Energy-saving temperature and humidity regulation and control air conditioner and regulation and control method

Abstract

The invention provides an energy-saving temperature and humidity regulation and control air conditioner and a regulation and control method, the method is applied to fresh air temperature and humidity regulation and control of indoor air entering a data center, and the method comprises the steps that the real-time air mass flow speed, dry-bulb temperature and relative humidity of a return air inlet part, a return air flow outlet, a fresh air flow inlet and a fresh air outlet part are monitored in real time; the dry-bulb temperature, the moisture content and the relative humidity of the mixed air subjected to heat exchange through the gas cross-flow exchange part are calculated, and the ideal dry-bulb temperature threshold value and the ideal relative humidity threshold value of indoor air are determined; the positions of the dry-bulb temperature and the relative humidity of the mixed air in different temperature threshold intervals are judged, the humidity threshold interval formed by the relative humidity thresholds of the mixed air is further judged, and then the mixed air state is determined according to the positions of the dry-bulb temperature and the relative humidity of the mixed air in different intervals. A hot water coil pipe, a cold water coil pipe or a spraying system or any one or two combinations of the hot water coil pipe, the cold water coil pipe and the spraying system are selected to be started, and mixed air flows out from a fresh air outflow part after being subjected to further temperature and humidity treatment; or, the mixed air directly flows out of the fresh air flowing-out part and is conveyed into a room only by not opening the fresh air purifier. By optimizing the temperature and humidity control method and the equipment operation mode, the indoor environment is accurately adjusted, so that the energy consumption of the air conditioner is reduced, the energy utilization efficiency is improved, and the operation cost is reduced.

Description

Technical Field

[0001] The present invention belongs to the technical field of energy-saving air conditioners, and in particular relates to an energy-saving temperature and humidity control air conditioner and a control method. Background Art

[0002] With the rapid development of digitalization and informatization, data centers, as core infrastructure, are growing in size and energy consumption. The stable operation of data centers has extremely strict requirements on the temperature and humidity of the indoor environment. It is usually necessary to maintain the temperature and humidity within a specific threshold range to ensure the performance and life of servers and other electronic equipment. However, the traditional air-conditioning system has the following problems in the process of temperature and humidity control: 1) High energy consumption problem: The energy consumption of the data center air-conditioning system accounts for more than 30% of the total energy consumption, especially in the high temperature and high humidity summer or low temperature and low humidity winter, the demand for heating, cooling or humidification of fresh air is extremely high. Traditional air-conditioning systems usually operate in a constant mode and do not adjust the strategy according to the dynamic changes of the external environment, resulting in excessive heating, cooling or humidification, causing a lot of energy waste. 2) Insufficient control accuracy When dealing with complex environments, it is difficult for existing air-conditioning systems to achieve high-precision temperature and humidity control requirements, especially in the case of seasonal alternation between the north and the south or sudden climate change, the indoor environment may deviate from the ideal threshold in a short time. Inaccurate control may cause the equipment to operate under high humidity or over-dry conditions, increasing the risk of failure and maintenance costs. 3) Equipment wear and life issues Frequent switching or high-load operation will accelerate the aging of cold water coils, hot water coils and other key components, resulting in a significant increase in equipment maintenance and replacement costs. Long-term high-load operation may also affect the overall efficiency of the air-conditioning system, further increasing operating costs. 4) Insufficient intelligence and automation Traditional air-conditioning systems mostly rely on preset programs and manual control, making it difficult to achieve dynamic optimization and real-time response. Under different seasons and regional climate conditions, the heat exchange capacity of the outside fresh air is not fully utilized, resulting in low energy utilization.

[0003] Therefore, there is an urgent need for an energy-saving air conditioning system based on dynamic temperature and humidity control, efficient heat exchange and intelligent control. The system can dynamically adjust the ratio of fresh air and return air and the temperature and humidity processing strategy according to the environmental conditions of different seasons and regions, thereby achieving the goal of energy saving and consumption reduction while ensuring the stability of data center operation. Summary of the invention

[0004] In view of the above-mentioned defects, the present invention provides a method for controlling an air conditioner for energy saving and temperature and humidity control. The present invention provides the following technical solution: a method for controlling an air conditioner for energy saving and temperature and humidity control, the method is applied to control the temperature and humidity of fresh air entering the indoor air of a data center, comprising the following steps:

[0005] S1: Real-time monitoring of the real-time air mass flow rate, dry bulb temperature and relative humidity of the return air inlet, return air outlet, fresh air inlet and fresh air outlet;

[0006] S2: Calculate the dry bulb temperature T of the mixed air after heat exchange in the gas cross flow exchange section mix , moisture content W mix and relative humidity RH mix , determine the ideal dew point temperature minimum threshold Ideal dry bulb temperature maximum threshold Ideal dry bulb temperature minimum threshold Ideal relative humidity maximum threshold RH ex，max , Ideal relative humidity minimum threshold RH ex，min ;

[0007] S3: Determine the dry bulb temperature T of the mixed air mix The position in the different temperature threshold intervals composed of the temperature thresholds in step S2 determines the dry bulb temperature T of the mixed air. mix After the temperature is within the threshold range, the relative humidity RH of the mixed air is further determined. mix In which humidity threshold interval is it composed of various relative humidity thresholds, and then according to the dry bulb temperature T of the mixed air mix and relative humidity RH mix The mixed air state is determined by the different interval positions. The hot water coil, cold water coil or spray system or any one or a combination of two is selected to be turned on. After further temperature and humidity treatment, the mixed air flows out from the fresh air outlet. Alternatively, none of them are selected to be turned on, and only the mixed air flows out directly from the fresh air outlet and is delivered to the room.

[0008] Furthermore, in step S2, the dry-bulb temperature T of the mixed air is calculated. mix , moisture content W mix and relative humidity RH mix The formula is as follows:

[0009]

[0010]

[0011] Among them, W in,new are the relative humidity RH of the fresh air flowing into the fresh air inlet obtained by real-time monitoring according to step S1 in,new and dry bulb temperature T in,new The calculated humidity content of the fresh air flowing into the fresh air inlet, W in,re is the relative humidity RH of the return air flowing into the return air inlet portion obtained by real-time monitoring according to step S1 in,re and dry bulb temperature T in,reThe calculated humidity content of the return air flowing into the return air inlet is:

[0012]

[0013] According to the calculated mixed air humidity W mix , and further calculate the relative humidity of the mixed air:

[0014]

[0015] in, T in,new and W in,new They are the fresh air inflow velocity, dry-bulb temperature and relative humidity of the fresh air at the fresh air inlet obtained by real-time monitoring. T in,re and W in,re They are respectively the return air inflow velocity, the return air dry bulb temperature and the return air relative humidity of the return air inlet part obtained by real-time monitoring; are the fresh air outflow velocity at the fresh air outflow part and the return air outflow velocity at the return air outlet respectively; e s (T mix ) is the mixed air at dry bulb temperature T mix Saturated water vapor pressure, e s (T in,re ) is the return air flowing into the return air inlet at the dry bulb temperature T in,re Saturated water vapor pressure under s (T in,new ) is the dry-bulb temperature T of the fresh air flowing into the fresh air inlet in,new The saturated water vapor pressure under; P is the air pressure, P = 101325Pa.

[0016] Furthermore, in step S3, the dry-bulb temperature T of the mixed air is mix and relative humidity RH mix The mixed air processing methods between different temperature threshold ranges and humidity threshold ranges include the following situations:

[0017] 1) If The hot water coil is controlled to be turned on to heat the mixed air isothermally, and then the spray system (5) is turned on to continue to humidify the heated mixed air isothermally;

[0018] 2) If And RH mix >RH ex,max , then control to open the cold water coil to cool and dehumidify the mixed air, and then open the hot water coil to further heat the cooled and dehumidified mixed air;

[0019] 3) If And RH ex,min ≤RHmix ≤RH ex,max , then turn on the hot water coil to heat the mixed air with equal humidity;

[0020] 4) If And RH mix <RH ex,min , then turn on the hot water coil to heat the mixed air isothermally, and then turn on the spray system to continue isothermally humidifying the heated mixed air;

[0021] 5) If And RH mix >RH ex,max , then turn on the cold water coil to cool and dehumidify the mixed air;

[0022] 6) If And RH ex,min ≤RH mix ≤RH ex,max , then the dynamic heat exchange balance equation of cold and hot air in the cross-flow gas heat exchange core is constructed to solve the optimal inflow and outflow speeds of fresh air and return air;

[0023] 7) If And RH mix <RH ex,min , only the spray system is turned on to perform isothermal humidification on the mixed air;

[0024] 8) If And RH mix >RH ex,max , only the cold water coil is turned on to cool and dehumidify the mixed air;

[0025] 9) If And RH ex,min ≤RH mix ≤RH ex,max , then turn on the cold water coil at the same time to cool the mixed air;

[0026] 10) If And RH mix <RH ex,min , then turn on the cold water coil and spray system to humidify, cool and reduce the temperature of the mixed air.

[0027] Furthermore, when the dry-bulb temperature of the mixed air is T mix and relative humidity RH mix The situations between different temperature threshold intervals and humidity threshold intervals are as follows: And RH ex,min ≤RH mix ≤RH ex,max When the cross-flow gas heat exchange core cold and hot air dynamic heat exchange balance equation is constructed, the optimal fresh air and return air inflow and outflow rates are solved, including the following steps:

[0028] S301: Calculate the enthalpy value i of the fresh air flowing into the gas cross-flow exchange part from the fresh air inlet in,new , the enthalpy value i of the mixed air flowing out of the gas cross exchange section mix , the enthalpy value i of the return air entering the return air inlet into the gas cross-flow exchange part in,re , the air enthalpy value i of the gas cross-flow exchange section flowing out of the return air outlet out,re :

[0029] i in,new =c a T in,new +W in,new (c s T in,new +i fg );

[0030] i mix =c a T mix +W mix (c s T mix +i fg );

[0031] i in,re =c a T in,re +W in,re (c s T in,re +i fg );

[0032] i out,re =c a T out,re +W out,re (c s T out,re +i fg );

[0033] Among them, c a is the specific heat capacity of dry air, c a = =1.005 kJ / (kg·℃); c s is the specific heat capacity of water vapor, c s =1.82kJ / (kg·℃),i fg is the latent heat of vaporization of water, i fg =2500kJ / kg; T out,re and W out,re They are respectively the outflow return air dry bulb temperature and the outflow return air humidity content at the return air outlet obtained by real-time monitoring;

[0034] S302: Construct the dynamic heat exchange balance equation of cold and hot air in the cross-flow gas heat exchange core:

[0035]

[0036] h tr is the convective heat transfer coefficient, Among them, Nu in,new is the Nusselt number of the fresh air flowing into the fresh air inlet, Nu in,re is the Nusselt number of the return air flowing into the return air inlet, k is the thermal conductivity of air, k = 0.026W (m·K); L is the side length of the square section of the cross-flow gas heat exchange core; Re in,new , Pr in,new are the Reynolds number and Prandtl number of the fresh air flowing into the fresh air inlet, Pr in,new =(c a +W in,new c a )μ / k; Re in,re , Pr in,re are the Reynolds number and Prandtl number of the return air flowing into the return air inlet, Pr in,re =(c a +W in,re c a )μ / k; μ is the air dynamic viscosity, μ = 18.1 = μPa·s; ρ in,new is the density of the fresh air flowing into the fresh air inlet, ρ in,re is the density of the return air flowing into the return air inlet;

[0037] Where, =R is the specific gas constant of air, R = 287 J / (kg·K);

[0038] S303: Under the limitation of the equilibrium equation constructed in step S302, a cold and hot air enthalpy exchange maximization model is constructed to solve the optimal fresh air and return air inflow and outflow speeds:

[0039]

[0040] in, The gas coupling flow velocity of the fresh air and the return air in the gas cross-flow heat exchange section (11);

[0041]

[0042] Then according to the optimal fresh air inflow speed obtained Optimal fresh air outflow speed Optimal return air inflow velocity Optimal return air outflow speed The fresh air inflow velocity at the fresh air inlet, the fresh air outflow velocity at the fresh air outflow portion, the return air inflow velocity at the return air inlet portion and the return air outflow velocity at the return air outlet are controlled respectively.

[0043] Furthermore, in the temperature and humidity processing process except for the case 6) and the case 2), when only the cold water pan is turned on, only the hot water coil is turned on, only the spray system is turned on, when the cold water coil and the spray system are turned on at the same time, or when the hot water coil is turned on first and then the spray system is turned on, the optimal dry-bulb temperature of the fresh air outflowing from the fresh air outflow part is controlled. and optimal relative humidity and / or optimal spray speed of the spray system The solution model is as follows:

[0044]

[0045] Among them, i fg is the latent heat of vaporization of water, i fg =2500kJ / kg; c a is the specific heat capacity of dry air, c a =1.005 kJ / (kg·℃); and points The expected fresh air dry-bulb temperature, expected fresh air relative humidity and expected fresh air moisture content of the fresh air flowing out of the fresh air outlet are T out,new The dry-bulb temperature of the fresh air flowing out of the fresh air outflow part is monitored in real time; is the spray speed of the spray system; α is the opening coefficient of the spray system; β is the calculation coefficient for the latent heat of mixed air or evaporation heat loss;

[0046]

[0047] The corresponding working time of the hot water coil and / or the cold water coil and / or the spray speed of the spray system are further controlled according to the solution results.

[0048] Further, for the second case, the optimal fresh air dry-bulb temperature of the fresh air outflow portion that minimizes the air conditioning energy consumption is constructed. Optimal fresh air relative humidity And control the midpoint dry bulb temperature T ter Solve the equation:

[0049]

[0050] 18℃≤T out,new ≤27℃

[0051] 45% ≤ RH out,new ≤60%;

[0052] Among them, W terTo control the moisture content at the midpoint, It is the expected fresh air humidity content of the fresh air flowing out of the fresh air outflow portion (16).

[0053] According to the optimal dry-bulb temperature of the fresh air outlet (16) obtained by the solution Optimum relative humidity and optimally control the midpoint dry bulb temperature Based on this, the corresponding working time of the hot water coil and the cold water coil is further controlled.

[0054] Furthermore, the minimum threshold of the ideal dew point temperature 5.5℃, the ideal dry bulb temperature maximum threshold The ideal dry bulb temperature minimum threshold is 27℃ and the minimum threshold is 18℃, the ideal relative humidity maximum threshold RH ex,max The ideal relative humidity minimum threshold RH is 60% and ex,min 45%.

[0055] The present invention also provides an energy-saving temperature and humidity control air conditioner using the control method as described above, wherein the air conditioner is used to further control the temperature and humidity of the mixed air after the fresh air and the return air of the data center undergo heat exchange, and then discharge the mixed air into the data center room, wherein the air conditioner comprises an equipment cabinet, the equipment cabinet is divided into a gas cross-flow exchange part, a return air outlet and a fresh air inlet arranged on one side of the gas cross-flow exchange part, a cross-flow gas heat exchange core is arranged in the gas cross-flow exchange part, the air conditioner further comprises a return air inlet, a fresh air heating part, a fresh air cooling part and a fresh air outlet, the return air inlet and the fresh air outlet are respectively provided with a first negative pressure fan and a second negative pressure fan, the return air inlet and the fresh air outlet are both connected to the indoor of the data center, and the return air outlet and the fresh air inlet are both connected to the outdoor of the data center;

[0056] The air conditioner also includes a central control single chip, a first air mass flow meter and a first temperature and humidity monitoring sensor arranged at the return air inlet, a second air mass flow meter and a second temperature and humidity monitoring sensor arranged at the return air outlet, a third air mass flow meter and a third temperature and humidity monitoring sensor arranged at the fresh air inlet, and a fourth air mass flow meter and a fourth temperature and humidity monitoring sensor arranged at the fresh air outlet; the first air mass flow meter, the first temperature and humidity monitoring sensor, the second air mass flow meter, the second temperature and humidity monitoring sensor, the third air mass flow meter, the third temperature and humidity monitoring sensor, the fourth air mass flow meter and the fourth temperature and humidity monitoring sensor are all connected to the central control single chip for communication;

[0057] The air conditioner also includes a hot water coil arranged in the fresh air heating part, a cold water coil and a spray system arranged in the fresh air cooling part; the hot water coil is connected to the water heater through a hot water inlet pipe and a hot water return pipe, the water heater is arranged on the front side of the return air inlet part, and the cold water pipe coil is connected to the chiller through a cold water inlet pipe and a cold water return pipe.

[0058] Furthermore, a return air inlet guide plate is provided in the gas cross-flow exchange section, and a mixed air filtering device is provided in the fresh air heating section.

[0059] The beneficial effects of the present invention are:

[0060] 1. The present invention achieves precise adjustment of the indoor environment by optimizing the temperature and humidity control method and the equipment operation mode, thereby reducing the energy consumption of the air conditioner, improving the energy utilization efficiency, and reducing the operating cost. The optimized operation mode reduces the frequent start and stop of the equipment and high-load operation, reduces the wear and aging rate of mechanical parts, and thus extends the service life of the air conditioner. Since the equipment operates under better working conditions, the failure rate is reduced, thereby reducing the frequency of maintenance and replacement of parts, and reducing the subsequent maintenance costs. By reducing electricity consumption and refrigerant use through energy-saving technology, greenhouse gas emissions are indirectly reduced, which meets the requirements of sustainable development and environmental protection.

[0061] 2. The present invention can maintain the data center within the optimal operating range of the equipment through precise control of the temperature and humidity of the mixed air, avoid hardware failures caused by overheating or overcooling, and significantly improve the stability of servers and other equipment. Through energy-saving temperature and humidity control technology, the load of refrigeration equipment can be reduced, thereby reducing overall energy consumption and achieving green operation. It avoids sudden changes in temperature and humidity that may cause equipment in the data center to shut down or even be damaged. Stable temperature and humidity control can effectively avoid such risks and ensure continuous and stable operation of the data center 24 hours a day.

[0062] 3. The present invention calculates the dry bulb temperature, relative humidity and moisture content of the mixed air obtained after the fresh air entering from the outside is heat exchanged with the return air by the cross-flow gas heat exchange core, and then compares them with the ideal dew point temperature minimum threshold, Ideal dry bulb temperature maximum threshold Ideal dry bulb temperature minimum threshold Different temperature thresholds and the ideal relative humidity maximum threshold Ideal relative humidity minimum threshold RH ex,min The humidity thresholds of the components are compared in turn, and then the following is obtained: Figure 5The control method for opening or closing the hot water coil of the fresh air heating part and the cold water coil of the fresh air cooling part and / or the spray system of the 10 different air conditioners shown in the figure further constructs the dynamic heat exchange balance equation of the hot and cold air of the cross-flow gas heat exchange core according to 10 different situations, and then solves the optimal fresh air and return air inflow and outflow rate; or for the temperature and humidity processing process except the 6th situation and the 2nd situation, constructs the optimal dry-bulb temperature of the fresh air outflowing from the fresh air outflow part and optimal relative humidity and / or optimal spray speed of the spray system The solution model is used to perform different controls according to different situations, dynamically adjust the opening or closing status of the fresh air heating unit, cooling unit and spray system, avoid unnecessary heating or cooling operations, accurately control humidity increase, and save water resources. At the same time, by controlling the optimal dry-bulb temperature and optimal relative humidity of the fresh air outflow, the working time of the chiller and / or water heater is minimized, and the temperature and humidity of the fresh air flowing into the room are controlled with the lowest energy consumption, reducing the frequent start and stop of key equipment (such as hot water coils, cold water coils, and spray systems) and reducing equipment wear. Effectively optimize the operation strategy, avoid long-term high-load operation of equipment, and extend the life of the system.

[0063] 4. The present invention monitors the inflow and outflow speed of the indoor return air in the data center and the speed of the fresh air flowing into and out of the room from the outside in real time, and then measures the gas coupling flow speed of the fresh air and the return air in the cross-flow gas heat exchange core. After accurate calculation, the return air and fresh air inflow and outflow rates are optimized when the mixed air is directly input into the room without heating and / or cooling the mixed air in the fresh air heating unit and / or fresh air cooling unit in case 6), thereby achieving accurate control of the ratio of fresh air to return air, ensuring that the temperature and humidity of the mixed air are always within the ideal range, thereby ensuring that the data center equipment operates under the best environmental conditions. In addition, when the external environment or indoor load changes, the flow rate can be adjusted quickly, the response time can be shortened, and the temperature and humidity of the mixed air entering the data center can be kept stable. BRIEF DESCRIPTION OF THE DRAWINGS

[0064] The present invention will be described in more detail below based on embodiments and with reference to the accompanying drawings, wherein:

[0065] Figure 1 An overall schematic diagram of the connection between the air conditioner provided by the present invention and the indoor environment of a data center;

[0066] Figure 2 The right side view of the air conditioning gas flow direction and structure provided by the present invention;

[0067] Figure 3 This is a schematic diagram of the left side structure of the air conditioner provided by the present invention without the chiller;

[0068] Figure 4 For the present invention Figure 3 A magnified view of part A in FIG.

[0069] Figure 5 This is a schematic diagram of a table for collecting different scenarios corresponding to embodiments 1-10 of the present invention;

[0070] Figure 6 Enthalpy-humidity diagram of the air conditioner controlling the mixed air after the cross-flow heat exchange in Example 1 of the present invention;

[0071] Figure 7 Enthalpy-humidity diagram of the air conditioner controlling the mixed air after the cross-flow heat exchange in Example 2 of the present invention;

[0072] Figure 8 Enthalpy-humidity diagram of the air conditioner controlling the mixed air after the cross-flow heat exchange in Example 3 of the present invention;

[0073] Fig. 9 Enthalpy-humidity diagram of the air conditioner controlling the mixed air after the cross-flow heat exchange in Example 4 of the present invention;

[0074] Fig.10 Enthalpy-humidity diagram of the air conditioner controlling the mixed air after the cross-flow heat exchange in Example 5 of the present invention;

[0075] Fig.11 Enthalpy-humidity diagram of the air conditioner controlling the mixed air after the cross-flow heat exchange in Example 7 of the present invention;

[0076] Fig.12 Enthalpy-humidity diagram of the air conditioner controlling the mixed air after the cross-flow heat exchange in Example 8 of the present invention;

[0077] Fig.13 Enthalpy-humidity diagram of the air conditioner controlling the mixed air after the cross-flow heat exchange in Example 9 of the present invention;

[0078] Fig.14 This is a psychrometric diagram of the mixed air regulation after the cross-flow heat exchange by the air conditioner in Example 10 of the present invention. DETAILED DESCRIPTION

[0079] The following will be combined with the drawings in the embodiments of the present invention to clearly and completely describe the technical solutions in the embodiments of the present invention. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention.

[0080] The present invention provides a method for controlling temperature and humidity of an air conditioner in an energy-saving manner. The method is applied to Figure 1The fresh air temperature and humidity control of the indoor air in the data center shown includes the following steps:

[0081] S1: real-time monitoring of the real-time air mass flow rate, dry-bulb temperature and relative humidity of the return air inlet 13, the return air outlet 12, the fresh air inlet 10 and the fresh air outlet 16;

[0082] S2: Calculate the dry-bulb temperature T of the mixed air after heat exchange in the gas cross-flow exchange section 11 mix , moisture content W mix (mass moisture content) and relative humidity RH mix , determine the maximum threshold of the ideal dew point temperature of indoor air Ideal dew point temperature minimum threshold Ideal dry bulb temperature maximum threshold Ideal dry bulb temperature minimum threshold Ideal relative humidity maximum threshold RH ex,max , Ideal relative humidity minimum threshold RH ex,min ;

[0083] S3: Determine the dry bulb temperature T of the mixed air mix The position in the different temperature threshold intervals composed of the temperature thresholds in step S2 determines the dry bulb temperature T of the mixed air. mix After the temperature is within the threshold range, the relative humidity RH of the mixed air is further determined. mix In which humidity threshold interval is it composed of various relative humidity thresholds, and then according to the dry bulb temperature T of the mixed air mix and relative humidity RH mix The mixed air state is determined by the different interval positions. The hot water coil, cold water coil or spray system or any one or a combination of two is selected to be turned on. After further temperature and humidity treatment, the mixed air flows out from the fresh air outlet. Alternatively, none of them are selected to be turned on and only the mixed air flows out from the fresh air outlet directly to the room.

[0084] like Figure 1As shown, a plurality of cabinets are arranged in the data center. The hot air return air emitted during the operation of the cabinets is sucked into the air conditioner by the first negative pressure fan at the return air inlet 13 of the air conditioner used in the present application, and enters the gas cross flow exchange part 11 through the guide of the return air guide plate 61 in the air conditioner. At the same time, the second negative pressure fan at the fresh air inlet 16 at the lower right side of the return air inlet 13 will also cause negative pressure in the gas cross flow exchange part 11, thereby allowing the outside fresh air to flow in through the fresh air flow inlet 10. The flow of the fresh air and the return air is on the same horizontal plane and in opposite directions, and both enter the gas cross flow exchange part 11. After cross heat exchange in the gas cross flow exchange part 11 and in the cross flow gas heat exchange core 111 of the gas cross flow exchange part 11, they flow in opposite directions and are both on the next horizontal plane of the fresh air and return air inflow direction. The mixed air obtained by the exchange passes through the filter device 62 and enters the fresh air heating part 14, the fresh air cooling part (15) and the fresh air outflow part (16) in the direction of entering the data center room in turn. After temperature and humidity control or without temperature and humidity control, it directly enters the data center room. After heat exchange in the cross flow gas heat exchange core 111, the return air flows out of the air conditioner through the return air outlet 12 and enters the atmospheric environment. Through the control of the air conditioner, the temperature and humidity of the mixed air entering the data center can meet the indoor air environment requirements of the data center in different seasons and working environments.

[0085] Preferably, the minimum threshold of the ideal dew point temperature of indoor air is =5.5℃, the maximum threshold of ideal dry bulb temperature The ideal dry bulb temperature and minimum threshold are 27℃ and 10℃, respectively. 18℃, ideal relative humidity maximum threshold RH ex,max The ideal relative humidity minimum threshold RH is 60% and ex,min 45%.

[0086] Furthermore, in step S2, the dry-bulb temperature T of the mixed air is calculated. mix , moisture content W mix and relative humidity RH mix The formula is as follows:

[0087]

[0088] Among them, W in,new are the relative humidity RH of the fresh air flowing into the fresh air inlet 10 obtained by real-time monitoring according to step S1 in,new and dry bulb temperature T in,new The calculated humidity content of the fresh air flowing into the fresh air inlet 10 is W in,re is the relative humidity RH of the return air flowing into the return air inlet 13 obtained by real-time monitoring according to step S1 in,re and dry bulb temperature T in,re The calculated humidity content of the return air flowing into the return air inlet 13 is:

[0089]

[0090] According to the calculated mixed air humidity W mix , and further calculate the relative humidity of the mixed air:

[0091]

[0092] in, T in,new and W in,new They are the fresh air inflow velocity of the fresh air inlet 10 obtained by real-time monitoring in step S1 (the air mass inflow velocity of the fresh air per unit time, and the flow velocity monitored in real time at the return air inlet 13, the return air outlet 12 and the fresh air outflow 16 is also the air mass flow velocity), the dry-bulb temperature of the incoming fresh air and the relative humidity of the incoming fresh air, T in,re and W in,re The return air inflow velocity, the inflow return air dry bulb temperature and the inflow return air relative humidity of the return air inlet 13 obtained by real-time monitoring in step S1; are the fresh air outflow velocity at the fresh air outflow portion 16 and the return air outflow velocity at the return air outlet 12 obtained by real-time monitoring in step S1; s (T mix ) is the mixed air at dry bulb temperature T mix Saturated water vapor pressure, e s (T in,re ) is the return air flowing into the return air inlet 13 at the dry bulb temperature T in,re Saturated water vapor pressure under s (T in,new ) is the fresh air flowing into the fresh air inlet 10 at the dry bulb temperature T in,new The saturated water vapor pressure under the condition; P is the air pressure, P = 101325Pa;

[0093]

[0094] In step S3, the dry bulb temperature T of the mixed air mix and relative humidity RH mix The mixed air processing methods between different temperature threshold ranges and humidity threshold ranges include the following situations:

[0095] 1) If Then the hot water coil 3 is controlled to be turned on and the water heater 30 is turned on at the same time, and the mixed air is heated isothermally, and then the spray system 5 is turned on to continue to isothermally humidify the heated mixed air;

[0096] 2) If And RH mix >RHex,max , then control to open the cold water coil 4 and the chiller 40 to cool and dehumidify the mixed air, and then open the hot water coil (3) and the water heater 30 to further heat the cooled and dehumidified mixed air;

[0097] 3) If And RH ex,min ≤RH mix ≤RH ex,max , then the hot water coil 3 and the water heater 30 are turned on to perform isohumidity heating on the mixed air;

[0098] 4) If And RH mix <RH ex,min , then the hot water coil 3 and the water heater 30 are turned on to heat the mixed air isothermally, and then the spray system 5 is turned on to continue to humidify the heated mixed air isothermally;

[0099] 5) If And RH mix >RH ex,max , the cold water coil 4 and the chiller 40 are turned on to cool and dehumidify the mixed air;

[0100] 6) If And RH ex,min ≤RH mix ≤RH ex,max , then the dynamic heat exchange balance equation of cold and hot air in the cross-flow gas heat exchange core is constructed to solve the optimal inflow and outflow speeds of fresh air and return air;

[0101] 7) If And RH mix <RH ex,min , only the spray system 5 is turned on to perform isothermal humidification on the mixed air;

[0102] 8) If And RH mix >RH ex,max , only the cold water coil 4 and the chiller 30 are turned on to cool and dehumidify the mixed air;

[0103] 9) If And RH ex,min ≤RH mix ≤RH ex,max , then the cold water coil 4 and the chiller 30 are turned on at the same time, and the mixed air is cooled by heat exchange between the cold water of the cold water coil and the mixed air;

[0104] 10) If And RH mix <RH ex,min, the cold water coil 4, the chiller 30 and the spray system 5 are turned on, and the temperature of the cold water that is introduced into the cold water coil 4 through the cold water inlet pipe 41 for heat exchange with the mixed air is 10-12°C, which is lower than the dry bulb temperature of the mixed air at this time (due to the dry bulb temperature T mix At this time, the maximum threshold of the ideal indoor air dry bulb temperature has been exceeded ), the relative humidity of the mixed air is RH mix <RH ex,min For example, when Tmix is ​​30℃ and RH mix If it is 50%, the dew point temperature of the mixed air is 18.5℃, which is higher than 10-12℃. Therefore, part of the air condenses and condenses on the surface of the cold water coil 4. Therefore, its moisture content is reduced and the mixed air exchanges heat to the cold water due to heat exchange, the temperature of the mixed air itself decreases, and then its relative humidity increases. At the same time, further spraying is carried out, and the relative humidity of the mixed air is further increased. Therefore, in the 10th case, turning on the cold water coil 4 and the spray system can achieve humidification, cooling and lowering the temperature of the mixed air.

[0105] When the hot water coil 3 is turned on, in order to provide the hot water coil 3 with real-time dynamic inflow of hot water and to reflux and reheat the hot water after heat exchange, the water heater 30 is also turned on at the same time; similarly, when the cold water coil 4 is turned on, in order to provide the cold water coil 4 with real-time dynamic inflow of cold water and to reflux and recool the cold water after heat exchange and absorption of heat, the chiller 40 also needs to be turned on at the same time.

[0106] When the dry bulb temperature of the mixed air is T mix and relative humidity RH mix The situations between different temperature threshold intervals and humidity threshold intervals are as follows: And RH ex,min ≤RH mix ≤RH ex,max When (i.e., the sixth case), the temperature and relative humidity of the mixed air at this time meet the desired dry-bulb temperature and relative humidity thresholds in the data center. Therefore, the mixed air at this time can be directly discharged into the data center through the fresh air outflow portion 16. It is only necessary to control the inflow and outflow rates of the fresh air and the return air at the cross-flow gas heat exchange core 111 to ensure that the mixed air obtained after the fresh air passes through the cross-flow gas heat exchange core 111 is always kept within the desired dry-bulb temperature threshold range in the data center. and the relative humidity threshold range RH expected in the data center ex,min ≤RH mix ≤RH ex,max Therefore, as another preferred embodiment of the present invention, constructing a cross-flow gas heat exchange core cold and hot air dynamic heat exchange balance equation to solve the optimal fresh air and return air inflow and outflow rates includes the following steps:

[0107] S301: Calculating the enthalpy value i of the fresh air flowing from the fresh air inlet 10 into the gas cross-flow exchange unit 11 in,new , the enthalpy value i of the mixed air flowing out of the gas cross exchange section 11 mix , the enthalpy value i of the return air flowing into the gas cross-flow exchange part 11 from the return air inlet 13 in,re , the air enthalpy value i of the gas cross-flow exchange part 11 flowing out of the return air outlet 12 out,re :

[0108] i in,new =c a T in,new +W in,new (c s T in,new +i fg );

[0109] i mix =c a T mix +W mix (c s T mix +i fg );

[0110] i in,re =c a T in,re +W in,re (c s T in,re +i fg );

[0111] i out,re =c a T out,re +W out,re (c s T out,re +i fg );

[0112] Among them, c a is the specific heat capacity of dry air, c a = =1.005 kJ / (kg·℃); c s is the specific heat capacity of water vapor, c s =1.82kJ / (kg·℃),i fg is the latent heat of vaporization of water, i fg =2500kJ / kg; T out,re and W out,re They are respectively the outflow return air dry-bulb temperature and the outflow return air humidity at the return air outlet 12 obtained by real-time monitoring in step S1;

[0113] S302: Construct the dynamic heat exchange balance equation of cold and hot air in the cross-flow gas heat exchange core:

[0114]

[0115] h tr is the convective heat transfer coefficient, Among them, Nu in,new is the Nusselt number of the fresh air (cold air) flowing into the fresh air inlet 10, Nu in,re is the Nusselt number of the return air (hot air) flowing into the return air inlet 13, k is the thermal conductivity of air, k=0.026W (m·K); L is the side length of the square section of the cross-flow gas heat exchange core 111; Re in,new , Pr in,new are the Reynolds number and Prandtl number of the fresh air flowing into the fresh air inlet 10, Pr in,new =(c a +W in,new c a )μ / k; Re in,re , Pr in,re are the Reynolds number and Prandtl number of the return air flowing into the return air inlet 13, Pr in,re =(c a +W in,re c a )μ / k; μ is the air dynamic viscosity, μ = 18.1 = μPa·s; ρ in,new is the density of the fresh air flowing into the fresh air inlet (10), ρ in,re is the density of the return air flowing into the return air inlet 13;

[0116] Wherein, R is the specific gas constant of air, R = 287 J / (kg·K);

[0117] S303: Under the limitation of the equilibrium equation constructed in step S302, a cold and hot air enthalpy exchange maximization model is constructed to solve the optimal fresh air and return air inflow and outflow speeds:

[0118]

[0119] in, The gas coupling flow velocity of the fresh air and the return air in the gas cross-flow heat exchange section (11);

[0120]

[0121] Then according to the optimal fresh air inflow speed obtained Optimal fresh air outflow speed Optimal return air inflow velocity Optimal return air outflow speed The fresh air inflow velocity at the fresh air inlet 10 , the fresh air outflow velocity at the fresh air outflow portion 16 , the return air inflow velocity at the return air inlet 13 , and the return air outflow velocity at the return air outlet 12 are controlled respectively.

[0122] In the temperature and humidity treatment process except for the 6th case and the 2nd case, when only the cold water coil 4 is turned on, only the hot water coil 3 is turned on, only the spray system 5 is turned on, when both the cold water coil 4 and the spray system 5 are turned on at the same time, or when the hot water coil 3 is turned on first and then the spray system 5 is turned on, it is necessary to control within a unit time whether the cold water coil 3 and / or the hot water coil is turned on before the spray system is turned on, when only the cold water coil and the hot water coil are turned on, or when only the spray system is turned on, in order to improve the heat exchange efficiency, the heat exchange amount Q occurring at the fresh air heating part and / or the fresh air cooling part needs to reach the maximum within a unit time, even if maximum, Therefore, as another preferred embodiment of the present invention, the optimal dry-bulb temperature of the fresh air flowing out of the fresh air outflow portion (16) is controlled. and optimal relative humidity and / or optimal spray speed of the spray system The solution model is as follows:

[0123]

[0124] in; and points are respectively the desired fresh air dry-bulb temperature, the desired fresh air relative humidity and the desired fresh air moisture content of the fresh air flowing out of the fresh air outflow portion 16, T out,new The dry-bulb temperature of the fresh air flowing out of the fresh air outflow portion 16 is monitored in real time; is the spray speed of the spray system; α is the opening coefficient of the spray system; β is the calculation coefficient for the latent heat of mixed air or evaporation heat loss;

[0125] Real-time monitoring of T out,new and RH out,new It is not necessarily within the desired ideal threshold range of the dry-bulb temperature of the fresh air flowing out of the fresh air outlet 16. The ideal threshold range of relative humidity of fresh air Therefore, the desired fresh air dry-bulb temperature of the fresh air flowing out of the fresh air outflow portion 16 is At 18℃~27℃, the expected fresh air relative humidity The range of 45% to 60% is limited to solve the model The optimal result of the solution is limited to ensure that the solution result is within the expected ideal threshold range; the expected fresh air humidity content It can be calculated according to the following formula:

[0126] In addition, through This condition indicates that the ratio of the spray velocity of the spray system to the speed of the fresh air flowing out is the mixed air humidity W when it is not humidified by the spray system. mix (lower humidity content) and the expected humidity content of the fresh air after humidification The difference between the two indicates the contribution of the spray velocity of the spray system to the moisture content of the outflowing fresh air.

[0127]

[0128] The corresponding working time of the hot water coil 3 and / or the cold water coil 4 and / or the spraying speed of the spraying system 5 are further controlled according to the solution result.

[0129] In the calculation formula of the heat exchange amount Q occurring in the fresh air heating unit and / or the fresh air cooling unit per unit time, When the spray system is turned on, the mixed air increases its own moisture content due to the addition of moisture, and then evaporates the latent heat. Furthermore, when the cold water coil is turned on, since the temperature of the mixed air is higher than the temperature of the cold water inlet pipe of the cold water coil, it will condense on the surface of the cold water coil, thereby releasing latent heat, causing its own temperature to drop, thereby increasing the heat provided by the cold water inlet pipe for the mixed air cooling, and reducing the energy of the mixed air cooling. Therefore, β = 1; when the hot water coil is turned on, since the temperature of the mixed air is lower than that of the hot water coil, during the heating process, the water vapor will evaporate due to the heat received during the heating process, thereby releasing heat. This causes its own temperature to drop, offsetting part of the heat provided by the hot water inflow pipe for mixed air heating. Therefore, β = -1;

[0130] Solve the objective equation of the model: The dry-bulb temperature and relative humidity of the fresh air flowing out of the fresh air outlet 16 and the spray velocity of the spray system are solved to obtain the maximum heat exchange capacity Q per unit time. When only the spray system is turned on, T is also solved. out,new RH out,new and The optimal solution; when the spray system is not turned on, only the cold water pan or the hot water pan is turned on for separate cooling and dehumidification or equal humidity heating, only the solution The optimal solution of T is also solved when the spray system is turned on at the same time or after the cold water coil or hot water coil is turned on. out,new RH out,new and The optimal solution of .

[0131] As another preferred embodiment of the present invention, in the second case, the mixed air at this time is greater than or equal to the minimum threshold of the indoor ideal dew point temperature and less than the minimum threshold of the indoor ideal dry bulb temperature. The relative humidity is greater than the maximum threshold of the ideal relative humidity of indoor air (RH mix >RH ex,max ), therefore, it is necessary to open the cold water coil 4 to cool the mixed air first. The humidity after cooling may reach the threshold range or may still exceed the highest threshold of the ideal relative humidity of the indoor air, but its temperature is lower than the lowest threshold of the ideal indoor dry-bulb temperature. Therefore, it is necessary to further open the hot water coil 3 to heat it, so that the fresh air finally flowing out from the fresh air outlet 16 reaches the ideal threshold range. Therefore, it is necessary to minimize the total amount of heat exchange after the cold water coil 4 and the hot water coil 3 process the mixed air, thereby minimizing the energy consumption required for the air conditioner to adjust the fresh air input. Therefore, for the second case, the optimal fresh air dry-bulb temperature of the fresh air outlet 16 that minimizes the air conditioning energy consumption is constructed. Optimal fresh air relative humidity And control the midpoint dry bulb temperature T ter Solve the equation:

[0132]

[0133] 18℃≤T out,new ≤27℃

[0134] 45% ≤ RH out,new ≤60%

[0135] The solution model means that the humidity content of the fresh air input to the room is equal to the humidity content of the control midpoint. Solve under the limited conditions that the dry-bulb temperature of the fresh air input to the room is 18℃~27℃, the relative humidity is 45%~60%, and the relative humidity at the midpoint of the control is 100% (even if the mixed air reaches its dew point temperature after cooling). This equation;

[0136] Among them, W ter To control the moisture content at the midpoint, The desired fresh air humidity of the fresh air flowing out of the fresh air outflow portion 16. The humidity W at the midpoint is regulated ter It can be calculated according to the following formula:

[0137] According to the optimal dry-bulb temperature of the fresh air outflow part 16 obtained by the solution Optimum relative humidity and optimally control the midpoint dry bulb temperature Based on this, the corresponding working time of the hot water coil 3 and the cold water coil 4 is further controlled.

[0138] The present invention also provides an energy-saving temperature and humidity control air conditioner using the above control method, the air conditioner is used to further determine whether to open the hot water coil 3, the cold water coil 4 and / or the spray system 5 to control the temperature and humidity of the mixed air after the fresh air and the return air of the data center are heat exchanged, and then discharge them into the data center room. Figure 2-Figure 4 As shown, the air conditioner includes an equipment cabinet 1, the equipment cabinet 1 is divided into a gas cross flow exchange part 11, a return air outlet 12 and a fresh air inlet 10 arranged on one side of the gas cross flow exchange part 11, the fresh air inlet 13 is arranged above the return air outlet 12, and a cross flow gas heat exchange core 111 is arranged in the gas cross flow exchange part 11, the air conditioner also includes a return air inlet 13, a fresh air heating part 14 and a fresh air cooling part 15 arranged on the other side of the gas cross flow exchange part 11, and a fresh air outflow part 16 arranged on the side of the fresh air cooling part 15 away from the gas cross flow exchange part 11, the return air inlet 13 and the fresh air outflow part 16 are respectively provided with a first negative pressure fan 131 and a second negative pressure fan 161, the return air inlet 13 and the fresh air outflow part 16 are both connected to the indoor of the data center, and the return air outlet 12 and the fresh air inlet 13 are both connected to the outdoor of the data center;

[0139] The air conditioner also includes a central control single chip, a first air mass flow meter and a first temperature and humidity monitoring sensor arranged at the return air inlet 13, a second air mass flow meter and a second temperature and humidity monitoring sensor arranged at the return air outlet 12, a third air mass flow meter and a third temperature and humidity monitoring sensor arranged at the fresh air inlet 10, and a fourth air mass flow meter and a fourth temperature and humidity monitoring sensor arranged at the fresh air outlet 16; the first air mass flow meter, the first temperature and humidity monitoring sensor, the second air mass flow meter, the second temperature and humidity monitoring sensor, the third air mass flow meter, the third temperature and humidity monitoring sensor, the fourth air mass flow meter and the fourth temperature and humidity monitoring sensor are all communicatively connected to the central control single chip;

[0140] The first negative pressure fan 131 generates negative pressure on the side of the return air inlet 13 close to the gas cross flow exchange section 12, and then due to the atmospheric pressure, Figure 2 In The indoor air return represented by the red arrow of the flow rate enters the gas cross flow exchange part 12 from the return air inlet 13, and the second negative pressure fan 161 generates negative pressure on the side of the fresh air outlet 16 connected to the indoor part of the data center. Figure 2 The shown The fresh air represented by the blue arrow of the flow velocity flows from the fresh air inlet 13 and enters the gas cross-flow exchange part 12. After the cross-flow heat exchange with the indoor return air represented by the red arrow entering through the return air inlet 13 in the cross-flow gas heat exchange core 111, the fresh air is converted from the upper flow direction to the lower flow direction after the cross-flow to obtain a flow with T mix Dry bulb temperature, RH mix The mixed air represented by the blue arrow of the relative humidity is then heated in the fresh air heating unit 14 or cooled in the envelope cooling unit 15 to the required temperature and humidity according to the temperature and humidity requirements in the data center room. Figure 2 The green arrows shown represent The fresh air with a flow rate of 100° enters the data center through the fresh air outflow portion 16; after the fresh air cross-flow heat exchange between the gas cross-flow exchange portion 11 and the envelope flow inlet 13 (the gas coupling flow velocity of the gas cross-flow heat exchange is ), the return air changes from the upper flow direction to the lower flow direction, and then passes through the return air outlet 12 to obtain The red arrows represent the outflow return air flowing out of the room.

[0141] like Figure 2-Figure 3 As shown, the air conditioner further includes a hot water coil 3 disposed in the fresh air heating portion 14, a cold water coil 4 disposed in the fresh air cooling portion 15 close to the hot water coil 3 and a spray system 5 close to the fresh air outflow portion 16; Figure 4 As shown, the hot water coil 3 is connected to the water heater 30 through the hot water inlet pipe 31 and the hot water return pipe 32. The water heater is arranged on the front side of the return air inlet part 13. The cold water pipe coil 4 is connected to the chiller 40 through the cold water inlet pipe 41 and the cold water return pipe 42.

[0142] A return air inlet guide plate 61 is also provided in the gas cross-flow exchange section 11, and a mixed air filter device 62 is also provided in the fresh air heating section 14. The return air inlet guide plate 61 is provided on the middle horizontal plane close to the return air inlet section 13. On the one hand, its function is to guide the return air entering from the return air inlet section 13 to flow horizontally from right to left in the upper middle horizontal plane of the gas cross-flow exchange section 11, and then enter the cross-flow gas heat exchange core 111 from the upper right side to perform cross-flow heat exchange with the fresh air entering from the outside. On the other hand, it helps guide the mixed air after heat exchange inside the cross-flow gas heat exchange core from the lower right side to flow horizontally from left to right in the lower middle horizontal plane of the gas cross-flow exchange section 11, and then be guided to the mixed air filter device 62. After filtering, it is further subjected to temperature and humidity treatment in the direction from left to right, and finally flows out from the fresh air outflow section 16. Therefore, the return air guide plate 61 horizontally arranged on the middle horizontal plane in the gas cross-flow exchange part 11 prevents the incoming return air from being directly turned vertically from top to bottom on the left side of the cross-flow gas heat exchange core and then mixed with the mixed air by the negative pressure of the second negative pressure fan 161 for further temperature and humidity treatment, and also prevents the mixed air after heat exchange from being sucked by the negative pressure formed by the first negative pressure fan 131 from bottom to top and mixed with the newly entered return air again, and entering from the upper right of the cross-flow gas heat exchange core to exchange heat with the outside fresh air. After the mixed air passes through the mixed air filter device and is further heated by the hot water coil 3 or cooled by the cold water coil 4, it is further selected whether to humidify the mixed air by the spray system, or to simultaneously open the cold water coil 4 and the spray system to humidify and cool the filtered mixed air.

[0143] In order to clarify the effectiveness of the air conditioning and control method provided by the present application and the control conditions in response to the threshold range of mixed air after different cross-flow heat exchanges, the present invention provides Examples 1-10 to clarify the spray speed of the specific spray system during the air conditioning control process, the optimal dry-bulb temperature and relative humidity of the fresh air input into the room after control, and the corresponding working time of the cold water coil and / or hot water coil. Figure 5 As shown, it is a collection table of different scenarios corresponding to embodiments 1-10. The temperature of the chilled water flowing into the cold water coil 4 through the cold water inlet pipe 41 of the air conditioner 40 of the present invention is 5-9°C, and the temperature of the cold water returning to the chiller 40 through the cold water return pipe 42 is 10-16°C; the temperature of the hot water flowing into the hot water coil 3 through the hot water inlet pipe 31 in the water heater 30 is 75-80°C, and the temperature of the water returning to the water heater through the hot water return tank is 50-65°C.

[0144] Example 1

[0145] This embodiment is the dry bulb temperature of the mixed air after the cross-flow heat exchange. This situation is usually in the northern winter or spring. After the cross-flow heat exchange, the mixed air dry-bulb temperature Tmix =15℃ (the dew point temperature of the mixed air at this time Only 1.5℃), relative humidity is RH mix =40%, calculate the corresponding mixed air humidity W mix = Approximately 0.0042 kg water / kg dry air). In this case, the hot water coil is used to heat the mixed air isothermally, and then the spray system 5 is turned on to further humidify it isothermally. Therefore, α==-1, β==-1. During the isothermal heating process, the moisture content remains unchanged (no water vapor is added or removed), and the mixed air exchanges heat with the hot water flowing out of the hot water coil 3, absorbing heat from the hot water coil. In the solution process, the optimal dry-bulb temperature of the fresh air flowing out of the fresh air outflow part 16 is constructed. and optimal relative humidity and / or optimal spray speed of the spray system The solution model is as follows:

[0146]

[0147] st 18℃≤T out,new ≤27℃

[0148] 45% ≤ RH out,new ≤60%

[0149]

[0150] The dry-bulb temperature of the fresh air flowing out of the fresh air outlet 16 is obtained by solving 20℃, relative humidity 55%; optimal spray speed 0.000061 kg / h; that is, about 0.000061 kg of water is sprayed for evaporation every hour. Figure 6 As shown, during the control process, the mixed air is heated during isothermal heating, and the dry-bulb temperature gradually increases to 20°C. Isohumid heating means that the absolute moisture content remains unchanged. Therefore, after heating, its relative humidity becomes 30%, and further during the isothermal humidification process, the spray system 5 is turned on to humidify the mixed air to a relative humidity of 55%, and the dry-bulb temperature remains unchanged at 20°C.

[0151] Real-time monitoring is 0.0389kg / s. ; When the water heater is turned on for isohumid heating, Therefore, the heat exchange amount Q during one hour of air conditioning operation is heat It is about 0.1954725×3600=703.701kJ. In order to calculate the working time of the water heater in one hour, let

[0152] It is the difference between the flow rate of the hot water return pipe and the hot water outflow pipe, that is, the real-time flow rate of hot water in the hot water coil. About 28.90m 3 / h;c w is the specific heat capacity of water, c w =4.18kJ / (kg·℃), T hw,in The temperature of the hot water return pipe, T hw,in =79.8℃; T hw,out is the temperature of the hot water flowing out of the pipe, T hw,out =61.6℃,Δt h is the water heater on time, and Δt is calculated h =703.701 / (24.81×4.18×(79.8-61.6))=0.32h.

[0153] That is, the hot water inlet pipe 31, the hot water return pipe 32, the hot water coil 4 and the water heater 40 are all open to exchange heat with the mixed air (heat the mixed air) for 0.32 hours, and the mixed air is heated to 20°C. Then, the spraying is performed at a spraying speed of 0.000061 kg / h, and the dry-bulb temperature of the fresh air flowing out of the fresh air outlet 16 is finally 20℃, relative humidity is 55% (the state of the fresh air flowing out of the fresh air outflow section 16 is Figure 5 The light green color of the psychrometric chart indicates the ideal dry-bulb temperature threshold and the ideal relative humidity threshold for the data center room).

[0154] Example 2

[0155] In this embodiment, after the cross-flow heat exchange, the mixed air dry-bulb temperature T mix 16℃, relative humidity RH mix is 80%, at which time the humidity content of the mixed air is W mix The dry bulb temperature of the mixed air is 0.00906 kg / kg. Relative humidity RH mix >RH ex,max This situation usually occurs in the spring and autumn or winter in the south, and the mixed air needs to be cooled and dehumidified. Cooling and dehumidification will cause the temperature of the processed mixed air to be lower than the minimum dry-bulb temperature threshold of the ideal indoor air, so it needs to be further heated. Therefore, in this case, the optimal fresh air dry-bulb temperature of the fresh air outflow part 16 that minimizes the air conditioning energy consumption is Optimal fresh air relative humidity And control the midpoint dry bulb temperature T ter Solve the equation as follows:

[0156]

[0157] 18℃≤T out,new ≤27℃

[0158] 45% ≤ RH out,new ≤60%

[0159] like Figure 7 As shown, the solution is is 29°C, 23℃, The temperature of the fresh air in the data center is 48%, which makes the dry bulb temperature and relative humidity of the fresh air finally input into the data center room within the ideal threshold range (light green shaded area in the figure). When the chiller is turned on, due to the condensation of mixed air water vapor on the surface of the cold water coil, the air in the mixed air will release latent heat: And lose heat by exchanging heat with the chiller Heat is obtained by heat exchange with the water heater. is 0.0405kg / s, Therefore, the heat exchange amount Q during one hour of air conditioning operation is heat is about 1904.877 kJ, 30.25m 3 / h, real-time monitoring to obtain T hw,in =80℃, T hw,out =50.2℃, Δt h About 0.5h.

[0160] The heat exchange rate with the cold water coil during the start-up of the chiller is Therefore, the heat exchange amount Q during one hour of air conditioning operation is cool It is about 0.244215×3600=879.174kJ. In order to calculate the working time of the chiller in one hour, let It is the difference between the flow rate of the cold water return pipe and the cold water outflow pipe, that is, the real-time flow rate of hot water in the cold water coil. T cw,in The temperature of the cold water return pipe, T cw,in = = 9 ° C; T cw,out is the temperature of the cold water outflow pipe, T cw,out =15℃, then the chiller opening time Δt can be calculated c =0.67h.

[0161] Example 3

[0162] In this embodiment, the dry bulb temperature and relative humidity of the mixed air after the cross-flow heat exchange are respectively RH ex,min ≤RH mix ≤RH ex,max This situation usually occurs in spring and autumn in the north or winter in the south. In this case, since the relative humidity of the mixed air meets the relative humidity requirements of the data center, it is only necessary to further heat the mixed air with equal humidity to make the processed mixed air reach the ideal indoor dry-bulb temperature threshold range. Therefore, it is sufficient to only turn on the water heater to heat the mixed air with equal humidity, α=0, β=-1.

[0163] like Figure 8 As shown, the starting point is the mixed air that has undergone heat exchange in the gas cross-flow exchange section, and its dry bulb temperature is T mix 16℃, relative humidity RH mix 48%. The obtained fresh air temperature flowing out of the fresh air outlet 16 is 22℃, relative humidity is 45%; real-time monitoring 0.413kg / s

[0164] During the isohumid heating process, the heat loss rate of the hot water flowing into the pipe to heat the mixed air is as follows: Therefore, the heat exchange amount Q during one hour of air conditioning operation is heat is about 896.54 kJ, 19.65m 3 / h, real-time monitoring to obtain T hw,in =78.6℃, T hw,out =49.5℃, Δt h About 0.375h.

[0165] Example 4

[0166] In this embodiment, the dry bulb temperature and relative humidity of the mixed air after the cross-flow heat exchange are respectively RH mix <RH ex,minThis situation also occurs in the winter in the north or the drier spring and autumn in the north. Therefore, it is also necessary to open the hot water coil 3 to heat the mixed air isothermally, and then open the spray system 5 for isothermal humidification. Therefore, α==-1, β==-1. Isothermal heating is mainly used to increase the mixed air temperature to be closer to the minimum indoor temperature to avoid direct input into the room causing the temperature to be too low; during the isothermal heating process, the humidity ratio (absolute moisture content) remains unchanged. Raise the temperature to avoid the mixed air directly entering the room causing the temperature to be too low, while keeping the relative humidity of the mixed air at a low value. Then humidify to increase the air humidity to ensure that the relative humidity enters the ideal range to ensure human comfort or equipment operation requirements.

[0167] like Fig. 9 As shown, the starting point is the mixed air that has undergone heat exchange in the gas cross-flow exchange section, and its air temperature is T mix 16℃, relative humidity RH mix is 20%. Solving for 18℃, relative humidity 50%, real-time monitoring 0.0408kg / h. In the isothermal humidification process, the latent heat released by water vapor and the mixed air that has been heated to 18℃ and 20% relative humidity is humidified; The heat absorbed by the mixed air itself during the isohumidification heating process when the mixed air is heated by the hot water flowing out of the water heater. The difference between the heat released by the water vapor in the mixed air is due to therefore Then the mixed air completes the temperature rise after isohumid heating and reaches the midpoint of 18°C ​​and 20% relative humidity.

[0168] When the water heater is turned on for isohumid heating, Therefore, the heat exchange amount Q during one hour of air conditioning operation is heat is about 288.72 kJ, 12.30m 3 / h, real-time monitoring to obtain T hw,in =75.9℃, T hw,out =48.7℃, Δt h About 0.2h.

[0169] Example 5

[0170] In this embodiment, the dry bulb temperature and relative humidity of the mixed air after the cross-flow heat exchange are respectively RH mix >RH ex,maxThis situation usually occurs in the summer or rainy season in the south, when the humidity is high, especially when the heat exchange core is used for preheating, the humidity may exceed the standard. This situation also occurs in the north where the temperature is high in summer and the humidity is high from late July to early August. In this case, only the chiller is turned on for cooling and dehumidification, so α=0, β=1. Fig.10 As shown, in this embodiment, the mixed air temperature T after the cross-flow heat exchange is calculated. mix 23℃, relative humidity RH mix is 70%, after dynamic regulation, the chiller is turned on for surface cooling and dehumidification, and the optimal fresh air temperature flowing out of the fresh air outflow part 16 is dynamically regulated. The optimal fresh air relative humidity is 20℃ The real-time monitoring results are 50%. The heat exchange capacity of cold water is 0.0392kg / s. Real-time monitoring T cw,in =9.16℃, T cw,out =15.93℃; then the calculated working time of the chiller is, Δt c =0.62h.

[0171] Example 6

[0172] In this embodiment, the dry bulb temperature and relative humidity of the mixed air after the cross-flow heat exchange are respectively This situation is more likely to occur in the spring and autumn season in the north, corresponding to the 6th situation. The optimal fresh air inflow speed is obtained by directly solving the dynamic heat exchange balance equation of cold and hot air in the cross-flow gas heat exchange core constructed. Optimal fresh air outflow speed Optimal return air inflow velocity Optimal return air outflow speed Based on this, the implementation speed of fresh air inflow and outflow, return air inflow and outflow of air conditioning is controlled.

[0173] Example 7

[0174] In this embodiment, the dry bulb temperature and relative humidity of the mixed air after the cross-flow heat exchange are respectively RH mix <RH ex,min This situation is more likely to occur in the autumn and winter seasons in the north. It is sufficient to turn on the spray system for isothermal humidification. Therefore, α=1, β=0. Fig.11 As shown, the mixed air dry bulb temperature T at the starting point mix 24℃, mixed air relative humidity RHmix The optimal spray rate is 30%, and the optimal spray rate is 0.26 kg / s, that is, 0.26 kg of water is sprayed for evaporation per second on each square meter of air flow cross section. The optimal dry bulb temperature obtained is 24℃, optimal relative humidity is 50%,

[0175] Example 8

[0176] In this embodiment, the dry bulb temperature and relative humidity of the mixed air after the cross-flow heat exchange are respectively RH mix >RH ex,max This situation is more likely to occur in the summer or rainy season in the south. Therefore, only the cold water coil 4 needs to be turned on to cool and dehumidify the mixed air, so α=0, β=1. Fig.12 As shown, the mixed air dry bulb temperature T at the starting point mix 32℃, mixed air relative humidity RH mix is 75%, and the optimal dry-bulb temperature of the fresh air flowing out of the fresh air outflow portion 16 is obtained. The optimum relative humidity is 24°C. 50%, real-time monitoring is 0.0435kg / s, Therefore, the heat exchange amount Q during one hour of air conditioning operation is cool About 1259 kJ. In order to calculate the working time of the chiller in one hour, let It is the difference between the flow rate of the cold water return pipe and the cold water outflow pipe, that is, the real-time flow rate of hot water in the cold water coil. T cw,in = =5.5℃, T cw,out =15.8℃, then the chiller opening time Δt can be calculated c =0.53h.

[0177] Example 9

[0178] In this embodiment, the dry bulb temperature and relative humidity of the mixed air after the cross-flow heat exchange are respectively RH ex,min ≤RH mix ≤RH ex,max This situation is more likely to occur in the northern summer or early autumn season. Therefore, it is necessary to open only the cold water coil to cool the mixed air, so α=0, β=1. Fig.13 As shown, the mixed air dry bulb temperature T at the starting point mix 30℃, mixed air relative humidity RH mixis 50%, and the optimal dry-bulb temperature of the fresh air flowing out of the fresh air outflow portion 16 is obtained. The optimum relative humidity is 26°C. The real-time monitoring results are 55%. is 0.0420kg / s, Therefore, the heat exchange amount Q during one hour of air conditioning operation is cool It is 607.824kJ. T cw,in =5.1℃, T cw,out =16.0℃, then the chiller opening time Δt can be calculated c About 0.27h.

[0179] Example 10

[0180] In this embodiment, the dry bulb temperature and relative humidity of the mixed air after the cross-flow heat exchange are respectively ≤RH mix <RH ex,max This situation is more likely to occur in the northern summer or early autumn. Therefore, it is necessary to turn on the spray system and the cold water coil at the same time to perform evaporative cooling to assist cooling and increase the air humidity flowing into the data center. Therefore, α = 1, β = 1. Fig.14 As shown, the mixed air dry bulb temperature T at the starting point mix 32℃, mixed air relative humidity RH mix is 30%, the optimal spray speed of the spray system is The optimum dry-bulb temperature of the fresh air flowing out of the fresh air outlet 16 is 0.18 kg / s. The optimum relative humidity is 26°C. The real-time monitoring results are 50%. 0.0387kg / h, Therefore, the heat exchange amount Q during one hour of air conditioning operation is cool About 840.10kJ. T cw,in =5.8℃, T cw,out =15.6℃, then the chiller opening time Δt can be calculated c About 0.37h.

[0181] In summary, the air conditioning and control method provided by the present invention can dynamically adjust the operation strategy under different seasons and climate conditions, always maintain the stability of the indoor temperature and humidity of the data center, improve the reliability of equipment operation, and adapt to the climate differences between the north and the south, and is suitable for various regional environments. In addition, intelligent control reduces the need for manual intervention and further reduces labor costs. Through efficient energy consumption management, it can effectively reduce unnecessary energy consumption in the cooling, heating and humidification processes, reduce carbon emissions, and save 20%-30% of electricity and operation and maintenance costs each year, which meets the requirements of the data center industry for sustainable development and enhances market competitiveness.

[0182] The present invention constructs a dynamic solution model and flexibly adjusts the air conditioning system operation mode according to the external environment and indoor needs, thereby achieving maximum energy efficiency and equipment protection. This not only significantly reduces the operating costs of the data center, but also increases the commercial application value, helping the data center industry to develop in the direction of intelligence and greenness.

[0183] The above are only specific embodiments of the present invention, but the protection scope of the present invention is not limited thereto. Any person skilled in the art can easily think of changes or substitutions within the technical scope disclosed by the present invention, which should be included in the protection scope of the present invention. Therefore, the protection scope of the present invention should be based on the protection scope of the claims.

Claims

1. A method for controlling temperature and humidity of an air conditioner for energy saving, the method being applied to controlling the temperature and humidity of fresh air entering a data center, characterized in that: The following steps are involved: S1: real-time monitoring of the real-time air mass flow rate, dry-bulb temperature and relative humidity of the return air inlet (13), the return air outlet (12), the fresh air inlet (10) and the fresh air outlet (16); S2: Calculate the dry bulb temperature T of the mixed air after heat exchange in the gas cross flow exchange section (11) mix , moisture content W mix and relative humidity RH mix , determine the ideal dew point temperature minimum threshold Ideal dry bulb temperature maximum threshold Ideal dry bulb temperature minimum threshold Ideal relative humidity maximum threshold RH ex,max , Ideal relative humidity minimum threshold RH ex,min ; S3: Determine the dry bulb temperature T of the mixed air mix The position in the different temperature threshold intervals composed of the temperature thresholds in step S2 determines the dry bulb temperature T of the mixed air. mix After the temperature is within the threshold range, the relative humidity RH of the mixed air is further determined. mix In which humidity threshold interval is it composed of various relative humidity thresholds, and then according to the dry bulb temperature T of the mixed air mix and relative humidity RH mix The mixed air state is determined by the different interval positions, and the hot water coil (3), the cold water coil (4) or the spray system (5) or any one or a combination of the two is selected to be turned on, and the mixed air is further processed in terms of temperature and humidity before it flows out from the fresh air outflow portion (16); or none of them is selected to be turned on, and only the mixed air is directly flowed out from the fresh air outflow portion (16) and transported to the room.

2. The energy-saving temperature and humidity control method of air conditioning according to claim 1, characterized in that: In step S2, the dry bulb temperature T of the mixed air is calculated. mix , moisture content W mix and relative humidity RH mix The formula is as follows: Among them, W in,new are the relative humidity RH of the fresh air flowing into the fresh air inlet (10) obtained by real-time monitoring according to step S1 in,new and dry bulb temperature T in,new The calculated humidity content of the fresh air flowing into the fresh air inlet (10) is W in,re is the relative humidity RH of the return air flowing into the return air inlet portion (13) obtained by real-time monitoring according to step S1 in,re and dry bulb temperature T in，re The calculated humidity content of the return air flowing into the return air inlet (13) is: According to the calculated mixed air humidity W mix , and further calculate the relative humidity of the mixed air: in, T in,new and W in,new are respectively the fresh air inflow velocity, the dry-bulb temperature and the relative humidity of the fresh air at the fresh air inlet (10) obtained by real-time monitoring, T in,re and W in,re The return air inflow velocity, the dry bulb temperature of the inflow return air and the relative humidity of the inflow return air of the return air inlet portion (13) are respectively obtained by real-time monitoring; are respectively the fresh air outflow velocity at the fresh air outflow portion (16) and the return air outflow velocity at the return air outflow outlet (12); e s (T mix ) is the mixed air at dry bulb temperature T mix Saturated water vapor pressure, e s (T in,re ) is the return air flowing into the return air inlet (13) at the dry bulb temperature T in,re Saturated water vapor pressure under s (T in,new ) is the fresh air flowing into the fresh air inlet (10) at a dry bulb temperature T in,new The saturated water vapor pressure under; P is the air pressure, P = 101325Pa.

3. The energy-saving temperature and humidity control method of air conditioning according to claim 2, characterized in that: In step S3, the dry bulb temperature T of the mixed air is mix and relative humidity RH mix The mixed air processing methods between different temperature threshold ranges and humidity threshold ranges include the following situations: 1) If The hot water coil (3) is controlled to be turned on to heat the mixed air isothermally, and then the spray system (5) is turned on to continue to humidify the heated mixed air isothermally; 2) If And RH mix >RH ex,max , the cold water coil (4) is controlled to be turned on to cool and dehumidify the mixed air, and then the hot water coil (3) is turned on to further heat the cooled and dehumidified mixed air; 3) If And RH ex,min ≤RH mix ≤RH ex,max , the hot water coil (3) is turned on to perform isohumidification heating on the mixed air; 4) If And RH mix <RH ex,min , the hot water coil (3) is turned on to heat the mixed air isothermally, and then the spray system (5) is turned on to continue to humidify the heated mixed air isothermally; 5) If And RH mix >RH ex,max , the cold water coil (4) is turned on to cool and dehumidify the mixed air; 6) If And RH ex,min ≤RH mix ≤RH ex,max , then the dynamic heat exchange balance equation of cold and hot air in the cross-flow gas heat exchange core is constructed to solve the optimal inflow and outflow speeds of fresh air and return air; 7) If And RH mix <RH ex,min , only the spray system (5) is turned on to perform isothermal humidification on the mixed air; 8) If And RH mix >RG ex,max , only the cold water coil (4) is turned on to cool and dehumidify the mixed air; 9) If And RG ex,min ≤RH mix ≤RG ex,max , the cold water coil (4) is turned on at the same time to cool the mixed air; 10) If And RH mix <RH ex,min , the cold water coil (4) and the spray system (5) are turned on to humidify, cool and reduce the temperature of the mixed air.

4. The energy-saving temperature and humidity control method of air conditioning according to claim 3, characterized in that: When the dry bulb temperature of the mixed air is T mix and relative humidity RH mix The situations between different temperature threshold intervals and humidity threshold intervals are as follows: And RH ex,min ≤RH mix ≤RH ex,max When the cross-flow gas heat exchange core cold and hot air dynamic heat exchange balance equation is constructed, the optimal fresh air and return air inflow and outflow rates are solved, including the following steps: S301: Calculate the enthalpy value i of the fresh air flowing into the gas cross-flow exchange section 11 from the fresh air inlet (10) in,new , the enthalpy value i of the mixed air flowing out of the gas cross exchange section (11) mix , the enthalpy value i of the return air flowing from the return air inlet (13) into the gas cross-flow exchange section (11) in,re , the enthalpy value i of the air flowing out of the gas cross-flow exchange section (11) at the return air outlet (12) out,re :: i in,new =c a T in,new +W in，new (c s T in,new +i fg ); i mix =c a T mix +W mix (c s T mix +i fg ); i in,re =c a T in,re +W in,re (c s T in,re +i fg ); i out,re =c a T out,re +W out,re (c s T out,re +i fg ); Among them, c a is the specific heat capacity of dry air, c a = =1.005 kJ / (kg·℃); c s is the specific heat capacity of water vapor, c s =1.82kJ / (kg·℃),i fg is the latent heat of vaporization of water, i fg =2500kJ / kg; T out,re and W out,re are respectively the outflow return air dry bulb temperature and the outflow return air humidity at the return air outlet (12) obtained by real-time monitoring; S302: Construct the dynamic heat exchange balance equation of cold and hot air in the cross-flow gas heat exchange core: h tr is the convective heat transfer coefficient, Among them, Nu in,new is the Nusselt number of the fresh air flowing into the fresh air inlet (10), Nu in,re is the Nusselt number of the return air flowing into the return air inlet (13), k is the thermal conductivity of air, k=0.026W (m·K); L is the side length of the square cross section of the cross-flow gas heat exchange core (111); Re in,new , Pr in,new are the Reynolds number and Prandtl number of the fresh air flowing into the fresh air inlet (10), Pr in,new =(c a +W in, new c a )μ / k; Re in,re , Pr in,re are the Reynolds number and Prandtl number of the return air flowing into the return air inlet (13), Pr in,re =(c a +W in,re c a )μ / k; μ is the air dynamic viscosity, μ = 18.1 = μPa·s; ρ in,new is the density of the fresh air flowing into the fresh air inlet (10), ρ in,re is the density of the return air flowing into the return air inlet (13); Where, =R is the specific gas constant of air, R = 287 J / (kg·K); S303: Under the limitation of the equilibrium equation constructed in step S302, a cold and hot air enthalpy exchange maximization model is constructed to solve the optimal fresh air and return air inflow and outflow speeds: in, The gas coupling flow velocity of the fresh air and the return air in the gas cross-flow heat exchange section (11); Then according to the optimal fresh air inflow speed obtained Optimal fresh air outflow speed Optimal return air inflow velocity Optimal return air outflow speed The fresh air inflow speed at the fresh air inlet (10), the fresh air outflow speed at the fresh air outflow portion (16), the return air inflow speed at the return air inflow portion (13) and the return air outflow speed at the return air outlet (12) are controlled respectively.

5. The energy-saving temperature and humidity control method of air conditioning according to claim 3, characterized in that: In the temperature and humidity treatment process except for the case 6) and the case 2), when only the cold water pan (4) is turned on, only the hot water coil (3) is turned on, only the spray system (5) is turned on, when the cold water coil (4) and the spray system (5) are turned on at the same time, or when the hot water coil (3) is turned on first and then the spray system (5), the optimal dry-bulb temperature of the fresh air flowing out of the fresh air outflow part (16) is controlled and optimal relative humidity and / or optimal spray speed of the spray system The solution model is as follows: Among them, i fg is the latent heat of vaporization of water, i fg =2500kJ / kg; c a is the specific heat capacity of dry air, c a =1.005 kJ / (kg·℃); and points are respectively the expected fresh air dry-bulb temperature, the expected fresh air relative humidity and the expected fresh air moisture content of the fresh air flowing out of the fresh air outflow portion (16), T out,new The dry-bulb temperature of the fresh air flowing out of the fresh air outflow portion (16) is monitored in real time; is the spray speed of the spray system; α is the opening coefficient of the spray system; β is the calculation coefficient for the latent heat of mixed air or evaporation heat loss; The corresponding working time of the hot water coil (3) and / or the cold water coil (4) and / or the spray speed of the spray system (5) are further controlled according to the solution result.

6. The energy-saving temperature and humidity control method of air conditioning according to claim 3, characterized in that: For the second case, the optimal fresh air dry-bulb temperature of the fresh air outflow portion (16) is constructed to minimize the air conditioning energy consumption. Optimal fresh air relative humidity and control the midpoint dry bulb temperature T ter Solve the equation: 18℃≤T out,new ≤27℃ 45%≤RH out,new ≤60%; Among them, W ter To control the moisture content at the midpoint, It is the expected fresh air humidity content of the fresh air flowing out of the fresh air outflow portion (16). According to the optimal dry-bulb temperature of the fresh air outlet (16) obtained by the solution Optimum relative humidity and optimally control the midpoint dry bulb temperature Based on this, the corresponding working time of the hot water coil (3) and the cold water coil (4) is further controlled.

7. The energy-saving temperature and humidity control method of air conditioning according to claim 1, characterized in that: The ideal dew point temperature minimum threshold The ideal dry-bulb temperature maximum threshold The ideal dry bulb temperature minimum threshold is 27°C The ideal relative humidity maximum threshold RH ex,max The ideal relative humidity minimum threshold RH is 60% ex,min 45%.

8. An energy-saving temperature and humidity control air conditioner using the control method according to any one of claims 1 to 7, wherein the air conditioner is used to further control the temperature and humidity of the mixed air after heat exchange between the fresh air and the return air of the data center, and then discharge it into the data center, characterized in that: The air conditioner comprises an equipment cabinet (1), the equipment cabinet (1) is divided into a gas cross-flow exchange part (11), a return air outlet (12) and a fresh air inlet (10) arranged on one side of the gas cross-flow exchange part (11), a cross-flow gas heat exchange core (111) is arranged in the gas cross-flow exchange part (11), the air conditioner also comprises a return air inlet (13), a fresh air heating part (14), a fresh air cooling part (15) and a fresh air outlet (16), the return air inlet (13) and the fresh air outlet (16) are respectively provided with a first negative pressure fan (131) and a second negative pressure fan (161), the return air inlet (13) and the fresh air outlet (16) are both connected to the indoor of the data center, and the return air outlet (12) and the fresh air inlet (13) are both connected to the outdoor of the data center; The air conditioner further comprises a central control single chip computer, a first air mass flow meter and a first temperature and humidity monitoring sensor arranged at the return air inlet (13), a second air mass flow meter and a second temperature and humidity monitoring sensor arranged at the return air outlet (12), a third air mass flow meter and a third temperature and humidity monitoring sensor arranged at the fresh air inlet (10), and a fourth air mass flow meter and a fourth temperature and humidity monitoring sensor arranged at the fresh air outlet (16); the first air mass flow meter, the first temperature and humidity monitoring sensor, the second air mass flow meter, the second temperature and humidity monitoring sensor, the third air mass flow meter, the third temperature and humidity monitoring sensor, the fourth air mass flow meter and the fourth temperature and humidity monitoring sensor are all connected to the central control single chip computer for communication; The air conditioner also includes a hot water coil (3) arranged in the fresh air heating section (14), a cold water coil (4) and a spray system (5) arranged in the fresh air cooling section (15); the hot water coil (3) is connected to a water heater (30) through a hot water inlet pipe (31) and a hot water return pipe (32); the water heater is arranged on the front side of the return air inlet section (13); the cold water coil (4) is connected to a chiller (40) through a cold water inlet pipe (41) and a cold water return pipe (42).

9. The energy-saving temperature and humidity regulating air conditioner according to claim 8, characterized in that: A return air inlet guide plate (61) is also provided in the gas cross-flow exchange section (11), and a mixed air filtering device (62) is also provided in the fresh air heating section (14).

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