for cooling airflow within an internal circulation airflow channel. The cooling unit includes a first evaporator, a first compressor, a second evaporator, and a second compressor. The first evaporator includes multiple first heat exchange pipes arranged in parallel within the internal circulation airflow channel. These first heat exchange pipes utilize a first refrigerant flow circulating within them to cool the airflow passing through the first evaporator within the internal circulation airflow channel. The first compressor is in fluid communication with the first evaporator and is used to compress the first refrigerant flow. The second evaporator includes multiple second heat exchange pipes arranged in parallel within the internal circulation airflow channel. These second heat exchange pipes utilize a second refrigerant flow circulating within them to cool the airflow passing through the second evaporator within the internal circulation airflow channel. The multiple second heat exchange pipes are arranged parallel to and spaced apart from the multiple first heat exchange pipes. The second compressor is in fluid communication with the second evaporator and is used to compress the second refrigerant flow.

[0006] This disclosure provides a cooling unit for cooling airflow within an internal circulation air supply channel. The internal circulation air supply channel has an internal circulation cross-section comprising a first region and a second region. The cooling unit includes a first evaporator, a first compressor, a second evaporator, a second compressor, a third evaporator, a third compressor, a fourth evaporator, and a fourth compressor. Specifically: the first evaporator includes multiple first heat exchange pipes arranged in parallel within the first region; these pipes utilize a first refrigerant flow circulating within them to cool the airflow passing through the first evaporator within the internal circulation air supply channel; the first compressor is in fluid communication with the first evaporator and is used to compress the first refrigerant flow; the second evaporator includes multiple second heat exchange pipes arranged in parallel within the first region; these pipes utilize a second refrigerant flow circulating within them to cool the airflow passing through the second evaporator within the internal circulation air supply channel. The system comprises: a second heat exchange pipeline arranged in parallel with a plurality of first heat exchange pipelines at intervals; a second compressor in fluid communication with the second evaporator for compressing the second refrigerant flow; a third evaporator comprising a plurality of third heat exchange pipelines arranged in parallel in the second region, the plurality of third heat exchange pipelines being used to cool the airflow flowing through the third evaporator in the internal circulation air supply channel using the third refrigerant flow circulating in the third heat exchange pipelines; a third compressor in fluid communication with the third evaporator for compressing the third refrigerant flow; a fourth evaporator comprising a plurality of fourth heat exchange pipelines arranged in parallel in the second region, the plurality of fourth heat exchange pipelines being used to cool the airflow flowing through the fourth evaporator in the internal circulation air supply channel using the fourth refrigerant flow circulating in the fourth heat exchange pipelines; a plurality of fourth heat exchange pipelines arranged in parallel with a plurality of third heat exchange pipelines at intervals; a fourth compressor in fluid communication with the fourth evaporator for compressing the fourth refrigerant flow.

[0007] This disclosure provides a cooling control method applied to any of the above-described cooling units. The method includes: controlling the first compressor to start; obtaining a first target speed; controlling the first compressor to increase its speed with a first acceleration and obtaining the current speed of the first compressor at a first frequency; obtaining a second target speed, the second target speed being obtained based on the first target speed, a first cooling demand corresponding to the cooling unit, and the oil return speed of the second compressor; if the current speed of the first compressor is maintained at the first target speed greater than or equal to a first duration, then controlling the first compressor to decrease its speed to the second target speed with a second acceleration and controlling the second compressor to start; and controlling the second compressor to increase its speed to the second target speed with a third acceleration.

[0008] This disclosure provides a cooling control method applied to any of the above-described cooling units. The method includes: controlling the start of a first compressor; obtaining a first target speed; controlling the first compressor to increase its speed with a first acceleration and obtaining the current speed of the first compressor at a first frequency; obtaining a second target speed, the second target speed being obtained based on the first target speed, a first cooling demand corresponding to the cooling unit, and the oil return speed of the third compressor; if the current speed of the first compressor is maintained at the first target speed greater than or equal to a first duration, then controlling the first compressor to decrease its speed to the second target speed with a second acceleration, and controlling the start of the third compressor; and controlling the third compressor to increase its speed to the second target speed with a third acceleration.

[0009] This disclosure provides a cooling control device applied to any of the above-described cooling units. The device includes: a switch control module for controlling the start of a first compressor; the switch control module is further configured to control the start of a second compressor if the current speed of the first compressor is maintained at a first target speed greater than or equal to a first duration; a parameter acquisition module for acquiring a first target speed; the parameter acquisition module is further configured to acquire the current speed of the first compressor at a first frequency; the parameter acquisition module is further configured to acquire a second target speed, the second target speed being obtained based on the first target speed, a first cooling demand corresponding to the cooling unit, and the oil return speed of the second compressor; a speed control module for controlling the first compressor to increase its speed with a first acceleration; the speed control module is further configured to control the first compressor to decrease its speed to the second target speed with a second acceleration if the current speed of the first compressor is maintained at a first target speed greater than or equal to the first duration; the speed control module is further configured to control the second compressor to increase its speed to the second target speed with a third acceleration.

[0010] According to one embodiment of this disclosure, the parameter acquisition module is further configured to acquire the running time of the first compressor and the running time of the second compressor respectively; the switch control module is further configured to control the first compressor to start if the running time of the first compressor is not greater than the running time of the second compressor.

[0011] According to one embodiment of this disclosure, the parameter acquisition module is further configured to acquire a third target rotational speed; the rotational speed control module is further configured to control the first compressor and the second compressor to increase their rotational speed to the third target rotational speed with a fourth acceleration; the parameter acquisition module is further configured to acquire the current cooling demand corresponding to the cooling unit at a second frequency; the rotational speed control module is further configured to control the rotational speeds of the first compressor and the second compressor according to the current cooling demand corresponding to the cooling unit, and acquire the current rotational speeds of the first compressor and the second compressor at a third frequency; the parameter acquisition module is further configured to acquire a fourth target rotational speed, which is acquired based on the current cooling demand corresponding to the cooling unit and the first cooling demand; the parameter acquisition module is further configured to acquire a fifth target rotational speed, which is acquired based on the fourth target rotational speed and the current cooling demand corresponding to the cooling unit; the switch control module is further configured to, if the current rotational speed of the first compressor is maintained at the fourth target rotational speed greater than or equal to a second duration, and the current rotational speed of the second compressor is maintained at the fourth target rotational speed greater than or equal to a second duration, control the second compressor to shut down, and control the first compressor to increase its rotational speed to the fifth target rotational speed with a fifth acceleration.

[0012] According to an embodiment of this disclosure, the parameter acquisition module is further configured to acquire the running time of the first compressor and the running time of the second compressor respectively; the switch control module is further configured to control the second compressor to shut down if the running time of the first compressor is not greater than the running time of the second compressor, and control the first compressor to increase its speed to the fifth target speed with a fifth acceleration.

[0013] This disclosure provides a cooling control device applied to any of the above-described cooling units. The device includes: a switch control module, configured to: control the start of the first compressor; if the current speed of the first compressor is maintained at a first target speed greater than or equal to a first duration, then control the start of the third compressor; a parameter acquisition module, configured to: acquire a first target speed; acquire the current speed of the first compressor at a first frequency; acquire a second target speed, the second target speed being obtained based on the first target speed, a first cooling demand corresponding to the cooling unit, and the oil return speed of the third compressor; and a speed control module, configured to control the first compressor to increase its speed with a first acceleration; if the current speed of the first compressor is maintained at a first target speed greater than or equal to the first duration, then control the first compressor to decrease its speed to the second target speed with a second acceleration; and control the third compressor to increase its speed to the second target speed with a third acceleration.

[0014] This disclosure provides a cooling system including any of the cooling units described above, and a heat exchange unit, wherein the heat exchange unit is used to cool the airflow in the internal circulation air supply channel using an external circulation airflow.

[0015] This disclosure provides an electronic device, including: a memory, a processor, and executable instructions stored in the memory and executable in the processor, wherein the processor executes the executable instructions to implement any of the methods described above.

[0016] This disclosure provides a computer-readable storage medium having computer-executable instructions stored thereon, which, when executed by a processor, implement any of the methods described above.

[0017] This disclosure provides a computer program product or computer program including computer instructions stored in a computer-readable storage medium. A processor of a computer device reads the computer instructions from the computer-readable storage medium and executes the computer instructions, causing the computer device to perform the methods provided in the various optional implementations described above.

[0018] The cooling unit provided in the embodiments of this disclosure arranges multiple first heat exchange pipes of the first evaporator and multiple second heat exchange pipes of the second evaporator in parallel and spaced apart in the internal circulation air supply channel. Since the first evaporator (or the second evaporator) can fill the internal circulation cross-section of the internal circulation air supply channel, it is possible to cool the entire airflow of the internal circulation cross-section through the multiple first heat exchange pipes of the first evaporator or the multiple second heat exchange pipes of the second evaporator when only the first compressor or the second compressor is turned on, thereby improving the uniformity of air supply. Therefore, it is not necessary to provide a lower evaporation temperature or a larger air volume when starting each compressor one by one to achieve the same cooling capacity to meet the cooling demand, thereby improving the energy efficiency of the multi-compressor system. Attached Figure Description

[0019] Figure 1 A schematic diagram of a cooling system according to an embodiment of the present disclosure is shown.

[0020] Figure 2 A schematic diagram of the structure of a cooling unit according to an embodiment of the present disclosure is shown.

[0021] Figure 3 A schematic diagram of another cooling unit in an embodiment of this disclosure is shown.

[0022] Figure 4 A schematic diagram of the structure of another cooling unit in an embodiment of this disclosure is shown.

[0023] Figure 5 Based on Figure 4 The diagram shows a heat exchange piping arrangement for a cooling unit.

[0024] Figure 6 Based on Figure 3 A schematic diagram of another cooling unit is shown.

[0025] Figure 7 A schematic diagram of the structure of another cooling unit in an embodiment of this disclosure is shown.

[0026] Figure 8 A schematic diagram of the structure of another cooling unit in an embodiment of this disclosure is shown.

[0027] Figure 9 Based on Figure 8 The diagram shows a heat exchange piping arrangement for a cooling unit.

[0028] Figure 10 A schematic diagram of the structure of another cooling unit in an embodiment of this disclosure is shown.

[0029] Figure 11 Based on Figure 10 The diagram shows a heat exchange piping arrangement for a cooling unit.

[0030] Figure 12 This is a flowchart illustrating a cooling control method according to an exemplary embodiment.

[0031] Figure 13 This is a schematic diagram illustrating the relationship between compressor speed and time according to an exemplary embodiment.

[0032] Figure 14 This is a flowchart illustrating another cooling control method according to an exemplary embodiment.

[0033] Figure 15 This is a flowchart illustrating yet another cooling control method according to an exemplary embodiment.

[0034] Figure 16 This is a schematic diagram illustrating the relationship between compressor speed regulation and CFC according to an exemplary embodiment.

[0035] Figure 17 This is a block diagram illustrating a cooling control device according to an exemplary embodiment.

[0036] Figure 18 This is a block diagram illustrating another cooling control device according to an exemplary embodiment.

[0037] Figure 19 A schematic diagram of the structure of an electronic device according to an embodiment of the present disclosure is shown. Detailed Implementation

[0038] Exemplary embodiments will now be described more fully with reference to the accompanying drawings. However, these exemplary embodiments can be implemented in many forms and should not be construed as limited to the examples set forth herein; rather, these embodiments are provided to make this application more comprehensive and complete, and to fully convey the concept of the exemplary embodiments to those skilled in the art.

[0039] Furthermore, the described features, structures, or characteristics can be combined in any suitable manner in one or more embodiments. Numerous specific details are provided in the following description to give a thorough understanding of embodiments of this application. However, those skilled in the art will recognize that the technical solutions of this application can be practiced without one or more of the specific details, or other methods, components, apparatuses, steps, etc., can be employed. In other instances, well-known methods, apparatuses, implementations, or operations are not shown or described in detail to avoid obscuring various aspects of this application.

[0040] Exemplary embodiments will now be described more fully with reference to the accompanying drawings. However, these exemplary embodiments can be implemented in many forms and should not be construed as limited to the examples set forth herein; rather, they are provided so that this disclosure will be more comprehensive and complete, and will fully convey the concept of the exemplary embodiments to those skilled in the art. The drawings are merely illustrative of this disclosure and are not necessarily drawn to scale. The same reference numerals in the drawings denote the same or similar parts, and therefore repeated descriptions of them will be omitted.

[0041] Furthermore, the described features, structures, or characteristics can be combined in any suitable manner in one or more embodiments. Numerous specific details are provided in the following description to give a thorough understanding of embodiments of this disclosure. However, those skilled in the art will recognize that the technical solutions of this disclosure can be practiced with one or more of the specific details omitted, or other methods, apparatuses, steps, etc., can be employed. In other instances, well-known structures, methods, apparatuses, implementations, or operations are not shown or described in detail to avoid obscuring various aspects of this disclosure.

[0042] Furthermore, in the description of this disclosure, unless otherwise expressly specified and limited, terms such as "connection" should be interpreted broadly, for example, meaning an electrical connection or the ability to communicate with each other; it can be a direct connection or an indirect connection through an intermediate medium. A structure or device with "fluid connectivity" may have interconnected channels in which fluids (e.g., gases, liquids, etc.) can flow. "A plurality of" means at least two, such as two, three, etc., unless otherwise expressly and specifically defined. Those skilled in the art will understand the specific meaning of the above terms in this disclosure according to the specific circumstances.

[0043] The following is an explanation of the terms used in this disclosure.

[0044] Indirect evaporative cooling refers to the process of transferring the cooling capacity of humidified air obtained by direct evaporation and cooling of fresh air (e.g., secondary side intake air) through a non-direct contact heat exchanger (e.g., "air-to-air heat exchange core" below) to the air to be treated (e.g., "primary side return air" below), thus achieving isohumidified cooling of the air. A system that implements indirect evaporative cooling is called an indirect evaporative cooling unit, also known as a cabinet-type air conditioner, or Air Handle Unit (AHU) in English.

[0045] Air-to-air heat exchange core: also known as an air heat exchanger, its core component is a heat exchange element. The indoor recirculated air (also known as "indoor return air", such as "primary side return air" below) and the outdoor fresh air (also known as "outdoor intake air", such as "secondary side intake air" below) can exchange temperatures through the heat exchange element. When operating in winter, because the outdoor intake air temperature is lower than the indoor return air temperature, the indoor return air can obtain cooling from the outdoor intake air through the air-to-air heat exchange core, thereby reducing the indoor return air temperature and achieving the effect of natural cooling of the indoor return air. This cooling mode is called "natural cooling mode".

[0046] Dry operating condition: A type of operating condition under natural cooling mode, in which the secondary side air intake does not undergo spray humidification treatment, and directly exchanges heat with the primary side return air through the air-to-air heat exchange core.

[0047] Wet operating condition: A type of operating condition under natural cooling mode, in which the secondary side intake air is humidified by spraying, and then heat is exchanged with the primary side return air through the air-to-air heat exchange core.

[0048] Hybrid operating condition: A type of electric cooling mode. When natural cooling cannot fully meet the cooling demand of an indirect evaporative cooling unit, the compressor is activated to supplement the cooling. This mode, where cooling is achieved through the compressor system, is called electric cooling mode. In hybrid operating conditions, natural cooling and compressor cooling (also known as mechanical cooling or mechanical supplemental cooling) jointly meet the cooling needs of the indirect evaporative cooling unit.

[0049] Power Usage Effectiveness (PUE) refers to the ratio of energy effectively utilized by a system to the energy actually consumed. Taking a data center as an example, PUE is an indicator for evaluating the energy efficiency of a data center. It is the ratio of all energy consumed by the data center (total energy consumption) to the energy consumed by IT (Information Technology) loads (i.e., equipment). The formula is: PUE = Total Data Center Energy Consumption / IT Equipment Energy Consumption. Total data center energy consumption includes the energy consumption of IT equipment as well as the energy consumption of non-IT equipment such as cooling and power distribution systems. A PUE value greater than 1, and the closer the value is to 1, the less energy is consumed by non-IT equipment, indicating a better energy efficiency level.

[0050] Cooling Load Factor (CLF): Defined as the ratio of power consumption of cooling equipment to power consumption of the load. Taking the data center as an example, CLF is the ratio of power consumption of cooling equipment to power consumption of IT equipment in the data center. The smaller the value, the better the energy efficiency.

[0051] Coefficient of Performance (COP): Also known as the energy efficiency ratio, it is expressed by the formula: COP = Capacity / Power Consumption. It represents the efficiency of energy conversion, where "capacity" can include cooling capacity and / or heating capacity. The higher the COP of a cooling or heating system, the greater its cooling or heating capacity with less power consumption.

[0052] Call For Cooling (CFC): When controlling cooling units (such as air conditioning units), the number of operating compressors is usually increased or decreased (hereinafter referred to as adding or removing compressors) or compressor speed is controlled according to the corresponding cooling demand. Cooling demand can be obtained by PID (Proportion Integral Differential) calculation based on the difference between the set supply air temperature and the actual supply air temperature.

[0053] Figure 1 A schematic diagram of a cooling system to which the cooling unit of the present disclosure can be applied is shown.

[0054] like Figure 1 As shown, the cooling system 10 may include a heat exchange unit 102 and a cooling unit 104. The cooling system 10 may be, for example, the indirect evaporative cooling unit described above; in this case, the cooling system 10 may also be referred to as an indirect cooling system. The indirect evaporative cooling unit is one of the large modular air conditioning chiller units that can be used in data centers.

[0055] The heat exchange unit 102 can be used to cool the airflow in the internal circulation air supply channel 1082 using the external circulation airflow, thereby achieving natural cooling of the primary side return air. The heat exchange unit 102 can be, for example, an air-to-air heat exchange core, and the internal circulation air supply channel 1082 can be a channel that allows the primary side return air to circulate and generate primary side air supply. When the ambient temperature rises, causing the natural cooling mode to be unable to fully meet the cooling demand of the indirect evaporative cooling unit, the cooling unit 104 can be turned on to supplement part of the cooling. In this mode, natural cooling and the compressor cooling in the cooling unit 104 jointly undertake the cooling demand of the cooling system 10. The cooling unit 104 may include an evaporator 1042, a compressor 1044, a condenser 1046, an electronic expansion valve 1047, and other devices. When the compressor 1044 is turned on, it compresses the refrigerant flowing through it, producing high-pressure refrigerant gas (HPS). This high-pressure refrigerant then flows through the condenser 1046 and becomes high-pressure liquid refrigerant. After passing through the electronic expansion valve 1047, the high-pressure liquid refrigerant becomes low-pressure liquid refrigerant. The low-pressure refrigerant gas (LPS) that evaporates in the evaporator 1042 cools the air flowing out of the heat exchange unit 102. The LPS then flows back into the compressor 1044 for circulation. The connection arrangement between the devices can be referenced. Figure 1 .

[0056] The cooling system 10 may also include a primary-side fan 1085 and a secondary-side fan 1086. The primary-side return air flows through the heat exchange unit 102 for natural cooling, and then flows through the internal circulation air supply channel 1082 for further cooling via the evaporator 1042 to meet the required air temperature. The primary-side fan 1085 then generates primary-side supply air, which is delivered to applications requiring cooling, such as data centers. The secondary-side intake air (e.g., fresh air, natural air) flows through the heat exchange unit 102, absorbing heat from the primary-side return air and becoming warmer. It then flows through the condenser 1046, absorbing heat from the condenser 1046 and becoming warmer. Finally, the secondary-side fan 1086 generates secondary-side exhaust air, forming an external circulation airflow.

[0057] The cooling system 10 may also include a secondary side spray system 106, which may include a water supply pipe 1062 and a drain pipe 1064, etc. When the cooling system 10 operates under mixed conditions, if the wet-condition natural cooling mode cannot meet the primary side air supply temperature requirements under the normal operating conditions of the secondary side spray system 106, the compressor 1044 in the cooling unit 104 is activated for cooling, and the primary side air is further cooled through the evaporator 1042, while the heat is discharged to the secondary side air through the condenser 1046. During this process, the secondary side fan 1086 is controlled and adjusted according to the condensing pressure, and the control method can be PID speed regulation. If the secondary side spray system 106 cannot operate normally, the heat exchange unit 102 operates in the dry-condition natural cooling mode, which usually cannot meet the primary side air supply temperature requirements. Therefore, the compressor 1044 in the cooling unit 104 is activated for cooling, and the primary side air is further cooled through the evaporator 1042, while the heat is discharged to the secondary side air through the condenser 1046. During this process, the secondary side fan 1086 is controlled and adjusted according to the condensing pressure, and the control method can be PID to adjust the speed.

[0058] It should be understood that Figure 1 The number of evaporators, compressors, and condensers shown is merely illustrative. Any number of evaporators, compressors, and condensers can be used depending on the implementation requirements.

[0059] As mentioned above, data centers, server rooms, and similar environments generate significant heat, resulting in substantial cooling demands. When using a cooling system 10, such as an indirect evaporative cooling unit, for cooling, the required supplemental cooling power is also substantial, typically exceeding 200kW. Therefore, mechanical refrigeration may be divided into several independent subsystems, such as two, four, or six subsystems, each capable of meeting half, a quarter, or a sixth of the cooling demand. In related technologies, for mechanical refrigeration systems divided into several independent subsystems, the evaporator and compressor are typically arranged one-to-one, independently, with the evaporators of each subsystem sequentially arranged to fill the entire internal circulation airflow channel. The evaporators of the compressor system can be arranged individually, with one compressor and one evaporator's heat exchange pipes in fluid communication. The heat exchange pipes of each evaporator are sequentially arranged to fill the entire internal circulation cross-section of the internal circulation airflow channel. During the sequential startup of each compressor, the airflow area of ​​the corresponding evaporator's heat exchange pipe can occupy a portion of the internal circulation cross-section.

[0060] Figure 2 A schematic diagram of the structure of a cooling unit according to an embodiment of the present disclosure is shown. Figure 2 A cooling unit for mechanical refrigeration, divided into two subsystems, is shown. For example... Figure 2As shown, the cooling unit may include a first subsystem 2042 and a second subsystem 2044. The first subsystem 2042 may include a first evaporator 20422, a first compressor 20424, and a first condenser 20426 in fluid communication. The second subsystem 2044 may include a second evaporator 20442, a second compressor 20444, and a second condenser 20446 in fluid communication. Both the first evaporator 20422 and the second evaporator 20442 are designed as serpentine pipes, arranged sequentially to fill the entire internal circulation air supply channel 202. For example, they may be arranged side-by-side on an internal circulation section 2022 of the internal circulation air supply channel 202, or they may be arranged along the air supply direction in the internal circulation air supply channel 202. Figure 2 (The middle arrow points to) The arrangement is staggered front and back.

[0061] In actual operation, mechanical cooling supplementation is typically not 100% loaded; that is, not all subsystem compressors are activated when the mechanical cooling supplementation system is turned on. The loading ratio is calculated based on changes in ambient temperature and server room load (primary side supply air temperature). For example, the loading ratio is usually in the range of 10% to 75%. The number of compressors in the subsystems that are activated can be controlled according to the loading ratio. Figure 2 Taking a cooling unit consisting of two subsystems as an example, when the load ratio is less than 50%, only one compressor system needs to be started. The corresponding evaporator-covered frontal area (the area of ​​the evaporator receiving the air from the heat exchange unit is called the "frontal area", and the area of ​​the evaporator cooling the air from the heat exchange unit and then supplying (cold) air is called the "supply area". The frontal area is actually equal to the supply area) is 1 / 2 of the internal circulation section 2022.

[0062] Figure 3 A schematic diagram of the structure of a cooling unit according to an embodiment of this disclosure is shown. Figure 3 The cooling unit 30 shown includes two compressor subsystems, which can be applied, for example, to the cooling system 10 described above, for cooling the airflow within the internal circulation air supply channel 202.

[0063] The cooling unit 30 may include a first evaporator 302, a first compressor 304 and a first condenser 310 in fluid communication, and a second evaporator 306, a second compressor 308 and a second condenser 312 in fluid communication.

[0064] The first evaporator 302 may include multiple first heat exchange pipes 3022, which may be arranged in parallel within the internal circulation air supply channel 202. The multiple first heat exchange pipes 3022 are used to cool the air flow flowing through the first evaporator 302 in the internal circulation air supply channel 202 by utilizing the first refrigerant flow circulating in the first heat exchange pipes 3022.

[0065] In some embodiments, the parallel arrangement can be a transverse parallel arrangement in the inner circulation section 2022, a vertical parallel arrangement in the inner circulation section 2022, or a staggered parallel arrangement along the air supply direction. Figure 3 The embodiment is illustrated by arranging multiple first heat exchange pipes 3022 horizontally side by side in the internal circulation air supply channel 202, but this disclosure is not limited to this.

[0066] Multiple first heat exchange pipes 3022 can be connected sideways. The multiple connected first heat exchange pipes 3022 have at least one inlet and at least one outlet. The liquid first refrigerant flow generated by the condensation of the first condenser 310 flows into the multiple first heat exchange pipes 3022 through the inlet. The low-pressure refrigerant gas obtained by evaporating the first refrigerant flow in the multiple first heat exchange pipes 3022 flows into the first compressor 304 through the outlet for compression.

[0067] The first compressor 304 is used to compress the first refrigerant stream flowing through it, generating a high-pressure refrigerant gas. This high-pressure refrigerant gas flows through the first condenser 310 and becomes a high-pressure liquid first refrigerant stream. The liquid first refrigerant stream passes through an electronic expansion valve or capillary tube (not shown in the figure) and becomes a low-pressure liquid first refrigerant stream. It then flows into the multiple first heat exchange pipes 3022 of the first evaporator 302 and evaporates into a low-pressure refrigerant gas. This low-pressure refrigerant gas flows back into the first compressor 304 for compression, forming a cycle of the first refrigerant stream.

[0068] The first condenser 310 and the second condenser 312 can be arranged side by side.

[0069] The second evaporator 306 may include multiple second heat exchange pipes 3062, which are arranged in parallel within the internal circulation air supply channel 202. The multiple second heat exchange pipes 3062 are used to cool the air flow flowing through the second evaporator 306 in the internal circulation air supply channel 202 by utilizing the second refrigerant flow circulating in the second heat exchange pipes 3062.

[0070] Multiple second heat exchange pipelines 3062 and multiple first heat exchange pipelines 3022 are arranged in parallel at intervals.

[0071] In some embodiments, such as Figure 3 As shown, multiple second heat exchange pipes 3062 can be arranged side by side with multiple first heat exchange pipes 3022 on an internal circulation section 2022 within the internal circulation air supply channel 202.

[0072] In other embodiments, multiple second heat exchange pipes 3062 may be arranged side-by-side with multiple first heat exchange pipes 3022 on two internal circulation sections within the internal circulation air supply channel 202. That is, from the perspective of the air supply direction, the arrangement of the multiple second heat exchange pipes 3062 and the multiple first heat exchange pipes 3022 is as follows: Figure 3 As shown, but from a perspective perpendicular to the air supply direction, multiple second heat exchange pipes 3062 are on one inner circulation section, and multiple first heat exchange pipes 3022 are on another inner circulation section 2024. The two inner circulation sections are staggered along the air supply direction.

[0073] Multiple second heat exchange pipes 3062 can be connected sideways. The multiple connected second heat exchange pipes 3062 have at least one inlet and at least one outlet. The liquid second refrigerant flow generated by the condensation of the second condenser 312 flows into the multiple second heat exchange pipes 3062 through the inlet. The low-pressure refrigerant gas obtained by evaporating the second refrigerant flow in the multiple second heat exchange pipes 3062 flows into the second compressor 308 through the outlet for compression.

[0074] The second compressor 308 is used to compress the second refrigerant stream flowing through it, generating a high-pressure refrigerant gas. This high-pressure refrigerant gas flows through the second condenser 312 and becomes a liquid second refrigerant stream. The liquid second refrigerant stream passes through an electronic expansion valve or capillary tube (not shown in the figure) and becomes a low-pressure liquid second refrigerant stream. It then flows into the multiple second heat exchange pipes 3062 of the second evaporator 306 and evaporates into a low-pressure refrigerant gas. This low-pressure refrigerant gas flows back into the second compressor 308 for compression, forming a cycle of the second refrigerant stream.

[0075] Figure 2 In the related art shown, the first evaporator 20422 and the second evaporator 20442 are arranged independently. When only one compressor system is started, the corresponding evaporator covers half of the airflow area of ​​the inner circulation cross-section 2022. According to the cooling unit provided in this embodiment, multiple first heat exchange pipes of the first evaporator and multiple second heat exchange pipes of the second evaporator are arranged side-by-side and spaced apart in the inner circulation air supply channel. Regardless of whether only the first compressor or only the second compressor is turned on, the airflow area covered by the first evaporator or the second evaporator is the entire inner circulation cross-section, i.e., equal to... Figure 2 Compared to the corresponding windward area, it doubles the size, improving the uniformity of air delivery. Therefore, it is not necessary to provide a lower evaporation temperature or a larger air volume when starting each compressor to achieve the same cooling capacity to meet the cooling demand. This improves the energy efficiency of the compressor cooling system. In data center applications, it can improve the operating efficiency of the data center and save power consumption.

[0076] Figure 4A schematic diagram of another cooling unit in an embodiment of this disclosure is shown. For example... Figure 4 As shown, the cooling unit 40 may include a first evaporator 402, a first compressor 404 and a first condenser 410 in fluid communication, and a second evaporator 406, a second compressor 408 and a second condenser 412 in fluid communication. Figure 4 and Figure 3 The difference lies in that the multiple first heat exchange pipes of the first evaporator are arranged in two groups, and the multiple first heat exchange pipes of the second evaporator are arranged in two groups.

[0077] like Figure 4 As shown, the internal circulation cross-section 420 of the internal circulation air supply channel can be divided into a first region 422 and a second region 424. Multiple first heat exchange pipes can be divided into a first group 4022 and a second group 4024. The first heat exchange pipes 40222 in the first group are arranged side-by-side in the first region 422, and the first heat exchange pipes 40242 in the second group are arranged side-by-side in the second region 424. The first heat exchange pipes 40222 in the first group and 40242 in the second group fill the internal circulation cross-section 420, so that the sum of the air supply area of ​​the first heat exchange pipes 40222 in the first group and the air supply area of ​​the first heat exchange pipes 40242 in the second group is not less than the total area of ​​the internal circulation cross-section 420.

[0078] In some embodiments, such as Figure 4 As shown, the first heat exchange pipe 40222 in the first group and the first heat exchange pipe 40242 in the second group can both be arranged parallel to the inner circulation section 420. In this case, the air supply area of ​​the first heat exchange pipe 40222 in the first group is equal to the area of ​​the first region 422, and the air supply area of ​​the first heat exchange pipe 40242 in the second group is equal to the area of ​​the second region 424. That is, the sum of the air supply area of ​​the first heat exchange pipe 40222 in the first group and the air supply area of ​​the first heat exchange pipe 40242 in the second group is equal to the total area of ​​the inner circulation section 420.

[0079] In other embodiments, Figure 5 Based on Figure 4 A schematic diagram of the heat exchange piping arrangement for a cooling unit is shown. Figure 5 As shown, in the first group, the first heat exchange pipe 50222 is on the first heat exchange surface 512, and in the second group, the first heat exchange pipe 50242 is on the second heat exchange surface 514. The first heat exchange surface 512 and the second heat exchange surface 514 form a first angle 532. In this case, with Figure 4 In contrast, if the length and width of the inner circulation section 520 and the inner circulation section 420 are equal, then the transverse length of each first heat exchange pipe 50222 is greater than that of the second circulation section 420. Figure 4In the first heat exchange pipe 40222, the sum of the area of ​​the first heat exchange surface 512 and the area of ​​the second heat exchange surface 514 is the sum of the air supply area of ​​the first heat exchange pipe 50222 in the first group and the air supply area of ​​the first heat exchange pipe 50242 in the second group. At this time, the sum of the air supply area of ​​the first heat exchange pipe 50222 in the first group and the air supply area of ​​the first heat exchange pipe 50242 in the second group is greater than the total area of ​​the internal circulation section 520.

[0080] Similar to the first heat exchange pipeline, multiple second heat exchange pipelines can be divided into a third group 4062 and a fourth group 4064. The second heat exchange pipelines 40622 in the third group are arranged side by side in the first area 422, and the second heat exchange pipelines 40642 in the fourth group are arranged side by side in the second area 424. The second heat exchange pipelines 40622 in the third group and the second heat exchange pipelines 40642 in the fourth group fill the inner circulation cross section 420, so that the sum of the air supply area of ​​the second heat exchange pipelines 40622 in the third group and the air supply area of ​​the second heat exchange pipelines 40642 in the fourth group is not less than the total area of ​​the inner circulation cross section 420.

[0081] In some embodiments, such as Figure 4 As shown, the second heat exchange pipe 40622 in the third group and the second heat exchange pipe 40642 in the fourth group can both be arranged parallel to the inner circulation section 420. In this case, the sum of the air supply area of ​​the second heat exchange pipe 40622 in the third group and the air supply area of ​​the second heat exchange pipe 40642 in the fourth group is equal to the total area of ​​the inner circulation section 420.

[0082] In other embodiments, such as Figure 5 As shown, the second heat exchange pipe 50622 in the third group is on the first heat exchange surface 512, and the second heat exchange pipe 50642 in the fourth group is on the second heat exchange surface 514. The first heat exchange surface 512 and the second heat exchange surface 514 form a first angle 532. In this case, the sum of the air supply area of ​​the second heat exchange pipe 50622 in the third group and the air supply area of ​​the second heat exchange pipe 50642 in the fourth group is greater than the total area of ​​the internal circulation cross section 520.

[0083] In this arrangement, the second heat exchange pipe 40622 in the third group is arranged in parallel with the first heat exchange pipe 40222 in the first group, with spacing between them; the second heat exchange pipe 40642 in the fourth group is arranged in parallel with the first heat exchange pipe 40242 in the second group, with spacing between them. For a detailed description of the parallel-spacing arrangement, please refer to... Figure 3 .

[0084] According to the cooling unit provided in this embodiment, by arranging the two sets of evaporators corresponding to the two compressors side-by-side and spaced apart in the internal circulation air supply channel, regardless of whether only the first compressor or only the second compressor is turned on, the air-facing area covered by the first or second evaporator is the entire internal circulation cross-section, thus improving the uniformity of air supply. Setting the two heat exchange surfaces where the heat exchange pipes of the two sets of evaporators are located at a certain angle further increases the air supply area, thereby further improving the energy efficiency of the compressor refrigeration system.

[0085] Figure 6 Based on Figure 3 A schematic diagram of another cooling unit is shown. (See diagram for example.) Figure 6 As shown, Figure 6 Cooling unit 60 and Figure 3 The difference between the cooling unit 30 shown is that the arrangement of the heat exchange pipes of the first condenser 610 and the second condenser 612 of the cooling unit 60 is different from that of the cooling unit 30.

[0086] like Figure 6 As shown, the cooling unit 60 dissipates heat through the external circulation air outlet channel 602. The first condenser 610 is in fluid communication with the first compressor 304 and the first evaporator 302, and the second condenser 612 is in fluid communication with the second compressor 308 and the second evaporator 306.

[0087] The first condenser 610 may include multiple third heat exchange pipes 6102, which are arranged in parallel in the external circulation air outlet channel 602 to transfer the heat of the first refrigerant flow circulating in the third heat exchange pipes 6102 to the air through the external circulation air outlet channel.

[0088] The second condenser 612 includes multiple fourth heat exchange pipes 6122, which are arranged in parallel within the external circulation air outlet channel 602. These pipes are used to transfer the heat of the second refrigerant flow circulating in the fourth heat exchange pipes 6122 to the air through the external circulation air outlet channel 602.

[0089] Multiple third heat exchange pipes 6102 and multiple fourth heat exchange pipes 6122 are arranged side-by-side with intervals. For a specific implementation method of the parallel and interval arrangement of the multiple third heat exchange pipes 6102 and multiple fourth heat exchange pipes 6122 at the external circulation cross-section 6022, please refer to... Figure 3 A specific embodiment of the parallel and spaced arrangement of the first heat exchange pipe 3022 of the first evaporator 302 and the second heat exchange pipe 3062 of the second evaporator 306.

[0090] According to the cooling unit provided in the embodiments of this disclosure, the heat exchange pipelines of the evaporator and condenser are arranged in parallel and spaced apart, so that the heat exchange area of ​​the entire evaporator and condenser can be fully utilized when only one compressor is turned on (partial load), thereby further improving the system energy efficiency.

[0091] Figure 7 A schematic diagram of another cooling unit in an embodiment of this disclosure is shown. Figure 7 Let's take a refrigeration system consisting of four compressors as an example. Figure 7 As shown, the cooling unit may include a first subsystem 7042, a second subsystem 7044, a third subsystem 7046, and a fourth subsystem 7048. The first subsystem 7042 may include a first evaporator 70422, a first compressor 70424, and a first condenser 70426 in fluid communication. The second subsystem 7044 may include a second evaporator 70442, a second compressor 70444, and a second condenser 70446 in fluid communication. The third subsystem 7046 may include a third evaporator 70462, a third compressor 70464, and a third condenser 70466 in fluid communication. The fourth subsystem 7048 may include a fourth evaporator 70482, a fourth compressor 70484, and a fourth condenser 70486 in fluid communication.

[0092] Among them, the first evaporator 70422, the second evaporator 70442, the third evaporator 70462 and the fourth evaporator 70482 are all designed as serpentine pipes, which are arranged in sequence to fill the entire internal circulation air supply channel 720. For example, they can be arranged side by side on one internal circulation section of the internal circulation air supply channel 720, or they can be arranged alternately back and forth along the air supply direction in the internal circulation air supply channel 720.

[0093] The following examples illustrate Figure 7 Parameter configurations of each subsystem during operation of the four compressor systems:

[0094] Condenser: Condensation temperature 49.1℃, discharge pressure 30.3 bar

[0095] Exhaust valve: Exhaust superheat 18.5℃, electronic valve expansion opening 74%.

[0096] Compressor: Power 12.4kW, controlled speed 90rpm (revolutions per second), output speed 90rpm

[0097] Evaporator: Evaporation superheat 5.8℃, evaporation pressure 12.0 bar

[0098] Evaporation temperature: 16.1℃.

[0099] by Figure 7Taking a four-compressor refrigeration system as an example, when the load ratio is ≤25%, only one compressor system needs to be started, and the corresponding evaporator covers 1 / 4 of the internal circulation cross-section; when 25% < load ratio ≤50%, two compressor systems need to be started, and the corresponding evaporator covers 1 / 2 of the internal circulation cross-section; when 50% < load ratio ≤75%, three compressor systems need to be started, and the corresponding evaporator covers 3 / 4 of the internal circulation cross-section.

[0100] Figure 8 A schematic diagram of the structure of another cooling unit in an embodiment of this disclosure is shown. Figure 8 The cooling unit 80 shown is Figure 4 The difference in the cooling unit 40 shown is that, Figure 8 The cooling unit 80 shown includes four compressor subsystems, which can be applied, for example, to the cooling system 10 described above, for cooling the airflow within the internal circulation air supply channel 202.

[0101] The internal circulation section 880 of the cooling internal circulation air supply channel where the cooling unit 80 is located may include a first region 882 and a second region 884. The cooling unit 80 may include a first evaporator 802, a first compressor 804 and a first condenser 818 in fluid communication; a second evaporator 806, a second compressor 808 and a second condenser 820 in fluid communication; a third evaporator 810, a third compressor 812 and a third condenser 822 in fluid communication; and a fourth evaporator 814, a fourth compressor 816 and a fourth condenser 824 in fluid communication.

[0102] The first evaporator 802 may include multiple first heat exchange pipes 8022, which are arranged in parallel in the first region 882. The multiple first heat exchange pipes 8022 are used to cool the air flow flowing through the first evaporator 802 in the internal circulation air supply channel by utilizing the first refrigerant flow circulating in the first heat exchange pipes 8022.

[0103] The second evaporator 806 may include multiple second heat exchange pipes 8062, which are arranged in parallel in the first region 882. The multiple second heat exchange pipes 8062 are used to cool the air flow flowing through the second evaporator 806 in the internal circulation air supply channel by utilizing the second refrigerant flow circulating in the second heat exchange pipes 8062.

[0104] Among them, multiple second heat exchange pipes 8062 and multiple first heat exchange pipes 8022 are arranged in parallel and at intervals. The specific implementation method of the parallel and at intervals arrangement can be referred to Figure 3 .

[0105] The third evaporator 810 may include multiple third heat exchange pipes 8102, which are arranged in parallel in the second region 884. The multiple third heat exchange pipes 8102 are used to cool the airflow flowing through the third evaporator 810 in the internal circulation air supply channel by utilizing the third refrigerant flow circulating in the third heat exchange pipes 8102.

[0106] The fourth evaporator 814 may include multiple fourth heat exchange pipes 8142, which are arranged in parallel in the second region 884. The multiple fourth heat exchange pipes 8142 are used to cool the air flow flowing through the fourth evaporator 814 in the internal circulation air supply channel by utilizing the fourth refrigerant flow circulating in the fourth heat exchange pipes 8142.

[0107] Among them, multiple fourth heat exchange pipes 8142 and multiple third heat exchange pipes 8102 are arranged in parallel and at intervals. The specific implementation method of the parallel and at intervals arrangement can be referred to Figure 3 .

[0108] According to the cooling unit provided in the embodiments of this disclosure, by arranging the four evaporators corresponding to the four compressors in parallel and spaced apart in two areas within the internal circulation air supply channel, the air-facing area of ​​the compressor cooling one subsystem reaches 50% of the internal circulation cross-section, and the air-facing area of ​​the dual system reaches 100% of the internal circulation cross-section. This avoids uneven air supply temperature distribution when only one subsystem compressor is turned on, thereby improving the system's working efficiency.

[0109] Figure 9 Based on Figure 8 A schematic diagram of the heat exchange piping arrangement for a cooling unit is shown. Figure 9 As shown, multiple first heat exchange pipes 9022 and multiple second heat exchange pipes 9042 are on a first heat exchange surface 912, and multiple third heat exchange pipes 9062 and multiple fourth heat exchange pipes 9082 are on a second heat exchange surface 914. The first heat exchange surface 912 and the second heat exchange surface 914 form a first angle 932, so that the sum of the air supply area of ​​the multiple first heat exchange pipes 9022 and the air supply area of ​​the multiple second heat exchange pipes 9042 is greater than the total area of ​​the inner circulation cross section 920 corresponding to the inner circulation channel, and the sum of the air supply area of ​​the multiple third heat exchange pipes 9062 and the air supply area of ​​the multiple fourth heat exchange pipes 9082 is greater than the total area of ​​the inner circulation cross section 920.

[0110] According to the cooling unit provided in the embodiments of this disclosure, the two heat exchange surfaces where the heat exchange pipes of the four evaporators are located are set at a certain angle, which increases the air supply area and thus improves the energy efficiency of the compressor refrigeration system.

[0111] Figure 10 A schematic diagram of the structure of another cooling unit according to an embodiment of this disclosure is shown. For example... Figure 10The cooling unit 100 shown may include a first evaporator 1002, a first compressor 1004 and a first condenser 1018 in fluid communication; a second evaporator 1006, a second compressor 1008 and a second condenser 1020 in fluid communication; a third evaporator 1010, a third compressor 1012 and a third condenser 1022 in fluid communication; and a fourth evaporator 1014, a fourth compressor 1016 and a fourth condenser 1024 in fluid communication. Figure 10 and Figure 8 The difference lies in that the multiple heat exchange pipes of each evaporator are arranged in two groups.

[0112] like Figure 10 As shown, the first region 1081 of the internal circulation cross-section 1080 of the internal circulation air supply channel can be divided into a first sub-region 10812 and a second sub-region 10814. The second region 1084 is further divided into a third sub-region 10842 and a fourth sub-region 10844. Multiple first heat exchange pipes can be divided into a first group and a second group; multiple second heat exchange pipes can be divided into a third group and a fourth group; multiple third heat exchange pipes can be divided into a fifth group and a sixth group; and multiple fourth heat exchange pipes can be divided into a seventh group and an eighth group. The first heat exchanger pipe 10022 in the first group and the second heat exchanger pipe 10062 in the third group are arranged side-by-side with intervals in the first sub-region 10812; the first heat exchanger pipe 10024 in the second group and the second heat exchanger pipe 10064 in the fourth group are arranged side-by-side with intervals in the second sub-region 10814; the third heat exchanger pipe 10102 in the fifth group and the fourth heat exchanger pipe 10142 in the seventh group are arranged side-by-side with intervals in the third sub-region 10842; the third heat exchanger pipe 10104 in the sixth group and the fourth heat exchanger pipe 10144 in the eighth group are arranged side-by-side with intervals in the fourth sub-region 10844, so that the first heat exchanger pipe 10022 in the first group is arranged side-by-side with intervals in the fourth sub-region 10844. The sum of the air supply area of ​​heat exchange pipe 10022, the air supply area of ​​the first heat exchange pipe 10024 in the second group, the air supply area of ​​the third heat exchange pipe 10102 in the fifth group, and the air supply area of ​​the third heat exchange pipe 10104 in the sixth group is not less than the total area of ​​the inner circulation cross section 1080, and the sum of the air supply area of ​​the second heat exchange pipe 10062 in the third group, the air supply area of ​​the second heat exchange pipe 10064 in the fourth group, the air supply area of ​​the fourth heat exchange pipe 10142 in the seventh group, and the air supply area of ​​the fourth heat exchange pipe 10144 in the eighth group is not less than the total area of ​​the inner circulation cross section 1080 corresponding to the inner circulation channel.

[0113] In some embodiments, the heat exchange piping of each group can be arranged parallel to the inner circulation cross-section 1080, such as... Figure 10As shown, in this case, the sum of the air supply area of ​​the first heat exchange pipe 10022 in the first group, the air supply area of ​​the first heat exchange pipe 10024 in the second group, the air supply area of ​​the third heat exchange pipe 10102 in the fifth group, and the air supply area of ​​the third heat exchange pipe 10104 in the sixth group is equal to the total area of ​​the inner circulation cross section 1080, and the sum of the air supply area of ​​the second heat exchange pipe 10062 in the third group, the air supply area of ​​the second heat exchange pipe 10064 in the fourth group, the air supply area of ​​the fourth heat exchange pipe 10142 in the seventh group, and the air supply area of ​​the fourth heat exchange pipe 10144 in the eighth group is equal to the total area of ​​the inner circulation cross section 1080.

[0114] In other embodiments, the heat exchange pipes in different sub-regions can be arranged at a certain angle. In this case, the sum of the air supply area of ​​the first heat exchange pipe 10022 in the first group, the air supply area of ​​the first heat exchange pipe 10024 in the second group, the air supply area of ​​the third heat exchange pipe 10102 in the fifth group, and the air supply area of ​​the third heat exchange pipe 10104 in the sixth group is greater than the total area of ​​the inner circulation cross-section 1080. Furthermore, the sum of the air supply areas of the second heat exchange pipe 10062 in the third group, the second heat exchange pipe 10064 in the fourth group, the fourth heat exchange pipe 10142 in the seventh group, and the fourth heat exchange pipe 10144 in the eighth group is greater than the total area of ​​the inner circulation cross-section 1080. For specific implementation details, please refer to [reference needed]. Figure 11 .

[0115] According to the embodiments of this disclosure, a cooling unit comprising four compressor systems is provided, each subsystem providing one-quarter of the cooling demand. In the evaporator arrangement, the first heat exchange pipe in the first group and the second heat exchange pipe in the third group are arranged in the first sub-region of the inner circulation cross-section; the first heat exchange pipe in the second group and the second heat exchange pipe in the fourth group are arranged in the second sub-region of the inner circulation cross-section; the third heat exchange pipe in the fifth group and the fourth heat exchange pipe in the seventh group are arranged in the third sub-region of the inner circulation cross-section; and the third heat exchange pipe in the sixth group and the fourth heat exchange pipe in the eighth group are arranged in the fourth sub-region of the inner circulation cross-section. This ensures that when only one compressor is activated, the corresponding evaporator's airflow area reaches 50% of the inner circulation cross-section. When another compressor, whose evaporator is not in the same sub-region, is activated, the corresponding evaporator's airflow area reaches 100% of the inner circulation cross-section. This allows for a more uniform distribution of the supply air temperature, and the increased cross-sectional area helps to increase the evaporation temperature, thereby improving the energy efficiency of the compressor system and reducing the operating CLF of the indirect evaporator unit, thus reducing the operating electricity costs of the computer room.

[0116] Figure 11 Based on Figure 10 A schematic diagram of the heat exchange piping arrangement for a cooling unit is shown. Figure 11 As shown, the first heat exchange pipe 11022 in the first group and the second heat exchange pipe 11062 in the third group are on the third heat exchange surface 1122, and the first heat exchange pipe 11024 in the second group and the second heat exchange pipe 11064 in the fourth group are on the fourth heat exchange surface 1124.

[0117] The third heat exchange pipe 11102 in the fifth group and the fourth heat exchange pipe 11142 in the seventh group are on the fifth heat exchange surface 1126, and the third heat exchange pipe 11104 in the sixth group and the fourth heat exchange pipe 11144 in the eighth group are on the sixth heat exchange surface 1128.

[0118] The third heat exchange surface 1122 and the fourth heat exchange surface 1124 form a second angle 1132, the fourth heat exchange surface 1124 and the fifth heat exchange surface 1126 form a third angle 1134, and the fifth heat exchange surface 1126 and the sixth heat exchange surface 1128 form a fourth angle 1136, so that the third heat exchange surface 1122, the fourth heat exchange surface 1124, the fifth heat exchange surface 1126 and the sixth heat exchange surface 1128 are arranged in a zigzag shape. Therefore, the sum of the air supply area of ​​the first heat exchange pipe 11022 in the first group, the air supply area of ​​the first heat exchange pipe 11024 in the second group, the air supply area of ​​the third heat exchange pipe 11102 in the fifth group, and the air supply area of ​​the third heat exchange pipe 11104 in the sixth group is greater than the total area of ​​the inner circulation cross section 1180, and the sum of the air supply area of ​​the second heat exchange pipe 11062 in the third group, the air supply area of ​​the second heat exchange pipe 11064 in the fourth group, the air supply area of ​​the fourth heat exchange pipe 11142 in the seventh group, and the air supply area of ​​the fourth heat exchange pipe 11144 in the eighth group is greater than the total area of ​​the inner circulation cross section 1180.

[0119] According to the cooling unit provided in this embodiment, by arranging eight sets of evaporators corresponding to four compressors side-by-side and spaced apart in the internal circulation air supply channel, when only one compressor is turned on, the corresponding evaporator covers 50% of the airflow area of ​​the internal circulation cross-section. After turning on a different set of compressors, the corresponding evaporator covers 100% of the airflow area of ​​the internal circulation cross-section, thus improving the uniformity of air supply. Arranging the four heat exchange surfaces of the eight sets of parallel and spaced heat exchange pipes in a zigzag shape further increases the air supply area, thereby improving the energy efficiency of the compressor refrigeration system.

[0120] The relevant technology employs PID control based on the primary side supply air temperature of the unit or the indoor cold aisle temperature (e.g., average indoor cold aisle temperature, maximum indoor cold aisle temperature, or minimum indoor cold aisle temperature, etc.). (Users can select one of these temperature parameters as the input for PID control.) Simultaneously, it uses compressor speed control based on the upper limit of the compressor's operating frequency (speed and frequency have a one-to-one correspondence). That is, after starting the first compressor, its speed is increased until it reaches its rated speed (e.g., 90Hz, 95Hz, or 100Hz, etc.). If the cooling capacity of the first compressor is insufficient to meet the cooling demand after running at its rated speed for a period of time, a second compressor is started to supplement the cooling capacity, and its speed is also increased until it reaches its rated speed. If the cooling capacity is still insufficient after running at the second compressor's rated speed for a period of time, a third compressor is started, and so on.

[0121] The compressor's factory settings typically include inherent starting logic. According to this logic, after the compressor starts and its speed increases to a certain inherent speed, it will, for oil return protection purposes, follow the inherent speed (e.g., ...). Figure 13 The rotational speed corresponding to point d in the middle) runs for a relatively long period of time (e.g. Figure 13 The duration of segment B (usually around 3 minutes) allows the lubricating oil to fully distribute throughout the compressor component circuit before gradually increasing the speed to the rated speed. This prevents the compressor from burning out due to insufficient lubrication during high-speed operation. The process of gradually increasing the speed to the rated speed from the start of the compressor to the end of the oil return cycle is typically called the soft start process.

[0122] This inherent startup logic leads to the following drawbacks in the control method of adding or removing compressors based on the upper limit of the compressor's operating frequency. First, when starting a second compressor, it also undergoes a soft-start process. That is, after increasing its speed to its inherent speed, it needs to operate at that speed for a considerable period before increasing to the rated speed. During this period, the supply air temperature may fluctuate significantly. In fact, according to third-party test and acceptance data from the field, the supply air temperature fluctuation is above ±2℃ when adding or removing compressors. Second, while using supply air temperature as the input parameter for PID control of compressor speed can achieve relatively high control accuracy when the compressor is running stably, the feedback-based PID control method cannot avoid the relatively long soft-start process when adding or removing compressors. This results in a delayed response and a tendency to overshoot, leading to low temperature control accuracy when adding or removing compressors. Third, tests have shown that the power consumption of two low-speed compressors is less than that of one high-speed compressor. Therefore, the control method of waiting until the compressor reaches its rated speed before adding more compressors is not energy-efficient.

[0123] Figure 12This is a flowchart illustrating a cooling control method according to an exemplary embodiment. Figure 12 The method shown can be applied, for example, to... Figure 3 ,or Figure 4 ,or Figure 6 The cooling unit shown.

[0124] refer to Figure 12 The method 120 provided in this embodiment may include the following S1202 to S1222.

[0125] In S1202, the first compressor is started.

[0126] In some embodiments, all compressors are variable frequency compressors equipped with frequency converters, meaning that the compressor speed can be controlled and adjusted by the frequency converter.

[0127] In some embodiments, before starting the first compressor, it is possible to select which compressor to start. For example, the running time of the first compressor and the running time of the second compressor can be obtained separately. If the running time of the first compressor is not greater than the running time of the second compressor, it is determined that the first compressor should be started. This can balance the usage time of multiple compressors and extend the service life of each compressor.

[0128] In S1204, the first target rotational speed is obtained.

[0129] In some embodiments, for the "target speed" (including the first target speed, the second target speed, the third target speed, the fourth target speed, etc.) involved in the embodiments of this disclosure, a corresponding target speed can be set for the compressor, and its frequency converter can increase the speed at a certain acceleration according to the target speed.

[0130] In some embodiments, the first target speed is the maximum speed set for the compressor when only one compressor (the first compressor) is turned on. The first target speed of the first compressor can be set to about twice the minimum speed of the first compressor (e.g., 30 rpm), such as 65 rpm, 70 rpm, or 75 rpm, etc.

[0131] In S1206, the first compressor is controlled to increase its speed with a first acceleration.

[0132] In some embodiments, after a target speed is set for the compressor that is turned on, its frequency converter can increase the speed at a certain acceleration according to the target speed. The compressor may have a certain speed acceleration at different stages according to its model, and parameters such as minimum speed and rated speed are all set by default at the factory.

[0133] For example, Figure 13As an example of the relationship between compressor speed variation and start-up time, refer to Figure 13 If the speed corresponding to segment D is the rated speed (e.g., 90 rpm), and the speed corresponding to point d is the return oil speed (e.g., 50 rpm), then the first target speed is in segment C. The first acceleration can include the acceleration from point 0 to point b, the acceleration from point b to point c (i.e., the acceleration during the asynchronous drive phase), the acceleration of segment A, the acceleration of segment B (which is 0), and the acceleration of segment C.

[0134] In S1208, the current speed of the first compressor is obtained at a first frequency.

[0135] In some embodiments, the current rotational speed of the first compressor can be acquired at a first frequency during the control process. The first frequency may be, for example, 0.5s, 1s, 1.5s, etc.

[0136] In S1210, a second target speed is obtained, which is based on the first target speed, the first cooling demand corresponding to the cooling unit, and the oil return speed of the second compressor.

[0137] In some embodiments, after the first compressor operates at a first target speed for a certain period of time, it may be unable to meet the full cooling demand (i.e., the first cooling demand) and instead reaches the second cooling demand (the second cooling demand is lower than the full cooling demand, for example, 50% of the full cooling demand in a two-compressor system). In such cases, it is necessary to prepare to start the second compressor. A target speed, i.e., the second target speed, can be designed for the compressor that is about to be started.

[0138] In some embodiments, based on the first target speed and the first cooling demand corresponding to the cooling unit, and following the principle that the cooling capacity of two compressors operating at the second target speed is equivalent to the cooling capacity of one compressor operating at the first target speed (in this embodiment, the example is given that all compressors are of the same model and therefore have the same cooling capacity at the same speed), the second target speed can be calculated. An example of the correspondence between cooling demand and compressor speed can be found in [reference needed]. Figure 16 .

[0139] In some embodiments, the design of the second target speed may take into account the oil return speed of the second compressor, which is the inherent speed of the compressor during a relatively long period of operation for oil return protection purposes in its inherent starting logic (e.g., Figure 13(The rotational speed corresponding to point d in the middle) By setting the second target rotational speed to be less than the oil return speed of the second compressor, the rotational speed of the second compressor can be quickly increased to the second target rotational speed. For example, if the first target rotational speed is 70 rpm, considering the cooling demand and the oil return speed (e.g., 50 rpm), the second target rotational speed can be 34 rpm, 35 rpm, or 36 rpm, etc.

[0140] In S1212, it is determined whether the current speed of the first compressor has reached the first target speed. If the current speed of the first compressor has not reached the first target speed, the process returns to S1208.

[0141] In S1214, if the current speed of the first compressor reaches the first target speed, control the first compressor to increase its speed with the first acceleration is stopped.

[0142] In S1216, the duration for which the current speed of the first compressor is maintained at the first target speed is recorded.

[0143] In S1218, it is determined whether the duration for which the current speed of the first compressor is maintained at the first target speed is greater than or equal to the first duration. If the duration for which the current speed of the first compressor is maintained at the first target speed is less than the first duration, then return to S1216.

[0144] In some embodiments, after the speed of the first compressor increases to the first target speed, it can be set to run stably for a period of time before adding more compressors. This period of time is the settable first duration (also known as the delay time). The first duration can be, for example, 50s, 60s, or 70s, etc.

[0145] In S1220, if the current speed of the first compressor is maintained at a first target speed greater than or equal to a first duration, the first compressor is controlled to reduce its speed to the second target speed with a second acceleration, and the second compressor is controlled to start.

[0146] In some embodiments, refer to Figure 13 The second acceleration can be the acceleration corresponding to segment E, with a maximum of 3 rps / s, for example, it can be 1 rps / s, or 2 rps / s, or 3 rps / s.

[0147] In S1222, the second compressor is controlled to increase its speed to the second target speed with a third acceleration.

[0148] In some embodiments, refer to Figure 13 Since the second target rotational speed is set in segment A (less than the rotational speed corresponding to point d), the third acceleration can include the acceleration from point o to point b, the acceleration from point b to point c (i.e., the acceleration during the asynchronous drive phase), and the acceleration in segment A.

[0149] In some embodiments, when controlling the compressor, the speed of the second compressor can be increased and the speed of the first compressor can be decreased simultaneously, with the control target being the second target speed. For example, refer to... Figure 13 Taking a first target speed of 70 rpm and a second target speed of 35 rpm as an example, for the second compressor that is accelerating, the time from point O to point A is less than 15 seconds, the speed corresponding to point C is less than 20 rpm, and the acceleration in segment A is between 1 rpm / s and 3 rpm / s, for example, it can be 2 rpm. Therefore, the time for the second compressor to increase its speed to the second target speed is within 30 seconds, for example, it can be 10 seconds. For the first compressor that is decelerating, the maximum acceleration in segment E is 3 rpm / s, so the time for it to decrease its speed to the second target speed is also within 30 seconds, and can reach more than ten seconds.

[0150] According to the cooling unit and its corresponding control method provided in the embodiments of this disclosure, by simultaneously matching and controlling the compressor start-up sequence, the air supply temperature distribution of the unit can be more uniform and the unit's energy efficiency can be higher under the partial load with the longest running time.

[0151] The compressor is controlled by adding and controlling its speed according to the cooling demand. The second target speed after adding the compressor is obtained by using the first target speed and the first cooling demand corresponding to the cooling unit. The second target speed is designed to be less than the oil return speed of the second compressor. Feedforward is added during the compressor start-up process. The inherent start-up logic of the compressor start-up process and the energy-saving optimization control strategy of multiple compressors operating under the same cooling capacity are also taken into account. The time to reach the second target speed is shortened while ensuring that the cooling capacity remains basically unchanged during the addition process. Therefore, the control accuracy of the air supply temperature and the energy efficiency of the unit are improved.

[0152] By starting the compressor with the shortest running time each time it is started, the running time of each compressor is balanced, thus achieving the effect of balancing the running time of each compressor within the same unit and extending the service life of the compressor.

[0153] In mixed operating mode, regardless of whether the secondary side spray system is working normally, the cooling control method provided in this embodiment can be used. The number of compressors started and the speed are controlled and adjusted according to the cooling demand, which can improve the air supply temperature control accuracy of the compressor system when adding or removing compressors in mixed mode, and at the same time improve the energy efficiency of the compressor system during operation.

[0154] Figure 13 This is a schematic diagram illustrating the relationship between compressor speed and time according to an exemplary embodiment. Figure 13 This is an example of the speed control settings for one type of compressor.

[0155] like Figure 13As shown, point O (the origin of the time axis) is the time when the compressor starts, at which point the speed is 0. The time corresponding to point A is less than 15 seconds, for example, it could be 12 seconds, 13 seconds, or 14 seconds. The speed corresponding to point B can be 15 rpm. The speed corresponding to point C is less than 20 rpm, for example, it could be 17 rpm, 18 rpm, or 19 rpm, etc. The period from point O to point A is the time period during which the compressor slowly accelerates after starting, and the compressor uses an asynchronous drive motor during this process. Synchronous drive is determined at the time point corresponding to point A. If synchronous drive is determined, a synchronous drive motor is used after point A. The speed corresponding to point d can be 50 rpm.

[0156] The recommended acceleration for segment A is 1 rps / s, with a maximum of 3 rps / s. Segment B corresponds to a duration exceeding 3 minutes. The recommended acceleration for segment C is 1 rps / s, with a maximum of 3 rps / s. Segment D corresponds to the maximum speed, which can be the rated speed (e.g., 90 rps or 100 rps) or a set target speed (e.g., 70 rps or 75 rps).

[0157] The maximum acceleration during frequency reduction in segment E is 3 rpm. Segment F involves frequency reduction followed by acceleration, with a maximum acceleration of 3 rpm. Segment G involves frequency reduction when the device is off, with a maximum acceleration of 10 rpm.

[0158] Figure 14 This is a flowchart illustrating another cooling control method according to an exemplary embodiment. Figure 14 The method shown can be applied, for example, to... Figure 3 ,or Figure 4 ,or Figure 6 The cooling unit shown.

[0159] Figure 14 The method shown is the same as Figure 12 The difference between the methods shown is that, Figure 14 This method is used in the reduction process. (Reference) Figure 14 The method 140 provided in this embodiment may include the following steps S1402 to S1424, and can be executed in... Figure 12 After S1222.

[0160] In S1402, the third target rotational speed is obtained.

[0161] In some embodiments, the third target speed can be the rated speed of the first compressor (or the second compressor) (e.g., the speed corresponding to segment D). For a refrigeration unit with two compressors, after both compressors are turned on, they can be controlled to increase to the rated speed to meet all refrigeration needs.

[0162] In S1404, the first compressor and the second compressor are controlled to increase their speed to the third target speed with a fourth acceleration.

[0163] In some embodiments, refer to Figure 13 The fourth acceleration can be the acceleration corresponding to segment C.

[0164] In S1406, the current cooling demand corresponding to the cooling unit is obtained at a second frequency.

[0165] In some embodiments, the current cooling demand can be calculated based on the primary side supply air temperature or the indoor cold aisle temperature. As the first and second compressors operate at the third target speed, the primary side supply air temperature or the indoor cold aisle temperature gradually decreases, thus reducing the current cooling demand.

[0166] In some embodiments, the current cooling demand can be calculated at a second frequency based on the collected primary side supply air temperature or indoor cold aisle temperature. The second frequency can be between 0.5 and 3 seconds, for example, it can be 0.5 seconds, 1 second, or 1.5 seconds, etc.

[0167] In S1408, the speeds of the first and second compressors are controlled according to the current cooling demand corresponding to the cooling unit.

[0168] In some embodiments, during the operation of the first compressor and the second compressor at the third target speed, the primary side supply air temperature or the indoor cold aisle temperature will gradually decrease, and the current cooling demand will also decrease. The speed of the first compressor and the second compressor can be reduced by PID control.

[0169] In S1410, the current speed of the first compressor and the current speed of the second compressor are obtained at a third frequency.

[0170] In some embodiments, the current rotational speed of the first compressor and the second compressor can be acquired at a third frequency during the control process. The third frequency can be between 0.5 and 3 seconds, for example, it can be 0.5 seconds, 1 second, or 1.5 seconds, etc.

[0171] In S1412, the fourth target speed is obtained, which is based on the current cooling demand of the cooling unit and the first cooling demand.

[0172] In some embodiments, the current cooling demand decreases to a certain level, such as 60% (or 55%, or 65%, etc.) of the first cooling demand, so that after reducing the speed of the first and second compressors to a fourth target speed through PID control, the compressors can be controlled to reduce speed. For example, if the first target speed is 70 rpm, the second target speed is 34 rpm, and the third target speed is 90 rpm, then the fourth target speed can be 40 rpm, 42 rpm, or 45 rpm, etc.

[0173] In S1414, the fifth target speed is obtained, which is based on the fourth target speed and the current cooling demand of the cooling unit.

[0174] In some embodiments, the fifth target speed is the pre-calculated target speed of the remaining compressor after the reduction of the number of compressors. The fifth target speed can be calculated based on the fourth target speed, the current cooling demand corresponding to the cooling unit, and the principle that the cooling capacity of two compressors operating at the fourth target speed is equivalent to the cooling capacity of one compressor operating at the fifth target speed. For example, if the fourth target speed is 42 rpm, the fifth target speed can be obtained as 60 rpm.

[0175] In S1416, it is determined whether the current speed of the first compressor is the fourth target speed and whether the current speed of the second compressor is the fourth target speed. If the current speed of the first compressor is not the fourth target speed and the current speed of the second compressor is not the fourth target speed, then return to S1408.

[0176] In some embodiments, multiple compressors that are simultaneously operating stably are controlled to run at the same speed.

[0177] In S1418, if the current speed of the first compressor is the fourth target speed and the current speed of the second compressor is the fourth target speed, the speeds of the first compressor and the second compressor continue to be controlled according to the current cooling demand corresponding to the cooling unit.

[0178] In S1420, the duration for which the current speed of the first compressor and the current speed of the second compressor remain at the fourth target speed is recorded.

[0179] In S1422, it is determined whether the current speed of the first compressor is maintained at the fourth target speed for a duration greater than or equal to the second duration, and whether the current speed of the second compressor is maintained at the fourth target speed for a duration greater than or equal to the second duration. If the current speed of the first compressor is maintained at the fourth target speed for a duration less than the second duration, and the current speed of the second compressor is maintained at the fourth target speed for a duration less than the second duration, then return to S1420.

[0180] In some embodiments, the first compressor and the second compressor are operated stably at the fourth target speed for a period of time before the compressor is reduced. This period of time is the settable second duration, which can be, for example, 50s, 60s, or 70s, etc.

[0181] In S1424, if the current speed of the first compressor is maintained at the fourth target speed greater than or equal to the second duration, and the current speed of the second compressor is maintained at the fourth target speed greater than or equal to the second duration, then the second compressor is controlled to be shut down, and the first compressor is controlled to increase its speed to the fifth target speed with the fifth acceleration.

[0182] In some embodiments, before shutting down a compressor, it is possible to select which compressor to shut down. The running time of the first compressor and the running time of the second compressor are obtained respectively. If the running time of the first compressor is not greater than the running time of the second compressor, the second compressor is shut down, and the first compressor is controlled to increase its speed to the fifth target speed with a fifth acceleration. This can balance the usage time of multiple compressors and extend the service life of each compressor.

[0183] According to the cooling unit and its corresponding control method provided in the embodiments of this disclosure, the compressor is controlled to reduce its operating time and speed according to the cooling demand, so as to ensure that the cooling capacity remains basically unchanged during the reduction process and improve the control accuracy of the air supply temperature. When reducing the operating time, the compressor with the longest stop time is selected to balance the running time of each compressor, thereby achieving the effect of balancing the running time of each compressor in the same unit and extending the service life of the compressor.

[0184] In related technologies, for a refrigeration unit comprising a four-compressor system, the start-up control of each compressor is as follows: Level 1 start-up condition (starting the first compressor) is electric refrigeration mode start-up (refer to the natural cooling to electric refrigeration switching conditions under each operating mode); Level 2 start-up condition (starting the second compressor while keeping the first compressor running, and so on for Levels 3 and 4) is that the operating frequency of the (already started) compressor is greater than HI2 (HI2 is used to represent the Level 2 start-up frequency; HI2 defaults to 100Hz, adjustable), with a delay time T1 (T1 defaults to 60s, adjustable); Level 3 start-up condition is that the operating frequency is greater than HI3 (HI3 defaults to 90Hz, adjustable), with a delay time T1 (T1 defaults to 60s, adjustable); Level 4 start-up condition is that the operating frequency is greater than HI4 (HI4 defaults to 80Hz, adjustable), with a delay time T1 (T1 defaults to 60s, adjustable).

[0185] The compressor stop control for each level is as follows: Level 4 stop condition is operating frequency less than HO4 (default 50Hz, adjustable), delay time T3 (default 180s, adjustable); Level 3 stop condition is operating frequency less than HO3 (default 60Hz, adjustable), delay time T3 (default 180s, adjustable); Level 2 stop condition is operating frequency less than HO2 (default 70Hz, adjustable), delay time T3 (default 180s, adjustable); Level 1 stop condition is the same as the electric cooling to natural cooling condition (refer to the electric cooling mode to natural cooling condition under each working mode).

[0186] As mentioned above, if the addition, reduction, and speed control are performed according to these default frequencies, the supply air temperature fluctuates greatly during the soft start process when adding a machine, making it easy to over-adjust. The temperature control accuracy is not high when adding or reducing a machine, and the control method of adding a machine only after the compressor reaches its rated speed is not energy-efficient.

[0187] Figure 15 This is a flowchart illustrating another cooling control method according to an exemplary embodiment. Figure 15 The method shown can be applied, for example, to applications such as... Figure 8 or Figure 10 The cooling unit shown.

[0188] refer to Figure 15 The method 150 provided in this embodiment may include the following S1502 to S1536.

[0189] In S1502, the first compressor is started.

[0190] In S1504, the first target rotational speed is obtained.

[0191] In S1506, the first compressor is controlled to increase its speed with a first acceleration.

[0192] In S1508, the current speed of the first compressor is obtained at a first frequency.

[0193] In S1510, a second target speed is obtained, which is based on the first target speed, the first cooling demand corresponding to the cooling unit, and the oil return speed of the third compressor.

[0194] In S1512, it is determined whether the current speed of the first compressor has reached the first target speed. If the current speed of the first compressor has not reached the first target speed, the process returns to S1508.

[0195] In S1514, if the current speed of the first compressor reaches the first target speed, control of the first compressor to increase its speed with the first acceleration is stopped.

[0196] In S1516, the duration for which the current speed of the first compressor is maintained at the first target speed is recorded.

[0197] In S1518, it is determined whether the duration for which the current speed of the first compressor is maintained at the first target speed is greater than or equal to a first duration. If the duration for which the current speed of the first compressor is maintained at the first target speed is less than the first duration, then return to S1516.

[0198] In S1520, if the current speed of the first compressor is maintained at a first target speed greater than or equal to a first duration, the first compressor is controlled to reduce its speed to the second target speed with a second acceleration, and the third compressor is controlled to start.

[0199] In S1522, the third compressor is controlled to increase its speed to the second target speed with a third acceleration.

[0200] In some embodiments, the specific implementation of S1502 to S1522 can be referred to S1202 to S1222, the difference being that... Figure 15 The second compressor to be turned on is the third compressor (or the fourth compressor, depending on the running time; the compressor with the shorter running time is selected to be turned on each time a compressor is added) in order to ensure that when two compressors are turned on, the corresponding evaporator covers 100% of the internal circulation cross-section.

[0201] In S1524, the third target rotational speed is obtained.

[0202] In S1526, the first compressor and the third compressor are controlled to increase their speed to the third target speed with a fourth acceleration.

[0203] In S1528, a fourth target speed is obtained, which is based on the third target speed, the first cooling demand corresponding to the cooling unit, and the oil return speed of the second compressor.

[0204] In S1530, the duration for which the current speed of the first compressor and the current speed of the third compressor remain at the third target speed is recorded.

[0205] In S1532, it is determined whether the current speed of the first compressor is maintained at the third target speed for a duration greater than or equal to the second duration, and whether the current speed of the third compressor is maintained at the third target speed for a duration greater than or equal to the second duration. If the current speed of the first compressor is maintained at the third target speed for a duration less than the second duration, and the current speed of the third compressor is maintained at the third target speed for a duration less than the second duration, then return to S1530.

[0206] In S1534, if the current speed of the first compressor is maintained at the third target speed greater than or equal to the second duration, and the current speed of the third compressor is maintained at the third target speed greater than or equal to the second duration, then the first compressor and the third compressor are controlled to reduce their speed to the fourth target speed with the fifth acceleration, and the second compressor is controlled to start.

[0207] In S1536, the second compressor is controlled to increase its speed to the fourth target speed with a sixth acceleration.

[0208] In some embodiments, S1524 to S1536 is the process of increasing the number of compressors from 2 to 3. Specific implementations can refer to embodiments S1504 to S1522 involving the addition of a second compressor. The values ​​of the third and fourth target speeds can be determined by referring to... Figure 16 The values ​​for the fourth, fifth, and sixth accelerations can be found by referring to... Figure 13 .

[0209] In some embodiments, after S1536, a step of adding a fourth compressor and controlling the four compressors to speed up to their rated speed may be included. Table 1 exemplarily lists the correspondence between cooling demand and the evaporators that are turned on. In the "Operating Evaporators" column, System 1, System 2, etc. represent the first evaporator, the second evaporator, etc., and in the "Operating Condensers" column, System 1, System 2, etc. represent the first condenser, the second condenser, etc.

[0210] Table 1

[0211]

[0212] According to the cooling unit and its corresponding control method provided in the embodiments of this disclosure, by dividing the four compressor systems into two groups and selecting different groups for the first addition of compressors, it can be ensured that the evaporator has the largest airflow area during operation. By adopting this compressor start-up method, when two or more compressor systems are turned on, the airflow area of ​​the evaporator can reach 100%. When the compressors in the group are started, the compressor with the shortest running time is started each time, and the compressor with the longest running time is stopped when the system is stopped. This can balance the compressor running time and extend its service life.

[0213] Figure 16 This is a schematic diagram illustrating the relationship between compressor speed regulation and CFC according to an exemplary embodiment. For a cooling unit with four compressors (i.e., four compressor subsystems), when the cooling demand corresponding to the added compressor node is determined, it can be calculated according to... Figure 16 Determine the target speed corresponding to the machine addition node.

[0214] As shown in Figure 16, the compressor speed control is divided into 4 stages and 4 levels of control. CFC 0~100% corresponds to the natural cooling mode of the indirect evaporative air conditioner (which can include dry mode and wet mode), and CFC 100~200% corresponds to the mechanical cooling mode (hybrid mode) of the indirect evaporative air conditioner. There is a linear correspondence between the compressor speed and CFC for each level.

[0215] Table 2 provides an example of the correspondence between compressor start-up when adding capacity and CFC when reducing capacity. For specific settings, please refer to the compressor selection specifications for your unit. The four start-up values ​​in Table 2 correspond to... Figure 16 CFC at the four machining inflection points on the horizontal axis.

[0216] Table 2

[0217]

[0218] As shown in Figure 16, the maximum compressor speed in stages 1, 2, and 3 is approximately twice the compressor's minimum speed (30 rpm) (e.g., 65-70 rpm). Figure 16 (The maximum speed is set to 70 rpm). After all four compressors are running, the maximum speed control is set to the rated speed, such as 90 rpm. Compared with the control method of adding a compressor only after the previous compressor has reached its rated speed, this reduces the time of adding a compressor and also reduces the time that the first compressor runs at its rated speed, which can effectively save energy.

[0219] Depend on Figure 13 It is known that a compressor takes 15 seconds to reach 20 rpm, about 30 seconds to reach 50 rpm, and about 3 minutes to reach above 50 rpm, such as 70 rpm. Figure 16 At the three inflection points during the installation process, the compressor speeds are 34 rpm, 46 rpm, and 55 rpm, respectively. This ensures that the corresponding compressor speed is less than 50 rpm (corresponding to the oil return plateau speed in the compressor's specifications), or close to 50 rpm. This avoids the oil return time (3 minutes) during the soft start process where the actual compressor speed is not externally controlled, allowing the speed adjustment time to be reached quickly within 30 seconds. This minimizes the fluctuations in the supply air temperature during installation caused by the delay in the soft start process in the compressor's inherent start-up logic. Simultaneously, by setting the target speed of the newly started compressor during installation, feedforward control of the compressor speed is implemented, ensuring that the pre-set compressor speed before and after installation maintains a relatively constant cooling capacity.

[0220] Table 3 shows the enthalpy difference test data for the operation of one compressor and two compressors in hybrid mode. In hybrid mode, under the same refrigeration conditions, the cooling capacity produced by one compressor operating at 65 rpm (i.e., 65 Hz) is equivalent to that produced by two compressors operating at 30 rpm (i.e., 30 Hz). However, referring to Table 3, the total power consumption of two compressors operating at low speed is 1.8 kW lower than the power consumption of one high-speed compressor (7.8-3). (2=1.8). Therefore, although the rated speed of a single compressor can reach 90 rpm, it is still necessary to control the compressor to start running earlier at 65 rpm, which is more energy-efficient.

[0221] Regarding the operational relationship, limiting the maximum operating speed of compressors 1, 2, and 3 to around 70 rpm allows the compressors to operate in the most energy-efficient mode. When all four compressors are running simultaneously, the maximum operating speed is limited to 90 rpm (rated speed) to ensure the air conditioning unit can output its rated cooling capacity in mechanical refrigeration mode.

[0222] Table 3

[0223] like Figure 16 As shown, at the compressor loading switching point, the compressor speed changes as follows: from stage 1 to stage 2, 70→34 rpm; from stage 2 to stage 3, 70→46 rpm; from stage 3 to stage 4, 70→55 rpm. When upgrading from stage 1 (1 compressor) to stage 2 (2 compressors), the cooling capacity of one 70 rpm compressor is approximately equal to the cooling capacity of two 34 rpm compressors; the cooling capacity of two 70 rpm compressors is approximately equal to the cooling capacity of three 46 rpm compressors; and the cooling capacity of three 70 rpm compressors is approximately equal to the cooling capacity of four compressors. This allows for pre-determining the compressor control speed setting during operation, ensuring a relatively constant cooling capacity, rather than waiting for temperature fluctuations and then adjusting the compressor speed based on feedback, thus avoiding the over-adjustment caused by adjustment lag.

[0224] Similarly, the compressor speed changes when the load is reduced: from stage 4 to stage 3, 42→60 rpm; from stage 3 to stage 2, 40→60 rpm; from stage 2 to stage 1, 30→40 rpm. The compressor's control speed setting can be determined in advance during the load reduction process to ensure that the cooling capacity remains essentially constant.

[0225] According to the enthalpy difference laboratory test results, the above control method can make the air supply temperature more uniform during the entire compressor cooling process, and the control accuracy can reach less than ±1℃, which is better than the air supply control accuracy of the indirect evaporative cooling unit used in related technologies.

[0226] Figure 17This is a block diagram illustrating a cooling control device according to an exemplary embodiment. Figure 17 The device shown can be applied, for example, to applications such as Figure 3 ,or Figure 4 ,or Figure 6 The cooling unit shown.

[0227] refer to Figure 17 The device 170 provided in this embodiment may include a switch control module 1702, a parameter acquisition module 1704, and a speed control module 1706.

[0228] The switch control module 1702 can be used to control the start of the first compressor.

[0229] The switch control module 1702 can also be used to control the start of the second compressor if the current speed of the first compressor is maintained at a first target speed greater than or equal to a first duration.

[0230] The switch control module 1702 can also be used to control the start of the first compressor if the running time of the first compressor is not greater than the running time of the second compressor.

[0231] The switch control module 1702 can also be used to control the shutdown of the second compressor and control the first compressor to increase its speed to the fifth target speed with a fifth acceleration if the current speed of the first compressor is maintained at the fourth target speed greater than or equal to the second duration, and the current speed of the second compressor is maintained at the fourth target speed greater than or equal to the second duration.

[0232] The switch control module 1702 can also be used to control the second compressor to shut down and control the first compressor to increase its speed to the fifth target speed with the fifth acceleration if the running time of the first compressor is not greater than the running time of the second compressor.

[0233] The parameter acquisition module 1704 can be used to obtain the first target rotational speed.

[0234] The parameter acquisition module 1704 can also be used to obtain the current speed of the first compressor at a first frequency.

[0235] The parameter acquisition module 1704 can also be used to obtain a second target speed, which is obtained based on the first target speed, the first cooling demand corresponding to the cooling unit, and the oil return speed of the second compressor.

[0236] The parameter acquisition module 1704 can also be used to obtain the running time of the first compressor and the running time of the second compressor, respectively.

[0237] The parameter acquisition module 1704 can also be used to obtain a third target rotational speed.

[0238] The parameter acquisition module 1704 can also be used to obtain the current cooling demand corresponding to the cooling unit at a second frequency.

[0239] The parameter acquisition module 1704 can also be used to obtain a fourth target speed, which is obtained based on the current cooling demand of the cooling unit and the first cooling demand.

[0240] The parameter acquisition module 1704 can also be used to obtain the fifth target speed, which is obtained based on the fourth target speed and the current cooling demand of the cooling unit.

[0241] The parameter acquisition module 1704 can also be used to obtain the running time of the first compressor and the running time of the second compressor, respectively.

[0242] The speed control module 1706 can be used to control the first compressor to increase its speed with a first acceleration.

[0243] The speed control module 1706 can also be used to control the first compressor to reduce its speed to the second target speed with a second acceleration if the current speed of the first compressor is maintained at a first target speed greater than or equal to the first duration.

[0244] The speed control module 1706 can also be used to control the second compressor to increase its speed to the second target speed with a third acceleration.

[0245] The speed control module 1706 can also be used to control the first compressor and the second compressor to increase their speed to the third target speed with a fourth acceleration.

[0246] The speed control module 1706 can also be used to control the speed of the first compressor and the second compressor according to the current cooling demand of the cooling unit, and obtain the current speed of the first compressor and the current speed of the second compressor at a third frequency.

[0247] Figure 18 This is a block diagram illustrating another cooling control device according to an exemplary embodiment. Figure 18 The device shown can be applied, for example, to applications such as Figure 8 or Figure 10 The cooling unit shown.

[0248] refer to Figure 18 The device 180 provided in this embodiment may include a switch control module 1802, a parameter acquisition module 1804, and a speed control module 1806.

[0249] The switch control module 1802 can be used to control the start of the first compressor.

[0250] The switch control module 1802 can also be used to control the start of the third compressor if the current speed of the first compressor is maintained at a first target speed greater than or equal to a first duration.

[0251] The parameter acquisition module 1804 can be used to obtain the first target rotational speed.

[0252] The parameter acquisition module 1804 can also be used to obtain the current speed of the first compressor at a first frequency.

[0253] The parameter acquisition module 1804 can also be used to obtain a second target speed, which is obtained based on the first target speed, the first cooling demand corresponding to the cooling unit, and the oil return speed of the third compressor.

[0254] The speed control module 1806 can be used to control the first compressor to increase its speed with a first acceleration.

[0255] The speed control module 1806 can also be used to control the first compressor to reduce its speed to the second target speed with a second acceleration if the current speed of the first compressor is maintained at a first target speed greater than or equal to the first duration.

[0256] The speed control module 1806 can also be used to control the third compressor to increase its speed to the second target speed with a third acceleration.

[0257] The specific implementation of each module in the device provided in this embodiment can be referred to the content of the above method, and will not be repeated here.

[0258] Figure 19 A schematic diagram of the structure of an electronic device according to an embodiment of this disclosure is shown. It should be noted that... Figure 19 The devices shown are merely examples of computer systems and should not be construed as limiting the functionality and scope of use of the embodiments disclosed herein.

[0259] like Figure 19 As shown, device 1900 includes a central processing unit (CPU) 1901, which can perform various appropriate actions and processes according to a program stored in read-only memory (ROM) 1902 or a program loaded from storage section 1908 into random access memory (RAM) 1903. RAM 1903 also stores various programs and data required for the operation of device 1900. CPU 1901, ROM 1902, and RAM 1903 are interconnected via bus 1904. Input / output (I / O) interface 1905 is also connected to bus 1904.

[0260] The following components are connected to I / O interface 1905: input section 1906 including keyboard, mouse, etc.; output section 1907 including cathode ray tube (CRT), liquid crystal display (LCD), etc., and speakers, etc.; storage section 1908 including hard disk, etc.; and communication section 1909 including network interface card, such as LAN card, modem, etc. Communication section 1909 performs communication processing via a network such as the Internet. Drive 1910 is also connected to I / O interface 1905 as needed. Removable media 1911, such as disk, optical disk, magneto-optical disk, semiconductor memory, etc., are installed on drive 1910 as needed so that computer programs read from them can be installed into storage section 1908 as needed.

[0261] In particular, according to embodiments of this disclosure, the processes described above with reference to the flowcharts can be implemented as computer software programs. For example, embodiments of this disclosure include a computer program product comprising a computer program carried on a computer-readable medium, the computer program containing program code for performing the methods shown in the flowcharts. In such embodiments, the computer program can be downloaded and installed from a network via communication section 1909, and / or installed from removable medium 1911. When the computer program is executed by central processing unit (CPU) 1901, it performs the functions defined above in the system of this disclosure.

[0262] It should be noted that the computer-readable medium disclosed herein may be a computer-readable signal medium or a computer-readable storage medium, or any combination thereof. A computer-readable storage medium may be, for example,—but not limited to—an electrical, magnetic, optical, electromagnetic, infrared, or semiconductor system, apparatus, or device, or any combination thereof. More specific examples of a computer-readable storage medium may include, but are not limited to: an electrical connection having one or more wires, a portable computer disk, a hard disk, random access memory (RAM), read-only memory (ROM), erasable programmable read-only memory (EPROM or flash memory), optical fiber, portable compact disk read-only memory (CD-ROM), optical storage device, magnetic storage device, or any suitable combination thereof. In this disclosure, a computer-readable storage medium may be any tangible medium containing or storing a program that can be used by or in conjunction with an instruction execution system, apparatus, or device. In this disclosure, a computer-readable signal medium may include a data signal propagated in baseband or as part of a carrier wave, carrying computer-readable program code. Such propagated data signals may take various forms, including but not limited to electromagnetic signals, optical signals, or any suitable combination thereof. Computer-readable signal media can also be any computer-readable medium other than computer-readable storage media, which can send, propagate, or transmit a program for use by or in connection with an instruction execution system, apparatus, or device. The program code contained on the computer-readable medium can be transmitted using any suitable medium, including but not limited to: wireless, wire, optical fiber, RF, etc., or any suitable combination thereof.

[0263] The flowcharts and block diagrams in the accompanying drawings illustrate the architecture, functionality, and operation of possible implementations of systems, methods, and computer program products according to various embodiments of this disclosure. In this regard, each block in a flowchart or block diagram may represent a module, segment, or portion of code containing one or more executable instructions for implementing a specified logical function. It should also be noted that in some alternative implementations, the functions indicated in the blocks may occur in a different order than those indicated in the drawings. For example, two consecutively indicated blocks may actually be executed substantially in parallel, and they may sometimes be executed in reverse order, depending on the functions involved. It should also be noted that each block in a block diagram or flowchart, and combinations of blocks in a block diagram or flowchart, may be implemented using a dedicated hardware-based system that performs the specified function or operation, or using a combination of dedicated hardware and computer instructions.

[0264] The modules described in the embodiments of this disclosure can be implemented in software or hardware. The described modules can also be housed in a processor; for example, a processor may be described as including a switch control module, a parameter acquisition module, and a speed control module. The names of these modules do not necessarily limit the module itself; for example, the switch control module may also be described as "a module that controls the starting or stopping of the compressor."

[0265] This disclosure also provides a computer-readable medium, which may be included in the device described in the above embodiments; or it may exist independently and not assembled into the device. The computer-readable medium carries one or more programs, which, when executed by the device, cause the device to perform:

[0266] The system controls the first compressor to start; obtains a first target speed; controls the first compressor to increase its speed with a first acceleration and obtains the current speed of the first compressor at a first frequency; obtains a second target speed, which is obtained based on the first target speed, the first cooling demand corresponding to the cooling unit, and the oil return speed of the second compressor; if the current speed of the first compressor is maintained at the first target speed greater than or equal to the first duration, the system controls the first compressor to decrease its speed to the second target speed with a second acceleration and controls the second compressor to start; and controls the second compressor to increase its speed to the second target speed with a third acceleration.

[0267] This disclosure provides a computer program product or computer program including computer instructions stored in a computer-readable storage medium. A processor of a computer device reads the computer instructions from the computer-readable storage medium and executes the computer instructions, causing the computer device to perform the methods provided in the various optional implementations described above.

[0268] Exemplary embodiments of this disclosure have been specifically shown and described above. It should be understood that this disclosure is not limited to the detailed structures, arrangements, or implementations described herein; rather, this disclosure is intended to cover various modifications and equivalent arrangements contained within the spirit and scope of the appended claims.

Claims

1. A cooling unit, characterized in that, The cooling unit is used to cool the airflow within the internal circulation air supply channel. The cooling unit includes a first evaporator, a first compressor, a second evaporator, and a second compressor, wherein: The first evaporator includes multiple first heat exchange pipes, which are arranged in parallel within the internal circulation air supply channel. The multiple first heat exchange pipes are used to cool the air flow passing through the first evaporator in the internal circulation air supply channel using the first refrigerant flow circulating in the first heat exchange pipes. The first compressor is in fluid communication with the first evaporator and is used to compress the first refrigerant flow; The second evaporator includes multiple second heat exchange pipes arranged in parallel within the internal circulation air supply channel. The multiple second heat exchange pipes are used to cool the air flow passing through the second evaporator within the internal circulation air supply channel using a second refrigerant flow circulating in the second heat exchange pipes. Multiple second heat exchange pipelines are arranged in parallel and at intervals with multiple first heat exchange pipelines, so that the sum of the air supply areas of the multiple second heat exchange pipelines is not less than the total area of ​​the internal circulation cross-section corresponding to the internal circulation air supply channel, and the sum of the air supply areas of the multiple first heat exchange pipelines is not less than the total area of ​​the internal circulation cross-section corresponding to the internal circulation air supply channel. The second compressor is in fluid communication with the second evaporator and is used to compress the second refrigerant flow.

2. The cooling unit according to claim 1, characterized in that, The internal circulation cross-section of the internal circulation air supply channel includes a first region and a second region; The multiple first heat exchange pipelines are divided into a first group and a second group; The first heat exchange pipes in the first group are arranged in parallel in the first area, and the first heat exchange pipes in the second group are arranged in parallel in the second area, so that the sum of the air supply area of ​​the first heat exchange pipes in the first group and the air supply area of ​​the first heat exchange pipes in the second group is not less than the total area of ​​the internal circulation cross section corresponding to the internal circulation air supply channel.

3. The cooling unit according to claim 2, characterized in that, The multiple second heat exchange pipelines are divided into a third group and a fourth group; The second heat exchange pipeline in the third group is arranged in parallel in the first area, and the second heat exchange pipeline in the third group is arranged in parallel with the first heat exchange pipeline in the first group at intervals. The second heat exchange pipeline in the fourth group is arranged in parallel in the second area. The second heat exchange pipeline in the fourth group is arranged in parallel with the first heat exchange pipeline in the second group at intervals. The sum of the air supply area of ​​the second heat exchange pipeline in the third group and the air supply area of ​​the second heat exchange pipeline in the fourth group is not less than the total area of ​​the internal circulation cross section.

4. The cooling unit according to claim 3, characterized in that, The first heat exchange pipeline in the first group and the second heat exchange pipeline in the third group are on the first heat exchange surface, and the first heat exchange pipeline in the second group and the second heat exchange pipeline in the fourth group are on the second heat exchange surface. Wherein, the first heat exchange surface and the second heat exchange surface form a first angle, such that the sum of the air supply area of ​​the first heat exchange pipe in the first group and the air supply area of ​​the first heat exchange pipe in the second group is greater than the total area of ​​the inner circulation cross section, and the sum of the air supply area of ​​the second heat exchange pipe in the third group and the air supply area of ​​the second heat exchange pipe in the fourth group is greater than the total area of ​​the inner circulation cross section.

5. The cooling unit according to claim 1, characterized in that, The cooling unit dissipates heat through an external circulating air outlet duct. The cooling unit further includes: a first condenser and a second condenser, wherein: The first condenser is in fluid communication with the first compressor and the first evaporator; The first condenser includes multiple third heat exchange pipes, which are arranged in parallel in the external circulation air outlet channel to transfer the heat of the first refrigerant flow circulating in the third heat exchange pipes to the air through the external circulation air outlet channel. The second condenser is in fluid communication with the second compressor and the second evaporator; The second condenser includes multiple fourth heat exchange pipes, which are arranged in parallel within the external circulation air outlet channel to transfer the heat of the second refrigerant flow circulating in the fourth heat exchange pipes to the air through the external circulation air outlet channel. Multiple third heat exchange pipelines and multiple fourth heat exchange pipelines are arranged in parallel at intervals.

6. A cooling unit, characterized in that, The cooling unit is used to cool the airflow within the internal circulation air supply channel. The internal circulation cross-section of the internal circulation air supply channel includes a first region and a second region. The cooling unit includes a first evaporator, a first compressor, a second evaporator, a second compressor, a third evaporator, a third compressor, a fourth evaporator, and a fourth compressor, wherein: The first evaporator includes multiple first heat exchange pipes arranged in parallel in the first region. The multiple first heat exchange pipes are used to cool the airflow flowing through the first evaporator in the internal circulation air supply channel by utilizing the first refrigerant flow circulating in the first heat exchange pipes. The first compressor is in fluid communication with the first evaporator and is used to compress the first refrigerant flow; The second evaporator includes multiple second heat exchange pipes arranged in parallel in the first region. The multiple second heat exchange pipes are used to cool the airflow flowing through the second evaporator in the internal circulation air supply channel by utilizing the second refrigerant flow circulating in the second heat exchange pipes. Multiple second heat exchange pipelines are arranged in parallel and at intervals with multiple first heat exchange pipelines, so that the sum of the air supply areas of the multiple second heat exchange pipelines is not less than the total area of ​​the first region of the internal circulation cross section, and the sum of the air supply areas of the multiple first heat exchange pipelines is not less than the total area of ​​the first region of the internal circulation cross section. The second compressor is in fluid communication with the second evaporator and is used to compress the second refrigerant flow; The third evaporator includes multiple third heat exchange pipes arranged in parallel in the second region. The multiple third heat exchange pipes are used to cool the airflow flowing through the third evaporator in the internal circulation air supply channel by utilizing the third refrigerant flow circulating in the third heat exchange pipes. The third compressor is in fluid communication with the third evaporator and is used to compress the third refrigerant flow; The fourth evaporator includes multiple fourth heat exchange pipes arranged in parallel in the second region. The multiple fourth heat exchange pipes are used to cool the airflow flowing through the fourth evaporator in the internal circulation air supply channel by utilizing the fourth refrigerant flow circulating in the fourth heat exchange pipes. Multiple fourth heat exchange pipelines are arranged in parallel with multiple third heat exchange pipelines at intervals, so that the sum of the air supply areas of the multiple fourth heat exchange pipelines is not less than the total area of ​​the second region of the inner circulation cross section, and the sum of the air supply areas of the multiple third heat exchange pipelines is not less than the total area of ​​the second region of the inner circulation cross section. The fourth compressor is in fluid communication with the fourth evaporator and is used to compress the fourth refrigerant stream.

7. The cooling unit according to claim 6, characterized in that, The plurality of first heat exchange pipes and the plurality of second heat exchange pipes are on the first heat exchange surface, and the plurality of third heat exchange pipes and the plurality of fourth heat exchange pipes are on the second heat exchange surface; Wherein, the first heat exchange surface and the second heat exchange surface form a first angle, such that the sum of the air supply area of ​​the plurality of first heat exchange pipes and the air supply area of ​​the plurality of second heat exchange pipes is greater than the total area of ​​the internal circulation cross section corresponding to the internal circulation air supply channel, and the sum of the air supply area of ​​the plurality of third heat exchange pipes and the air supply area of ​​the plurality of fourth heat exchange pipes is greater than the total area of ​​the internal circulation cross section.

8. The cooling unit according to claim 6, characterized in that, The plurality of first heat exchange pipelines are divided into a first group and a second group, the plurality of second heat exchange pipelines are divided into a third group and a fourth group, the plurality of third heat exchange pipelines are divided into a fifth group and a sixth group, and the plurality of fourth heat exchange pipelines are divided into a seventh group and an eighth group. The first region is divided into a first sub-region and a second sub-region, and the second region is divided into a third sub-region and a fourth sub-region; The first heat exchange pipeline in the first group and the second heat exchange pipeline in the third group are arranged side by side and spaced apart in the first sub-region; the first heat exchange pipeline in the second group and the second heat exchange pipeline in the fourth group are arranged side by side and spaced apart in the second sub-region. The third heat exchange pipe in the fifth group and the fourth heat exchange pipe in the seventh group are arranged side-by-side and spaced apart in the third sub-region, and the third heat exchange pipe in the sixth group and the fourth heat exchange pipe in the eighth group are arranged side-by-side and spaced apart in the fourth sub-region, so that the sum of the air supply area of ​​the first heat exchange pipe in the first group, the first heat exchange pipe in the second group, the third heat exchange pipe in the fifth group, and the third heat exchange pipe in the sixth group is not less than the total area of ​​the internal circulation cross-section corresponding to the internal circulation air supply channel, and the sum of the air supply area of ​​the second heat exchange pipe in the third group, the second heat exchange pipe in the fourth group, the fourth heat exchange pipe in the seventh group, and the fourth heat exchange pipe in the eighth group is not less than the total area of ​​the internal circulation cross-section corresponding to the internal circulation air supply channel.

9. The cooling unit according to claim 8, characterized in that, The first heat exchange pipeline in the first group and the second heat exchange pipeline in the third group are on the third heat exchange surface, and the first heat exchange pipeline in the second group and the second heat exchange pipeline in the fourth group are on the fourth heat exchange surface. The third heat exchange pipeline in the fifth group and the fourth heat exchange pipeline in the seventh group are on the fifth heat exchange surface, and the third heat exchange pipeline in the sixth group and the fourth heat exchange pipeline in the eighth group are on the sixth heat exchange surface. Wherein, the third heat exchange surface forms a second angle with the fourth heat exchange surface, the fourth heat exchange surface forms a third angle with the fifth heat exchange surface, and the fifth heat exchange surface forms a fourth angle with the sixth heat exchange surface, so that the third, fourth, fifth, and sixth heat exchange surfaces are arranged in a zigzag shape, and the sum of the air supply area of ​​the first heat exchange pipe in the first group, the first heat exchange pipe in the second group, the third heat exchange pipe in the fifth group, and the third heat exchange pipe in the sixth group is greater than the total area of ​​the inner circulation cross section, and the sum of the air supply area of ​​the second heat exchange pipe in the third group, the second heat exchange pipe in the fourth group, the fourth heat exchange pipe in the seventh group, and the fourth heat exchange pipe in the eighth group is greater than the total area of ​​the inner circulation cross section.

10. A cooling control method, characterized in that, Applied to the cooling unit as described in any one of claims 1-5, the method comprises: Control the start-up of the first compressor; Obtain the first target rotational speed; The first compressor is controlled to increase its speed with a first acceleration, and the current speed of the first compressor is obtained at a first frequency; A second target speed is obtained, which is based on the first target speed, the first cooling demand corresponding to the cooling unit, and the oil return speed of the second compressor. If the current speed of the first compressor remains greater than or equal to the first target speed for a first duration, then the first compressor is controlled to reduce its speed to the second target speed with a second acceleration, and the second compressor is controlled to start. The second compressor is controlled to increase its speed to the second target speed with a third acceleration.

11. The method according to claim 10, characterized in that, Controlling the start of the first compressor includes: The running time of the first compressor and the running time of the second compressor are obtained respectively; If the running time of the first compressor is not greater than the running time of the second compressor, then the first compressor is turned on.

12. The method according to claim 10, characterized in that, Also includes: Obtain the third target rotational speed; Control the first compressor and the second compressor to increase their speed to the third target speed with a fourth acceleration; The current cooling demand corresponding to the cooling unit is obtained at a second frequency; The speeds of the first compressor and the second compressor are controlled according to the current cooling demand corresponding to the cooling unit, and the current speeds of the first compressor and the second compressor are obtained at a third frequency. A fourth target rotational speed is obtained, which is based on the current cooling demand corresponding to the cooling unit and the first cooling demand. A fifth target rotational speed is obtained, which is based on the fourth target rotational speed and the current cooling demand corresponding to the cooling unit. If the current speed of the first compressor is maintained at the fourth target speed greater than or equal to the second duration, and the current speed of the second compressor is maintained at the fourth target speed greater than or equal to the second duration, then the second compressor is controlled to be shut down, and the first compressor is controlled to increase its speed to the fifth target speed with a fifth acceleration.

13. The method according to claim 12, characterized in that, Controlling the shutdown of the second compressor and controlling the first compressor to increase its speed to the fifth target speed with a fifth acceleration includes: The running time of the first compressor and the running time of the second compressor are obtained respectively; If the running time of the first compressor is not greater than the running time of the second compressor, then the second compressor is shut down, and the first compressor is controlled to increase its speed to the fifth target speed with a fifth acceleration.

14. A cooling control method, characterized in that, Applied to the cooling unit as described in any one of claims 6-9, the method comprises: Control the start-up of the first compressor; Obtain the first target rotational speed; The first compressor is controlled to increase its speed with a first acceleration, and the current speed of the first compressor is obtained at a first frequency; A second target speed is obtained, which is based on the first target speed, the first cooling demand corresponding to the cooling unit, and the oil return speed of the third compressor. If the current speed of the first compressor remains greater than or equal to the first target speed for a first duration, then the first compressor is controlled to reduce its speed to the second target speed with a second acceleration, and the third compressor is controlled to start. The third compressor is controlled to increase its speed to the second target speed with a third acceleration.

15. A cooling control device, characterized in that, Applied to the cooling unit as described in any one of claims 1-5, the device comprises: A switch control module is used to control the start-up of the first compressor; The parameter acquisition module is used to obtain the first target rotational speed; The switch control module is further configured to control the second compressor to start if the current speed of the first compressor is maintained at the first target speed for a first duration greater than or equal to the first speed. The parameter acquisition module is further configured to acquire the current rotational speed of the first compressor at a first frequency; The parameter acquisition module is further configured to obtain a second target speed, which is obtained based on the first target speed, the first cooling demand corresponding to the cooling unit, and the oil return speed of the second compressor. The speed control module is used to control the first compressor to increase its speed with a first acceleration; The speed control module is further configured to control the first compressor to reduce its speed to the second target speed with a second acceleration if the current speed of the first compressor is maintained at the first target speed for a first duration greater than or equal to the first target speed. The speed control module is also used to control the second compressor to increase its speed to the second target speed with a third acceleration.

16. A cooling system, characterized in that, Includes a cooling unit as described in any one of claims 1-5 or any one of claims 6-9, and a heat exchange unit, wherein the heat exchange unit is used to cool the airflow in the internal circulation air supply channel using the external circulation airflow.

17. An electronic device comprising: A memory, a processor, and executable instructions stored in the memory and executable in the processor, characterized in that the processor, when executing the executable instructions, implements the method as claimed in any one of claims 10-13 or claim 14.

18. A computer-readable storage medium having computer-executable instructions stored thereon, characterized in that, When the executable instructions are executed by the processor, they implement the method as described in any one of claims 10-13 or claim 14.

19. A computer program product comprising a computer program / instructions, characterized in that, When the computer program / instructions are executed by the processor, they implement the method as described in any one of claims 10-13 or claim 14.

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