Integrated server cabinet capable of waste heat recovery and control method

Abstract

The application provides an integrated server cabinet capable of waste heat recycling and a control method, belongs to the field of servers, and comprises multiple servers, a cooling distribution unit and a control assembly, wherein the multiple servers are laid in multiple rows and multiple columns on a site; the cooling distribution unit comprises a primary circulation pipeline, and the waste heat utilization module comprises a secondary circulation pipeline; the primary circulation pipeline and the secondary circulation pipeline realize online adjustment of water flow in the primary circulation pipeline and the secondary circulation pipeline through an electric three-way regulating valve; the primary circulation pipeline is used for cooling and heat dissipation of the multiple servers; the secondary circulation pipeline is used as a bypass branch of a liquid cooling system and is used for waste heat recycling and bearing part or all of the heat exchange function of the primary circulation pipeline, and simultaneously satisfies the supply of heat of the external heat source demand assembly. The application integrates liquid cooling server operation, waste heat utilization heat exchange station, server and heat supply management, and has high thermal efficiency.

Description

TECHNICAL FIELD

[0001] The application belongs to the technical field of servers, and relates to an integrated server cabinet, in particular to an integrated server cabinet capable of recycling waste heat and a control method. BACKGROUND

[0002] In the era of big data explosion, especially with the development of AI technology, the amount of data is growing at a geometric rate, and the memory space occupied by the stored files is becoming larger and larger. In order to ensure the security of data, the timeliness of storage, the convenience of calling, etc., most companies have their own servers for timely uploading, storing backup and transferring data files. The server is crucial to the enterprise, bearing all electronic data information of the enterprise. In the current information age of big data, once the server fails, it will directly affect the normal operation and operation of the enterprise. Therefore, the stable operation of the server is very important.

[0003] Due to the importance of the server, many enterprises set up a special area or room for the server and match corresponding cooling measures to ensure the good continuous operation of the highly integrated server. In the process of high-speed continuous operation and cooling of the server, a large amount of heat is generated. At present, these heat is directly discharged into the atmosphere, and suitable cooling measures need to be matched for cooling. The cooling equipment consumes a large amount of energy, and the heat is directly discharged, which cannot recycle the heat in time, so that the operation of the server causes a large amount of energy consumption. In addition to the cost of the server equipment itself, the energy consumption of operation also becomes part of the cost of the enterprise. SUMMARY

[0004] The problem to be solved by the present application is to provide an integrated server cabinet capable of recycling waste heat and a control method. In view of the problems in the background art, a primary circulation pipeline and a secondary circulation pipeline are provided. The primary circulation pipeline is used to cool the server, and the secondary circulation pipeline is used to realize heat exchange. The heat generated by the server is recycled and communicated with the external heat source demand component to meet the supply of hot water source. The water flow can be adjusted online according to the temperature of the external environment to meet the heating demand of different temperatures under different conditions. Recycling and reuse not only reduce the energy consumption cost of the enterprise, but also realize better environmental protection demand.

[0005] To solve the above technical problems, the technical scheme adopted by the present application is as follows: an integrated server cabinet capable of recycling waste heat and a control method, comprising a plurality of servers, a cooling distribution unit, a waste heat utilization module and a control component.

[0006] The cooling distribution unit comprises a primary circulation pipeline. The primary circulation pipeline serves as a cooling source and cools and dissipates heat of the plurality of servers through circulation of medium.

[0007] The waste heat utilization module comprises a secondary circulation pipeline for waste heat recovery to meet the heat supply of the external heat source demand assembly, and the primary circulation pipeline and the secondary circulation pipeline are adjusted in line by an electric three-way regulating valve to adjust the flow of the medium after temperature rise in the primary circulation pipeline and the secondary circulation pipeline, so as to switch the entire system among multiple modes of primary temperature control, waste heat utilization mode and secondary temperature control.

[0008] The plate heat exchanger assembly is further included, the medium after temperature rise in the primary circulation pipeline is used as the heat source supply of the plate heat exchanger assembly, part of the medium after heat exchange in the plate heat exchanger assembly is returned to the primary circulation pipeline, and the other part of the medium after temperature rise is used as the supply source of the heat source in the secondary circulation pipeline. In the present application, the plate heat exchanger assembly is adopted, and other structures capable of realizing medium heat exchange in the market are also capable of realizing the technical solution of the present application, and are all within the protection scope of the present application.

[0009] Further, the cabinet body is included, a plurality of server positions are arranged in the cabinet body, and the plurality of servers are arranged in multiple rows and multiple columns on the server positions. The cabinet body is divided into an upper part and a lower part, the upper part is used for placing the plurality of servers, and the lower part is used for placing the cooling distribution unit, the plate heat exchanger assembly and laying the pipeline. The cooling distribution unit forms a skid structure, the primary circulation pipeline is arranged on the back of the cabinet, and the pipeline and the cooling distribution unit are arranged in the same direction. A soft connection for preventing the cooling distribution unit from vibrating is arranged between the pipeline and the cooling distribution unit.

[0010] Further, the primary circulation pipeline comprises a primary circulation pump, a primary circulation main water inlet pipeline and a primary circulation main water return pipeline. One server corresponds to one water inlet branch and one water outlet branch. The primary circulation main water inlet pipeline enters the cooling area of the plurality of servers through the plurality of water inlet branches and then returns to the primary circulation main water return pipeline through the water outlet branches. Valves for controlling the water flow are arranged on each water inlet branch and each water outlet branch.

[0011] The first valve, the primary water circulation flow meter FIT01 and the primary water inlet temperature signal meter TT01 are sequentially arranged on the primary circulation main water inlet pipeline from the dry cooler fan end to the server end. The primary water return temperature signal meter TT02, the primary circulation water pump P01, the electric three-way regulating valve V001 and the second valve V002 are sequentially arranged on the primary circulation main water return pipeline from the server end to the dry cooler fan end. The primary water circulation flow meter FIT01 feeds back a signal to the control assembly. The control assembly compares the feedback value of the primary water circulation flow meter FIT01 with the set target flow through the PID algorithm module, and then adjusts the frequency of the primary circulation water pump, so that the value of the primary water circulation flow meter FIT01 is leveled with the set target flow.

[0012] Further, the secondary circulation pipeline comprises a secondary circulation pump, a secondary circulation water inlet main pipe and a secondary water return water temperature signal meter TT11, the secondary water return water temperature signal meter TT11 feeds back a signal to the control assembly, and further comprises an outdoor temperature signal meter TT21 and an indoor temperature signal meter TT22, both of which are electrically connected with the control assembly and feed back real-time temperatures to the control assembly.

[0013] Further, the water outlet end of the plate heat exchanger assembly is divided into two branches, one of which returns the cooled medium to the primary circulation main water inlet pipeline in the primary circulation pipeline and is connected between the first valve V003 and the primary water circulation flow meter FIT01, and the other branch is in communication with the external heat source demand assembly.

[0014] Further, in the structural layout, the length and width of the cooling distribution unit are not greater than the length and width of the cabinet, and space is reserved for the server, if the electric three-way throttling valve is installed at the water inlet of the plate heat exchanger assembly, a shunt three-way is selected, and if the electric three-way throttling valve is installed at the water outlet of the plate heat exchanger assembly, a confluence three-way is selected.

[0015] Further, the specifications of the product are determined by parameter calculation, and the steps are as follows:

[0016] S1, determine the total power of a plurality of servers, calculate the amplification coefficient according to the total power, and then determine the heat exchange power of the cooling distribution unit after rounding;

[0017] S2, calculate the flow of the primary circulation pump, derive the primary circulation temperature difference△t according to the limit water inlet and outlet temperature difference of the server, and calculate the flow of the primary circulation pump according to the following formula,

[0018] Q=cm△t;

[0019] Q=c(ρv)△t;

[0020] V=Q / (cρ△t);

[0021] In the above formula, the characteristics of the cooling medium include freezing point, boiling point, density and specific heat capacity, C represents specific heat capacity; it represents the ability of a substance to absorb heat when its temperature increases, and the unit of specific heat capacity is joule per kilogram per degree Celsius; m: mass of the object;△t represents the change of temperature, i.e. the temperature of the object increases (or decreases), ρ: represents the density of the substance, which is the ratio of the mass of the substance to the volume, and the unit is kilogram per cubic meter; v: represents the volume of the substance, and the unit is cubic meter;

[0022] Finally, set the amplification coefficient to determine the flow;

[0023] S3, calculate the head of the primary circulation pump, select the pipe specification, and determine the pipe specific friction according to the selected pipe specification,

[0024] Pipe resistance loss calculation formula △P=L·△p

[0025] L=pipe+elbow+tee+valve group+plate heat exchanger assembly+server, the equivalent length of the most unfavorable loop of the primary circulation;

[0026] △p: pipe specific friction, the head of the primary circulation pump is greater than △P;

[0027] S4, calculate the flow and head of the secondary circulation pump, the calculation process is the same as that of the primary circulation pump, the difference is that L=pipe+elbow+valve group+plate heat exchanger assembly+heating terminal, the equivalent length of the most unfavorable loop of the secondary circulation;

[0028] S5, plate heat exchanger assembly selection, the power of the plate heat exchanger assembly is slightly larger than the sum of the powers of multiple servers, and then according to the primary supply and return water temperature difference and the secondary supply and return water temperature difference, the plate heat exchanger assembly is selected, and the heat exchange area is calculated;

[0029] S6, pipe, pipe fitting, valve group selection and determination, according to the flow of the primary circulation pipe and the secondary circulation pipe, the economic specific friction pipe is selected, the square pipe is used for vertical pipe, and the specific friction is close to the space can be more effectively utilized; pipe fitting.

[0030] The control method of the integrated server cabinet with waste heat recovery and utilization includes the control modes of switchable primary return water temperature control mode, waste heat utilization mode and climate compensation automatic control mode.

[0031] The primary return water temperature control method is as follows:

[0032] Set the primary return water target temperature TT91; adjust the opening and speed of V001 and G01 / G02 through the PID algorithm module; make TT01 pursue TT91;

[0033] The control method of the waste heat utilization mode is as follows:

[0034] Set the primary return water target temperature TT91 and the secondary return water target temperature TT92; compare TT92 with TT11 to determine whether waste heat utilization is needed; adjust the opening and speed of V001 and G01 / G02 through the PID algorithm module; make TT01 pursue TT91; after a period of stabilization, return to the first step and adjust again;

[0035] The secondary temperature control method, i.e. the climate compensation automatic control method, is as follows:

[0036] According to outdoor temperature TT21 calculates secondary return water target temperature TT94; through PID algorithm module to P02 frequency adjustment; make TT11 pursue TT94; end temperature control; set indoor target temperature TT96; through PID algorithm module to P02 frequency adjustment; make TT22 pursue TT96; heating circulating water temperature control; set heating return water target temperature TT92; through PID algorithm module to P02 frequency adjustment; make TT11 pursue TT92.

[0037] Further, the control method of waste heat utilization mode is as follows:

[0038] 1), manually set a primary target temperature value TT91, the tolerance is ±2℃, the value and range value are required to be displayed on the setting screen, manually set a secondary target temperature value TT92, the tolerance is ±2℃, the value and range value are required to be displayed on the setting screen;

[0039] 2), compare the values of TT11 and TT92, if TT11≥TT92, execute 3), if TT11<TT92, execute 5);

[0040] 3), electric three-way regulating valve V001's dry cooler passage is 100%, plate exchange assembly passage is 0%, TT91 and TT01's value are compared, through PID algorithm module to G01 / G02 frequency adjustment, make TT01 infinitely close to TT91;

[0041] 4), set time interval time02, when heating balance is reached, time02 will start timing, after timing, the system will automatically return to 2 to adjust again, the time interval of adjustment again is required to be displayed on the setting screen;

[0042] 5), electric three-way regulating valve V001's dry cooler passage is 0%, plate exchange assembly passage is 100%;

[0043] 6), compare the values of TT01 and TT91, if TT01>TT91, execute 7), if TT01<TT91, execute 8), if TT01=TT91, execute 9);

[0044] 7), dry cooler passage slowly increases, plate exchange assembly passage slowly decreases, when plate exchange assembly passage opening degree≤20%, dry cooler fan G01 / G02 through PID algorithm module adjusts the speed to slowly increase, until TT01=TT91 effect in step 9 is reached;

[0045] 8), the dry cooler fan G01 / G02 is adjusted to slow down the speed by the PID algorithm module, when the dry cooler fan stops, the dry cooler passage is slowly reduced, the plate exchange assembly passage is slowly increased, until the effect of TT01=TT91 in step 9 is reached;

[0046] 9), the electric valve V001 keeps the current opening and G01 / 02 keeps the current speed;

[0047] 10), the set time interval time02, when the heating balance is reached, the time interval time02 will start timing, after the timing is over, the system will automatically return to 2) for re-adjustment, the time interval of re-adjustment is required to be displayed on the setting screen;

[0048] 11), there are two setting parameters on the PLC panel, which are the time01 of each dynamic adjustment of the three-way valve and the adjustment opening OP01 of each dynamic, the upper limit is set to 30 seconds and 10% opening, to prevent misoperation.

[0049] The new application of the integrated server cabinet with waste heat recovery can be applied to multiple places with heat source demand, including but not limited to the following:

[0050] Heating: apartments, villas, shopping malls, restaurants, office buildings, venues, theaters, workshops, warehouses, agricultural greenhouses, fresh air preheating and any area with heating demand;

[0051] Hot water: domestic hot water, swimming pool heating, fish pond heating, to meet the daily water demand;

[0052] Others: drying, high-temperature sterilization, steam generator preheating parts that require heat.

[0053] Compared with the prior art, the application has the advantages and positive effects as follows.

[0054] 1, on the basis of the existing cabinet, the heat generated by the server operation is utilized, the heating demand is realized, the medium is conveyed to the heat point through the water pump, the plate exchange assembly and other equipment, the heating output is controlled through the three-way valve, the flow meter, the frequency converter and other equipment, the total heating amount is counted through the heat meter, the demand of different area heat is met, the liquid cooling server operation, the waste heat utilization heat exchange station, the server and the heating management are integrated, the single cabinet load of the application is relatively small and can be combined with the cabinet for joint operation, highly integrated and easy to install;

[0055] 2. This invention adopts a modular structure, dividing the cabinet into upper and lower parts, separating the electrical components and waste heat utilization module. This helps ensure the safe operation of the server area and improves the stability of data protection. The cooling distribution unit in the lower part adopts a modular design, forming a skid-mounted structure. It can be directly replaced to accommodate different server integration types, enabling rapid disassembly and reassembly. Maintenance and upkeep are also convenient, reducing relocation costs. The built-in pump station simplifies the on-site installation process, allowing for immediate production after connecting cables and pipes.

[0056] 3. The present invention sets up a plate heat exchanger unit, which can be used as a heating unit to realize waste heat recovery. The heat emitted by the server is used as the heat source of the plate heat exchanger component for full recovery. After heat exchange, the cooled medium flows back to the CDU module. The heated medium output meets the heating and cooling needs of various occasions, etc., realizing the integration of multiple functions. At the same time, the heat recovery and reuse reduces energy consumption.

[0057] 4. Due to the integration of multiple functions and waste heat utilization, this application is energy-efficient and highly efficient, with an overall thermal efficiency of up to 97%. It can be regarded as one unit of energy that simultaneously meets the needs of server operation and heat supply, resulting in low carbon emissions. The carbon emissions from server operation and heating are reduced to one unit. Moreover, additional revenue can be generated on this basis, as server computing power revenue can be generated while providing heating. Attached Figure Description

[0058] The accompanying drawings, which form part of this invention, are used to provide a further understanding of the invention. The illustrative embodiments of the invention and their descriptions are used to explain the invention and do not constitute an undue limitation of the invention. In the drawings:

[0059] Figure 1 This is the control logic diagram of RACKCAB as the server in this embodiment of the invention;

[0060] Figure 2 This is the control logic diagram of HYDROCAB as the server in this embodiment of the invention;

[0061] Figure 3 This is the logic diagram of the single-cycle flow control system of the present invention;

[0062] Figure 4 This is the logic diagram of the normal mode of the single-cycle temperature control system of the present invention;

[0063] Figure 5 This is a logic diagram of the waste heat utilization mode of the primary cycle temperature control system of the present invention.

[0064] Figure 6 This is a logic diagram of the climate compensation mode of the secondary cycle temperature control system of this invention.

[0065] Figure 7This is the logic diagram of the secondary cycle temperature control system of the present invention - the terminal temperature control logic diagram;

[0066] Figure 8 This is the logic diagram of the secondary circulation temperature control system of the present invention - the logic diagram of circulating water temperature control;

[0067] Figure 9 This is an explanatory table of illustrations and names of graphic symbols in this invention;

[0068] Figure 10 This invention relates to a table for the first character and description of letter symbols;

[0069] Figure 11 This is a structural diagram of the RACKCAB server in an embodiment of the present invention, without the rear view of the cabinet;

[0070] Figure 12 This is a schematic diagram of the structure of the server as RACKCAB in the embodiment of the present invention, without the side view of the cabinet;

[0071] Figure 13 This is a schematic diagram of the structure of the server (HYDROCAB) without the cabinet rear view in the embodiment of the present invention;

[0072] Figure 14 This is a structural diagram of the server as a HYDROCAB in the embodiment of the present invention, without the cabinet viewed from below; Attached image description:

[0074] 1. Server; 2. Primary circulation main inlet pipe; 3. Primary circulation main return pipe; 5. Cold water inlet of primary circulation pipe; 6. Hot water return outlet of primary circulation pipe; 7. Hot water outlet of secondary circulation pipe; 8. Cold water return outlet of secondary circulation pipe; 9. Plate heat exchanger assembly. Detailed Implementation

[0075] It should be noted that, unless otherwise specified, the embodiments and features described in the present invention can be combined with each other.

[0076] In the description of this invention, it should be understood that the terms "center," "longitudinal," "lateral," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," and "outer," etc., indicating orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, are only for the convenience of describing the invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of the invention. Furthermore, the terms "first," "second," etc., are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of indicated technical features. Thus, a feature defined with "first," "second," etc., may explicitly or implicitly include one or more of that feature. In the description of this invention, unless otherwise stated, "a plurality of" means two or more.

[0077] In the description of this invention, it should be noted that, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "linking" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection of two components. Those skilled in the art will understand the specific meaning of the above terms in this invention based on the specific circumstances.

[0078] The specific embodiments of the present invention will now be described in detail with reference to the accompanying drawings.

[0079] The working principle of a dry cooler is primarily based on heat exchange. Specifically, a refrigerant circulates within the dry cooler through pipes, which are typically designed for efficient heat dissipation. When the high-temperature refrigerant flows through these pipes, a fan or natural wind blows air across the pipe surface, creating heat exchange. During this process, the refrigerant transfers heat to the outside air through the pipe walls, lowering its temperature and achieving a cooling effect. The outside air, having absorbed the heat from the refrigerant, warms up and is subsequently exhausted or dissipates naturally. This heat exchange process continues, with the refrigerant circulating within the dry cooler, constantly releasing heat to maintain its temperature at a low level. Therefore, a dry cooler effectively lowers the temperature of liquids, achieving cooling. Notably, dry coolers do not consume water during operation, resulting in significant water conservation. Furthermore, because heat exchange occurs through air, dry coolers do not produce water mist or droplets during operation, making them suitable for environments with high humidity requirements. In general, dry coolers achieve cooling by utilizing the temperature difference between air and refrigerant through heat exchange, making them a highly efficient and energy-saving cooling device.

[0080] Plate heat exchanger units are high-efficiency heat exchanger assemblies composed of a series of corrugated metal sheets stacked together. They consist of many stamped corrugated thin plates spaced at regular intervals, sealed around the edges with gaskets, and then overlapped and pressed together by a frame and clamping screws. The four corner holes of the plates and gaskets form fluid distribution and collection pipes, while also effectively separating hot and cold fluids, allowing them to flow in the channels on both sides of each plate for heat exchange. Thin rectangular channels are formed between the plates, facilitating heat exchange. Plate heat exchanger units are ideal for liquid-liquid and liquid-vapor heat exchange. They feature high heat exchange efficiency, low heat loss, compact and lightweight structure, small footprint, wide application, and long service life.

[0081] like Figures 1-14 As shown, this invention relates to an integrated server rack and control method capable of waste heat recovery and utilization. Targeting rack-type liquid cooling systems, it provides a suitable working environment for liquid-cooled servers, ensuring stable operation under favorable conditions. Traditional liquid-cooled server circulation involves connecting to a cold source and dissipating heat into the atmosphere. This device, however, can utilize the heat generated by the server's operation as waste heat for heating. The medium is transported to the hotspot via water pumps, heat exchanger components, and other equipment. The heating output is controlled by devices such as three-way valves, flow meters, and frequency converters, and the total heating volume is statistically analyzed using a heat meter.

[0082] An integrated server rack capable of waste heat recovery is often used in independent rack structures with less than 100K servers. It includes multiple servers, a cooling distribution unit and control components. Multiple servers can be arranged in multiple rows and columns on the rack.

[0083] The cooling distribution unit (CDD) includes a primary circulation pipeline, and the waste heat utilization module includes a secondary circulation pipeline. The primary and secondary circulation pipelines are connected online through an electric three-way regulating valve to adjust the water flow rate in the primary and secondary circulation pipelines, so as to enable the entire system to switch between multiple modes such as primary temperature control, waste heat utilization mode and secondary temperature control.

[0084] The primary circulation pipeline serves as a cooling source, cooling and dissipating heat from multiple servers through the circulation of the medium.

[0085] The secondary circulation pipeline, serving as a bypass branch of the liquid cooling system, is used for waste heat recovery to meet the heat supply requirements of external heat sources for components.

[0086] It also includes plate heat exchangers. The medium heated by the server in the primary circulation pipeline is supplied as the heat source for the plate heat exchanger. After heat exchange by the plate heat exchanger, the cooled medium flows back to the primary circulation pipeline. At the same time, the heated medium serves as the heat source for the secondary circulation pipeline. In this application, plate heat exchangers are used. Considering cost and installation space factors, if there are other structures on the market that can achieve medium heat exchange, they can also realize the technical solution of this application, and they are all within the protection scope of this application.

[0087] More preferably, the structure of this application is a cabinet structure, including a cabinet body, which adopts a highly integrated structure and is divided into upper and lower parts. Multiple servers are located in the upper part, the length and width of the cooling distribution unit are equal to the length and width of the cabinet, and the height is compressed as much as possible to leave space for server placement. It occupies the lower half of the cabinet and is assembled into a pry bar for easy and quick disassembly and assembly.

[0088] The primary circulation piping is located at the back of the rack, arranged in parallel. A flexible connection is provided between the piping and the Cooling Distribution Unit (CDU) to prevent CDU vibration from affecting the stability of server operation. The control components are primarily electrical, located at the top front of the rack, away from the piping and CDU, and are isolated. Key equipment includes the main switch, branch switches, frequency converter, PLC module, screen, terminal blocks, cables, and copper busbars.

[0089] The structural layout of this application follows the principles of proximity and non-interference. The proximity principle minimizes interfaces, cables, and conduits, ensuring related parts are adjacent. The non-interference principle minimizes or eliminates overlap between zones. Based on these principles, detailed partitioning is performed, determining the maximum space limits for each component. Finally, based on these limits, a highly integrated, unified rack is formed. Next, the partitioning is designed separately for servers, control components, primary and secondary circulation piping, and so on. Assembly is then carried out, and final adjustments are made, assembling all zones according to the initial plan, checking for interference and ensuring proper functionality, and making necessary adjustments.

[0090] During the structural layout process, the final cabinet dimensions need to be calculated using parameters. The detailed calculation steps are as follows:

[0091] S1. Determine the total power of multiple servers, calculate the amplification factor based on the total power, and then round down to determine the heat exchange power of the CDU.

[0092] S2. Calculate the primary circulation pump flow rate. Based on the server's maximum inlet and outlet water temperature difference, obtain the primary circulation temperature difference Δt. Calculate the primary circulation pump flow rate using the following formula.

[0093] Q = cmΔt;

[0094] Q = c(ρv)Δt;

[0095] V = Q / (cρ△t);

[0096] In the above formulas, the properties of the cooling medium include freezing point, boiling point, density, and specific heat capacity. C represents specific heat capacity, which indicates the ability of a substance to increase its temperature. The unit of specific heat capacity is joules per kilogram per degree Celsius. m: the mass of the object. Δt represents the change in temperature, i.e., the temperature increase (or decrease) of the object. ρ: the density of the substance, which is the ratio of the mass to the volume of the substance, and the unit is kilograms per cubic meter. v: the volume of the substance, and the unit is cubic meters.

[0097] Finally, set the amplification factor to determine the flow rate;

[0098] S3. Calculate the head of the primary circulation pump, select the pipe specifications, and determine the pipe specific friction resistance based on the selected pipe specifications.

[0099] The formula for calculating pipeline resistance loss is △P=L·△p.

[0100] L = pipe + elbow + tee + valve group + plate heat exchanger assembly + server, which is the equivalent length of the most unfavorable loop in one cycle;

[0101] △p: Pipeline frictional resistance; the head of the primary circulation pump is greater than △P.

[0102] S4. Calculate the flow path and head of the secondary circulation pump. The calculation process is the same as that of the primary circulation pump. The difference is that L = pipe + elbow + valve group + heat exchanger assembly + heating terminal, which is the equivalent length of the most unfavorable loop in the secondary circulation.

[0103] S5. Plate heat exchanger component selection: The power of the plate heat exchanger component is consistent with the power of multiple servers, or slightly larger than the sum of the power of multiple servers. Then, the plate heat exchanger component is selected based on the temperature difference between the primary supply and return water and the temperature difference between the secondary supply and return water, and the heat exchange area is calculated.

[0104] S6. The selection of pipelines, fittings, and valve groups is determined by rounding up the flow rate of the primary and secondary circulation pipelines. The economical friction ratio pipeline is selected, and the riser uses square pipes, which can make more efficient use of space while maintaining a similar friction ratio. Fittings and valve groups are selected with the same pipe diameter.

[0105] After completing the above calculations, the structural layout needs to be planned so that the length and width of the CDU are equal to the length and width of the rack, and the height is minimized to leave space for server placement. If the electric three-way throttle valve is installed at the inlet of the heat exchange component, a diverting tee should be selected; if it is installed at the outlet of the plate heat exchange component, a confluence tee should be selected.

[0106] The structural layout of Implementation Example 1-RACKCAB is as follows: the primary circulation pump and the secondary circulation pump are arranged in parallel vertically, with the primary circulation pump located above the secondary circulation pump and positioned on one side of the cabinet. The dry cooler fan and the plate heat exchanger assembly are arranged vertically and in parallel on the same side, located on the side of the cabinet away from the primary circulation pump. After the primary circulation pump and the secondary circulation pump are arranged vertically and alternately, the total vertical space occupied by them is not greater than the total height of the plate heat exchanger assembly or the air cooler fan. The middle position on both sides is used for laying pipelines.

[0107] The inlet and outlet are centrally laid horizontally and parallel, located at the bottom of the CDU structure. From left to right, they are: cold water inlet 5 of the primary circulation pipeline, hot water return 6 of the primary circulation pipeline, hot water outlet 7 of the secondary circulation pipeline, and cold water return 8 of the secondary circulation pipeline. The primary circulation pipeline path is as follows: Cooling medium enters the primary circulation pipeline through the cold water inlet, cooling multiple servers. The medium then heats up, passing through an electric three-way regulating valve. Part of the heated medium enters the heat exchanger assembly, while the other part flows back to the dry cooler fan through the three-way valve, thus forming the primary circulation pipeline. The secondary circulation pipeline: enters the heat exchanger assembly... After being heated, the medium is heated by heat exchange. The plate heat exchanger outputs the heated medium as a heat source and supplies it into the secondary circulation pipeline to achieve waste heat recovery and reuse. During the reuse process, the medium in the secondary circulation pipeline cools down and is returned to the plate heat exchanger for heat exchange again by the secondary circulation pump. The waste heat utilization part forms the secondary circulation pipeline. Furthermore, the upper end of the plate heat exchanger is connected to the hot water return port of the primary circulation pipeline and the hot water outlet of the secondary circulation pipeline, and the lower end is connected to the cold water inlet of the primary circulation pipeline and the cold water return port of the secondary circulation pipeline. The upper end has a heat source inlet and a heat source outlet, and the lower end has a low temperature inlet and a low temperature outlet, which meets the heat exchange requirements of the maximum path and has high heat exchange efficiency.

[0108] The structural layout of HYDROCAB in Embodiment 2 is as follows: the primary circulation pump and the secondary circulation pump are arranged in parallel left and right, located on one side of the cabinet. The dry cooler fan is arranged horizontally, and its center line in the length direction is parallel to the axis of the primary circulation pump. The plate heat exchanger assembly is located at the upper end of the dry cooler fan, and both are located on one side of the cabinet in the length direction. The tail ends of the primary circulation pump and the secondary circulation pump are located near the rear end of the cabinet. The side of the plate heat exchanger assembly and the front end of the cabinet are used for laying pipelines.

[0109] The inlet and outlet are centrally laid horizontally and parallel, located at the bottom of the CDU structure. From left to right, they are the cold water return port of the secondary circulation pipeline, the hot water outlet of the secondary circulation pipeline, the cold water inlet of the primary circulation pipeline, and the hot water return port of the primary circulation pipeline. The primary circulation pipeline path is as follows: the cooling medium enters the primary circulation pipeline through the cold water inlet to cool multiple servers. Then, the medium heats up and enters the plate heat exchanger assembly as a heat source for heat exchange. After heat exchange, the high-temperature medium passes through an electric three-way regulating valve. Part of the heated medium enters the plate heat exchanger assembly, and the other part flows back to the dry cooler fan through the three-way valve, thus forming the primary circulation pipeline. Secondary circulation pipeline: The heated medium entering the plate heat exchanger assembly undergoes heat exchange, and the heated medium output by the plate heat exchanger assembly serves as a heat source to supply the secondary circulation pipeline, realizing waste heat recovery and reuse. During the reuse process, the medium in the secondary circulation pipeline cools down and is returned to the plate heat exchanger assembly for further heat exchange via a secondary circulation pump. This forms the secondary circulation pipeline for the waste heat utilization portion. Furthermore, the front end of the plate heat exchanger assembly, near the cabinet, connects to the hot water return port of the primary circulation pipeline and the hot water outlet of the secondary circulation pipeline, while the rear end connects to the cold water inlet of the primary circulation pipeline and the cold water return port of the secondary circulation pipeline. With one heat source inlet and one heat source outlet at the front end, and one low-temperature inlet and one low-temperature outlet at the rear end, the heat exchange demand is maximized, resulting in high heat exchange efficiency.

[0110] More preferably, the cabinet has a frame structure, housing multiple servers with gaps between adjacent servers for the arrangement of a primary circulation water circuit. The primary circulation pipeline includes, but is not limited to, a dry cooler fan, and can also use other liquid-cooled servers, as long as a cooling medium supply source is available. It also includes a primary circulation main inlet pipe 2 and a primary circulation main return pipe 3. Each server corresponds to one inlet branch and one outlet branch. The primary circulation main inlet pipe enters the cooling area of ​​multiple servers simultaneously through multiple inlet branches, and then flows back to the primary circulation main return pipe through the outlet branches. Each inlet branch and each outlet branch is equipped with a valve to control the water flow. The opening and closing of each valve can be determined and adjusted according to the actual number of servers arranged in the cabinet to meet the cooling needs of servers of different sizes, ensuring targeted and efficient cooling and avoiding unnecessary energy waste.

[0111] It should be noted that the cooling medium in this application is water, but other cooling media can also be used. There are no specific limitations, as long as the cooling requirements are met. The water outlet and the like described in this application refer to the liquid outlet end, and water is one of the embodiments.

[0112] More preferably, the primary circulation main inlet pipeline from the dry cooler fan end to the server end is equipped with a first valve V003, a primary water circulation flow meter FIT01, and a primary water inlet temperature signal meter TT01 in sequence. The primary circulation main return water pipeline from the server end to the dry cooler fan end is equipped with a primary water return temperature signal meter TT02, a primary circulation water pump P01, an electric three-way regulating valve V001, and a second valve V002 in sequence. The primary water circulation flow meter FIT01 feeds back a signal to the control component. The control component compares the feedback value of the primary water circulation flow meter FIT01 with the set target flow rate through the PID algorithm module, and then adjusts the frequency of the primary circulation water pump so that the value of the primary water circulation flow meter FIT01 matches the set target flow rate.

[0113] One of the ports of the electric three-way regulating valve V001 is connected to one of the secondary circulation inlet pipes of the secondary circulation pipeline. The secondary circulation pipeline also includes a plate heat exchanger assembly. The inlet of the plate heat exchanger assembly has two inputs: one is a secondary circulation inlet pipe connected to the electric three-way regulating valve V001, serving as the heat source for heat exchange; the other is a water supply pipe connected to the outside, which is the water source cooled after waste heat utilization. That is, after the medium in the secondary circulation pipeline is cooled by circulation, it flows back to the plate heat exchanger assembly through the secondary circulation water pump for further heat exchange and external supply of hot water. The secondary circulation inlet main pipe is equipped with a secondary circulation water pump P02 and a secondary water return temperature signal meter TT11. The water return temperature signal meter TT11 feeds back the signal to the control component. At the same time, outdoor temperature signal meter TT21 and indoor temperature signal meter TT22 are set to indicate the temperature inside the heated room. Both outdoor temperature signal meter TT21 and indoor temperature signal meter TT22 are electrically connected to the control component and feed back the real-time temperature to the control component. The outlet of the plate heat exchanger is also divided into two branches. One branch returns the cooled medium to the primary circulation main inlet pipe in the primary circulation pipeline and connects between the first valve V003 and the primary water circulation flow meter FIT01. The other branch is connected to the external heat source demand component. Waste heat utilization can also be used in multiple fields, as detailed below.

[0114] Heating: Any area with heating needs, such as apartments, villas, shopping malls, restaurants, office buildings, stadiums, theaters, factories, warehouses, agricultural greenhouses, and fresh air preheating. These areas are mostly densely populated areas with certain heating requirements. Moreover, in the current social environment, densely populated areas have a large amount of big data processing and often have server racks. The technical solution of this application can be used to re-recover waste heat.

[0115] Hot water: domestic hot water, swimming pool heating, fish pond heating, etc., to meet daily water needs;

[0116] Other: Drying, high-temperature sterilization, steam generator preheating, and other parts that require heat.

[0117] More preferably, when the heat source supply of the primary circulation pipeline cannot meet the heat recovery requirements, the heat source supply pipeline connected to the outside can serve as a supplement, so that the entire heat recovery utilization can operate well and meet the usage requirements. Of course, the structure of this application does not have an external heat source, and it makes full use of the server's own heat for recovery and utilization, which is environmentally friendly.

[0118] Before explaining the steps of different control methods, the various signals or numerical codes are first described in the table below.

[0119]

[0120]

[0121] The control method for single-pass flow control is as follows:

[0122] Manually set a target flow value of FIT91, which should be displayed on the settings screen.

[0123] The values ​​of FIT91 and FIT01 are compared, and the frequency of the primary circulating water pump P01 is adjusted by the PID algorithm module so that FIT01 is infinitely close to FIT91.

[0124] The method for controlling the primary return water temperature is as follows:

[0125] Set the primary return water target temperature TT91; use the PID algorithm module to adjust the opening degree and speed of V001 and G01 / G02; make TT01 track TT91.

[0126] In detail: Manually set a single target temperature value TT91(±2), and the value and range should be displayed on the settings screen.

[0127] The dry cooler passage of the electric three-way regulating valve V001 is 100%, and the plate heat exchanger assembly passage is 0%.

[0128] The values ​​of TT91 and TT01 are compared, and the frequency of G01 / G02 is adjusted by the PID algorithm module so that TT01 is infinitely close to TT91.

[0129] The control method for waste heat utilization mode is as follows:

[0130] Set the primary return water target temperature TT91 and the secondary return water target temperature TT92; compare TT92 with TT11 to determine whether waste heat utilization is needed; use the PID algorithm module to adjust the opening degree and speed of V001 and G01 / G02; make TT01 track TT91; after stabilizing for a period of time, return to the first step to readjust. The detailed steps are as follows:

[0131] 1. Manually set a primary target temperature value TT91 (±2℃). This value and range should be displayed on the setting screen. Manually set a secondary target temperature value TT92 (±2℃). This value and range should be displayed on the setting screen.

[0132] 2. Compare the values ​​of TT11 and TT92. If TT11≥TT92, execute (3); if TT11<TT92, execute (5).

[0133] 3. The dry cooler passage of the electric three-way regulating valve V001 is 100%, the plate heat exchanger assembly passage is 0%, the values ​​of TT91 and TT01 are compared, and the frequency of G01 / G02 is adjusted by the PID algorithm module so that TT01 is infinitely close to TT91.

[0134] 4. The set time interval time02 will start timing after the heating balance is reached. After the timing ends, the system will automatically return to (2) for readjustment. The readjustment time interval requirement is displayed on the setting screen.

[0135] 5. The dry cooler passage of the electric three-way regulating valve V001 is 0%, and the plate heat exchanger assembly passage is 100%.

[0136] 6. Compare the values ​​of TT01 and TT91. If TT01 > TT91, execute (7). If TT01 < TT91, execute (8). If TT01 = TT91, execute (9).

[0137] 7. The dry cooler passage is gradually increased, and the plate heat exchanger assembly passage is gradually decreased. When the plate heat exchanger assembly passage opening is ≤20%, the dry cooler fan G01 / G02 adjusts the speed through the PID algorithm module to gradually increase until the effect of TT01=TT91 is achieved in step 9.

[0138] 8. The speed of the dry cooler fan G01 / G02 is gradually reduced by adjusting the PID algorithm module. When the dry cooler fan stops, the dry cooler passage gradually decreases and the heat exchanger component passage gradually increases until the effect of TT01=TT91 in step 9 is achieved.

[0139] 9. Electric valve V001 maintains its current opening and G01 / 02 maintains its current speed.

[0140] 10. The set time interval time02 will start timing after the heating balance is reached. After the timing ends, the system will automatically return to (2) for readjustment. The readjustment time interval requirement is displayed on the setting screen.

[0141] 11. There are two setting parameters on the PLC panel: time01 for each movement of the three-way valve and OP01 for each movement. The upper limit is set to 30 seconds and 10% opening to prevent accidental operation.

[0142] The secondary temperature control method, namely the climate compensation automatic control method, is as follows:

[0143] Calculate the secondary return water target temperature TT94 based on the outdoor temperature TT21; adjust the frequency of P02 using the PID algorithm module to make TT11 track TT94; control the terminal temperature; set the indoor target temperature TT96; adjust the frequency of P02 using the PID algorithm module to make TT22 track TT96; control the heating circulating water temperature; set the heating return water target temperature TT92; adjust the frequency of P02 using the PID algorithm module to make TT11 track TT92. Detailed steps are as follows:

[0144] 1. Set the base outdoor temperature TT93, base circulating temperature TT95, compensation curvature 1CT01, compensation curvature 2CT02, curvature selection interval division value TT97 / TT98, and system recharge time value time03. All values ​​are displayed on the screen and can be modified;

[0145] 2. The outdoor temperature probe measures the current outdoor temperature TT21;

[0146] 3. Calculate △T, △T = TT93 - TT21;

[0147] 4. Determine which interval △T is in. If TT98℃≤△T≤TT97, then execute (5). If △T>TT97 or △T<TT98, then execute 6.

[0148] 5. Calculations were performed using CT01;

[0149] 6. Calculations were performed using CT02;

[0150] 7. Calculate the cycle temperature TT94 = TT95 + (ΔT × curvature), and this value needs to be displayed on the screen;

[0151] 8. Calculate the target value of the cycle temperature TT94 for TT11;

[0152] 9. The pump speed is adjusted by the PID algorithm module to control the circulation flow, so that the heating return water temperature TT11 approaches TT94 infinitely.

[0153] 10. Set a time value time03, which is used to measure the outdoor temperature every hour to obtain the current calculated cycle temperature TT94.

[0154] The above three modes can be connected in parallel and can be switched manually.

[0155] The terminal temperature control system is as follows:

[0156] Manually set an indoor temperature target value TT96(±2), and this value and range should be displayed on the settings screen;

[0157] The values ​​of TT22 and TT96 are compared, and the frequency of P02 is adjusted using a PID algorithm module to make TT22 as close as possible to TT96.

[0158] The temperature of the heating circulating water is controlled as follows:

[0159] Manually set a target value for the heating return water temperature TT92 (±2), and this value and range should be displayed on the setting screen; compare the values ​​of TT11 and TT92, and use the PID algorithm module to adjust the frequency of P02 so that TT11 is infinitely close to TT92.

[0160] The following is an example.

[0161] Cabinet dimensions: Similar to a standard server rack, width * depth * height = 800 * 1000 * 2200 mm

[0162] Server load: 10-15 servers, occupying the upper half of the rack;

[0163] Cooling Distribution Unit (CDU): The length and width are equal to the length and width of the rack, and the height is minimized to leave space for server placement. It occupies the lower half of the rack and is assembled into a skid. After forming a skid-mounted structure, it is easy to quickly disassemble and assemble as a component, which facilitates rapid relocation and assembly. It also facilitates overall maintenance and upkeep. The main equipment includes a primary circulating water pump, a secondary circulating water pump, a plate heat exchanger assembly, a water storage tank, a makeup water pump, a flow meter, an electric three-way regulating valve, a filter, a valve assembly, and pipes, etc.

[0164] The CDU is designed as follows:

[0165] Heat exchange power

[0166] Based on the dimensions of the servers and racks, the design is as follows: RACKCAB has 12 rack slots and HYDROCAB has 15 rack slots, occupying a total of 1400mm of upper space. The power of the servers is 12*7.5=90kW and 15*5.5=82.5kW respectively.

[0167] Based on the power calculation amplification factor and rounding, the heat exchange power of the CDU can be determined to be 100kW.

[0168] The difference between RACKCAB and HYDROCAB is that RACKCAB servers are arranged in parallel, with the water inlet on one side and the water outlet on the other side, presenting an overall structure of left inlet and right outlet. For HYDROCAB servers, an overall structure of upper inlet and lower outlet is adopted. Regardless of which structure the server adopts, the inlet and outlet branches are equipped with individually controlled valves, and they all converge into the main inlet and outlet pipes.

[0169] Primary circulating water pump:

[0170] The server's maximum inlet and outlet water temperatures are 45 / 55℃, which gives us a temperature difference of Δt1 = 10℃ for one cycle.

[0171] The server's primary circulation medium is pure water, with the following properties: freezing point 0℃, boiling point 100℃.

[0172] Density 999.84 kg / m³ 3 Specific heat capacity: 4.2 kJ / kg·K.

[0173] Substituting the above data into the heat calculation formula Q=cm△t, the flow rate of the primary circulation pump can be calculated as:

[0174] Q = cmΔt;

[0175] Q = c(ρv)Δt;

[0176] V=Q / (cρ△t)=100*3600 / (4.2*1000*10)=8.57m 3 / h;

[0177] Calculating with a magnification factor of 1.1, the flow rate should be 9.427 m³ / s. 3 / h;

[0178] C represents specific heat capacity; it indicates the ability of a substance to increase its temperature by the amount of heat required. The unit of specific heat capacity is joules per kilogram per degree Celsius; m: the mass of the object; Δt represents the change in temperature, that is, the temperature increase (or decrease) of the object. When heat is absorbed, Δt refers to the increase in temperature; when heat is released, Δt refers to the decrease in temperature. When heat is absorbed, Q = cmΔT_rise (actual temperature increase minus initial temperature); when heat is released, Q = cmΔT_fall (actual initial temperature minus temperature decrease), or Q = cmΔT = cm(T_final - T_initial). When Q > 0, it is heat absorption; when Q < 0, it is heat release.

[0179] ρ: represents the density of a substance, which is the ratio of mass to volume, and the unit is kilograms per cubic meter; v: represents the volume of a substance, and the unit is cubic meters.

[0180] According to the "Hydraulic Calculation Table for Hot Water Pipelines", the pipe resistance is approximately 713.9 Pa / m and the pipe cross-sectional area is approximately 1900 mm² when a DN50 pipe is selected for this flow rate. 2 When a DN65 pipe is selected, the pipe resistance is approximately 128.3 Pa / m, and the pipe cross-sectional area is approximately 3300 mm². 2 .

[0181] Due to limited space inside the cabinet, most of the pipes are 40×40mm square pipes, the interface agent is approximately the cross-sectional area of ​​DN50 pipes, and the pipe specific friction is taken as 713.9Pa / m.

[0182] Based on preliminary design, the equivalent length of the most unfavorable loop in a single cycle is approximately the sum of the pipe, elbow, tee, valve assembly, heat exchanger assembly, and server.

[0183] =6+30+45+85+120+150=296m.

[0184] Substitute the above data into the formula for calculating pipeline resistance loss:

[0185] ΔP=L·Δp=296×713.9=211,314.4Pa=0.211MPa.

[0186] Calculating the amplification factor of 1.1, the flow rate should be 0.2311 MPa.

[0187] Therefore, the head of the circulating pump should be greater than 23m to meet the requirements.

[0188] Based on the above calculations, the parameters of the primary circulating water pump can be determined:

[0189] Q = 10m 3 / h; H=23m.

[0190] The calculations for the secondary circulating water pump are as follows.

[0191] The typical heating system design has a circulating temperature difference of 10℃, which perfectly matches the inlet and outlet water temperature difference of the server. Therefore, the secondary circulation temperature difference Δt2 = 10℃.

[0192] Because the server needs to operate year-round and requires an outdoor cooling source, a 50% volume concentration ethylene glycol solution is selected as the antifreeze medium inside the secondary piping. The solution properties are: freezing point -37.9℃, boiling point 107.8℃, and density 1063.66 kg / m³. 3 Specific heat capacity: 3.358 kJ / kg·K.

[0193] Substituting the above data into the heat calculation formula Q=cm△t, the flow rate of the secondary circulation pump can be calculated as:

[0194] Q = cmΔt

[0195] Q = c(ρv)Δt

[0196] V=Q / (cρ△t)=100*3600 / (3.358*1063.66*10)=10.079m 3 / h

[0197] Calculating with a magnification factor of 1.1, the flow rate should be 11.0869 m³ / s. 3 / h

[0198] Considering that the equipment is used in parallel with 4 units (inclusive) or less, the total heating load will not exceed 400kW. 400kW can meet the heating demand of about 8,000 square meters. The average pipe friction is about 120Pa / m. The estimated equivalent length of the most unfavorable loop in the secondary circulation is pipe + elbow + valve group + plate heat exchanger assembly + heating terminal = 1000 + 500 + 200 + 120 + 500 = 2320m.

[0199] Substitute the above data into the formula for calculating pipeline resistance loss:

[0200] ΔP=L·Δp=2320×120=278,400Pa=0.278MPa.

[0201] The calculated flow rate, based on a magnification factor of 1.1, should be 0.3058 MPa.

[0202] Therefore, the head of the circulating pump should be greater than 30m to meet the requirements.

[0203] Based on the above calculations, the parameters of the primary circulating water pump can be determined:

[0204] Q = 11m 3 / h; H=30m.

[0205] Calculation of water supply pump parameters.

[0206] The total water volume of the circulation system is calculated to be approximately 300L. The initial water replenishment time is designed to be 30 minutes, so the flow rate of the water replenishment pump should not be less than 10L / min.

[0207] The highest point of the server is about 2.2m away from the water supply point, and the server's maximum pressure resistance is about 3.5bar, so the head of the water supply pump should be between 2.5 and 3.5m.

[0208] Calculation of panel-type panel heat exchanger components.

[0209] The heat exchange capacity has been confirmed to be 100kW.

[0210] If the logarithmic temperature difference is set to 5℃, then the heat exchange supply and return water temperatures can also be confirmed through the above calculation process:

[0211] Primary supply and return water temperature: 45 / 55℃; Secondary supply and return water temperature: 40 / 50℃.

[0212] The above data was used to calculate the selection of panel-type heat exchanger components.

[0213] The heat exchange area is 6.496㎡; the pressure drop in the primary cycle is 38.6kPa; and the pressure drop in the secondary cycle is 26.5kPa.

[0214] The calculation of the plate-type plate-type heat exchanger can be achieved by referring to existing selection manuals or selection apps on the market. This is a well-known technical method, and the same principle applies to the structure of this application.

[0215] Pipelines, fittings, and valve assemblies are determined.

[0216] Based on the above calculations, the flow rates for the first and second quadratic cycles are rounded up to 11 m³. 3 According to the table "Hydraulic Calculation Table for Hot Water Pipes", DN50 pipes should be selected for their economical specific friction resistance, while 40×40mm square pipes should be selected for the riser, which can make more efficient use of space while maintaining a similar specific friction resistance.

[0217] The valve should be selected with the same diameter as the pipeline.

[0218] The flow meter is the same as the valve, and the same pipe diameter should be selected.

[0219] The electric three-way regulating valve is also selected with the same pipe diameter. When it is installed at the inlet of the plate heat exchanger unit, a diversion tee is selected, and when it is installed at the outlet of the plate heat exchanger unit, a confluence tee is selected.

[0220] The above calculations can be used to select all equipment and obtain the equipment's external dimensions before starting the equipment layout.

[0221] Design principles: proximity principle, non-interference principle, and power supply and drainage principle. The proximity principle not only aims to simplify the pipeline but also to reduce the number of bends and lower pipeline resistance. The non-interference principle ensures that equipment, pipelines, and valve groups do not interfere with each other, making it convenient to replace equipment and valve groups, and ensuring simple and convenient maintenance and operation with high installation feasibility. The power supply and drainage principle is for safety considerations, preventing the occurrence of interlocking leakage accidents that could lead to greater losses.

[0222] The structure described above can be used for small-scale (below 100kW) liquid-cooled server deployment, i.e., integrated independent cabinet; or for large-scale liquid-cooled server deployment, i.e. parallel cabinet operation. Waste heat utilization can also be used in multiple fields, as detailed below.

[0223] Heating: Any area with heating needs, such as apartments, villas, shopping malls, restaurants, office buildings, stadiums, theaters, factories, warehouses, agricultural greenhouses, and fresh air preheating. These areas are mostly densely populated areas with certain heating requirements. Moreover, in the current social environment, densely populated areas have a large amount of big data processing and often have server racks. The technical solution of this application can be used to re-recover waste heat.

[0224] Hot water: domestic hot water, swimming pool heating, fish pond heating, etc., to meet daily water needs;

[0225] Other: Drying, high-temperature sterilization, steam generator preheating, and other parts that require heat.

[0226] During the application process, enterprises can meet the needs of heating and daily hot water supply. Hot water supply is an essential requirement for many office areas or factories. Factories with production workshops or accommodation areas can meet the daily bathing needs of employees, especially in winter. At the same time, water heating can be used for office heating, which is particularly suitable for areas where heating is inconvenient. Moreover, there is no additional energy consumption, and waste heat is fully recovered, improving the environment.

[0227] Compared with existing heating products on the market, such as electric boilers and wall-hung boilers, the advantages of this application are as follows.

[0228] 1. Energy-saving and efficient: With a thermal efficiency of up to 97%, it can be considered as one unit of energy that simultaneously meets the server's operating and heat requirements.

[0229] 2. Low carbon emissions: The carbon emissions from server operation and heating are reduced from two parts to one.

[0230] 3. Additional benefits: While keeping warm, you can also generate server computing power revenue.

[0231] 4. Highly integrated and easy to install, the built-in pump station simplifies the on-site installation process, and can be put into production immediately after connecting cables and pipelines.

[0232] The foregoing has provided a detailed description of one embodiment of the present invention, but this description is merely a preferred embodiment and should not be construed as limiting the scope of the invention. All equivalent variations and modifications made within the scope of the claims of this invention should still fall within the patent coverage of this invention.

Claims

1. A control method for an integrated server rack capable of waste heat recovery and utilization, characterized in that: For rack-mounted liquid cooling systems, an integrated server rack capable of waste heat recovery is installed. This rack includes multiple servers, a cooling distribution unit, a waste heat recovery module, and control components. The cooling distribution unit includes a primary circulation pipeline, which serves as the cooling source. It includes dry cooler fans G01 / G02 and an electrically operated three-way regulating valve V001. Through the circulation of the cooling medium, multiple servers are cooled and dissipated. The method for controlling the primary return water temperature is as follows: Set the primary return water target temperature TT91; use the PID algorithm module to adjust the opening and speed of the electric three-way regulating valve V001 and the dry cooler fan G01 / G02; make the primary water inlet temperature signal meter TT01 track TT91; the waste heat utilization module includes a secondary circulation pipeline for waste heat recovery to meet the heat supply requirements of external heat source components. The primary circulation pipeline and the secondary circulation pipeline are adjusted online through the electric three-way regulating valve to adjust the flow rate of the medium after heating in the primary circulation pipeline and the secondary circulation pipeline, so as to realize the switching of the entire system in multiple modes of primary temperature control, waste heat utilization mode and secondary temperature control. The secondary circulation pipeline includes a secondary circulation water pump P02 and a secondary water return temperature signal meter TT11; it also includes an outdoor temperature signal meter TT21 and an indoor temperature signal meter TT22, which are used to provide real-time temperature feedback. It also includes plate heat exchangers. The medium heated by the server in the primary circulation pipeline is used as the heat source for the plate heat exchanger. After heat exchange by the plate heat exchanger, part of the cooled medium flows back to the primary circulation pipeline, and the other part of the heated medium is used as the heat source for the secondary circulation pipeline. The control method for the waste heat utilization mode is as follows: Set the primary return water target temperature TT91 and the secondary return water target temperature TT92; compare TT92 with TT11 to determine whether waste heat utilization is needed; adjust the opening and speed of the electric three-way regulating valve V001 and the dry cooler fan G01 / G02 through the PID algorithm module; make TT01 catch up with TT91; after stabilizing for a period of time, return to the first step and readjust; The secondary temperature control method, i.e., the climate compensation automatic control method, is as follows: Calculate the secondary return water target temperature TT94, i.e., the heating cycle temperature TT94, based on the outdoor temperature TT21; adjust the frequency of P02 through the PID algorithm module; make TT11 catch up with TT94; Terminal temperature control: Set the indoor target temperature TT96; adjust the frequency of P02 through the PID algorithm module; make TT22 track TT96; Heating circulation water temperature control: Set the secondary return water target temperature TT92, i.e. the heating return water target temperature; adjust the frequency of P02 through the PID algorithm module; make TT11 follow TT92.

2. The control method for the integrated server rack capable of waste heat recovery and utilization according to claim 1, characterized in that: The control method for the waste heat utilization mode is detailed as follows: 1) Manually set a primary target temperature value TT91 with a tolerance of ±2℃. The value and range are displayed on the setting screen. Manually set a secondary target temperature value TT92 with a tolerance of ±2℃. The value and range are also displayed on the setting screen. 2) Compare the values ​​of TT11 and TT92. If TT11 ≥ TT92, proceed to step 3). If TT11 < TT92, proceed to step 5. 3) The dry cooler passage of the electric three-way regulating valve V001 is 100%, and the plate heat exchanger assembly passage is 0%. The values ​​of TT91 and TT01 are... The values ​​are compared, and the frequency of G01 / G02 is adjusted by the PID algorithm module so that TT01 is infinitely close to TT91; 4) The set time interval time02 will start timing when heat balance is reached. After the timing ends, the system will automatically return to 2 for readjustment. The readjustment time interval requirement is displayed on the setting screen; 5) The dry cooler passage of the electric three-way regulating valve V001 is 0%, and the plate heat exchanger assembly passage is 100%; 6) Compare the values ​​of TT01 and TT91. If TT01 > TT91, then execute 7). If TT01 > TT91, then execute 7). If 1 < TT91, then execute 8); if TT01 = TT91, then execute 9); 7) The dry cooler passage increases slowly, and the heat exchanger assembly passage decreases slowly. When the heat exchanger assembly passage opening is ≤ 20%, the dry cooler fan G01 / G02 adjusts its speed through the PID algorithm module to increase slowly until the effect of TT01 = TT91 is achieved in step 9; 8) The dry cooler fan G01 / G02 adjusts its speed through the PID algorithm module to decrease slowly. When the dry cooler fan stops, the dry cooler passage decreases slowly, and the heat exchanger assembly passage increases slowly until the effect of T in step 9 is achieved. T01 = TT91 effect; 9) Electric valve V001 maintains the current opening and G01 / 02 maintains the current speed; 10) The set time interval time02 will start timing after the heat supply balance is reached. After the timing ends, the system will automatically return to 2) for readjustment. The readjustment time interval requirement is displayed on the setting screen; 11) There are two setting parameters on the PLC panel, namely the adjustment time time01 for each movement of the three-way valve and the adjustment opening OP01 for each movement. The upper limit is set to 30 seconds and 10% opening to prevent misoperation.

3. The control method for the integrated server rack capable of waste heat recovery and utilization according to claim 1, characterized in that: The system includes a cabinet with multiple server bays. Multiple servers are arranged in multiple rows and columns on the server bays. The cabinet is divided into upper and lower parts. The upper part is used to place multiple servers, and the lower part is used to place the cooling distribution unit, heat exchanger components and lay pipelines. The cooling distribution unit forms a skid-mounted structure. The primary circulation pipeline is arranged on the back of the cabinet in a parallel arrangement. There is a soft connection between the pipeline and the cooling distribution unit to prevent vibration of the cooling distribution unit.

4. The control method for the integrated server rack capable of waste heat recovery and utilization according to claim 1, characterized in that: The primary circulation pipeline includes a primary circulation pump, a primary circulation main inlet pipeline, and a primary circulation main return pipeline. Each server corresponds to one inlet branch and one outlet branch. The primary circulation main inlet pipeline simultaneously enters the cooling areas of multiple servers through multiple inlet branches, and then returns to the primary circulation main return pipeline through the outlet branches. Each inlet and outlet branch is equipped with a valve to control the water flow. The primary circulation main inlet pipeline, from the dry cooler fan end to the server end, is sequentially equipped with a first valve, a primary water circulation flow meter FIT01, and a primary water inlet temperature signal meter TT01. The main return water pipeline from the server end to the dry cooler fan end is equipped with a primary water return temperature signal meter TT02, a primary circulating water pump P01, and a second valve V002. An electric three-way regulating valve V001 is located between the primary circulating water pump P01 and the second valve V002. The primary water circulation flow meter FIT01 feeds back a signal to the control component. The control component uses a PID algorithm module to compare the feedback value of the primary water circulation flow meter FIT01 with the set target flow rate, and then adjusts the frequency of the primary circulating water pump so that the value of the primary water circulation flow meter FIT01 matches the set target flow rate.

5. The control method for the integrated server rack capable of waste heat recovery and utilization according to claim 1, characterized in that: The secondary circulation pipeline includes a secondary circulation pump and a secondary circulation inlet main pipe. The secondary water return temperature signal meter TT11 feeds back the signal to the control component. The outdoor temperature signal meter TT21 and the indoor temperature signal meter TT22 are both electrically connected to the control component and feed back the real-time temperature to the control component.

6. The control method for the integrated server rack capable of waste heat recovery and utilization according to claim 1, characterized in that: The outlet of the plate heat exchanger is divided into two branches. One branch returns the cooled medium to the primary circulation main inlet pipe in the primary circulation pipeline and connects between the first valve V003 and the primary water circulation flow meter FIT01. The other branch is connected to the external heat source demand component.

7. The control method for the integrated server rack capable of waste heat recovery and utilization according to claim 1, characterized in that: When designing the layout, the length and width of the cooling distribution unit should not exceed the length and width of the server rack to reserve space for the server. If the electric three-way throttle valve is installed at the inlet of the board heat exchanger assembly, a split tee should be selected. If the electric three-way throttle valve is installed at the outlet of the board heat exchanger assembly, a merge tee should be selected.

8. The control method for the integrated server rack capable of waste heat recovery and utilization according to claim 1, characterized in that: The product specifications are determined through parameter calculations, following these steps: S1. Determine the total power of multiple servers. Calculate the amplification factor based on the total power and round it to determine the heat exchange power of the cooling distribution unit. S2. Calculate the primary circulation pump flow rate. Based on the extreme inlet and outlet water temperature difference of the servers, obtain the primary circulation temperature difference Δt. Calculate the primary circulation pump flow rate using the following formulas: Q = cmΔt; Q = c(ρv)Δt; V = Q / (cρΔt). In the above formulas, the characteristics of the cooling medium include freezing point, boiling point, density, and specific heat capacity. C represents specific heat capacity, which indicates the ability of a substance to increase its temperature. The unit of specific heat capacity is joules per kilogram per degree Celsius. m: the mass of the object; Δt represents the change in temperature, i.e., the temperature increase (or decrease) of the object; ρ: represents the density of the substance, which is the ratio of the mass to the volume of the substance, in kilograms per cubic meter. v: represents the volume of the substance, in cubic meters; finally, set the amplification factor to determine the flow rate; S3. Calculate the head of the primary circulation pump, select the pipe specifications, and determine the pipe specific friction resistance based on the selected pipe specifications. The pipe resistance loss calculation formula is △P=L·△p, where L=pipe + elbow + tee + valve assembly + heat exchanger assembly + server, i.e., the equivalent length of the most unfavorable loop in the primary circulation; △p: pipe specific friction resistance, and the head of the primary circulation pump is greater than △P. S4. Calculate the flow path and head of the secondary circulation pump. The calculation process is the same as that of the primary circulation pump, except that L=pipe + elbow + valve assembly + heat exchanger assembly + heating terminal, i.e., the secondary circulation... The equivalent length of the most unfavorable loop; S5, plate heat exchanger component selection: the power of the plate heat exchanger component is consistent with the sum of the power of multiple servers, or slightly less than the sum of the power of multiple servers. Then, plate heat exchanger components are selected based on the temperature difference between the primary and secondary supply and return water, and the heat exchange area is calculated; S6, selection and determination of pipelines, fittings, and valve groups: based on the flow rate of the primary and secondary circulation pipelines, round up to the nearest whole number, and select economical specific friction pipes. Square pipes are used for risers, which can make more efficient use of space while maintaining a similar specific friction; fittings and valve groups are selected with the same pipe diameter.

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