Air handling unit control method and apparatus, fresh air system and air conditioning equipment

Abstract

The application relates to an air handling unit control method and device, a fresh air system and air conditioning equipment, and comprises the following steps: controlling an air handling unit to start, so that the air handling unit operates according to control parameters corresponding to a set working gear; obtaining a set air parameter, return air parameter and supply air parameter; adjusting the inlet air control parameter according to the set air parameter, the return air parameter and the supply air parameter; after the opening degree of the bypass air valve is stabilized, obtaining the exhaust pressure change rate of the evaporative heat pipe and the supply air temperature difference change rate of the supply air outlet; and adjusting the heat exchange control parameter according to the exhaust pressure change rate and the supply air temperature difference change rate. The application proposes a novel air handling unit structure design, and air is sent into a room after being deeply dehumidified and cooled for the second time during the operation of the air handling unit, so that the terminal dehumidification and temperature control function can be efficiently and energy-savingly realized.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of air conditioning system energy-saving control, in particular to an air handling unit control method and device, fresh air system and air conditioning equipment. BACKGROUND

[0002] The air handling system terminal equipment of medium-temperature water circulation has the problem of insufficient dehumidification capacity. For example, the performance of the cold coil in the conventional combined cabinet changes with water temperature and temperature difference. When the inlet water temperature increases by 1℃, the refrigeration capacity decreases by about 12%, and the dehumidification capacity decreases by 30%. When the water temperature difference increases by 1℃, the refrigeration capacity decreases by about 12.5%, and the dehumidification capacity decreases by 31%. Therefore, the dehumidification performance of the air handling system of medium-temperature water circulation changes greatly, and only increasing the air volume increases the actual power consumption, and it is difficult to meet the comfort requirement when the cold water inlet temperature is above 9℃.

[0003] The existing series air handling adjustment mode is not suitable for the air handling system of medium-temperature water circulation. This mode applied to the air handling system of medium-temperature water circulation has the problem of insufficient heat exchange capacity of the cold coil, which cannot meet the dehumidification demand, and the heat pipe cannot play its high-efficiency heat transfer performance because it does not have the dehumidification function, but only can play the role of auxiliary pre-cooling and heat recovery. SUMMARY

[0004] Therefore, it is necessary to provide an air handling unit control method and device, fresh air system and air conditioning equipment which can realize deep dehumidification and effectively save energy.

[0005] In a first aspect, the present application provides an air handling unit control method applied to an air handling unit, wherein the air handling unit comprises an air inlet, an air outlet, an air return, an air exhaust, an air inlet motor, a cold coil, a bypass air valve, an evaporation heat pipe, an electromagnetic pump, a condensation heat pipe and an air exhaust motor. The air inlet motor is connected to the air inlet end of the cold coil through the air inlet. One end of the bypass air valve is connected to the outdoor environment, and the other end of the bypass air valve and the air outlet end of the cold coil are both connected to the air inlet end of the evaporation heat pipe. The evaporation heat pipe is connected to the condensation heat pipe through the electromagnetic pump. The air outlet end of the evaporation heat pipe is connected to the air outlet. The air inlet end of the condensation heat pipe is connected to the air return. The air outlet end of the condensation heat pipe is connected to the air exhaust through the air exhaust motor.

[0006] The method comprises:

[0007] controlling the air handling unit to start, so that the air handling unit operates according to the control parameters corresponding to the set working gear;

[0008] obtaining a set air parameter, an air return parameter and an air supply parameter, wherein the air parameter comprises a dry-bulb temperature, a wet-bulb temperature and an enthalpy value.

[0009] adjusting the air intake control parameter according to the set air parameter, the return air parameter and the supply air parameter, wherein the air intake control parameter comprises a mixed air target temperature, an air intake gear of the air intake motor and an opening degree of the bypass air valve;

[0010] after the opening degree of the bypass air valve is stabilized, obtaining a change rate of exhaust pressure of the evaporative heat pipe and a change rate of supply air temperature difference of the air supply outlet;

[0011] adjusting a heat exchange control parameter according to the change rate of exhaust pressure and the change rate of supply air temperature difference, wherein the heat exchange control parameter comprises a gear of the electromagnetic pump.

[0012] In one embodiment, the adjusting the air intake control parameter according to the set air parameter, the return air parameter and the supply air parameter comprises:

[0013] calculating a room sensible heat ratio according to the set air parameter and the return air parameter;

[0014] calculating a cold coil sensible heat ratio according to the return air parameter and the supply air parameter;

[0015] adjusting the air intake control parameter according to the room sensible heat ratio and the cold coil sensible heat ratio.

[0016] In one embodiment, the adjusting the air intake control parameter according to the room sensible heat ratio and the cold coil sensible heat ratio comprises:

[0017] if a proportion of the cold coil sensible heat ratio and the room sensible heat ratio belongs to a first range, controlling the mixed air target temperature to be set as a first temperature, the air intake gear being unchanged and the bypass air valve being opened at a first opening degree;

[0018] if the proportion of the cold coil sensible heat ratio and the room sensible heat ratio belongs to a second range, controlling the mixed air target temperature to be set as a second temperature, the air intake gear being unchanged and the bypass air valve being opened at a second opening degree, wherein the second temperature is greater than the first temperature and the second opening degree is greater than the first opening degree;

[0019] if the proportion of the cold coil sensible heat ratio and the room sensible heat ratio belongs to a third range, controlling the mixed air target temperature to be set as a third temperature, the air intake gear being increased and the bypass air valve being opened at a third opening degree, wherein the third temperature is greater than the second temperature and the third opening degree is greater than the second opening degree.

[0020] In one embodiment, the adjusting the heat exchange control parameter according to the change rate of exhaust pressure and the change rate of supply air temperature difference comprises:

[0021] if the air supply temperature difference change rate is less than or equal to a preset temperature difference change rate threshold value and the ratio of the cold coil sensible heat ratio to the room sensible heat ratio belongs to a first range, maintaining the current gear of the electromagnetic pump;

[0022] if the air supply temperature difference change rate is less than or equal to a preset temperature difference change rate threshold value and the ratio of the cold coil sensible heat ratio to the room sensible heat ratio belongs to a second range or a third range, adjusting the gear of the electromagnetic pump according to the real-time exhaust pressure and the exhaust pressure change rate;

[0023] if the air supply temperature difference change rate is greater than a preset temperature difference change rate threshold value, adjusting the gear of the electromagnetic pump according to the real-time exhaust pressure.

[0024] In one of the embodiments, the adjusting the gear of the electromagnetic pump according to the real-time exhaust pressure and the exhaust pressure change rate comprises:

[0025] if the real-time exhaust pressure is less than or equal to a first pressure threshold value, increasing the gear of the electromagnetic pump;

[0026] if the real-time exhaust pressure is greater than the first pressure threshold value and less than or equal to a second pressure threshold value, increasing the gear of the electromagnetic pump according to the exhaust pressure change rate;

[0027] if the real-time exhaust pressure is greater than the second pressure threshold value and less than or equal to a third pressure threshold value, increasing or decreasing the gear of the electromagnetic pump according to the exhaust pressure change rate;

[0028] if the real-time exhaust pressure is greater than the third pressure threshold value, maintaining the current gear of the electromagnetic pump, wherein the first pressure threshold value is less than the second pressure threshold value, and the second pressure threshold value is less than the third pressure threshold value.

[0029] In one of the embodiments, the adjusting the gear of the electromagnetic pump according to the real-time exhaust pressure comprises:

[0030] if the real-time exhaust pressure is less than or equal to a first pressure threshold value, increasing the gear of the electromagnetic pump by a first amplitude;

[0031] if the real-time exhaust pressure is greater than the first pressure threshold value and less than or equal to a second pressure threshold value, increasing the gear of the electromagnetic pump by a second amplitude;

[0032] if the real-time exhaust pressure is greater than the second pressure threshold value, judging whether the difference between the real-time mixed air temperature and the set mixed air temperature is greater than a preset difference threshold value, and adjusting the gear of the electromagnetic pump according to the difference comparison result.

[0033] In one of the embodiments, the adjusting the gear of the electromagnetic pump according to the difference comparison result comprises:

[0034] If the difference between the real-time mixed air temperature and the set mixed air temperature is less than or equal to the preset difference threshold, increasing the opening of the bypass air valve according to a preset ratio, and re-adjusting the inlet air control parameter according to the real-time exhaust air pressure;

[0035] If the difference between the real-time mixed air temperature and the set mixed air temperature is greater than the preset difference threshold, re-adjusting the inlet air control parameter according to the room sensible heat ratio and the cold coil sensible heat ratio.

[0036] In one of the embodiments, the control air handling unit to start, so that the air handling unit operates according to the control parameter corresponding to the set working gear, comprising:

[0037] Controlling the inlet air motor, the cold coil, the evaporative heat pipe, the electromagnetic pump, the condensing heat pipe and the exhaust air motor to start to operate according to the control parameter corresponding to the set working gear;

[0038] Controlling the bypass air valve to keep closed.

[0039] Secondly, the application also provides an air handling unit control device, which is applied to an air handling unit, wherein the air handling unit comprises an air inlet, an air outlet, an air return, an air exhaust, an inlet air motor, a cold coil, a bypass air valve, an evaporative heat pipe, an electromagnetic pump, a condensing heat pipe and an exhaust air motor, the inlet air motor is connected to the air inlet end of the cold coil, one end of the bypass air valve is connected to the outdoor environment, the other end of the bypass air valve and the air outlet end of the cold coil are both connected to the air inlet end of the evaporative heat pipe, the evaporative heat pipe is connected to the condensing heat pipe through the electromagnetic pump, the air outlet end of the evaporative heat pipe is connected to the air outlet, the air inlet end of the condensing heat pipe is connected to the air return, and the air outlet end of the condensing heat pipe is connected to the air exhaust through the exhaust air motor;

[0040] The device comprises:

[0041] The starting module is configured to control the air handling unit to start, so that the air handling unit operates according to the control parameter corresponding to the set working gear;

[0042] The first obtaining module is configured to obtain a set air parameter, an air return air parameter and an air outlet air parameter, wherein the air parameter comprises a dry-bulb temperature, a wet-bulb temperature and an enthalpy value;

[0043] The first adjusting module is configured to adjust the air intake control parameter according to the set air parameter, the return air parameter, and the supply air parameter, wherein the air intake control parameter comprises a mixed air target temperature, an air intake gear of the air intake motor, and an opening degree of the bypass air valve.

[0044] The second obtaining module is configured to obtain a change rate of exhaust pressure of the evaporative heat pipe and a change rate of supply air temperature difference of the supply air outlet after the opening degree of the bypass air valve is stabilized.

[0045] The second adjusting module is configured to adjust a heat exchange control parameter according to the change rate of exhaust pressure and the change rate of supply air temperature difference, wherein the heat exchange control parameter comprises a gear of the electromagnetic pump.

[0046] In a third aspect, the present application further provides an air handling unit, comprising a controller, an air intake outlet, a supply air outlet, a return air outlet, an exhaust air outlet, an air intake motor, a cold coil, a bypass air valve, an evaporative heat pipe, an electromagnetic pump, a condensing heat pipe, and an exhaust air motor.

[0047] The air intake motor is connected to an air inlet end of the cold coil through the air intake outlet, one end of the bypass air valve is connected to an outdoor environment, the other end of the bypass air valve and an air outlet end of the cold coil are both connected to an air inlet end of the evaporative heat pipe, the evaporative heat pipe is connected to the condensing heat pipe through the electromagnetic pump, an air outlet end of the evaporative heat pipe is connected to the supply air outlet, an air inlet end of the condensing heat pipe is connected to the return air outlet, and an air outlet end of the condensing heat pipe is connected to the exhaust air outlet through the exhaust air motor.

[0048] The controller is connected to the air intake motor, the cold coil, the bypass air valve, the evaporative heat pipe, the electromagnetic pump, the condensing heat pipe, and the exhaust air motor, respectively.

[0049] The controller is configured to implement the steps of the air handling unit control method of the first aspect.

[0050] In a fourth aspect, the present application further provides a fresh air system comprising the air handling unit of the third aspect.

[0051] In a fifth aspect, the present application further provides an air conditioning device comprising the air handling unit of the third aspect.

[0052] In a sixth aspect, the present application further provides a computer device comprising a memory and a processor, wherein the memory stores a computer program, and the processor implements the steps of the air handling unit control method of the first aspect when executing the computer program.

[0053] In a seventh aspect, the present application also provides a computer readable storage medium, having stored thereon a computer program, which, when executed by a processor, implements the steps of the air handling unit control method of the first aspect.

[0054] In an eighth aspect, the present application also provides a computer program product, comprising a computer program which, when executed by a processor, implements the steps of the air handling unit control method of the first aspect.

[0055] In summary, the present application provides an air handling unit control method, device, fresh air system and air conditioning equipment, comprising: controlling the air handling unit to start, so that the air handling unit operates according to the control parameters corresponding to the set working gear; obtaining the set air parameter, return air parameter and supply air parameter, wherein; adjusting the inlet control parameter according to the set air parameter, return air parameter and supply air parameter; after the opening degree of the bypass damper is stable, obtaining the exhaust pressure change rate of the evaporative heat pipe and the supply air temperature difference change rate of the supply air outlet; adjusting the heat exchange control parameter according to the exhaust pressure change rate and the supply air temperature difference change rate. The present application proposes a novel air handling unit structure design, and during the operation of the air handling unit, the air is sent into the indoor after being deeply dehumidified and cooled for the second time, so that the terminal dehumidification and temperature control function can be efficiently and energy-savingly realized. BRIEF DESCRIPTION OF DRAWINGS

[0056] Figure 1 It is a structural block diagram of the air handling unit in an embodiment;

[0057] Figure 2 It is a flowchart of the air handling unit control method in an embodiment;

[0058] Figure 3 It is a flowchart of the air handling unit control method in an embodiment;

[0059] Figure 4 It is a flowchart of the air handling unit control method in an embodiment;

[0060] Figure 5 It is a flowchart of the air handling unit control method in an embodiment;

[0061] Figure 6 It is a flowchart of the air handling unit control method in an embodiment;

[0062] Figure 7 It is a flowchart of the air handling unit control method in an embodiment;

[0063] Figure 8A structural block diagram of an air handling unit control device in an embodiment;

[0064] Figure 9 An internal structural diagram of a computer device in an embodiment. DETAILED DESCRIPTION

[0065] In order to make the purposes, technical solutions and advantages of the present application clearer, the present application is further described in detail below with reference to the drawings and embodiments. It should be understood that the specific embodiments described herein are only used to explain the present application and not to limit the present application.

[0066] As described in the foregoing background, the existing air handling unit has a low dehumidification capacity when circulating medium temperature water. When a conventional combination of a cold coil and a reheater is used, the performance of the cold coil of the air handling unit varies with the water temperature and the water temperature difference, for example, the refrigeration capacity decreases by about 12% and the dehumidification capacity decreases by about 30% when the water inlet temperature increases by 1℃. The refrigeration capacity decreases by about 12.5% and the dehumidification capacity decreases by about 31% when the water temperature difference increases by 1℃. Therefore, the dehumidification capacity of the conventional air handling unit varies greatly under the condition of medium temperature water circulation. Increasing the air volume to adjust the dehumidification capacity and the refrigeration capacity will increase the actual power consumption, and the cold water inlet temperature needs to be higher than 9℃, which cannot meet the demand of providing comfortable air for users.

[0067] In actual application, the water temperature classification of the air conditioning water system is as follows. If the chilled water is less than 6℃, the cold coil is in a low temperature water circulation state. If the chilled water is in the range of 6-8℃, the cold coil is in a normal temperature water circulation state. If the chilled water is in the range of 9-13℃, the cold coil is in a medium temperature water circulation state. If the chilled water is in the range of 14-17℃, the cold coil is in a high temperature water circulation state. In the following embodiments, medium and low temperature refer to the temperature of water covered by medium temperature water and normal temperature water, i.e., water below 13℃ can be referred to as medium and low temperature water.

[0068] There is an urgent need for an energy-saving air handling unit design scheme that can effectively meet the air dehumidification and cooling demand without increasing the cost, and improve the problems of low dehumidification capacity of the medium temperature water cold coil and low heat pipe heat exchange efficiency of the existing air handling unit.

[0069] The air handling unit control method provided by the embodiments of the present application can be applied to the air handling unit as shown in Figure 1 The air handling unit in the embodiment includes an air inlet, an air outlet, an air return, an air exhaust, an air inlet motor 110, a cold coil 120, a bypass air valve 130, an evaporation heat pipe 140, an electromagnetic pump 150, a condensation heat pipe 160 and an air exhaust motor 170.

[0070] In the embodiment, the air inlet motor 110 is connected to the air inlet end of the cold coil 120 through the air inlet, one end of the bypass air valve 130 is connected to the outdoor environment, the other end of the bypass air valve 130 and the air outlet end of the cold coil 120 are both connected to the air inlet end of the evaporative heat pipe 140, the evaporative heat pipe 140 is connected to the condensing heat pipe 160 through the electromagnetic pump 150, and the air outlet end of the evaporative heat pipe 140 is connected to the air outlet through the air outlet motor 170, and the air inlet end of the condensing heat pipe 160 is connected to the air inlet, and the air outlet end of the condensing heat pipe 160 is connected to the air outlet through the air outlet motor 170.

[0071] In the embodiment, the air inlet motor 110 is used to introduce a certain flow of fresh air from the outdoor environment according to the gear corresponding to the set working mode and real-time working state, and make the fresh air flow into the cold coil 120 through the air inlet at a preset flow rate, so as to perform the first round of dehumidification and cooling treatment on the fresh air.

[0072] The cold coil 120 includes a water inlet pipeline and a water return pipeline, wherein the water inlet pipeline is used to introduce medium-temperature water, and the high-temperature water is output through the water return pipeline to realize water circulation. The cold coil 120 is used to perform dehumidification and cooling treatment on the fresh air introduced by the air inlet motor 110, convert the fresh air into medium-low temperature air, and adjust the air humidity of the medium-low temperature air to medium-high humidity.

[0073] The bypass air valve 130 is used to introduce fresh air and mix the fresh air with the medium-low temperature air output by the cold coil 120 to obtain medium-high temperature and humidity air.

[0074] The evaporative heat pipe 140 is used to process the medium-high temperature and humidity air into low-temperature and low-humidity air through the evaporative heat absorption effect, and deliver the low-temperature and low-humidity air to the indoor environment.

[0075] The indoor air flows into the condensing heat pipe 160 through the air inlet, and the condensing heat pipe 160 performs heat recovery on the medium-low temperature air to obtain cooled liquid condensate water and high-temperature air. The liquid condensate water is delivered back to the evaporative heat pipe 140 to perform cooling and dehumidification treatment on the mixed air flowing through the evaporative heat pipe 140. The high-temperature air is discharged to the outdoor environment through the air outlet under the action of the air outlet motor 170.

[0076] In the embodiment, the evaporative heat pipe 140 is also connected to the condensing heat pipe 160 through the electromagnetic pump 150. The electromagnetic pump 150 is used to control the exhaust pressure and exhaust rate of the high-temperature steam discharged from the evaporative heat pipe 140 to the condensing heat pipe 160. The electromagnetic pump 150 includes multiple gears. In actual application, the gears of the electromagnetic pump 150 can be adjusted to adjust the exhaust pressure and exhaust rate of the evaporative heat pipe 140. Specifically, the higher the gear of the electromagnetic pump 150, the greater the exhaust pressure and exhaust rate, the greater the heat exchange amount between the evaporative heat pipe 140 and the condensing heat pipe 160, and the higher the heat exchange efficiency.

[0077] In one embodiment, as shown in Figure 2 Fig. 1, a method for controlling an air handling unit is provided, which is applied to an air handling unit in Figure 1 and includes the following steps:

[0078] S201, controlling the air handling unit to start, so that the air handling unit operates according to the control parameters corresponding to the set working gear.

[0079] In this embodiment, the main machine of the air handling unit can start working according to the start control signal sent by the user through the terminal device. After receiving the start control signal, the main machine controls the related elements of the air handling unit to start working. The terminal device can be a remote controller, a smart panel or a mobile terminal, which can communicate and interact with the air handling unit. The starting control terminal of the air handling unit is not limited in this embodiment.

[0080] In this embodiment, the air handling unit is in a cooling mode, and the return water temperature is set in a preset temperature range. In the normal working mode, the air handling unit can adjust the temperature and humidity of the fresh air according to the control logic corresponding to the working mode.

[0081] S202, obtaining the set air parameters, return air parameters and supply air parameters, wherein the air parameters include dry bulb temperature, wet bulb temperature and enthalpy.

[0082] In this embodiment, the set air parameters include the set dry bulb temperature, the set wet bulb temperature and the enthalpy at the set dry bulb temperature and the set wet bulb temperature. The return air parameters include the return air dry bulb temperature, the return air wet bulb temperature and the enthalpy at the return air dry bulb temperature and the return air wet bulb temperature. The supply air parameters include the supply air dry bulb temperature, the supply air wet bulb temperature and the enthalpy at the supply air dry bulb temperature and the supply air wet bulb temperature.

[0083] The dry bulb temperature can be obtained by a dry bulb thermometer exposed to the air without direct sunlight. The dry bulb thermometer transmits the corresponding dry bulb temperature value to the controller of the air handling unit after recording the dry bulb temperature value at the corresponding position. For example, the return air dry bulb temperature can be obtained by testing the dry bulb temperature at the return air inlet, and the supply air dry bulb temperature can be obtained by testing the dry bulb temperature at the supply air inlet.

[0084] The wet bulb temperature refers to the lowest temperature that the current environment can reach only through evaporation of water. The enthalpy value is used to indicate whether the current environment is in a state of absorbing heat or losing heat. Both the wet bulb temperature and the enthalpy value can be obtained by an air parameter calculation tool arranged at a corresponding position. It should be noted that the air parameter calculation tool can be configured according to the needs of the actual application scene.

[0085] In S203, the air intake control parameter is adjusted according to the set air parameter, the return air parameter and the supply air parameter. The air intake control parameter includes a mixed air target temperature, an air intake gear of an air intake motor and an opening degree of a bypass air valve.

[0086] In this embodiment, after the set air parameter, the return air parameter and the supply air parameter are obtained, the room sensible heat ratio and the cold coil sensible heat ratio can be further calculated, and the air intake control parameter is adjusted according to the room sensible heat ratio and the cold coil sensible heat ratio.

[0087] Specifically, the room sensible heat ratio is calculated according to the set air parameter and the return air parameter, and the cold coil sensible heat ratio is calculated according to the return air parameter and the supply air parameter.

[0088] For example, if the set dry bulb temperature is T, the set wet bulb temperature is Ts, the enthalpy value at the set dry bulb temperature and the set wet bulb temperature is H, after the air handling unit is started, the detected indoor return air dry bulb temperature is T1, the return air wet bulb temperature is Ts1, and the enthalpy value at the return air dry bulb temperature and the return air wet bulb temperature is H1, after the air handling unit is started, the initial supply air dry bulb temperature is T2, the supply air wet bulb temperature is Ts2, and the enthalpy value at the supply air dry bulb temperature and the supply air wet bulb temperature is H2.

[0089] The formula for calculating the room sensible heat ratio is S0= (T1-T) / (H1-H), where S0 is the room sensible heat ratio.

[0090] The formula for calculating the cold coil sensible heat ratio in the medium temperature water circulation state is S1= (T1-T2) / (H1-H2), where S1 is the cold coil sensible heat ratio.

[0091] Further, the supply air temperature Ts and the total supply air volume V can be collected by a temperature detection component and a flow monitoring component arranged at the supply air outlet of the air handling unit, the fresh air temperature T0 can be detected by a temperature detection component arranged at the bypass air valve, and the real-time mixed air temperature Tz can be detected by a temperature detection component arranged at the inlet of the evaporative heat pipe.

[0092] It should be noted that the real-time supply air temperature of the supply air outlet of the air handling component can be calculated by the following formula:

[0093] Ts= (V * (1-N) * Tz+V * N * T0) / V, wherein Ts is the real-time mixed air temperature, V is the supply air flow, N is the opening degree of the bypass damper, T0 is the temperature of the fresh air, and Tz is the real-time supply air temperature.

[0094] S204, after the opening degree of the bypass damper is stabilized, the exhaust pressure change rate of the evaporative heat pipe and the supply air temperature difference change rate of the supply air outlet are obtained.

[0095] In the embodiment, after the opening degree of the bypass damper is stabilized, the evaporative heat pipe and the condensing heat pipe have entered the stable heat exchange stage in parallel, the exhaust pressure P1 in the exhaust pipe connected to the electromagnetic pump of the evaporative heat pipe is detected, and the initial exhaust pressure P of the evaporative heat pipe detected when the air handling unit is started is combined to calculate the exhaust pressure change rate ΔP, wherein ΔP=(P1-P) / 30s. It should be noted that the calculation of the exhaust pressure change rate can be real-time calculation, the time interval between P1 and P can be fixed as 30 seconds (s), P1 represents the real-time exhaust pressure, and P represents the exhaust pressure 30s before the real-time exhaust pressure.

[0096] Similarly, the supply air temperature of the supply air outlet can be collected in real time by the temperature detection assembly arranged at the supply air outlet, and the supply air temperature difference ΔT=T2-T2' is calculated, wherein T2 is the real-time supply air temperature, and T2' is the supply air temperature after a fixed time of detecting the real-time supply air temperature. The supply air temperature difference change rate is ΔTm=ΔT / 30S.

[0097] In the embodiment, the preset exhaust pressure change rate threshold PM and the supply air temperature difference change rate threshold TM are also included. By comparing the size relationship between the exhaust pressure change rate of the evaporative heat pipe and the supply air temperature difference change rate of the supply air outlet and the exhaust pressure change rate threshold PM and the supply air temperature difference change rate threshold TM, the real-time state of the air handling unit can be accurately judged, so that the air handling unit can be accurately adjusted based on the real-time state to improve the heat exchange efficiency of the air handling unit.

[0098] S205, adjusting the heat exchange control parameter according to the exhaust pressure change rate and the supply air temperature difference change rate, wherein the heat exchange control parameter includes the gear of the electromagnetic pump.

[0099] In the embodiment, adjusting the gear of the electromagnetic pump can change the exhaust pressure of the evaporative heat pipe to the condensing heat pipe and the flow rate and pressure of the refrigerant inside the heat pipe, so as to improve the heat exchange efficiency of the heat pipe. In the embodiment, the gear of the electromagnetic pump is adjusted in real time based on the exhaust pressure change rate and the supply air temperature difference change rate, so that the heat exchange efficiency can be higher, and the supply air temperature and humidity of the air handling unit can be accurately controlled.

[0100] In one embodiment, as Figure 3The air inlet control parameters are adjusted according to the room sensible heat ratio and the cooling coil sensible heat ratio, including:

[0101] In S301, if the ratio of the cooling coil sensible heat ratio to the room sensible heat ratio belongs to a first range, the mixed air target temperature is set to a first temperature, the air inlet gear is unchanged, and the bypass damper is opened at a first opening degree.

[0102] In S302, if the ratio of the cooling coil sensible heat ratio to the room sensible heat ratio belongs to a second range, the mixed air target temperature is set to a second temperature, the air inlet gear is unchanged, and the bypass damper is opened at a second opening degree, wherein the second temperature is greater than the first temperature, and the second opening degree is greater than the first opening degree.

[0103] In S303, if the ratio of the cooling coil sensible heat ratio to the room sensible heat ratio belongs to a third range, the mixed air target temperature is set to a third temperature, the air inlet gear is increased, and the bypass damper is opened at a third opening degree, wherein the third temperature is greater than the second temperature, and the third opening degree is greater than the second opening degree.

[0104] In the embodiment, the first range can be configured as 1-1.2, the second range can be configured as 1.2-1.3, and the third range can be configured as 1.3-1.4.

[0105] In an actual application scenario, assuming that the cooling coil sensible heat ratio is S1, the room sensible heat ratio is S0, and the ratio of the cooling coil sensible heat ratio to the room sensible heat ratio is S1 / S0. In specific embodiments, the S1 / S0 ratio can be used to determine the relationship between the cooling coil cooling and dehumidifying capacity under the medium-temperature water circulation state and the total load of the room.

[0106] If S1 / S0 belongs to the range of 1-1.2, it indicates that the cooling coil under the medium-temperature water circulation state needs to meet the load demand of 90% indoor air temperature and humidity regulation. At this time, the air inlet gear of the air inlet motor is unchanged, the mixed air target temperature is set to a first temperature Tz1, the bypass damper is adjusted to open at a first opening degree N1, a small amount of bypass air flows into the air circulation unit, mixes with the medium-temperature and low-temperature air output by the cooling coil, and then performs secondary heat exchange through the evaporative heat pipe, thereby slowly and stably achieving secondary dehumidification and cooling regulation of the mixed air.

[0107] If S1 / S0 belongs to the range of 1.2-1.3, it indicates that the cooling coil under the medium-temperature water circulation state needs to meet the load demand of 60% indoor air temperature and humidity regulation. At this time, the air inlet gear of the air inlet motor is unchanged, the mixed air target temperature is set to a second temperature Tz2, the bypass damper is adjusted to open at a second opening degree N2, a large amount of bypass air flows into the air circulation unit, mixes with the medium-temperature and low-temperature air output by the cooling coil, and then performs secondary heat exchange through the evaporative heat pipe, thereby increasing the regulation speed of the secondary dehumidification and cooling regulation of the mixed air.

[0108] If S1 / S0 falls within the range of 1.3-1.4, it indicates that the cooling coil under medium-temperature water circulation needs to meet the load requirement of 40% indoor air temperature and humidity regulation. At this time, the air intake motor is adjusted to a higher level, the target temperature of the mixed air is set to the third temperature Tz3, and the bypass ventilation valve is opened at the third opening degree N3, so that a larger amount of bypass ventilation flows into the air circulation unit. After mixing with the medium-low temperature air output by the cooling coil, it undergoes secondary heat exchange through the evaporative heat pipe, further increasing the regulation speed of secondary dehumidification and cooling regulation of the mixed air.

[0109] It should be noted that the air intake setting can be set to medium speed when starting up; here, it is adjusted to medium-high speed.

[0110] The higher the opening degree of the bypass vent valve, the greater its air intake volume and velocity. In one feasible embodiment, an intake motor connected to the bypass vent valve can be configured to regulate its air intake flow rate and velocity. The mixed air temperature is related to the air intake volume and velocity of the bypass vent valve; the greater the air intake volume, the higher the mixed air temperature.

[0111] In practice, the opening degree of the bypass ventilation valve can also be determined based on the above formula Ts=(V*(1-N)*Tz+V*N*T0) / V, where Ts is the real-time mixed air temperature and Tz is the real-time supply air temperature.

[0112] In one embodiment, such as Figure 4 As shown, the heat exchange control parameters are adjusted according to the rate of change of exhaust pressure and the rate of change of supply air temperature difference, including:

[0113] S401, if the supply air temperature difference change rate is less than or equal to the preset temperature difference change rate threshold, and the ratio of the sensible heat ratio of the cold coil to the sensible heat ratio of the room is within the first range, maintain the current setting of the electromagnetic pump.

[0114] S402, if the supply air temperature difference change rate is less than or equal to the preset temperature difference change rate threshold, and the ratio of the sensible heat ratio of the cold coil to the sensible heat ratio of the room is in the second or third range, adjust the speed of the electromagnetic pump according to the real-time exhaust pressure and the exhaust pressure change rate.

[0115] S403: If the rate of change of the supply air temperature difference is greater than the preset temperature difference rate threshold, the electromagnetic pump speed will be adjusted according to the real-time exhaust pressure.

[0116] In this embodiment, assuming the air supply temperature difference change rate is △Tm and the preset temperature difference change rate threshold is TM, the real-time operating status of the air handling unit can be divided into three cases.

[0117] In the first case, when △Tm≤TM and S1 / S0 is within the range of 1-1.2, it can be determined that the evaporation heat pipe and the condensation heat pipe can fully perform the secondary heat exchange treatment, and thus the exhaust pressure of the evaporation heat pipe does not need to be changed, i.e., the gear of the electromagnetic pump does not need to be adjusted, and the current gear of the electromagnetic pump is maintained.

[0118] In the second case, when △Tm≤TM and S1 / S0 is within the range of 1.2-1.4, it can be determined that the evaporation heat pipe and the condensation heat pipe cannot fully perform the secondary heat exchange treatment, and thus the exhaust pressure of the evaporation heat pipe and the internal refrigerant flow rate need to be changed.

[0119] In the third case, when △Tm>Tm, it can be determined that the evaporation heat pipe and the condensation heat pipe cannot fully perform the secondary heat exchange treatment, and thus the exhaust pressure of the evaporation heat pipe and the internal refrigerant flow rate need to be changed.

[0120] In one embodiment, as shown in FIG. 2, in the second case, the gear of the electromagnetic pump is adjusted according to the real-time exhaust pressure and the exhaust pressure change rate, including: Figure 5

[0121] S501, if the real-time exhaust pressure is less than or equal to a first pressure threshold, the gear of the electromagnetic pump is increased;

[0122] S502, if the real-time exhaust pressure is greater than the first pressure threshold and less than or equal to a second pressure threshold, the gear of the electromagnetic pump is increased according to the exhaust pressure change rate;

[0123] S503, if the real-time exhaust pressure is greater than the second pressure threshold and less than or equal to a third pressure threshold, the gear of the electromagnetic pump is increased or decreased according to the exhaust pressure change rate;

[0124] S504, if the real-time exhaust pressure is greater than the third pressure threshold, the current gear of the electromagnetic pump is maintained, wherein the first pressure threshold is less than the second pressure threshold, and the second pressure threshold is less than the third pressure threshold.

[0125] In this embodiment, it is assumed that the real-time exhaust pressure is P1, the first pressure threshold is A1, the second pressure threshold is A2, and the third pressure threshold is A3, wherein A1

[0126] When P1≤A1 is detected, it indicates that the evaporation heat pipe is in a low-pressure and low-flow-rate heat exchange state or a no-driving force heat exchange state, and the internal refrigerant flow rate and the steam exhaust pressure can be effectively increased by increasing the gear of the electromagnetic pump. Specifically, the gear of the electromagnetic pump can be increased by one gear amplitude. It should be noted that the gear increase amplitude of the electromagnetic pump can be determined based on the actual application scenario, which is not limited here.

[0127] ​When A1 < P1 ≤ A2 is detected, it indicates that the heat pipe is in a low-to-medium flow rate heat exchange state at this time. At this time, more refined adjustment can be performed in combination with the pressure change rate ΔP. If the pressure change rate ΔP ≤ PM, the heat pipe internal refrigerant flow rate and the pressure are increased to increase the heat pipe heat exchange efficiency, which can be achieved by adjusting the electromagnetic pump to 1 / 2 gear.

[0128] When A2 < P1 ≤ A3 is detected, it indicates that the heat pipe is in a medium-to-high flow rate heat exchange state at this time. At this time, more refined adjustment can be performed in combination with the pressure change rate ΔP. If the pressure change rate ΔP ≤ PM, the heat pipe internal refrigerant flow rate and the exhaust pressure are appropriately increased to improve the heat exchange efficiency, which can be achieved by adjusting the electromagnetic pump to 1 / 4 gear. If the pressure change rate ΔP > PM, the heat pipe internal refrigerant flow rate is relatively high, and the heat pipe heat exchange efficiency is stable, which can be achieved by adjusting the electromagnetic pump to 1 / 5 gear, so that the internal boiling bubbles flow more fully to the condensing section, the liquid refrigerant flow is reduced, the convective heat transfer is strengthened, and the air outlet temperature is lower.

[0129] When P1 > A3 is detected, it indicates that the heat pipe internal flow rate reaches the design critical boiling limit point, and the electromagnetic pump gear is kept unchanged.

[0130] In actual application scenarios, the adjustment of the electromagnetic pump gear amplitude can be determined based on the division of the electromagnetic pump gear amplitude, and can be adaptively changed based on the needs of actual application scenarios.

[0131] In one embodiment, as shown in FIG. 3, in the third case described above, the electromagnetic pump gear is adjusted according to the real-time exhaust pressure, including: Figure 6

[0132] S601, if the real-time exhaust pressure is less than or equal to the first pressure threshold, the gear of the electromagnetic pump is adjusted by the first amplitude;

[0133] S602, if the real-time exhaust pressure is greater than the first pressure threshold and less than or equal to the second pressure threshold, the gear of the electromagnetic pump is adjusted by the second amplitude;

[0134] S603, if the real-time exhaust pressure is greater than the second pressure threshold, it is judged whether the difference between the real-time mixed air temperature and the set mixed air temperature is greater than a preset difference threshold, and the gear of the electromagnetic pump is adjusted according to the difference comparison result.

[0135] In this embodiment, it is assumed that the real-time exhaust pressure is P1, the first pressure threshold is A1, the second pressure threshold is A2, and the third pressure threshold is A3, where A1 < A2 < A3.

[0136] ​When P1

[0137] When A1

[0138] When A2

[0139] In one embodiment, as shown in FIG. 7A, the gear of the electromagnetic pump is adjusted according to the comparison result of the difference, including: Figure 7

[0140] S701, if the difference between the real-time mixed air temperature and the set mixed air temperature is less than or equal to a preset difference threshold, the opening of the bypass air valve is increased by a preset ratio, and the gear of the electromagnetic pump is adjusted again according to the real-time exhaust air pressure;

[0141] S702, if the difference between the real-time mixed air temperature and the set mixed air temperature is greater than the preset difference threshold, the inlet air control parameter is adjusted again according to the room sensible heat ratio and the cold coil sensible heat ratio.

[0142] In this embodiment, if the difference between the real-time mixed air temperature and the set mixed air temperature is less than or equal to a preset difference threshold, it means that the bypass air valve is running in a normal opening range. If the difference between the real-time mixed air temperature and the set mixed air temperature is greater than the preset difference threshold, it means that the opening of the bypass air valve is in an abnormal state, and the opening of the bypass air valve needs to be adjusted according to the ratio of the room sensible heat ratio and the cold coil sensible heat ratio.

[0143] In actual application, the set mixed air temperature can be determined based on the above formula Ts= (V*(1-N)*Tz+V*N*T0) / V, at this time, Ts is the real-time mixed air temperature, and Tz is the real-time supply air temperature. The real-time mixed air temperature can be measured by a temperature detection component arranged at the inlet position of the evaporative heat pipe.

[0144] In this embodiment, the preset difference threshold can be set to ±0.5°. It should be noted that the specific value of the preset difference threshold can be determined according to the needs of the actual application scene.

[0145] In one embodiment, the air handling unit is controlled to start, so that the air handling unit runs according to the control parameter corresponding to the set working gear, including: ​

[0146] controlling the air inlet motor, the cold coil, the evaporative heat pipe, the electromagnetic pump, the condensing heat pipe and the air outlet motor to start to operate according to the control parameters corresponding to the set working gear;

[0147] controlling the bypass air valve to keep in a closed state.

[0148] In the embodiment, when the main machine starts the air handling unit according to the user setting mode, the return water temperature is set to 12-17℃, that is, the return water temperature is medium-low temperature, the total water pump operates to circulate the pipeline of the chilled water in and out of the cold coil in the building, and the terminal air handling unit operates according to the air volume of the user setting gear. The fresh air is processed by the medium-temperature cold coil to become medium-low temperature and humidity air. In order to more accurately control the heat pipe and compensate the dehumidification capacity, the bypass air valve is not opened at the first start, and the medium-low temperature and humidity air is directly sent into the indoor environment.

[0149] In summary, the embodiment provides an air handling unit control method, which can realize twice air temperature and humidity adjustment, two rounds of cooling and dehumidification processing, solve the terminal dehumidification capacity temperature of the medium-temperature water energy-saving system, and mix the fresh air with the medium-low temperature and humidity air output by the cold coil based on the bypass air valve to realize accurate temperature control. In addition, the air handling unit control method adjusts the gear of the electromagnetic pump between the evaporative heat pipe and the condensing heat pipe in real time according to the exhaust pressure data of the evaporative heat pipe and the supply air data, which can ensure efficient heat exchange of the heat pipe. The air handling unit does not need to use a rotary wheel for dehumidification, which reduces the number of system equipment and manufacturing cost, and reduces the maintenance rate and after-sales maintenance cost.

[0150] In a more detailed embodiment, the structure of the air handling unit shown in Figure 1 The flow direction of the fresh air and the refrigerant in the air handling unit control method provided by the embodiment is described.

[0151] The air inlet motor introduces the fresh air into the fan section of the unit, and the fresh air flows to the medium-temperature water cold coil and the bypass air valve. The fresh air is cooled and dehumidified by the medium-temperature cold coil to become medium-low temperature air with medium-high humidity, and the bypass air valve adjusts part of the fresh air to mix with the medium-low temperature air at the bypass air valve to obtain medium-high temperature and humidity air. After the medium-high temperature and humidity air is processed into low temperature and humidity air by the evaporative heat pipe, the low temperature and humidity air is sent into the indoor environment.

[0152] The indoor medium-low temperature air enters the condensing heat pipe through the return air inlet, and the medium-low temperature air is heat-recovered and utilized by the condensing heat pipe, and then processed into high temperature air. The high temperature air is discharged to the outdoor environment.

[0153] The initial state of the refrigerant in the evaporation heat pipe is low-temperature and low-pressure liquid state. After being converted into high-temperature and low-pressure steam through heat absorption and evaporation, the high-temperature and low-pressure steam is converted into high-temperature and high-pressure steam by the electromagnetic pump. The high-temperature and high-pressure steam flows into the condensation heat pipe, is converted into low-temperature and high-pressure liquid state through the condensation heat pipe, and finally, the low-temperature and high-pressure liquid state refrigerant flows to the evaporation heat pipe through the flow path and is converted into low-temperature and low-pressure liquid state refrigerant in the circulation process.

[0154] It should be understood that, although each step in the flowchart involved in each embodiment as described above is shown in sequence according to the arrow, these steps are not necessarily executed in the order indicated by the arrow. Unless otherwise specified herein, there is no strict order limitation for the execution of these steps, and these steps can be executed in other orders. Moreover, at least part of the steps in the flowchart involved in each embodiment as described above can include multiple steps or stages, which are not necessarily executed at the same time, but can be executed at different times, and the execution order of these steps or stages is not necessarily sequential, but can be alternately executed with at least part of other steps or steps or stages in other steps.

[0155] Based on the same inventive concept, the embodiments of the present application also provide an air handling unit control device for implementing the above-mentioned air handling unit control method. The implementation scheme for solving the problem provided by the device is similar to the implementation scheme described in the above method, so the specific limitations in one or more air handling unit control device embodiments provided below can refer to the limitations of the air handling unit control method described above, which will not be described here.

[0156] In one embodiment, as shown in Figure 8 An air handling unit control device 800 is provided, comprising: a starting module 810, a first acquisition module 820, a first adjustment module 830, a second acquisition module 840 and a second adjustment module 850, wherein:

[0157] The starting module 810 is configured to control the air handling unit to start, so that the air handling unit operates according to the control parameters corresponding to the set working gear;

[0158] The first acquisition module 820 is configured to acquire the set air parameters, the return air parameters and the supply air parameters, wherein the air parameters include dry-bulb temperature, wet-bulb temperature and enthalpy value;

[0159] The first adjustment module 830 is configured to adjust the inlet air control parameters according to the set air parameters, the return air parameters and the supply air parameters, wherein the inlet air control parameters include the mixed air target temperature, the inlet air gear of the inlet air motor and the opening degree of the bypass air valve;

[0160] The second acquisition module 840 is configured to acquire a change rate of exhaust pressure of the evaporative heat pipe and a change rate of air supply temperature difference of the air supply outlet after the opening degree of the bypass damper is stabilized.

[0161] The second adjustment module 850 is configured to adjust a heat exchange control parameter according to the change rate of exhaust pressure and the change rate of air supply temperature difference, wherein the heat exchange control parameter comprises a gear of the electromagnetic pump.

[0162] In one of the embodiments, the first adjustment module 830 is specifically configured to calculate a room sensible heat ratio according to the set air parameter and the return air parameter, calculate a cold coil sensible heat ratio according to the return air parameter and the air supply parameter, and adjust the supply air control parameter according to the room sensible heat ratio and the cold coil sensible heat ratio.

[0163] In one of the embodiments, the first adjustment module 830 is specifically configured to set the mixed air target temperature to a first temperature, keep the supply air gear unchanged, and open the bypass damper at a first opening degree if the ratio of the cold coil sensible heat ratio to the room sensible heat ratio belongs to a first range; set the mixed air target temperature to a second temperature, keep the supply air gear unchanged, and open the bypass damper at a second opening degree if the ratio of the cold coil sensible heat ratio to the room sensible heat ratio belongs to a second range, wherein the second temperature is greater than the first temperature, and the second opening degree is greater than the first opening degree; set the mixed air target temperature to a third temperature, increase the supply air gear, and open the bypass damper at a third opening degree if the ratio of the cold coil sensible heat ratio to the room sensible heat ratio belongs to a third range, wherein the third temperature is greater than the second temperature, and the third opening degree is greater than the second opening degree.

[0164] In one of the embodiments, the second adjustment module 850 is specifically configured to keep the current gear of the electromagnetic pump if the change rate of air supply temperature difference is less than or equal to a preset temperature difference change rate threshold value and the ratio of the cold coil sensible heat ratio to the room sensible heat ratio belongs to the first range; adjust the gear of the electromagnetic pump according to the real-time exhaust pressure and the change rate of exhaust pressure if the change rate of air supply temperature difference is less than or equal to the preset temperature difference change rate threshold value and the ratio of the cold coil sensible heat ratio to the room sensible heat ratio belongs to the second range or the third range; and adjust the gear of the electromagnetic pump according to the real-time exhaust pressure if the change rate of air supply temperature difference is greater than the preset temperature difference change rate threshold value.

[0165] In one of the embodiments, the second adjustment module 850 is specifically configured to increase the gear of the electromagnetic pump if the real-time exhaust pressure is less than or equal to a first pressure threshold value; increase the gear of the electromagnetic pump according to the change rate of pressure if the real-time exhaust pressure is greater than the first pressure threshold value and less than or equal to a second pressure threshold value; increase or decrease the gear of the electromagnetic pump according to the change rate of pressure if the real-time exhaust pressure is greater than the second pressure threshold value and less than or equal to a third pressure threshold value; and keep the current gear of the electromagnetic pump if the real-time exhaust pressure is greater than the third pressure threshold value, wherein the first pressure threshold value is less than the second pressure threshold value, and the second pressure threshold value is less than the third pressure threshold value.

[0166] In one of the embodiments, the second adjusting module 850 is specifically configured to increase the gear of the electromagnetic pump by a first amplitude if the real-time exhaust pressure is less than or equal to the first pressure threshold value; increase the gear of the electromagnetic pump by a second amplitude if the real-time exhaust pressure is greater than the first pressure threshold value and less than or equal to the second pressure threshold value; and judge whether the difference between the real-time mixed air temperature and the set mixed air temperature is greater than a preset difference threshold value if the real-time exhaust pressure is greater than the second pressure threshold value, and adjust the gear of the electromagnetic pump according to the difference comparison result.

[0167] In one of the embodiments, the second adjusting module 850 is specifically configured to increase the opening of the bypass air valve by a preset ratio if the difference between the real-time mixed air temperature and the set mixed air temperature is less than or equal to the preset difference threshold value, and re-adjust the gear of the electromagnetic pump according to the real-time exhaust pressure; and re-adjust the inlet air control parameter according to the room sensible heat ratio and the cold coil sensible heat ratio if the difference between the real-time mixed air temperature and the set mixed air temperature is greater than the preset difference threshold value.

[0168] In one of the embodiments, the starting module 810 is specifically configured to control the inlet air motor, the cold coil, the evaporative heat pipe, the electromagnetic pump, the condensing heat pipe and the exhaust air motor to start to operate according to the control parameters corresponding to the set working gear; and control the bypass air valve to keep in a closed state.

[0169] In summary, the air handling unit control device provided in the embodiment can realize twice air temperature and humidity adjustment, two rounds of cooling and dehumidification processing, solve the terminal dehumidification capacity temperature of the medium-temperature water energy-saving system, and enable the fresh air to be mixed with the medium-low temperature and humidity air output by the cold coil based on the bypass air valve to realize precise temperature control. In addition, the air handling unit control method adjusts the gear of the electromagnetic pump between the evaporative heat pipe and the condensing heat pipe in real time according to the exhaust pressure data and the supply air data of the evaporative heat pipe, which can ensure efficient heat recovery of the heat pipe. The air handling unit does not need to use a rotary wheel for dehumidification, which reduces the number of system equipment and manufacturing costs, and reduces the maintenance rate and after-sales maintenance costs.

[0170] The above-mentioned various modules in the air handling unit control device can be realized by software, hardware and combinations thereof, in whole or in part. The above-mentioned various modules can be embedded in or independent of the processor in the computer device in hardware form, or can be stored in the memory in the computer device in software form, so as to be called and executed by the processor to perform the operations corresponding to the above-mentioned various modules.

[0171] In one of the embodiments, a computer device is provided, which can be a terminal, and the internal structure diagram thereof can be as shown in Figure 9The computer device includes a processor, a memory, an input / output interface, a communication interface, a display unit and an input device. The processor, the memory and the input / output interface are connected through a system bus, and the communication interface, the display unit and the input device are connected to the system bus through the input / output interface. The processor of the computer device is configured to provide computing and control capabilities. The memory of the computer device includes a non-volatile storage medium and an internal memory. The non-volatile storage medium stores an operating system and a computer program. The internal memory provides an environment for running the operating system and the computer program in the non-volatile storage medium. The input / output interface of the computer device is configured to exchange information between the processor and external devices. The communication interface of the computer device is configured to perform wired or wireless communication with external terminals. The wireless communication can be achieved through WIFI, mobile cellular network, NFC (Near Field Communication) or other technologies. The computer program is executed by the processor to implement an air handling unit control method. The display unit of the computer device is configured to form a visually visible picture, which can be a display screen, a projection device or a virtual reality imaging device. The display screen can be a liquid crystal display screen or an electronic ink display screen. The input device of the computer device can be a touch layer overlaid on the display screen, or a key, trackball or touchpad arranged on the shell of the computer device, or an external keyboard, touchpad or mouse, etc.

[0172] Those skilled in the art can understand that, Figure 9 The skilled in the art can understand that,

[0173] In one embodiment, a computer device is provided, including a memory and a processor, the memory stores a computer program, and the processor executes the computer program to implement the following steps:

[0174] controlling the air handling unit to start, so that the air handling unit operates according to the control parameters corresponding to the set working gear;

[0175] obtaining the set air parameters, the return air parameters and the supply air parameters, wherein the air parameters include dry bulb temperature, wet bulb temperature and enthalpy value;

[0176] adjusting the inlet air control parameters according to the set air parameters, the return air parameters and the supply air parameters, wherein the inlet air control parameters include mixed air target temperature, inlet air gear of the inlet air motor and opening degree of the bypass air valve;

[0177] After the opening of the bypass damper is stable, the exhaust pressure change rate of the evaporative heat pipe and the air supply temperature difference change rate of the air supply outlet are obtained;

[0178] The heat exchange control parameter is adjusted according to the exhaust pressure change rate and the air supply temperature difference change rate, wherein the heat exchange control parameter comprises a gear of the electromagnetic pump.

[0179] In one embodiment, a computer readable storage medium is provided, and a computer program is stored on the computer readable storage medium, and the computer program is executed by a processor to implement the following steps:

[0180] The air handling unit is controlled to start, so that the air handling unit operates according to the control parameter corresponding to the set working gear;

[0181] The set air parameter, the return air parameter and the air supply parameter are obtained, wherein the air parameter comprises a dry-bulb temperature, a wet-bulb temperature and an enthalpy value;

[0182] The air intake control parameter is adjusted according to the set air parameter, the return air parameter and the air supply parameter, wherein the air intake control parameter comprises a mixed air target temperature, an air intake gear of an air intake motor and an opening of the bypass damper;

[0183] After the opening of the bypass damper is stable, the exhaust pressure change rate of the evaporative heat pipe and the air supply temperature difference change rate of the air supply outlet are obtained;

[0184] The heat exchange control parameter is adjusted according to the exhaust pressure change rate and the air supply temperature difference change rate, wherein the heat exchange control parameter comprises a gear of the electromagnetic pump.

[0185] In one embodiment, a computer program product is provided, and the computer program product comprises a computer program, and the computer program is executed by a processor to implement the following steps:

[0186] The air handling unit is controlled to start, so that the air handling unit operates according to the control parameter corresponding to the set working gear;

[0187] The set air parameter, the return air parameter and the air supply parameter are obtained, wherein the air parameter comprises a dry-bulb temperature, a wet-bulb temperature and an enthalpy value;

[0188] The air intake control parameter is adjusted according to the set air parameter, the return air parameter and the air supply parameter, wherein the air intake control parameter comprises a mixed air target temperature, an air intake gear of an air intake motor and an opening of the bypass damper;

[0189] After the opening of the bypass damper is stable, the exhaust pressure change rate of the evaporative heat pipe and the air supply temperature difference change rate of the air supply outlet are obtained;

[0190] The heat exchange control parameter includes a gear of the electromagnetic pump.

[0191] Those skilled in the art can understand that all or part of the processes in the above-mentioned embodiment methods can be completed by instructing the relevant hardware through a computer program. The computer program can be stored in a non-volatile computer readable storage medium, and when executed, can include the processes of the above-mentioned embodiment methods. Any reference to memory, databases or other media used in the embodiments provided in the present application can include at least one of non-volatile and volatile memory. Non-volatile memory can include read-only memory (ROM), magnetic tape, floppy disk, flash memory, optical storage, high-density embedded non-volatile memory, resistive memory (ReRAM), magnetoresistive random access memory (MRAM), ferroelectric memory (FRAM), phase change memory (PCM), graphene memory, etc. Volatile memory can include random access memory (RAM) or external cache memory, etc. As an illustration but not limitation, RAM can be in various forms, such as static random access memory (SRAM) or dynamic random access memory (DRAM), etc. The database involved in the embodiments provided in the present application can include at least one of a relational database and a non-relational database. The non-relational database can include a distributed database based on a block chain, etc., without being limited thereto. The processor involved in the embodiments provided in the present application can be a general-purpose processor, a central processing unit, a graphics processing unit, a digital signal processor, a programmable logic device, a data processing logic device based on quantum computing, etc., without being limited thereto.

[0192] The technical features of the above embodiments can be combined in any manner. To make the description concise, not all possible combinations of the technical features in the above embodiments are described, but as long as the combinations of the technical features do not exist contradictions, they should be considered as the scope of the present disclosure.

[0193] The above-described embodiments are merely illustrative of several embodiments of the present application, and the description is relatively specific and detailed, but should not be understood as a limitation on the scope of the patent. It should be noted that for those skilled in the art, without departing from the concept of the present application, a number of modifications and improvements can be made, which are all within the scope of the present application. Therefore, the scope of protection of the present application should be subject to the appended claims.

Claims

1. An air handling unit control method, characterized by, The application is applied to an air handling unit, wherein the air handling unit comprises an air inlet, an air outlet, an air return, an air exhaust, an air inlet motor, a cold coil, a bypass air valve, an evaporative heat pipe, an electromagnetic pump, a condensing heat pipe and an air exhaust motor, the air inlet motor is connected with the air inlet of the cold coil, one end of the bypass air valve is connected with an outdoor environment, the other end of the bypass air valve and the air outlet of the cold coil are connected with the air inlet of the evaporative heat pipe, the evaporative heat pipe is connected with the condensing heat pipe through the electromagnetic pump, the air outlet of the evaporative heat pipe is connected with the air outlet, the air inlet of the condensing heat pipe is connected with the air return, and the air outlet of the condensing heat pipe is connected with the air exhaust through the air exhaust motor; the cold coil comprises a water inlet pipeline and a water return pipeline, wherein the water inlet pipeline is used for introducing medium-temperature water, and high-temperature water is output through the water return pipeline to realize water circulation; the cold coil is used for cooling and dehumidifying the air introduced by the air inlet motor. The method comprises: controlling the air handling unit to start, so that the air handling unit operates according to the control parameters corresponding to the set working gear; obtaining a set air parameter, an air return parameter and an air outlet parameter, wherein the air parameter comprises a dry-bulb temperature, a wet-bulb temperature and an enthalpy value; adjusting an air inlet control parameter according to the set air parameter, the air return parameter and the air outlet parameter, wherein the air inlet control parameter comprises a mixed air target temperature, an air inlet gear of the air inlet motor and an opening degree of the bypass air valve; after the opening degree of the bypass air valve is stable, obtaining a change rate of exhaust pressure of the evaporative heat pipe and a change rate of air outlet temperature difference of the air outlet; adjusting a heat exchange control parameter according to the change rate of exhaust pressure and the change rate of air outlet temperature difference, wherein the heat exchange control parameter comprises a gear of the electromagnetic pump.

2. The method of claim 1, wherein, The adjusting of the air inlet control parameter according to the set air parameter, the air return parameter and the air outlet parameter comprises: calculating a room sensible heat ratio according to the set air parameter and the air return parameter; calculating a cold coil sensible heat ratio according to the air return parameter and the air outlet parameter; adjusting the air inlet control parameter according to the room sensible heat ratio and the cold coil sensible heat ratio.

3. The method of claim 2, wherein, The adjusting of the air inlet control parameter according to the room sensible heat ratio and the cold coil sensible heat ratio comprises: if the proportion of the cold coil sensible heat ratio and the room sensible heat ratio belongs to a first range, controlling the mixed air target temperature to be set as a first temperature, the air inlet gear being unchanged and the bypass air valve being opened at a first opening degree; if the proportion of the cold coil sensible heat ratio and the room sensible heat ratio belongs to a second range, controlling the mixed air target temperature to be set as a second temperature, the air inlet gear being unchanged and the bypass air valve being opened at a second opening degree, wherein the second temperature is greater than the first temperature, and the second opening degree is greater than the first opening degree. If the ratio of the cold coil sensible heat ratio to the room sensible heat ratio belongs to a third range, the mixed air target temperature is set to a third temperature, the outdoor air damper is increased, and the bypass damper is opened at a third opening degree, wherein the third temperature is greater than the second temperature, and the third opening degree is greater than the second opening degree.

4. The method of claim 3, wherein, The adjusting the heat exchange control parameter according to the exhaust air pressure change rate and the supply air temperature difference change rate comprises: If the supply air temperature difference change rate is less than or equal to a preset temperature difference change rate threshold value, and the ratio of the cold coil sensible heat ratio to the room sensible heat ratio belongs to a first range, the current gear of the electromagnetic pump is maintained; If the supply air temperature difference change rate is less than or equal to a preset temperature difference change rate threshold value, and the ratio of the cold coil sensible heat ratio to the room sensible heat ratio belongs to a second range or a third range, the gear of the electromagnetic pump is adjusted according to the real-time exhaust air pressure and the exhaust air pressure change rate; If the supply air temperature difference change rate is greater than a preset temperature difference change rate threshold value, the gear of the electromagnetic pump is adjusted according to the real-time exhaust air pressure.

5. The method of claim 4, wherein, The adjusting the gear of the electromagnetic pump according to the real-time exhaust air pressure and the exhaust air pressure change rate comprises: If the real-time exhaust air pressure is less than or equal to a first pressure threshold value, the gear of the electromagnetic pump is increased; If the real-time exhaust air pressure is greater than the first pressure threshold value and less than or equal to a second pressure threshold value, the gear of the electromagnetic pump is increased according to the exhaust air pressure change rate; If the real-time exhaust air pressure is greater than the second pressure threshold value and less than or equal to a third pressure threshold value, the gear of the electromagnetic pump is increased or decreased according to the exhaust air pressure change rate; If the real-time exhaust air pressure is greater than the third pressure threshold value, the current gear of the electromagnetic pump is maintained, wherein the first pressure threshold value is less than the second pressure threshold value, and the second pressure threshold value is less than the third pressure threshold value.

6. The method of claim 4, wherein, The adjusting the gear of the electromagnetic pump according to the real-time exhaust air pressure comprises: If the real-time exhaust air pressure is less than or equal to a first pressure threshold value, the gear of the electromagnetic pump is increased by a first amplitude; If the real-time exhaust air pressure is greater than the first pressure threshold value and less than or equal to a second pressure threshold value, the gear of the electromagnetic pump is increased by a second amplitude; If the real-time exhaust air pressure is greater than the second pressure threshold value, it is judged whether a difference between the real-time mixed air temperature and the set mixed air temperature is greater than a preset difference threshold value, and the gear of the electromagnetic pump is adjusted according to a difference comparison result.

7. The method of claim 6, wherein, The adjusting the gear of the electromagnetic pump according to the difference comparison result comprises: If the difference between the real-time mixed air temperature and the set mixed air temperature is less than or equal to the preset difference threshold value, the opening degree of the bypass damper is increased by a preset ratio, and the gear of the electromagnetic pump is adjusted again according to the real-time exhaust air pressure; If the difference between the real-time mixed air temperature and the set mixed air temperature is greater than the preset difference threshold value, the outdoor air control parameter is adjusted again according to the room sensible heat ratio and the cold coil sensible heat ratio.

8. The method of claim 1, wherein, The controlling the air handling unit to start so that the air handling unit operates according to the control parameter corresponding to the set working gear comprises: Controlling the air intake motor, the cold coil, the evaporative heat pipe, the electromagnetic pump, the condensing heat pipe and the exhaust fan to start to run according to the control parameters corresponding to the set working gear; Controlling the bypass air valve to keep closed.

9. An air handling unit control apparatus, characterized by, The application is applied to an air handling unit, wherein the air handling unit comprises an air inlet, an air outlet, an air return, an air exhaust, an air intake motor, a cold coil, a bypass air valve, an evaporative heat pipe, an electromagnetic pump, a condensing heat pipe and an exhaust fan, the air intake motor is connected to the air inlet end of the cold coil through the air inlet, one end of the bypass air valve is connected to an outdoor environment, the other end of the bypass air valve and the air outlet end of the cold coil are both connected to the air inlet end of the evaporative heat pipe, the evaporative heat pipe is connected to the condensing heat pipe through the electromagnetic pump, the air outlet end of the evaporative heat pipe is connected to the air outlet, the air inlet end of the condensing heat pipe is connected to the air return, and the air outlet end of the condensing heat pipe is connected to the air exhaust through the exhaust fan; the cold coil comprises a water inlet pipeline and a water return pipeline, wherein the water inlet pipeline is used for introducing medium-temperature water, and the high-temperature water is output through the water return pipeline to realize water circulation; the cold coil is used for cooling and dehumidifying the fresh air introduced by the air intake motor; The device comprises: A starting module configured to control the air handling unit to start to run according to the control parameters corresponding to the set working gear; A first obtaining module configured to obtain set air parameters, air return parameters and air supply parameters, wherein the air parameters comprise dry-bulb temperature, wet-bulb temperature and enthalpy; A first adjusting module configured to adjust air intake control parameters according to the set air parameters, the air return parameters and the air supply parameters, wherein the air intake control parameters comprise mixed air target temperature, air intake gear of the air intake motor and opening degree of the bypass air valve; A second obtaining module configured to obtain exhaust pressure change rate of the evaporative heat pipe and air supply temperature difference change rate of the air outlet after the opening degree of the bypass air valve is stabilized; A second adjusting module configured to adjust heat exchange control parameters according to the exhaust pressure change rate and the air supply temperature difference change rate, wherein the heat exchange control parameters comprise gear of the electromagnetic pump.

10. An air handling unit, comprising: The application comprises: A controller, an air inlet, an air outlet, an air return, an air exhaust, an air intake motor, a cold coil, a bypass air valve, an evaporative heat pipe, an electromagnetic pump, a condensing heat pipe and an exhaust fan; The air inlet motor is connected with the air inlet end of the cold coil through the air inlet, one end of the bypass air valve is connected with the outdoor environment, the other end of the bypass air valve and the air outlet end of the cold coil are both connected with the air inlet end of the evaporative heat pipe, the evaporative heat pipe is connected with the condensing heat pipe through the electromagnetic pump, the air outlet end of the evaporative heat pipe is connected with the air outlet, the air inlet end of the condensing heat pipe is connected with the return air inlet, and the air outlet end of the condensing heat pipe is connected with the exhaust outlet through the exhaust motor; the cold coil comprises a water inlet pipeline and a water return pipeline, wherein the water inlet pipeline is used for introducing medium-temperature water, and the high-temperature water is output through the water return pipeline to realize water circulation; the cold coil is used for cooling and dehumidifying the fresh air introduced by the air inlet motor. The controller is connected with the air inlet motor, the cold coil, the bypass air valve, the evaporative heat pipe, the electromagnetic pump, the condensing heat pipe and the exhaust motor. The controller is used for realizing the steps of the air handling unit control method in any one of claims 1 to 8.

11. A fresh air system characterized in that, The air handling unit comprises the air handling unit in claim 10.

12. An air conditioning apparatus characterized by comprising: The air handling unit comprises the air handling unit in claim 10.

13. A computer device comprising a memory and a processor, the memory storing a computer program, characterized in that, The processor realizes the steps of the air handling unit control method in any one of claims 1 to 8 when the processor executes the computer program.

14. A computer readable storage medium having stored thereon a computer program, characterized in that, The computer program realizes the steps of the air handling unit control method in any one of claims 1 to 8 when the computer program is executed by the processor.

15. A computer program product comprising a computer program, characterized in that, The computer program realizes the steps of the air handling unit control method in any one of claims 1 to 8 when the computer program is executed by the processor.

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