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

Abstract

The invention relates to an air handling unit control method and device, a fresh air system and air conditioning equipment, and the method comprises the steps that an air handling unit is controlled to be started, so that the air handling unit operates according to control parameters corresponding to set working gears; a set air parameter, an air return parameter and an air supply parameter are obtained, the air inlet control parameters are adjusted according to the set air parameters, the air return air parameters and the air supply air parameters; after the opening degree of the bypass air valve is stable, the exhaust pressure change rate of the evaporation heat pipe and the air supply temperature difference change rate of the air supply outlet are obtained; and heat exchange control parameters are adjusted according to the exhaust pressure change rate and the air supply temperature difference change rate. According to the novel structural design of the air handling unit, in the operation process of the air handling unit, secondary deep dehumidification and cooling are conducted on air, then the air is fed into a room, and the tail end dehumidification and temperature control function can be achieved efficiently in an energy-saving mode.

Description

Technical Field

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

[0002] The terminal equipment of the air handling system with 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 the water temperature and temperature difference. For every 1°C increase in the inlet water temperature, the refrigeration capacity decreases by about 12%, and the dehumidification capacity decreases by 30%. For every 1°C increase in the water temperature difference △T, the refrigeration capacity decreases by about 12.5%, and the dehumidification capacity decreases by 31%. Therefore, the dehumidification performance of the air handling system with medium-temperature water circulation varies greatly. The actual power consumption increases only by increasing the air volume, and it is difficult to meet the comfort requirements when the cold water inlet temperature is above 9°C.

[0003] The existing series air treatment and adjustment method is not suitable for air treatment systems with medium-temperature water circulation. This method is applied to air treatment systems with medium-temperature water circulation, but there is a problem that the heat exchange capacity of the cold coil is insufficient and cannot meet the dehumidification requirements. The heat pipe has no dehumidification function and cannot exert its efficient heat transfer performance. It can only play an auxiliary pre-cooling and heat recovery role. Summary of the invention

[0004] Based on this, it is necessary to provide an air handling unit control method, device, fresh air system and air-conditioning equipment that can achieve deep dehumidification and effectively save energy in response to the above technical problems.

[0005] In a first aspect, the present application provides an air handling unit control method, which is applied to an air handling unit, wherein the air handling unit comprises an air inlet, an air supply port, a return air port, an exhaust port, an air inlet motor, a cold coil, a bypass air valve, an evaporative heat pipe, an electromagnetic pump, a condensing heat pipe and an exhaust motor, the air inlet motor is connected to an 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 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, the air outlet end of the evaporative heat pipe is connected to the air supply port, the air inlet end of the condensing heat pipe is connected to the return air port, and the air outlet end of the condensing heat pipe is connected to the exhaust port through the 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] Acquire set air parameters, return air parameters and supply air parameters, wherein the air parameters include dry bulb temperature, wet bulb temperature and 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 includes a mixed air target temperature, an air intake gear position of the air intake motor and an opening degree of the bypass air valve;

[0010] After the opening of the bypass air valve is stabilized, obtaining the exhaust pressure change rate of the evaporating heat pipe and the supply air temperature difference change rate of the air supply port;

[0011] The heat exchange control parameters are adjusted according to the exhaust pressure change rate and the supply air temperature difference change rate, wherein the heat exchange control parameters include the gear position of the electromagnetic pump.

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

[0013] Calculate the room sensible heat ratio according to the set air parameters and the return air parameters;

[0014] Calculate the sensible heat ratio of the cold coil according to the return air parameters and the supply air parameters;

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

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

[0017] If the ratio of the sensible heat ratio of the cold coil to the sensible heat ratio of the room is within a first range, the mixed air target temperature is controlled to be set to a first temperature, the air inlet gear remains unchanged, and the bypass air valve is opened at a first opening degree;

[0018] If the ratio of the sensible heat ratio of the cold coil to the sensible heat ratio of the room is within a second range, the mixed air target temperature is controlled to be set to a second temperature, the air inlet gear remains unchanged, and the bypass air valve is opened at a second opening, wherein the second temperature is greater than the first temperature, and the second opening is greater than the first opening;

[0019] If the ratio of the sensible heat ratio of the cold coil to the sensible heat ratio of the room is within a third range, the mixed air target temperature is controlled to be set to a third temperature, the air inlet gear is increased, and the bypass air valve is opened at a third opening, wherein the third temperature is greater than the second temperature, and the third opening is greater than the second opening.

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

[0021] 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 cold coil sensible heat ratio to the room sensible heat ratio belongs to the first range, the current gear position of the electromagnetic pump is maintained;

[0022] 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 cold coil sensible heat ratio to the room sensible heat ratio belongs to the second range or the third range, the gear position of the electromagnetic pump is adjusted 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, the electromagnetic pump gear position is adjusted according to the real-time exhaust pressure.

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

[0025] If the real-time exhaust pressure is less than or equal to the first pressure threshold, raising the gear position of the electromagnetic pump;

[0026] If the real-time exhaust pressure is greater than the first pressure threshold and less than or equal to the second pressure threshold, increasing the gear position 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 and less than or equal to the third pressure threshold, the gear position of the electromagnetic pump is increased or decreased according to the exhaust pressure change rate;

[0028] If the real-time exhaust pressure is greater than the third pressure threshold, the current gear position 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.

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

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

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

[0032] If the real-time exhaust pressure is greater than the second pressure threshold, it is determined 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 position of the electromagnetic pump is adjusted according to the difference comparison result.

[0033] In one embodiment, adjusting the gear position of the electromagnetic pump according to the difference comparison result includes:

[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, the opening of the bypass air valve is increased according to a preset ratio, and the electromagnetic pump gear is re-adjusted according to the real-time exhaust pressure;

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

[0036] In one embodiment, the 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 includes:

[0037] Controlling the air inlet motor, the cold coil, the evaporation heat pipe, the electromagnetic pump, the condensation heat pipe and the exhaust motor to start up so as to operate according to the control parameters corresponding to the set working gear;

[0038] The bypass vent valve is controlled to remain in a closed state.

[0039] In a second aspect, the present application further 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 supply port, a return air port, an exhaust port, an air inlet motor, a cold coil, a bypass air valve, an evaporative heat pipe, an electromagnetic pump, a condensing heat pipe and an exhaust motor, the air inlet motor is connected to an 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 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, the air outlet end of the evaporative heat pipe is connected to the air supply port, the air inlet end of the condensing heat pipe is connected to the return air port, and the air outlet end of the condensing heat pipe is connected to the exhaust port through the exhaust motor;

[0040] The device comprises:

[0041] A starting module, used to control the start-up of the air handling unit so that the air handling unit operates according to the control parameters corresponding to the set working gear;

[0042] A first acquisition module is used to acquire set air parameters, return air parameters and supply air parameters, wherein the air parameters include dry bulb temperature, wet bulb temperature and enthalpy value;

[0043] a first regulating module, configured to regulate 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 position of the air intake motor and an opening degree of the bypass air valve;

[0044] A second acquisition module is used to acquire the exhaust pressure change rate of the evaporating heat pipe and the supply air temperature difference change rate of the air supply port after the opening of the bypass air valve is stabilized;

[0045] The second regulating module is used to adjust the heat exchange control parameters according to the exhaust pressure change rate and the supply air temperature difference change rate, wherein the heat exchange control parameters include the gear position of the electromagnetic pump.

[0046] In a third aspect, the present application further provides an air handling unit, including: a controller, an air inlet, an air supply outlet, an air return outlet, an air exhaust outlet, an air inlet motor, a cold coil, a bypass air valve, an evaporation heat pipe, an electromagnetic pump, a condensation heat pipe and an exhaust motor;

[0047] 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, 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 supply port, the air inlet end of the condensation heat pipe is connected to the return air port, and the air outlet end of the condensation heat pipe is connected to the exhaust port through the exhaust motor;

[0048] The controller is respectively connected to the air inlet motor, the cold coil, the bypass air valve, the evaporation heat pipe, the electromagnetic pump, the condensation heat pipe and the exhaust motor;

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

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

[0051] In a fifth aspect, the present application also provides an air-conditioning device, comprising the air handling unit described in 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 described in the first aspect when executing the computer program.

[0053] In a seventh aspect, the present application further provides a computer-readable storage medium having a computer program stored thereon, and when the computer program is executed by a processor, the steps of the air handling unit control method described in the first aspect are implemented.

[0054] In an eighth aspect, the present application further provides a computer program product, wherein the computer program product comprises a computer program, and when the computer program is executed by a processor, the steps of the air handling unit control method described in the first aspect are implemented.

[0055] In summary, the present application proposes an air handling unit control method, device, fresh air system and air conditioning equipment, including: controlling the start-up of the air handling unit so that the air handling unit operates according to the control parameters corresponding to the set working gear; obtaining the set air parameters, return air parameters and supply air parameters, wherein; adjusting the air intake control parameters according to the set air parameters, the return air parameters and the supply air parameters; obtaining the exhaust pressure change rate of the evaporating heat pipe and the supply air temperature difference change rate of the air supply port after the opening of the bypass air valve is stable; adjusting the heat exchange control parameters according to the exhaust pressure change rate and the supply air temperature difference change rate. The present application proposes a new air handling unit structural design, and during the operation of the air handling unit, the air is deeply dehumidified and cooled for a second time before being sent into the room, which can realize the terminal dehumidification and temperature control function with high efficiency and energy saving. BRIEF DESCRIPTION OF THE DRAWINGS

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

[0057] Figure 2 One of the flow charts of the air handling unit control method in one embodiment;

[0058] Figure 3 The second flow chart of the air handling unit control method in one embodiment;

[0059] Figure 4 The third flow chart of the air handling unit control method in one embodiment;

[0060] Figure 5 The fourth flowchart of the air handling unit control method in one embodiment;

[0061] Figure 6 FIG5 is a flow chart of a method for controlling an air handling unit in one embodiment;

[0062] Figure 7 The sixth flow chart of the air handling unit control method in one embodiment;

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

[0064] Fig. 9 FIG. 4 is a diagram showing the internal structure of a computer device in one embodiment. DETAILED DESCRIPTION

[0065] In order to make the purpose, technical solution and advantages of the present application more clearly understood, the present application is further described in detail below in conjunction with the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are only used to explain the present application and are not used to limit the present application.

[0066] As described in the background technology above, the dehumidification capacity of the existing air handling unit cold coil is insufficient when circulating medium-temperature water. When the conventional combination of cold coil and reheater is used, the performance of the cold coil of the air handling unit will change with the water temperature and the water temperature difference. For example, for every 1°C increase in the inlet water temperature, the refrigeration capacity decreases by about 12%, and the dehumidification capacity decreases by 30%; for every 1°C increase in the water temperature difference △T, the refrigeration capacity decreases by about 12.5%, and the dehumidification capacity decreases by 31%. Therefore, when using conventional air handling units under medium-temperature water circulation, the dehumidification capacity changes greatly. Only by increasing the air volume to adjust the dehumidification capacity and refrigeration capacity will increase the actual power consumption, and the cold water inlet temperature is required to be above 9°C, which cannot meet the needs 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°C, the cold coil is in a low-temperature water circulation state. If the chilled water is in the range of 6-8 degrees Celsius, the cold coil is in a normal-temperature water circulation state. If the chilled water is in the range of 9-13°C, the cold coil is in a medium-temperature water circulation state. If the chilled water is in the range of 14-17°C, the cold coil is in a high-temperature water circulation state. In the following embodiments, medium and low temperature refers to the temperature of water covered by both medium-temperature water and normal-temperature water, that is, water below 13°C can be called medium and low-temperature water.

[0068] There is an urgent need for an energy-saving air handling unit design that can effectively meet the needs of air dehumidification and cooling without increasing costs, and to improve the problems of low dehumidification capacity of medium-temperature water-cooled coils and low heat exchange efficiency of heat pipes in existing air handling units.

[0069] The air handling unit control method provided in the embodiment of the present application can be applied to Figure 1 The air handling unit in this embodiment includes an air inlet, an air supply port, an air return port, an air exhaust port, 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 exhaust motor 170.

[0070] In this embodiment, the air intake motor 110 is connected to the air intake 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 intake end of the evaporating heat pipe 140, the evaporating heat pipe 140 is connected to the condensing heat pipe 160 through the electromagnetic pump 150, the air outlet end of the evaporating heat pipe 140 is connected to the air supply port, the air intake end of the condensing heat pipe 160 is connected to the return air port, and the air outlet end of the condensing heat pipe 160 is connected to the exhaust port through the exhaust motor 170.

[0071] The air intake motor 110 in this embodiment 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 the real-time working status, and make the fresh air flow into the cold coil 120 through the air inlet at a preset flow rate to perform the first round of dehumidification and cooling treatment on the fresh air.

[0072] The cold coil 120 includes a water inlet pipe and a water return pipe, wherein the water inlet pipe is used to introduce medium-temperature water, and then output high-temperature water through the water return pipe to realize water circulation. The cold coil 120 is used to cool and dehumidify 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 humid air.

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

[0075] The indoor air flows into the condensing heat pipe 160 through the return air port, and the condensing action of the condensing heat pipe 160 recovers the heat of the medium and low temperature air to obtain cooled liquid condensed water and high temperature air. The liquid condensed water is transported back to the evaporating heat pipe 140 to cool and dehumidify the mixed air flowing through the evaporating heat pipe 140. The high temperature air is discharged to the outdoor environment through the exhaust port under the action of the exhaust motor 170.

[0076] In this embodiment, the evaporation heat pipe 140 is also connected to the condensation 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 evaporation heat pipe 140 to the condensation heat pipe 160. The electromagnetic pump 150 includes multiple gears. In actual application, the exhaust pressure and exhaust rate of the evaporation heat pipe 140 can be adjusted by adjusting the gear of the electromagnetic pump 150. Specifically, the higher the gear of the electromagnetic pump 150, the greater the exhaust pressure and exhaust rate, the greater the heat exchange between the evaporation heat pipe 140 and the condensation heat pipe 160, and the higher the heat exchange efficiency.

[0077] In one embodiment, Figure 2 As shown, a method for controlling an air handling unit is provided, and the method is applied to Figure 1 The air handling unit in the example is used to illustrate, including the following steps:

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

[0079] In this embodiment, the host of the air handling unit can control the relevant components of the air handling unit to start working according to the start control signal sent by the user through the terminal device. The terminal device can be a remote control, a smart panel or a mobile terminal, etc., which can communicate and interact with the air handling unit. This embodiment does not limit the start control terminal of the air handling unit.

[0080] In this embodiment, when the air handling unit is in cooling mode and the return water temperature is set within a preset temperature range, the subsequent steps S202-S205 are performed. In 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 set air parameters, return air parameters and supply air parameters, wherein the air parameters include dry bulb temperature, wet bulb temperature and enthalpy value.

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

[0083] Among them, the dry bulb temperature can be obtained by a dry bulb thermometer that is exposed to the air but not directly exposed to the sun. After recording the dry bulb temperature value at the corresponding position, the dry bulb thermometer transmits the corresponding dry bulb temperature value to the controller of the air handling unit. For example, the return air dry bulb temperature can be obtained by testing the dry bulb temperature at the return air outlet, and the supply air dry bulb temperature can be obtained by testing the dry bulb temperature at the supply air outlet.

[0084] The wet bulb temperature refers to the lowest temperature that the current environment can reach by evaporating water alone. 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 through the air parameter calculation tool set in the corresponding position. It should be noted that the air parameter calculation tool can be configured according to the needs of the actual application scenario.

[0085] S203, adjusting the air intake control parameters according to the set air parameters, the return air parameters and the supply air parameters, wherein the air intake control parameters include the mixed air target temperature, the air intake gear position of the air intake motor and the opening of the bypass air valve.

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

[0087] Specifically, the room sensible heat ratio is calculated based on the set air parameters and the return air parameters, and the cold coil sensible heat ratio is calculated based on the return air parameters and the supply air parameters.

[0088] For example, if the set dry-bulb temperature is T, the set wet-bulb temperature is Ts, and 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 enthalpy value 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 enthalpy value 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 sensible heat ratio of the cold coil under the medium-temperature water circulation state is S1= (T1-T2) / (H1-H2), where S1 is the sensible heat ratio of the cold coil.

[0091] Furthermore, 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 air supply 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 air inlet of the evaporating heat pipe.

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

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

[0094] S204, after the opening of the bypass air valve is stabilized, obtaining the exhaust pressure change rate of the evaporating heat pipe and the supply air temperature difference change rate of the supply air outlet.

[0095] In this embodiment, after the bypass air valve opening is stable, the evaporating heat pipe and the condensing heat pipe have entered a stable heat exchange stage in parallel, and the exhaust pressure P1 in the exhaust pipe connected to the electromagnetic pump of the evaporating heat pipe is detected, and combined with the initial exhaust pressure P of the evaporating heat pipe detected when the air handling unit is started, the exhaust pressure change rate △P can be calculated, where △P=(P1-P) / 30s. It should be noted that the calculation of the exhaust pressure change rate can be calculated in real time, and the time interval between P1 and P can be fixed to 30 seconds (s). The exhaust pressure represented by P1 is the real-time exhaust pressure, and the pressure represented by P is the exhaust pressure 30s before the real-time exhaust pressure.

[0096] Similarly, the air supply temperature of the air supply outlet can be collected in real time by the temperature detection component set at the air supply outlet, and the air supply temperature difference △T=T2-T2' can be calculated, where T2 is the real-time air supply temperature and T2' is the air supply temperature after the real-time air supply temperature is detected for a fixed time. The air supply temperature difference change rate is △Tm=△T / 30S.

[0097] In this embodiment, a preset exhaust pressure change rate threshold PM and a supply air temperature difference change rate threshold TM are also included. By comparing the exhaust pressure change rate of the evaporating heat pipe and the supply air temperature difference change rate of the air supply outlet with the exhaust pressure change rate threshold PM and the supply air temperature difference change rate threshold TM, the real-time status of the air handling unit can be accurately determined, thereby making precise adjustments based on the real-time status of the air handling unit to improve the heat exchange efficiency of the air handling unit.

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

[0099] In this embodiment, adjusting the gear position of the electromagnetic pump can change the exhaust pressure from the evaporating heat pipe to the condensing heat pipe and the refrigerant flow rate and pressure inside the heat pipe to improve the heat exchange efficiency of the heat pipe. This embodiment adjusts the gear position of the electromagnetic pump in real time based on the exhaust pressure change rate and the supply air temperature difference change rate, which can achieve higher heat exchange efficiency and accurately control the supply air temperature and supply air humidity of the air handling unit.

[0100] In one embodiment, Figure 3As shown in the figure, the air inlet control parameters are adjusted according to the room sensible heat ratio and the cold coil sensible heat ratio, including:

[0101] S301, if the ratio of the sensible heat ratio of the cold coil to the sensible heat ratio of the room is within the first range, the target temperature of the mixed air is controlled to be set to the first temperature, the air inlet gear remains unchanged, and the bypass air valve is opened at the first opening.

[0102] S302, if the ratio of the sensible heat ratio of the cold coil to the sensible heat ratio of the room is within the second range, the target temperature of the mixed air is controlled to be set to the second temperature, the air inlet gear remains unchanged, and the bypass air valve is opened at a second opening, wherein the second temperature is greater than the first temperature, and the second opening is greater than the first opening.

[0103] S303, if the ratio of the sensible heat ratio of the cold coil to the sensible heat ratio of the room is within the third range, the target temperature of the mixed air is controlled to be set to the third temperature, the air inlet gear is increased, and the bypass air valve is opened at the third opening, wherein the third temperature is greater than the second temperature, and the third opening is greater than the second opening.

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

[0105] In actual application scenarios, assuming that the sensible heat ratio of the cold coil is S1 and the sensible heat ratio of the room is S0, the ratio of the sensible heat ratio of the cold coil to the sensible heat ratio of the room is S1 / S0. In a specific embodiment, the ratio S1 / S0 can be used to determine the relationship between the cooling and dehumidification capacity of the medium-temperature water coil and the total load of the room.

[0106] If S1 / S0 is in the range of 1-1.2, it means that the cold coil in 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 controlled to remain unchanged, and the mixed air target temperature is set to the first temperature Tz1. The bypass air valve is opened according to the first opening N1, so that a small amount of bypass air flow flows into the air circulation unit. After mixing with the medium and low temperature air output by the cold coil, secondary heat exchange is carried out through the evaporating heat pipe, so as to slowly and stably realize the secondary dehumidification and cooling regulation of the mixed air.

[0107] If S1 / S0 is in the range of 1.2-1.3, it means that the cold 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 controlled to remain unchanged, and the mixed air target temperature is controlled to be set to the second temperature Tz2. The bypass air valve is opened according to the second opening N2, so that a large amount of bypass air flow flows into the air circulation unit. After mixing with the medium and low temperature air output by the cold coil, secondary heat exchange is carried out through the evaporating heat pipe, thereby increasing the adjustment speed of the secondary dehumidification and cooling regulation of the mixed air.

[0108] If S1 / S0 is in the range of 1.3-1.4, it means that the cold coil in the medium-temperature water circulation state needs to meet the load demand of 40% indoor air temperature and humidity regulation. At this time, the air inlet gear of the air inlet motor is controlled to be increased, and the mixed air target temperature is controlled to be set to the third temperature Tz3. The bypass air valve is opened according to the third opening N3, so that a large amount of bypass air flow flows into the air circulation unit. After mixing with the medium and low temperature air output by the cold coil, secondary heat exchange is carried out through the evaporating heat pipe, thereby further increasing the adjustment speed of the secondary dehumidification and cooling regulation of the mixed air.

[0109] It should be noted that the air inlet gear can be set to a medium speed at startup, and here it is adjusted to a medium to high speed.

[0110] The higher the opening of the bypass vent valve, the greater the air intake volume and air intake speed of the bypass vent valve. In a feasible embodiment, an air intake motor connected to the bypass vent valve can be configured to adjust the air intake flow rate and air intake speed of the bypass vent valve. The mixed air temperature is associated with the air intake volume and air intake speed of the bypass vent valve. The greater the air intake volume, the greater the mixed air temperature.

[0111] In a specific implementation, the opening of the bypass air 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, Figure 4 As shown, the heat exchange control parameters are adjusted according to the exhaust pressure change rate and the supply air temperature difference change rate, 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 cold coil sensible heat ratio to the room sensible heat ratio belongs to the first range, maintain the current gear position 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 cold coil sensible heat ratio to the room sensible heat ratio is within the second range or the third range, adjust the gear position of the electromagnetic pump according to the real-time exhaust pressure and the exhaust pressure change rate;

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

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

[0117] In the first case, when △Tm≤TM and S1 / S0 is in the range of 1-1.2, it can be determined that the evaporating heat pipe and the condensing heat pipe can fully perform secondary heat exchange treatment. At this time, there is no need to change the exhaust pressure of the evaporating heat pipe, that is, there is no need to adjust the gear of the electromagnetic pump, and the current gear of the electromagnetic pump is maintained.

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

[0119] In the third case, when △Tm>TM, it is determined that the evaporating heat pipe and the condensing heat pipe cannot fully perform secondary heat exchange processing at this time, and it is also necessary to change the exhaust pressure of the evaporating heat pipe and the internal refrigerant flow rate.

[0120] In one embodiment, Figure 5 As shown, in the second case, adjusting the gear position of the electromagnetic pump according to the real-time exhaust pressure and the exhaust pressure change rate includes:

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

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

[0124] S504: If the real-time exhaust pressure is greater than a third pressure threshold, the current gear position 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<A2<A3.

[0126] When P1≤A1 is detected, it means that the evaporating heat pipe is in a low pressure, low flow rate and no driving force heat exchange state. By increasing the gear of the electromagnetic pump, the internal refrigerant flow rate and steam exhaust pressure can be effectively increased. Specifically, the electromagnetic pump can be increased by 1 gear. It should be noted that the gear increase range of the electromagnetic pump can be determined based on the needs of the actual application scenario and is not limited here.

[0127] When A1<P1≤A2 is detected, it means that the heat pipe is in a medium-low flow rate heat exchange. At this time, more refined adjustment can be made in combination with the pressure change rate △P. If the pressure change rate △P≤PM, the refrigerant flow rate and pressure inside the heat pipe are increased, and the heat exchange efficiency of the heat pipe is increased, which can be achieved by raising the electromagnetic pump to 1 / 2 gear; if △P>PM, the refrigerant flow rate inside the heat pipe is relatively high, and the heat exchange efficiency of the heat pipe can be stabilized, which can be achieved by raising the electromagnetic pump to 1 / 3 gear.

[0128] When A2<P1≤A3 is detected, it means that the heat pipe is in a medium-high speed heat exchange state. At this time, the pressure change rate △P can also be combined for more refined adjustment. If △P≤PM, the refrigerant flow rate and exhaust pressure inside the heat pipe can be increased appropriately to improve the heat exchange efficiency. This can be achieved by increasing the electromagnetic pump to 1 / 4 gear. If △P>PM, the refrigerant flow rate inside the heat pipe is relatively high. Stabilizing the heat exchange efficiency of the heat pipe can be achieved by lowering the electromagnetic pump to 1 / 5 gear, so that the internal boiling bubbles can flow more fully to the condensation section, reducing the flow of liquid refrigerant, strengthening convective heat exchange, and lowering the air outlet temperature.

[0129] When it is detected that P1>A3, it means that the flow velocity in the heat pipe has reached the designed critical boiling limit point, and the electromagnetic pump gear position remains unchanged.

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

[0131] In one embodiment, Figure 6 As shown, in the third case, adjusting the gear position of the electromagnetic pump according to the real-time exhaust pressure includes:

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

[0134] S603, if the real-time exhaust pressure is greater than the second pressure threshold, determine whether the difference between the real-time mixed air temperature and the set mixed air temperature is greater than a preset difference threshold, and adjust the gear position of the electromagnetic pump 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, wherein A1<A2<A3.

[0136] When it is detected that P1<A1, it means that the heat pipe is exchanging heat at low pressure and low flow rate without driving force. In this embodiment, the electromagnetic pump 2 is adjusted to increase the gear position to increase the internal refrigerant flow rate and pressure, increase the heat exchange, and reduce the outlet air temperature.

[0137] When it is detected that A1<P1≤A2, it means that the heat pipe is in medium-low speed heat exchange but the heat exchange capacity does not meet the target demand. In this embodiment, the gear position of electromagnetic pump 1 is increased to appropriately increase the refrigerant flow rate and pressure inside the heat pipe to improve the heat exchange efficiency.

[0138] When A2<P1≤A3 is detected, it means that the heat pipe is in medium-high speed heat exchange and has high operating efficiency, but the heat exchange capacity does not meet the target demand, and the opening ratio of the bypass air valve needs to be re-determined.

[0139] In one embodiment, Figure 7 As shown, the gear position of the electromagnetic pump is adjusted according to the difference comparison result, including:

[0140] S701, 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, increase the opening of the bypass vent valve according to a preset ratio, and readjust the electromagnetic pump gear position according to the real-time exhaust pressure;

[0141] S702: If the difference between the real-time mixed air temperature and the set mixed air temperature is greater than a preset difference threshold, the air intake control parameters are re-adjusted 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 the preset difference threshold, it means that the bypass ventilator is operating within the 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 ventilator is in an abnormal state, and the opening of the bypass ventilator needs to be re-adjusted according to the judgment result of the ratio of the room sensible heat ratio and the cold coil sensible heat ratio.

[0143] In actual application, the mixed air temperature can be set 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 the temperature detection component set at the air inlet of the evaporating heat pipe.

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

[0145] In one embodiment, 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 includes:

[0146] Control the start-up of the air inlet motor, cold coil, evaporating heat pipe, electromagnetic pump, condensing heat pipe and exhaust motor to operate according to the control parameters corresponding to the set working gear;

[0147] Control the bypass vent valve to remain closed.

[0148] In this embodiment, when the host starts the air handling unit according to the user setting mode, when the return water temperature is set at 12-17°C, that is, when the return water temperature is medium-low temperature, the main 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 user-set gear air volume. The fresh air is processed by the medium-temperature cold coil to become medium-low temperature humid air. In order to more accurately control the parallel compensation dehumidification capacity of the heat pipe, the bypass air valve is not opened at the first start, and the medium-low temperature humid air is directly sent into the indoor environment.

[0149] In summary, this embodiment provides an air handling unit control method, which can not only realize two air temperature and humidity adjustments, perform two rounds of cooling and dehumidification treatment, and solve the terminal dehumidification capacity temperature of the medium-temperature water energy-saving system, but also can mix the fresh air with the medium-low temperature humidity air output by the cold coil based on the bypass air valve to achieve precise temperature control. In addition, the air handling unit control method adjusts the gear position of the electromagnetic pump between the evaporating heat pipe and the condensing heat pipe in real time according to the exhaust pressure data and air supply data of the evaporating heat pipe, which can ensure efficient heat exchange of the heat pipe recovery. And the air handling unit does not need to use a rotary wheel for dehumidification, which reduces the number of system equipment and production costs, and reduces the maintenance rate and after-sales maintenance costs.

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

[0151] The air inlet motor introduces fresh air into the fan section of the unit, and the air flows evenly to the medium-temperature water cooling coil and the bypass air valve. The fresh air is first cooled and dehumidified by the medium-temperature cold coil and then becomes medium-low temperature air with medium-high humidity. At the same time, the bypass air valve is logically adjusted to make part of the fresh air mix with the medium-low temperature air at the bypass air valve to obtain medium-high temperature and humidity air. The medium-high temperature and humidity air is processed into low-temperature and low-humidity air under the evaporation and heat absorption of the evaporating heat pipe, and then the low-temperature and low-humidity air is delivered into the room.

[0152] The medium and low temperature air in the room enters the condensing heat pipe through the return air outlet, and the medium and low temperature air is heat-recovered and utilized through the condensation and heat release effect of the condensing heat pipe. After the medium and low temperature air is processed into high temperature air, the high temperature air is discharged outdoors.

[0153] The initial state of the refrigerant in the evaporating heat pipe is a low-temperature, low-pressure liquid. After absorbing heat and evaporating, it is converted into high-temperature, low-pressure steam. The electromagnetic pump converts the high-temperature, low-pressure steam into high-temperature, high-pressure steam, and then allows the high-temperature, high-pressure steam to flow into the condensing heat pipe. After condensation and heat release by the condensing heat pipe, it is converted into a low-temperature, high-pressure liquid. Finally, the low-temperature, high-pressure liquid refrigerant flows to the evaporating heat pipe through the flow path and is converted into a low-temperature, low-pressure liquid refrigerant during the cycle.

[0154] It should be understood that, although the various steps in the flowcharts involved in the above-mentioned embodiments are displayed in sequence according to the indication of the arrows, these steps are not necessarily executed in sequence according to the order indicated by the arrows. Unless there is a clear explanation in this article, the execution of these steps does not have a strict order restriction, and these steps can be executed in other orders. Moreover, at least a part of the steps in the flowcharts involved in the above-mentioned embodiments can include multiple steps or multiple stages, and these steps or stages 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 to be carried out in sequence, but can be executed in turn or alternately with other steps or at least a part of the steps or stages in other steps.

[0155] Based on the same inventive concept, the embodiment of the present application also provides an air handling unit control device for implementing the air handling unit control method involved above. The implementation scheme for solving the problem provided by the device is similar to the implementation scheme recorded 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 above, and will not be repeated here.

[0156] In one embodiment, Figure 8 As shown, an air handling unit control device 800 is provided, comprising: a start 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 start-up module 810 is used to control the start-up of the air handling unit so that the air handling unit operates according to the control parameters corresponding to the set working gear;

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

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

[0160] The second acquisition module 840 is used to acquire the exhaust pressure change rate of the evaporating heat pipe and the supply air temperature difference change rate of the supply port after the opening of the bypass air valve is stabilized;

[0161] The second regulating module 850 is used to regulate the heat exchange control parameters according to the exhaust pressure change rate and the supply air temperature difference change rate, wherein the heat exchange control parameters include the gear position of the electromagnetic pump.

[0162] In one embodiment, the first adjustment module 830 is specifically used to calculate the room sensible heat ratio according to the set air parameters and the return air parameters; calculate the cold coil sensible heat ratio according to the return air parameters and the supply air parameters; and adjust the air intake control parameters 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 used to control the mixed air target temperature to be set to the first temperature, the air inlet gear remains unchanged, and the bypass air valve is opened at a first opening if the ratio of the sensible heat ratio of the cold coil to the sensible heat ratio of the room falls within a first range; if the ratio of the sensible heat ratio of the cold coil to the sensible heat ratio of the room falls within a second range, the mixed air target temperature is controlled to be set to the second temperature, the air inlet gear remains unchanged, and the bypass air valve is opened at a second opening, wherein the second temperature is greater than the first temperature, and the second opening is greater than the first opening; if the ratio of the sensible heat ratio of the cold coil to the sensible heat ratio of the room falls within a third range, the mixed air target temperature is controlled to be set to the third temperature, the air inlet gear is increased, and the bypass air valve is opened at a third opening, wherein the third temperature is greater than the second temperature, and the third opening is greater than the second opening.

[0164] In one embodiment, the second adjustment module 850 is specifically used to maintain the current gear of the electromagnetic pump 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 room sensible heat ratio is within the first range; 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 room sensible heat ratio is within the second range or the third range, adjust the gear of the electromagnetic pump according to the real-time exhaust pressure and the exhaust pressure change rate; if the supply air temperature difference change rate is greater than the preset temperature difference change rate threshold, adjust the gear of the electromagnetic pump according to the real-time exhaust pressure.

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

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

[0167] In one of the embodiments, the second adjustment module 850 is specifically used to increase the opening of the bypass air valve according to a preset ratio and readjust the electromagnetic pump gear according to the real-time exhaust pressure 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; if the difference between the real-time mixed air temperature and the set mixed air temperature is greater than the preset difference threshold, readjust the air intake control parameters according to the room sensible heat ratio and the cold coil sensible heat ratio.

[0168] In one embodiment, the start-up module 810 is specifically used to control the start-up of the air inlet motor, the cold coil, the evaporating heat pipe, the electromagnetic pump, the condensing heat pipe and the exhaust motor to operate according to the control parameters corresponding to the set working gear; and control the bypass air valve to remain in a closed state.

[0169] In summary, this embodiment provides an air handling unit control device, which can not only realize two air temperature and humidity adjustments, perform two rounds of cooling and dehumidification treatment, and solve the terminal dehumidification capacity temperature of the medium-temperature water energy-saving system, but also can mix the fresh air with the medium-low temperature humidity air output by the cold coil based on the bypass air valve to achieve precise temperature control. In addition, the air handling unit control method adjusts the gear position of the electromagnetic pump between the evaporating heat pipe and the condensing heat pipe in real time according to the exhaust pressure data and air supply data of the evaporating heat pipe, which can ensure efficient heat exchange of the heat pipe recovery. And the air handling unit does not need to use a rotary wheel for dehumidification, which reduces the number of system equipment and production costs, and reduces the maintenance rate and after-sales maintenance costs.

[0170] Each module in the above-mentioned air handling unit control device can be implemented in whole or in part by software, hardware and a combination thereof. Each of the above-mentioned modules can be embedded in or independent of the processor in the computer device in the form of hardware, or can be stored in the memory in the computer device in the form of software, so that the processor can call and execute the corresponding operations of each of the above modules.

[0171] In one embodiment, a computer device is provided. The computer device may be a terminal, and its internal structure diagram may be as follows: Fig. 9As shown. The 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 used 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 the operation of the operating system and the computer program in the non-volatile storage medium. The input / output interface of the computer device is used to exchange information between the processor and the external device. The communication interface of the computer device is used to communicate with an external terminal in a wired or wireless manner, and the wireless manner can be realized through WIFI, a mobile cellular network, NFC (near field communication) or other technologies. When the computer program is executed by the processor, an air handling unit control method is realized. The display unit of the computer device is used 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, and the input device of the computer device can be a touch layer covering the display screen, or a button, trackball or touchpad set on the computer device shell, or an external keyboard, touchpad or mouse.

[0172] Those skilled in the art will understand that Fig. 9 The structure shown in the figure is only a block diagram of a part of the structure related to the solution of the present application, and does not constitute a limitation on the computer device to which the solution of the present application is applied. The specific computer device may include more or fewer components than those shown in the figure, or combine certain components, or have a different arrangement of components.

[0173] In one embodiment, a computer device is provided, including a memory and a processor, wherein a computer program is stored in the memory, and when the processor executes the computer program, the following steps are implemented:

[0174] Control the start-up of the air handling unit so that the air handling unit operates according to the control parameters corresponding to the set working gear;

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

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

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

[0178] The heat exchange control parameters are adjusted according to the exhaust pressure change rate and the supply air temperature difference change rate, wherein the heat exchange control parameters include the gear position of the electromagnetic pump.

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

[0180] Control the start-up of the air handling unit so that the air handling unit operates according to the control parameters corresponding to the set working gear;

[0181] Obtaining set air parameters, return air parameters and supply air parameters, wherein the air parameters include dry bulb temperature, wet bulb temperature and enthalpy value;

[0182] Adjusting the air intake control parameters according to the set air parameters, the return air parameters and the supply air parameters, wherein the air intake control parameters include the mixed air target temperature, the air intake gear position of the air intake motor and the opening of the bypass air valve;

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

[0184] The heat exchange control parameters are adjusted according to the exhaust pressure change rate and the supply air temperature difference change rate, wherein the heat exchange control parameters include the gear position of the electromagnetic pump.

[0185] In one embodiment, a computer program product is provided, comprising a computer program, which, when executed by a processor, implements the following steps:

[0186] Control the start-up of the air handling unit so that the air handling unit operates according to the control parameters corresponding to the set working gear;

[0187] Obtaining set air parameters, return air parameters and supply air parameters, wherein the air parameters include dry bulb temperature, wet bulb temperature and enthalpy value;

[0188] Adjusting the air intake control parameters according to the set air parameters, the return air parameters and the supply air parameters, wherein the air intake control parameters include the mixed air target temperature, the air intake gear position of the air intake motor and the opening of the bypass air valve;

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

[0190] The heat exchange control parameters are adjusted according to the exhaust pressure change rate and the supply air temperature difference change rate, wherein the heat exchange control parameters include the gear position 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, and the computer program can be stored in a non-volatile computer-readable storage medium. When the computer program is executed, it can include the processes of the embodiments of the above-mentioned methods. Among them, any reference to the memory, database or other medium used in the embodiments provided in this 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 memory, high-density embedded non-volatile memory, resistive random access memory (ReRAM), magnetoresistive random access memory (MRAM), ferroelectric random access 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 and not limitation, RAM can be in various forms, such as static random access memory (SRAM) or dynamic random access memory (DRAM). The database involved in each embodiment provided in this application may include at least one of a relational database and a non-relational database. Non-relational databases may include distributed databases based on blockchains, etc., but are not limited to this. The processor involved in each embodiment provided in this application may be a general-purpose processor, a central processing unit, a graphics processor, a digital signal processor, a programmable logic device, a data processing logic device based on quantum computing, etc., but are not limited to this.

[0192] The technical features of the above embodiments may be combined arbitrarily. To make the description concise, not all possible combinations of the technical features in the above embodiments are described. However, as long as there is no contradiction in the combination of these technical features, they should be considered to be within the scope of this specification.

[0193] The above-described embodiments only express several implementation methods of the present application, and the descriptions thereof are relatively specific and detailed, but they cannot be understood as limiting the scope of the present application. It should be pointed out that, for a person of ordinary skill in the art, several variations and improvements can be made without departing from the concept of the present application, and these all belong to the protection scope of the present application. Therefore, the protection scope of the present application shall be subject to the attached claims.

Claims

1. A method for controlling an air handling unit, It is characterized in that Applied to an air handling unit, wherein the air handling unit comprises an air inlet, an air supply port, a return air port, an air outlet, an air inlet motor, a cold coil, a bypass air valve, an evaporating heat pipe, an electromagnetic pump, a condensing heat pipe and an 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, 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 evaporating heat pipe, the evaporating heat pipe is connected to the condensing heat pipe through the electromagnetic pump, the air outlet end of the evaporating heat pipe is connected to the air supply port, the air inlet end of the condensing heat pipe is connected to the return air port, and the air outlet end of the condensing heat pipe is connected to the air outlet through the exhaust 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; Acquire set air parameters, return air parameters and supply air parameters, wherein the air parameters include dry bulb temperature, wet bulb temperature and enthalpy value; 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 includes a mixed air target temperature, an air intake gear position of the air intake motor and an opening degree of the bypass air valve; After the opening of the bypass air valve is stabilized, obtaining the exhaust pressure change rate of the evaporating heat pipe and the supply air temperature difference change rate of the air supply port; The heat exchange control parameters are adjusted according to the exhaust pressure change rate and the supply air temperature difference change rate, wherein the heat exchange control parameters include the gear position of the electromagnetic pump.

2. The method according to claim 1, It is characterized in that The adjusting the air intake control parameter according to the set air parameter, the return air parameter and the supply air parameter comprises: Calculate the room sensible heat ratio according to the set air parameters and the return air parameters; Calculate the sensible heat ratio of the cold coil according to the return air parameters and the supply air parameters; The air intake control parameter is adjusted according to the room sensible heat ratio and the cold coil sensible heat ratio.

3. The method according to claim 2, It is characterized in that The adjusting the air intake control parameter according to the room sensible heat ratio and the cold coil sensible heat ratio comprises: If the ratio of the sensible heat ratio of the cold coil to the sensible heat ratio of the room is within a first range, the mixed air target temperature is controlled to be set to a first temperature, the air inlet gear remains unchanged, and the bypass air valve is opened at a first opening degree; If the ratio of the sensible heat ratio of the cold coil to the sensible heat ratio of the room is within a second range, the mixed air target temperature is controlled to be set to a second temperature, the air inlet gear remains unchanged, and the bypass air valve is opened at a second opening, wherein the second temperature is greater than the first temperature, and the second opening is greater than the first opening; If the ratio of the sensible heat ratio of the cold coil to the sensible heat ratio of the room is within a third range, the mixed air target temperature is controlled to be set to a third temperature, the air inlet gear is increased, and the bypass air valve is opened at a third opening, wherein the third temperature is greater than the second temperature, and the third opening is greater than the second opening.

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

5. The method according to claim 4, It is characterized in that The step of adjusting the gear position of the electromagnetic pump according to the real-time exhaust pressure and the exhaust pressure change rate comprises: If the real-time exhaust pressure is less than or equal to the first pressure threshold, raising the gear position of the electromagnetic pump; If the real-time exhaust pressure is greater than the first pressure threshold and less than or equal to the second pressure threshold, increasing the gear position of the electromagnetic pump according to the exhaust pressure change rate; If the real-time exhaust pressure is greater than the second pressure threshold and less than or equal to the third pressure threshold, the gear position of the electromagnetic pump is increased or decreased according to the exhaust pressure change rate; If the real-time exhaust pressure is greater than the third pressure threshold, the current gear position 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.

6. The method according to claim 4, It is characterized in that The adjusting the gear position of the electromagnetic pump according to the real-time exhaust pressure comprises: If the real-time exhaust pressure is less than or equal to a first pressure threshold, increasing the gear position of the electromagnetic pump according to a first amplitude; If the real-time exhaust pressure is greater than the first pressure threshold and less than or equal to the second pressure threshold, increasing the gear position of the electromagnetic pump according to a second amplitude; If the real-time exhaust pressure is greater than the second pressure threshold, it is determined 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 position of the electromagnetic pump is adjusted according to the difference comparison result.

7. The method according to claim 6, It is characterized in that The step of adjusting the gear position 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, the opening of the bypass air valve is increased according to a preset ratio, and the electromagnetic pump gear is re-adjusted according to the real-time exhaust pressure; If the difference between the real-time mixed air temperature and the set mixed air temperature is greater than a preset difference threshold, the air intake control parameter is re-adjusted according to the room sensible heat ratio and the cold coil sensible heat ratio.

8. The method according to claim 1, It is characterized in that The controlling the air handling unit to start up so that the air handling unit operates according to the control parameters corresponding to the set working gear includes: Controlling the air inlet motor, the cold coil, the evaporating heat pipe, the electromagnetic pump, the condensing heat pipe and the exhaust motor to start up so as to operate according to the control parameters corresponding to the set working gear; The bypass vent valve is controlled to remain in a closed state.

9. An air handling unit control device, It is characterized in that Applied to an air handling unit, wherein the air handling unit comprises an air inlet, an air supply port, a return air port, an air outlet, an air inlet motor, a cold coil, a bypass air valve, an evaporating heat pipe, an electromagnetic pump, a condensing heat pipe and an 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, 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 evaporating heat pipe, the evaporating heat pipe is connected to the condensing heat pipe through the electromagnetic pump, the air outlet end of the evaporating heat pipe is connected to the air supply port, the air inlet end of the condensing heat pipe is connected to the return air port, and the air outlet end of the condensing heat pipe is connected to the air outlet through the exhaust motor; The device comprises: A starting module, used to control the start-up of the air handling unit so that the air handling unit operates according to the control parameters corresponding to the set working gear; A first acquisition module is used to acquire set air parameters, return air parameters and supply air parameters, wherein the air parameters include dry bulb temperature, wet bulb temperature and enthalpy value; a first regulating module, configured to regulate 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 position of the air intake motor and an opening degree of the bypass air valve; A second acquisition module is used to acquire the exhaust pressure change rate of the evaporating heat pipe and the supply air temperature difference change rate of the air supply port after the opening of the bypass air valve is stabilized; The second regulating module is used to adjust the heat exchange control parameters according to the exhaust pressure change rate and the supply air temperature difference change rate, wherein the heat exchange control parameters include the gear position of the electromagnetic pump.

10. An air handling unit, It is characterized in that include: Controller, air inlet, air supply, return air, exhaust, air inlet motor, cold coil, bypass air damper, evaporation heat pipe, electromagnetic pump, condensation heat pipe and 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, 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 supply port, the air inlet end of the condensation heat pipe is connected to the return air port, and the air outlet end of the condensation heat pipe is connected to the exhaust port through the exhaust motor; The controller is respectively connected to the air inlet motor, the cold coil, the bypass air valve, the evaporation heat pipe, the electromagnetic pump, the condensation heat pipe and the exhaust motor; The controller is used to implement the steps of the air handling unit control method according to any one of claims 1 to 8.

11. A fresh air system, It is characterized in that Includes the air handling unit as described in claim 10.

12. An air conditioning device, It is characterized in that Comprising the air handling unit as described in claim 10.

13. A computer device comprising a memory and a processor, wherein the memory stores a computer program. It is characterized in that When the processor executes the computer program, the steps of the air handling unit control method according to any one of claims 1 to 8 are implemented.

14. A computer-readable storage medium having a computer program stored thereon, It is characterized in that When the computer program is executed by a processor, the steps of the air handling unit control method according to any one of claims 1 to 8 are implemented.

15. A computer program product comprising a computer program, It is characterized in that When the computer program is executed by a processor, the steps of the air handling unit control method according to any one of claims 1 to 8 are implemented.

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