CN114110884B - New fan, control method thereof and computer readable storage medium - Google Patents

New fan, control method thereof and computer readable storage medium Download PDF

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Publication number
CN114110884B
CN114110884B CN202111407967.8A CN202111407967A CN114110884B CN 114110884 B CN114110884 B CN 114110884B CN 202111407967 A CN202111407967 A CN 202111407967A CN 114110884 B CN114110884 B CN 114110884B
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Prior art keywords
fresh air
heat exchanger
temperature
compressor
parameter
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CN114110884A (en
Inventor
徐振坤
高卓贤
刘步东
李金波
杜顺开
黄剑云
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GD Midea Air Conditioning Equipment Co Ltd
Midea Group Wuhan Refrigeration Equipment Co Ltd
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GD Midea Air Conditioning Equipment Co Ltd
Midea Group Wuhan Refrigeration Equipment Co Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F7/00—Ventilation
    • F24F7/04—Ventilation with ducting systems, e.g. by double walls; with natural circulation
    • F24F7/06—Ventilation with ducting systems, e.g. by double walls; with natural circulation with forced air circulation, e.g. by fan positioning of a ventilator in or against a conduit
    • F24F7/08—Ventilation with ducting systems, e.g. by double walls; with natural circulation with forced air circulation, e.g. by fan positioning of a ventilator in or against a conduit with separate ducts for supplied and exhausted air with provisions for reversal of the input and output systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/62—Control or safety arrangements characterised by the type of control or by internal processing, e.g. using fuzzy logic, adaptive control or estimation of values
    • F24F11/63—Electronic processing
    • F24F11/64—Electronic processing using pre-stored data
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/89—Arrangement or mounting of control or safety devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F12/00—Use of energy recovery systems in air conditioning, ventilation or screening
    • F24F12/001—Use of energy recovery systems in air conditioning, ventilation or screening with heat-exchange between supplied and exhausted air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
    • F24F13/30—Arrangement or mounting of heat-exchangers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
    • F24F3/12—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling
    • F24F3/14—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification
    • F24F3/153—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification with subsequent heating, i.e. with the air, given the required humidity in the central station, passing a heating element to achieve the required temperature
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating

Abstract

The invention discloses a control method of a fresh air machine, the fresh air machine comprises a heat exchange module and a dehumidification module, the heat exchange module comprises a first heat exchanger, a second heat exchanger, a first throttling device and a third heat exchanger which are sequentially connected, the first heat exchanger is arranged in an exhaust air duct, the third heat exchanger, the dehumidification module and the second heat exchanger are sequentially arranged along a fresh air flow path, and the dehumidification module is independent of a first loop, the method comprises the following steps: acquiring humidity characteristic parameters representing the dehumidification requirement of the fresh air and characteristic temperature representing the heating requirement of the fresh air; and determining a target control parameter according to the humidity characteristic parameter and the characteristic temperature, and controlling the heat exchange module to operate according to the target control parameter so as to enable the fresh air outlet temperature and the fresh air outlet humidity of the fresh air machine to reach target comfortable states. The invention also discloses a new fan and a readable storage medium. The invention aims to improve the flexibility of temperature and humidity regulation of the fresh air fan and realize accurate matching of the temperature and humidity of the fresh air outlet and indoor comfort requirements.

Description

New fan, control method thereof and computer readable storage medium
Technical Field
The invention relates to the technical field of fresh air equipment, in particular to a control method of a fresh air machine, the fresh air machine and a computer readable storage medium.
Background
In recent years, with the improvement of the life quality of people, the quality of indoor air is increasingly emphasized. The fresh air unit is an important component of a room air conditioning system, and can send filtered outdoor fresh air into a room to replace polluted air on one hand; on the other hand, the fresh air can be subjected to heat-moisture treatment to bear part of room heat-moisture load.
The existing fresh air machine is characterized in that the heat pipe heat exchangers are respectively arranged at the front and the rear of the dehumidifying module, fresh air is subjected to heat absorption and temperature reduction through the heat pipe evaporator, is subjected to further dehumidification and temperature reduction through the dehumidifying module, and is heated and heated through the heat pipe condenser to be sent into a room.
However, at present, humidity adjustment and temperature adjustment in the reheating and dehumidifying process of the fresh air machine are independently regulated and controlled, the humidity is independently regulated through a dehumidifying module, a heat pipe heat exchanger can be only suitable for temperature adjustment, the flexibility of temperature and humidity adjustment is insufficient, and the temperature and humidity of fresh air outlet cannot meet indoor comfort requirements easily.
Disclosure of Invention
The invention mainly aims to provide a control method of a fresh air machine, the fresh air machine and a computer readable storage medium, and aims to improve the flexibility of temperature and humidity regulation in the reheating and dehumidification process of the fresh air machine and realize accurate matching of the temperature and humidity of fresh air outlet and indoor comfort requirements.
In order to achieve the above object, the present invention provides a control method of a fresh air fan, the fresh air fan includes a fresh air duct, an exhaust air duct, a heat exchange module and a dehumidification module, the heat exchange module includes a first loop, the first loop includes a first heat exchanger, a second heat exchanger, a first throttling device and a third heat exchanger which are sequentially connected, the first heat exchanger is disposed in the exhaust air duct, the third heat exchanger, the dehumidification module and the second heat exchanger are sequentially arranged in the fresh air duct along a fresh air flow path, the dehumidification module is independent of the first loop, and the control method of the fresh air fan includes the following steps:
acquiring humidity characteristic parameters and characteristic temperatures; the humidity characteristic parameter represents the dehumidification requirement of the fresh air, and the characteristic temperature represents the heating requirement of the fresh air;
determining target control parameters of the heat exchange module according to the humidity characteristic parameters and the characteristic temperature;
and controlling the heat exchange module to operate according to the target control parameter, so that the fresh air outlet temperature and the fresh air outlet humidity of the fresh air fan reach target comfort states.
Optionally, the step of determining the target control parameter of the heat exchange module according to the humidity characteristic parameter and the characteristic temperature includes:
When the humidity characteristic parameter is larger than a preset humidity parameter, if the characteristic temperature is larger than a target comfort temperature, determining a first control parameter as the target control parameter; the first control parameter is used for reducing the heating capacity of the heat exchange module to fresh air and increasing the dehumidifying capacity of the heat exchange module to the fresh air;
and if the characteristic temperature is smaller than the target comfort temperature, determining a second control parameter as the target control parameter, wherein the second control parameter is used for increasing the heating capacity of the heat exchange module on fresh air and increasing the dehumidifying capacity of the heat exchange module on the fresh air.
Optionally, the heat exchange module further includes an electromagnetic valve, a compressor, and a first check valve disposed between the refrigerant outlet of the third heat exchanger and the refrigerant inlet of the first heat exchanger, the compressor is connected in parallel with the first check valve, the electromagnetic valve is connected in series with the compressor, the heat exchange module further includes an exhaust fan disposed in the exhaust air duct, and the first control parameter includes at least one of the following parameters:
opening the compressor, opening the electromagnetic valve, increasing the rotating speed of the exhaust fan, and reducing the opening of the first throttling device;
And opening the compressor, opening the electromagnetic valve, increasing the rotating speed of the exhaust fan, and increasing the frequency of the compressor.
Optionally, the heat exchange module further includes an electromagnetic valve, a compressor, and a first check valve disposed between the refrigerant outlet of the third heat exchanger and the refrigerant inlet of the first heat exchanger, the compressor is connected in parallel with the first check valve, the electromagnetic valve is connected in series with the compressor, the heat exchange module further includes an exhaust fan disposed in the exhaust air duct, and the second control parameter includes at least one of the following parameters:
opening the compressor, opening the electromagnetic valve, reducing the rotating speed of the exhaust fan and reducing the opening of the first throttling device;
and opening the compressor, opening the electromagnetic valve, reducing the rotating speed of the exhaust fan, and increasing the frequency of the compressor.
Optionally, the step of determining a target control parameter according to the humidity characteristic parameter and the characteristic temperature includes:
when the humidity characteristic parameter is smaller than or equal to a preset humidity parameter, if the characteristic temperature is larger than a target comfort temperature, determining a third control parameter as the target control parameter; the third control parameter is used for reducing the heating capacity of the heat exchange module to fresh air;
And if the characteristic temperature is smaller than the target comfort temperature, determining a fourth control parameter as the target control parameter, wherein the fourth control parameter is used for increasing the heating amount of the heat exchange module to the fresh air.
Optionally, the heat exchange module further includes an electromagnetic valve, a compressor, and a first check valve disposed between the refrigerant outlet of the third heat exchanger and the refrigerant inlet of the first heat exchanger, the compressor is connected in parallel with the first check valve, the electromagnetic valve is connected in series with the compressor, the heat exchange module further includes an exhaust fan disposed in the exhaust air duct, and the third control parameter includes at least one of the following parameters:
the running rotating speed of the exhaust fan is increased;
controlling the compressor to switch from an open state to a closed state, controlling the electromagnetic valve to switch from an open state to a closed state, and controlling the first throttling device to maintain the open state;
and controlling the compressor to maintain a closed state, controlling the electromagnetic valve to switch from the closed state to the open state or controlling the first throttling device to switch from the open state to the closed state.
Optionally, the heat exchange module further includes an electromagnetic valve, a compressor, and a first check valve disposed between the refrigerant outlet of the third heat exchanger and the refrigerant inlet of the first heat exchanger, the compressor is connected in parallel with the first check valve, the electromagnetic valve is connected in series with the compressor, the heat exchange module further includes an exhaust fan disposed in the exhaust air duct, and the fourth control parameter includes at least one of the following parameters:
Reducing the running rotating speed of the exhaust fan;
controlling the compressor to switch from a closed state to an open state, controlling the electromagnetic valve to switch from the closed state to the open state, and controlling the first throttling device to maintain the open state;
controlling the compressor to maintain a closed state, controlling the electromagnetic valve to switch from an open state to a closed state, and controlling the first throttling device to maintain an open state;
the compressor is controlled to maintain a closed state, the solenoid valve is controlled to maintain a closed state, and the first throttle device is controlled to switch from a closed state to an open state.
Optionally, the step of acquiring the humidity characteristic parameter includes:
acquiring the exhaust temperature and the exhaust humidity of the fresh air fan;
calculating the exhaust moisture content according to the exhaust temperature and the exhaust humidity, wherein the humidity characteristic parameter comprises the exhaust moisture content;
or, acquiring the fresh air outlet temperature and the fresh air outlet humidity of the fresh air fan;
calculating the wind moisture content according to the fresh air outlet temperature and the fresh air outlet rheumatism, wherein the humidity characteristic parameters comprise the wind moisture content;
or, obtaining the fresh air temperature of the air outlet side of the dehumidification module;
And calculating the fresh air moisture content according to the fresh air temperature, wherein the humidity characteristic parameter comprises the fresh air moisture content.
In addition, in order to realize above-mentioned purpose, this application still provides a new fan, new fan includes:
fresh air duct;
an exhaust air duct;
the heat exchange module comprises a first loop, wherein the first loop comprises a first heat exchanger, a second heat exchanger, a first throttling device and a third heat exchanger which are sequentially connected, and the first heat exchanger is arranged in an exhaust air duct;
the dehumidification module is independent of the first loop, and the third heat exchanger, the dehumidification module and the second heat exchanger are sequentially arranged in the fresh air duct along a fresh air flow path;
the heat exchange module and the dehumidification module are both connected with the control device, and the control device comprises: the system comprises a memory, a processor and a control program of the fresh air fan, wherein the control program of the fresh air fan is stored in the memory and can run on the processor, and the control program of the fresh air fan realizes the steps of the control method of the fresh air fan when being executed by the processor.
In addition, in order to achieve the above object, the present application further proposes a computer-readable storage medium, on which a control program of a fresh air machine is stored, which when executed by a processor, implements the steps of the control method of a fresh air machine as set forth in any one of the above.
According to the fresh air machine provided by the invention, the first heat exchanger is arranged in the air exhaust duct, the third heat exchanger, the dehumidifying module and the second heat exchanger are arranged on the fresh air flow path at one time, the first heat exchanger, the second heat exchanger, the first throttling device and the third heat exchanger are sequentially connected in series to form the first loop, wherein the first heat exchanger can recover sensible heat exhausted in the air exhaust duct, a refrigerant after the sensible heat recovery in the first loop further enters the second heat exchanger to heat dehumidified fresh air so as to realize dehumidification reheating of the fresh air, and based on the fresh air machine, the method controls the operation of the heat exchange module based on the target control parameters determined by the humidity characteristic parameters and the characteristic temperature representing the fresh air temperature and humidity requirement, so that the heat exchange module is not only suitable for temperature requirement adjustment, but also suitable for humidity requirement adjustment, thereby improving the flexibility of temperature and humidity adjustment in the reheating and dehumidifying process of the fresh air, and realizing accurate matching of the temperature and humidity of fresh air outlet with indoor comfort requirement.
Drawings
FIG. 1 is a schematic diagram of a fresh air machine according to an embodiment of the present invention;
FIG. 2 is a schematic diagram of another embodiment of a fresh air blower according to the present invention;
FIG. 3 is a schematic view of a structure of a fresh air machine according to another embodiment of the present invention;
FIG. 4 is a schematic view of a structure of a fresh air machine according to another embodiment of the present invention;
FIG. 5 is a schematic diagram of a hardware architecture involved in operation of an embodiment of the new wind turbine of the present invention;
FIG. 6 is a flow chart of an embodiment of a method for controlling a fresh air machine according to the present invention;
FIG. 7 is a flow chart of another embodiment of a method for controlling a fresh air machine according to the present invention;
fig. 8 is a flowchart of a control method of a fresh air machine according to another embodiment of the present invention.
Reference numerals illustrate:
Figure BDA0003373068760000051
Figure BDA0003373068760000061
the achievement of the objects, functional features and advantages of the present invention will be further described with reference to the accompanying drawings, in conjunction with the embodiments.
Detailed Description
It should be understood that the specific embodiments described herein are for purposes of illustration only and are not intended to limit the scope of the invention.
The main solutions of the embodiments of the present invention are: the new fan includes new trend wind channel, the wind channel of airing exhaust, heat transfer module and dehumidification module, heat transfer module includes first return circuit, first return circuit is including first heat exchanger, second heat exchanger, first throttling arrangement and the third heat exchanger that connects gradually, the wind channel of airing exhaust is located to first heat exchanger, the third heat exchanger dehumidification module and the second heat exchanger is in the new trend wind channel is arranged in proper order along the new trend flow path, dehumidification module is independent of first return circuit sets up, and this method includes: acquiring humidity characteristic parameters and characteristic temperatures; the humidity characteristic parameter represents the dehumidification requirement of the fresh air, and the characteristic temperature represents the heating requirement of the fresh air; determining target control parameters of the heat exchange module according to the humidity characteristic parameters and the characteristic temperature; and controlling the heat exchange module to operate according to the target control parameter, so that the fresh air outlet temperature and the fresh air outlet humidity of the fresh air fan reach target comfort states.
Because the humidity adjustment and the temperature adjustment in the reheating and dehumidifying process of the fresh air machine are independently regulated and controlled in the prior art, the humidity is independently regulated through the dehumidifying module, the heat pipe heat exchanger can only be suitable for temperature adjustment, the flexibility of temperature and humidity adjustment is insufficient, and the temperature and humidity of fresh air outlet cannot meet indoor comfort requirements easily.
The invention provides the solution scheme, and aims to improve the flexibility of temperature and humidity regulation in the reheating and dehumidifying process of the fresh air machine and realize accurate matching of the temperature and humidity of the fresh air outlet and indoor comfort requirements.
The embodiment of the invention provides a new fan.
Referring to fig. 1, in an embodiment of the present invention, a fresh air fan includes: fresh air duct 1, exhaust air duct 2, heat transfer module 01 and dehumidification module.
The heat exchange module 01 comprises a first loop, wherein the first loop comprises a first heat exchanger 5, a second heat exchanger 6, a first throttling device 12 and a third heat exchanger 7 which are sequentially connected in series.
The dehumidification module 4 is arranged independently of the first circuit. In the present embodiment, the dehumidification module 4 is specifically a heat exchanger in an evaporated state. In other embodiments, the dehumidifying module 4 may also be any module having a dehumidifying function, such as a desiccant-loaded module or the like.
The first heat exchanger 5 set up in the wind channel of airing exhaust 2, second heat exchanger 6, third heat exchanger 7 and dehumidification module 8 set up in the fresh air wind channel 1, and third heat exchanger 7, dehumidification module 8 and second heat exchanger 6 are in arrange in proper order on the fresh air flow path in the fresh air wind channel 1, the fresh air that enters into in the fresh air wind channel 1 from the outdoor process third heat exchanger 7, dehumidification module 8 and second heat exchanger 6 in proper order, dehumidification module 8 can cool down the dehumidification to the fresh air.
Further, the heat exchange module 01 may further include an exhaust fan 3 and a fresh air fan 4 disposed in the exhaust air duct 2 and the fresh air duct 1 respectively, where the exhaust fan 3 is used to suck indoor air into the exhaust air duct 2 and exhaust the air to the outside, and the fresh air fan 4 is used to suck outdoor air into the fresh air duct 1 and exhaust the air to the inside.
Judging whether the fresh air needs to be dehumidified and reheated or not and the degree of dehumidification and reheating is determined by judging the temperature of the exhaust air at the inlet of the exhaust air duct 2 and the temperature of the fresh air at the inlet of the fresh air duct 1, and running in the most suitable mode under different working conditions; and meanwhile, the first heat exchanger is arranged in the exhaust channel 2, and sensible heat of exhaust air is recovered, so that an energy-saving effect is achieved.
When the indoor temperature is low and the fresh air temperature is moderate, the fresh air needs to be subjected to energy-saving dehumidification and reheating. At this time, the first throttling device 12 is turned on, and the fresh air ventilator starts the heat pipe heat recovery cycle, and at the same time, the dehumidification module 8 is turned on. The first heat exchanger 5 is arranged in the exhaust air duct 2, the indoor temperature is low, so that the exhaust air temperature in the exhaust air duct 2 is low, the medium-temperature gaseous refrigerant transfers heat to exhaust air outside the first heat exchanger 5 for liquefaction, and the temperature is reduced; the medium-temperature refrigerant is cooled by the fresh air with lower temperature, so that heat recovery is realized, and the energy utilization rate is improved. The refrigerant with reduced temperature is led out from the first heat exchanger 5 and enters the second heat exchanger 6, heat is transferred to fresh air outside the second heat exchanger 6, the temperature is further reduced, and the pressure and the temperature of the refrigerant are further reduced after flowing through the first throttling device 12. Then, the refrigerant flows in the first throttling device 12 to generate a siphoning effect and enter the third heat exchanger 7, the third heat exchanger 7 is arranged at a fresh air inlet, the fresh air temperature is moderate, and after the heat of the fresh air outside the third heat exchanger 7 is absorbed, the liquid refrigerant is converted into a gaseous refrigerant. The refrigerant at the inlet side of the first heat exchanger 5 is in a gaseous state, the refrigerant at the outlet side of the first heat exchanger is in a liquid state, and the gaseous refrigerant flowing out of the third heat exchanger 7 enters the first heat exchanger 5 under the action of pressure difference to perform the next cycle. The third heat exchanger 7, the dehumidifying module 8 and the second heat exchanger 6 are sequentially arranged in the fresh air duct 1, and the third heat exchanger 7 is positioned at the inlet of the fresh air duct 1. When the medium-temperature fresh air enters the fresh air duct 1, the medium-temperature fresh air passes through the third heat exchanger 7, and the temperature is reduced after heat is transferred to the refrigerant. After the dehumidification module 8, the dehumidification module 8 is in an operation state at the moment, the temperature and the humidity of fresh air are reduced, and finally, when the fresh air passes through the second heat exchanger 6, the fresh air absorbs the heat of a refrigerant, and after the temperature rises to a proper size, the fresh air enters a room, so that the indoor air comfort level is improved.
When the indoor temperature is higher, the fresh air needs to be dehumidified and cooled. The first throttle device 12 is closed at this time. Since the first throttling device 12 is closed, the refrigerant flowing out of the second heat exchanger 6 cannot enter the third heat exchanger 7, and the heat pipe circulation of the fresh air fan is interrupted. When the fresh air passes through the fresh air duct 1, the refrigerant cannot complete circulation, and the third heat exchanger 7 and the second heat exchanger 6 do not perform heat exchange work. Because dehumidification module 8 is in the open state, when new trend passes through dehumidification module 8, temperature and humidity all reduce, get into indoor later, improve indoor air comfort level.
In an embodiment, the dehumidification module 8 is provided with a cold water inlet and a cold water outlet, the cold source for cooling and dehumidifying the dehumidification module 8 is cold water, and the circulating flow of the cold water in the dehumidification module 8 is realized through an external cold water source, so that the effect of continuously cooling and dehumidifying fresh air is achieved.
With continued reference to fig. 1, in an embodiment, the heat exchange module 01 may further include the electromagnetic valve 22, the first compressor 16, and the first check valve 20 disposed between the refrigerant outlet of the third heat exchanger 7 and the refrigerant inlet of the first heat exchanger 5, where the first compressor 16 is connected in parallel with the first check valve 20, and the electromagnetic valve is connected in series with the first compressor 16. Based on the above, the adaptability of the fresh air machine to different working conditions is improved, the energy conservation of the heat pipe fan can be guaranteed when the fresh air temperature is low or high, and the temperature and humidity of the fresh air can be regulated to reach the comfortable state of indoor users.
Specifically, the first circuit is externally connected with a first compressor 16, the outlet of the first compressor 16 is communicated with the inlet of the first heat exchanger 5, the inlet of the first compressor 16 is communicated with the outlet of the third heat exchanger 7, a first check valve 20 which is connected in series with the first circuit and has a flow direction from the outlet of the third heat exchanger 7 to the inlet of the first heat exchanger 5, the first compressor 16 is connected in parallel with the first check valve 20, a second check valve 21 is arranged on a pipeline of the first circuit, which is connected with the outlet side of the first compressor 16, and a solenoid valve 22 is arranged on a pipeline of the first circuit, which is connected with the inlet side of the first compressor 16. The first compressor 16, the first throttling device 12 and the dehumidification module 8 are turned on and off to realize heat pump cycle dehumidification reheating or heat pipe cycle dehumidification reheating in different modes; the flow direction of the refrigerant in the fresh air machine in different modes is controlled by opening and closing the electromagnetic valve 22, and the first check valve 20 and the second check valve 21 limiting the flow direction.
When the indoor temperature is low and the fresh air temperature is high, dehumidification and reheating of the fresh air need to be enhanced. At this time, the first compressor 16 is controlled to be turned on, the electromagnetic valve 22 and the first throttling device 12 are opened, and the fresh air fan starts to perform a heat pump heat recovery cycle while the dehumidification module 8 is turned on. After the first compressor 16 is turned on, the sucked medium-temperature low-pressure gaseous refrigerant is compressed and converted into a high-temperature high-pressure gaseous refrigerant, and after being discharged from the first compressor 16, the high-temperature high-pressure gaseous refrigerant is led into the first heat exchanger 5 after passing through the second one-way valve 21. The first heat exchanger 5 is arranged in the exhaust air duct 2, the indoor temperature is low, so that the exhaust air temperature in the exhaust air duct 2 is low, the high-temperature and high-pressure gaseous refrigerant transfers heat to the exhaust air outside the first heat exchanger 5 for liquefaction, and the temperature is reduced; the fresh air with lower temperature is utilized to cool the high-temperature refrigerant, so that heat recovery is realized, and the energy utilization rate is improved. The refrigerant with reduced temperature is led out from the first heat exchanger 5 and enters the second heat exchanger 6, heat is transferred to fresh air outside the second heat exchanger 6, the temperature is further reduced, the refrigerant is changed from high pressure to low pressure after flowing through the first throttling device 12, and the temperature is further reduced. And then the refrigerant enters the third heat exchanger 7, the third heat exchanger 7 is arranged at a fresh air inlet, the fresh air temperature is higher, and after the heat of the fresh air outside the third heat exchanger 7 is absorbed, the low-temperature low-pressure liquid refrigerant is converted into a medium-temperature low-pressure gaseous refrigerant. Since the first compressor 16 is opened and the solenoid valve 22 is opened, the pressure at the outlet side of the first compressor 16 is higher than the pressure at the inlet side of the first compressor 16, so that the refrigerant does not pass through the first check valve 20, and the medium-temperature low-pressure gaseous refrigerant is led out of the third heat exchanger 7 and then is sucked into the first compressor 16 to perform the next cycle. The third heat exchanger 7, the dehumidifying module 8 and the second heat exchanger 6 are sequentially arranged in the fresh air duct 1, and the third heat exchanger 7 is positioned at the inlet of the fresh air duct 1. When the high-temperature fresh air enters the fresh air duct 1, the heat is transferred to the refrigerant through the third heat exchanger 7, and then the temperature is reduced. After the dehumidification module 8, the dehumidification module 8 is in an operation state at the moment, the temperature and the humidity of fresh air are reduced, and finally, when the fresh air passes through the second heat exchanger 6, the fresh air absorbs the heat of a refrigerant, and after the temperature rises to a proper size, the fresh air enters a room, so that the indoor air comfort level is improved.
When the indoor temperature is low and the fresh air temperature is moderate, the fresh air needs to be subjected to energy-saving dehumidification and reheating. At this time, the first compressor 16 and the solenoid valve 22 are closed, the first throttle device 12 is opened, the fresh air fan starts the heat pipe heat recovery cycle, and the dehumidification module 8 is simultaneously opened.
When the indoor temperature and the fresh air temperature are low, dehumidification and reheating of the fresh air need to be reduced. At this time, the first compressor 16 is controlled to be turned on, the electromagnetic valve 22 and the first throttling device 12 are opened, and the fresh air fan starts a heat pump heat recovery cycle while the dehumidification module 8 is turned off. After the first compressor 16 is turned on, the sucked medium-temperature low-pressure gaseous refrigerant is compressed and converted into a high-temperature high-pressure gaseous refrigerant, and after being discharged from the first compressor 16, the high-temperature high-pressure gaseous refrigerant is led into the first heat exchanger 5 after passing through the second one-way valve 21. The first heat exchanger 5 is arranged in the exhaust air duct 2, the indoor temperature is low, so that the exhaust air temperature in the exhaust air duct 2 is low, the high-temperature and high-pressure gaseous refrigerant transfers heat to the exhaust air outside the first heat exchanger 5 for liquefaction, and the temperature is reduced; the fresh air with lower temperature is utilized to cool the high-temperature refrigerant, so that heat recovery is realized, and the energy utilization rate is improved. The refrigerant with reduced temperature is led out from the first heat exchanger 5 and enters the second heat exchanger 6, heat is transferred to fresh air outside the second heat exchanger 6, the temperature is further reduced, the refrigerant is changed from high pressure to low pressure after flowing through the first throttling device 12, and the temperature is further reduced. And then the refrigerant enters a third heat exchanger 7, the third heat exchanger 7 is arranged at a fresh air inlet, and after absorbing the heat of the fresh air outside the third heat exchanger 7, the low-temperature low-pressure liquid refrigerant is converted into a medium-temperature low-pressure gaseous refrigerant. Since the first compressor 16 is opened and the solenoid valve 22 is opened, the pressure at the outlet side of the first compressor 16 is higher than the pressure at the inlet side of the first compressor 16, so that the refrigerant does not pass through the first check valve 20, and the medium-temperature low-pressure gaseous refrigerant is led out of the third heat exchanger 7 and then is sucked into the first compressor 16 to perform the next cycle. The third heat exchanger 7, the dehumidifying module 8 and the second heat exchanger 6 are sequentially arranged in the fresh air duct 1, and the third heat exchanger 7 is positioned at the inlet of the fresh air duct 1. When the low-temperature fresh air enters the fresh air duct 1, the temperature is further reduced after heat is transferred to the refrigerant through the third heat exchanger 7. Because the initial temperature of the fresh air is lower, and the fresh air is further cooled by the third heat exchanger 7, energy is not consumed and then the fresh air is cooled and dehumidified, so that the dehumidification module 8 is closed. And finally, when the fresh air passes through the second heat exchanger 6, the fresh air absorbs the heat of the refrigerant, and after the temperature rises to a proper level, the fresh air enters the room, so that the indoor air comfort level is improved.
When the indoor temperature is higher, the fresh air needs to be dehumidified and cooled. At this time, the first compressor 16 is turned off, the solenoid valve 22 is opened, and the dehumidification module 8 is simultaneously turned on. Since the solenoid valve 22 is opened, the refrigerant flowing out of the third heat exchanger 7 cannot flow into the first heat exchanger 5 by the pressure difference, and the heat pipe circulation of the fresh air fan is interrupted. When the fresh air passes through the fresh air duct 1, the refrigerant cannot complete circulation, and the third heat exchanger 7 and the second heat exchanger 6 do not perform heat exchange work. Because dehumidification module 8 is in the open state, when new trend passes through dehumidification module 8, temperature and humidity all reduce, get into indoor later, improve indoor air comfort level.
Referring to fig. 2, in view of this, in another embodiment, a fifth heat exchanger 9 is further included, where the fifth heat exchanger 9 is disposed in the fresh air duct and is located downstream of the second heat exchanger 6 in the fresh air flow direction, and the fifth heat exchanger 9 can heat the fresh air. The fifth heat exchanger 9 is provided with a hot water inlet and a hot water outlet, a heat source for reheating the fresh air by the fifth heat exchanger 9 is hot water, and the circulating flow of the hot water in the fifth heat exchanger 9 is realized through an external hot water source, so that the effect of continuously reheating the fresh air is achieved. An electric heating device can be arranged in the fifth heat exchanger 9, and when the fifth heat exchanger 9 is started, the electric heating device starts to be electrified and generates heat, and the heat is transferred to fresh air, so that the effect of reheating the fresh air is achieved.
Referring to fig. 3, in yet another embodiment, the dehumidification module 8 includes a seventh heat exchanger 11, a third compressor 18 and a fourth throttling device 15, where the third compressor 18, the seventh heat exchanger 11, the fourth throttling device 15 and the fourth heat exchanger 81 are sequentially connected by pipes to form a circulation loop, the fourth heat exchanger 81 is disposed in a fresh air duct, and a cold source for cooling and dehumidifying the dehumidification module 8 is a refrigerant. The third compressor 18 converts the refrigerant into a high temperature and high pressure gas state, and then flows into the seventh heat exchanger 11, and the seventh heat exchanger 11 may be placed outdoors, and the temperature of the refrigerant is reduced after transferring heat to the outdoor air. After flowing out from the seventh heat exchanger 11, the refrigerant is converted into a low-temperature low-pressure state after passing through the fourth throttling device 15, then flows into the fourth heat exchanger 81, the low-temperature low-pressure refrigerant absorbs the heat of the fresh air and is gasified, and the gaseous refrigerant is led out of the fourth heat exchanger 81 and is sucked by the third compressor 18 for the next cycle.
Referring to fig. 4, in this view, in yet another embodiment, the dehumidifying module 8 may cool down and dehumidify the fresh air, the fifth heat exchanger 9 may reheat the fresh air, and the dehumidifying module 8 and the fifth heat exchanger 9 may form a thermal cycle after being communicated with each other and adding other devices. In view of this, in an embodiment, the dehumidification module 8 is a fourth heat exchanger 81, the fresh air fan further includes a sixth heat exchanger 10, a second compressor 17, and a second throttling device 13, the second compressor 17, the sixth heat exchanger 10, the fifth heat exchanger 9, the second throttling device 13, and the fourth heat exchanger 81 are sequentially connected by pipes to form a circulation loop, and the fifth heat exchanger 9 reheat the fresh air through refrigerant circulation. The second compressor 17 converts the refrigerant into a high temperature and high pressure gas state, and then flows into the sixth heat exchanger 10, and the sixth heat exchanger 10 may be placed outdoors, and the temperature of the refrigerant is reduced after transferring heat to the outdoor air. After flowing out from the sixth heat exchanger 10, the refrigerant flows into the fifth heat exchanger 9, the refrigerant transfers heat to the fresh air through the fifth heat exchanger 9, and the fresh air is sent into a room after being reheated to a proper temperature. After flowing out from the fifth heat exchanger 9, the refrigerant is converted into a low-temperature and low-pressure state by the second throttling device 13, then flows into the fourth heat exchanger 81, the low-temperature and low-pressure refrigerant absorbs the heat of the fresh air and is gasified, the moisture content of the fresh air in the heat absorption process is reduced, and the gaseous refrigerant is sucked by the second compressor 17 after being led out of the fourth heat exchanger 81, so that the next cycle is performed.
Further, a third throttling device 14 is disposed between the fifth heat exchanger 9 and the sixth heat exchanger 10. When the third throttling device 14 is opened and does not perform throttling, and the second throttling device 13 is opened and performs throttling, the heat pump system formed between the fourth heat exchanger 81 and the fifth heat exchanger 9 performs dehumidifying and reheating functions on fresh air as in the previous embodiment. When the third throttling means 14 is opened and performs a throttling function, and the second throttling means 13 is opened and does not perform a throttling function, the refrigerant flowing out of the sixth heat exchanger 10 is changed into a low temperature state after passing through the three stages of devices, and then flows into the fifth heat exchanger 9. At this time, the fifth heat exchanger 9 plays a role in cooling the fresh air, and the heat pump system formed between the fourth heat exchanger 81 and the fifth heat exchanger 9 plays a role in cooling and dehumidifying the fresh air. By adding the third throttling device 14, the heat pump system formed between the fourth heat exchanger 81 and the fifth heat exchanger 9 can switch between a dehumidifying and reheating function and a cooling and dehumidifying function, so that the applicable range is widened.
The fresh air can be dehumidified by the fresh air blower, so that the humidity of the fresh air after heat exchange is not changed, and the third heat exchanger 7 and the second heat exchanger 6 are not suitable to be mixed with a mixed heat exchanger, so that the change of the humidity caused by mixed contact of the fresh air and a refrigerant is avoided. Typically, the second heat exchanger 6 and the third heat exchanger 7 are regenerative heat exchangers or dividing wall heat exchangers or a combination of both. In an embodiment, the second heat exchanger 6 and the third heat exchanger 7 are plate heat exchangers, and the plate heat exchangers have high heat exchange efficiency, small heat loss, compact and light structure, small occupied area, convenient installation and cleaning, wide application and long service life.
Further, based on any of the above embodiments, in an embodiment of the present invention, the fresh air machine may further include a control device. Referring to fig. 5, the heat exchange module 01 and the dehumidification module 8 may be connected to a control device. Specifically, the heat exchange module 01, the dehumidification module 8 and other components can be connected with a control device, and the control device can be used for controlling the operation of the heat exchange module 01, the dehumidification module 8 and other components.
Further, the fresh air fan may further include a temperature detection module 02 and/or a humidity detection module 03. The temperature detection module 02 can be used for detecting relevant temperature data required by the operation regulation of the fresh air fan. The temperature detection module 03 can be used for detecting relevant humidity data required by the operation regulation of the fresh air ventilator. The temperature detection module 02 and/or the humidity detection module 03 are connected with a control device, and the control device can be used for acquiring data detected by the temperature detection module 02 and/or the humidity detection module 03. Specifically, the temperature detection module 02 and the detection module 03 can be arranged at the outlet of the fresh air duct 1, the inlet of the fresh air duct 1, the front of the second heat exchanger 6 and the dehumidification module 8 in the fresh air duct 1, the indoor environment acted by the fresh air fan, the inlet of the exhaust air duct and/or the outlet of the exhaust air duct, etc.
In an embodiment of the present invention, referring to fig. 5, a control device of a fresh air machine includes: a processor 1001 (e.g., CPU), a memory 1002, a timer 1003, and the like. The memory 1002 may be a high-speed RAM memory or a stable memory (non-volatile memory), such as a disk memory. The memory 1002 may alternatively be a storage device separate from the processor 1001 described above.
It will be appreciated by those skilled in the art that the device structure shown in fig. 5 is not limiting of the device and may include more or fewer components than shown, or certain components may be combined, or a different arrangement of components.
As shown in fig. 5, a control program of the fresh air machine may be included in a memory 1002 as a computer-readable storage medium. In the apparatus shown in fig. 5, a processor 1001 may be used to call a control program of the fresh air blower stored in a memory 1002 and perform the relevant step operations of the control method of the fresh air blower in the following embodiments.
The embodiment of the invention also provides a control method of the fresh air machine, which is applied to control the fresh air machine.
Referring to fig. 6, an embodiment of a control method of the fresh air machine is provided. In this embodiment, the method for controlling the fresh air machine includes:
S10, acquiring humidity characteristic parameters and characteristic temperatures; the humidity characteristic parameter represents the dehumidification requirement of the fresh air, and the characteristic temperature represents the heating requirement of the fresh air;
the humidity characteristic parameter specifically represents the parameter of the fresh air dehumidification requirement. In this embodiment, the humidity characteristic parameter is the moisture content, and in other embodiments, the humidity characteristic parameter may be absolute humidity or relative humidity.
Specifically, in one implementation manner, the exhaust temperature and the exhaust humidity of the fresh air fan are obtained; and calculating the exhaust moisture content according to the exhaust temperature and the exhaust humidity, wherein the humidity characteristic parameter comprises the exhaust moisture content. In another implementation mode, the fresh air outlet temperature and the fresh air outlet humidity of the fresh air fan are obtained; and calculating the wind moisture content according to the fresh air outlet temperature and the fresh air outlet rheumatism, wherein the humidity characteristic parameters comprise the wind moisture content. In a further implementation mode, the fresh air temperature of the air outlet side of the dehumidification module is obtained; and calculating the fresh air moisture content according to the fresh air temperature, wherein the humidity characteristic parameter comprises the fresh air moisture content. Specifically, the air outlet side may be a position between the dehumidification module and the second heat exchanger. The air exhaust moisture content, the air outlet moisture content and the fresh air moisture content can accurately represent the humidification requirement of the fresh air.
In this embodiment, the characteristic temperature is the temperature detected by the air outlet of the fresh air duct. In other embodiments, the characteristic temperature may also be the temperature of the air inlet of the fresh air duct; the temperature of the position between the dehumidification module and the second heat exchanger in the fresh air duct and the like.
Step S20, determining target control parameters of the heat exchange module according to the humidity characteristic parameters and the characteristic temperature;
the target control parameter may be a target temperature and humidity value of a related component for performing temperature and humidity adjustment on the fresh air (for example, a target value of a coil temperature of the second heat exchanger or a target value of a coil temperature of the third heat exchanger, etc.), and may also be an operation parameter of a related component for performing temperature and humidity adjustment on the fresh air, for example, an operation rotation speed of a fan that affects temperature and humidity adjustment efficiency (for example, a rotation speed of a fresh air fan and/or a rotation speed of an exhaust fan), an opening degree of the first throttling device, a frequency control parameter of the compressor (for example, a target frequency value or a frequency adjustment direction, etc.), an on or off state of the compressor, and/or an on or off state of the electromagnetic valve, etc. In this embodiment, the target control parameter may include one or more than one of the parameters mentioned herein, and it is only required to ensure that the heat exchange amount supplied by the second heat exchanger and the third heat exchanger is accurately matched with the actual temperature and humidity adjustment requirement of the current fresh air when the operation of the heat exchange module is controlled according to the target control parameter.
Different humidity characteristic parameters and different characteristic temperatures correspond to different target control parameters, and if the target control parameters are different, the heat exchange amounts of the second heat exchanger and the third heat exchanger can be different. Specifically, a corresponding relation between the characteristic temperature and humidity characteristic parameters and the target control parameters can be established in advance, and the control parameters corresponding to the current characteristic temperature and humidity characteristic parameters are determined as the target control parameters according to the corresponding relation. For example, the target temperature corresponding to the characteristic temperature and the target humidity parameter corresponding to the humidity characteristic parameter may be determined according to the indoor comfort requirement, the characteristic temperature may be divided into at least two temperature intervals in advance based on the target temperature, the humidity characteristic parameter may be divided into at least two humidity parameter intervals based on the target humidity parameter, different temperature intervals and different humidity parameter intervals may be set with control parameters of different heat exchange modules correspondingly, based on this, the temperature interval in which the characteristic temperature is located and the humidity parameter interval in which the humidity characteristic parameter is located are determined, and the determined control parameters corresponding to the temperature interval and the humidity parameter interval may be obtained as the target control parameters. In the process of controlling the operation of the heat exchange module according to the obtained target control parameters, the heat dissipation capacity of the second heat exchanger and the third heat exchanger can be changed according to the corresponding adjustment direction of the heat dissipation capacity; for another example, when the target control parameter is an operation parameter of a component such as a compressor frequency or an opening degree of the first throttling device, a quantity relation between the characteristic temperature and humidity characteristic parameter and the operation parameter of a temperature and humidity adjusting component (such as a compressor, the first throttling device and the like) in the heat exchange module can be pre-established, and when the number of the related components is more than one, each component corresponds to one quantity relation, and the operation parameter of the corresponding temperature and humidity adjusting component can be obtained through calculation based on the characteristic temperature and humidity characteristic parameter through the quantity relation.
And step S30, controlling the heat exchange module to operate according to the target control parameters so that the fresh air outlet temperature and the fresh air outlet humidity of the fresh air fan reach target comfortable states.
It should be noted that, in this embodiment, in the fresh air mode, the outdoor fresh air enters the fresh air duct, is dehumidified by the dehumidification module after heat exchange by the third heat exchanger, is dehumidified by the dehumidification module, is subjected to heat exchange by the second heat exchanger, and the fresh air blown out by the second heat exchanger can be directly or further heated and then is sent into the indoor environment. When the heat exchange module is provided with a compressor and an electromagnetic valve connected in series with the compressor, and the target control parameters comprise the operation parameters of the compressor and/or the electromagnetic valve, the compressor and/or the electromagnetic valve operates according to the corresponding parameters in the target control parameters; when the target control parameter does not include the operation parameter of the compressor, the compressor can be started or shut down; when the target control parameter does not include an operating parameter of the solenoid valve, the solenoid valve may be opened or closed.
According to the control method of the fresh air machine, the first heat exchanger is arranged in the air exhaust duct, the third heat exchanger, the dehumidifying module and the second heat exchanger are arranged on the fresh air flow path at one time, the first heat exchanger, the second heat exchanger, the first throttling device and the third heat exchanger are sequentially connected in series to form a first loop, wherein the first heat exchanger can recover sensible heat exhausted in the air exhaust duct, a refrigerant after the sensible heat recovery in the first loop further enters the second heat exchanger to heat dehumidified fresh air so as to realize dehumidification and reheating of the fresh air, and based on the fresh air machine, the method controls the operation of the heat exchange module based on the target control parameters determined by the humidity characteristic parameters and the characteristic temperature representing the temperature and humidity requirements of the fresh air, so that the heat exchange module is not only suitable for temperature requirement adjustment, but also suitable for humidity requirement adjustment, and therefore the flexibility of temperature and humidity adjustment in the reheating and dehumidification process of the fresh air is improved, and the temperature and humidity of the fresh air is accurately matched with indoor comfort requirements.
Further, based on the above embodiment, another embodiment of the control method of the fresh air machine is provided. In this embodiment, referring to fig. 7, the step S20 includes:
step S21, when the humidity characteristic parameter is larger than a preset humidity parameter, if the characteristic temperature is larger than a target comfort temperature, determining a first control parameter as the target control parameter; the first control parameter is used for reducing the heating capacity of the heat exchange module to fresh air and increasing the dehumidifying capacity of the heat exchange module to fresh air.
The preset humidity parameter is specifically a maximum value of humidity parameters allowed by a preset indoor comfort state.
The humidity characteristic parameter is greater than when predetermineeing humidity parameter and indicates that new trend dehumidification demand is great, if the characteristic temperature is greater than the comfortable temperature of target this moment, and new trend has the cooling demand, through first control parameter control heat transfer module operation this moment to realize that heat transfer module increases new trend dehumidification volume and reduces the reheat volume to the new trend after the dehumidification simultaneously, make the humiture of new trend air-out can satisfy indoor comfortable demand.
The heating amount of the heat exchange module to fresh air can be understood as follows: the sum of the refrigerating capacity (Q1) of the fresh air passing through the third heat exchanger and the heating capacity (Q2) of the fresh air passing through the second heat exchanger, for example, heating capacity=q2-Q1; the heating capacity of the heat exchange module to fresh air can be further understood as follows: heating capacity (Q2) of fresh air per unit volume passing through the second heat exchanger, heating capacity=q2.
Specifically, the first control parameters include a first sub-control parameter for increasing the amount of dehumidification of the third heat exchanger and a second sub-control parameter for decreasing the amount of reheat of the second heat exchanger.
In this embodiment, the heat exchange module further includes a solenoid valve, a compressor, and a first check valve disposed between the refrigerant outlet of the third heat exchanger and the refrigerant inlet of the first heat exchanger, the compressor is connected in parallel with the first check valve, the solenoid valve is connected in series with the compressor, the heat exchange module further includes an exhaust fan disposed in the exhaust air duct, and the first control parameter includes at least one of the following parameters:
parameter 1, opening the compressor, opening the electromagnetic valve, increasing the rotating speed of the exhaust fan, and reducing the opening of the first throttling device;
and 2, opening the compressor, opening the electromagnetic valve, increasing the rotating speed of the exhaust fan, and increasing and reducing the frequency of the compressor.
Specifically, the first control parameter may include parameter 1 or parameter 2. The first control parameters may also include parameter 1 and parameter 2.
The exhaust fan is in an opening state in the running process of the fresh air fan, and based on the opening state, the rotating speed of the exhaust fan can be increased according to the parameter 1 or the parameter 2. Specifically, when the first throttle device is currently in an on state, determining the first control parameter includes parameter 1, for example, when the fresh air machine is currently in a heat pump cycle state (compressor on, solenoid valve on, first throttle device on) or a heat pipe cycle state (compressor off, solenoid valve off, first throttle device on) may determine that the first control parameter includes parameter 1. Determining the first control parameter includes parameter 2 when the compressor is currently on, e.g., determining the first control parameter includes parameter 2 when the fresh air mover is currently in a heat pump cycle state.
The running speed of the exhaust fan can be increased according to a preset fixed adjustment parameter, and the running speed of the exhaust fan can be increased according to an adjustment parameter determined by the actual running condition of the fresh air fan. In this embodiment, the rotational speed increasing range may be determined according to the exhaust temperature, the fresh air temperature, the first coil temperature of the first heat exchanger, the second coil temperature of the second heat exchanger, and the second set temperature, and the exhaust fan may be controlled to increase the operation rotational speed according to the determined rotational speed increasing range. The heat dissipation capacity of the first heat exchanger can be improved by improving the running rotating speed of the exhaust fan, and the reheat capacity of the second heat exchanger is effectively reduced, so that the reduction of the fresh air outlet temperature is realized.
The opening adjustment parameters (such as opening adjustment amplitude, opening adjustment rate, etc.) in the opening increasing process of the first throttling device and/or the frequency adjustment parameters (such as frequency adjustment amplitude, frequency adjustment rate, etc.) in the frequency reducing process of the compressor can be fixed adjustment parameters set in advance, and can also be adjustment parameters determined according to the current characteristic temperature and humidity characteristic parameters. In particular, the opening adjustment parameter and/or the frequency adjustment parameter may be determined here in combination with the characteristic temperature, the humidity characteristic parameter, the current condensation temperature of the second heat exchanger and the current evaporation temperature of the third heat exchanger.
The compressor is opened, the electromagnetic valve is opened, the first throttling device is opened, the fresh air machine is in a heat pump circulation state, high-temperature and high-pressure refrigerant is discharged from an exhaust port of the compressor in the heat pump circulation state and sequentially flows through the first heat exchanger and the second heat exchanger to exchange heat, sensible heat in outdoor air discharged indoors can be recovered by the first heat exchanger to achieve energy conservation, the refrigerant releases heat in the second heat exchanger to heat fresh air in a fresh air duct, the refrigerant flowing out of the second heat exchanger is throttled by the first throttling device to form a low-temperature refrigerant, the low-temperature refrigerant enters the third heat exchanger to evaporate to dehumidify the fresh air, and the evaporated low-temperature refrigerant flows back to an air return port of the compressor through the electromagnetic valve to be recompressed.
In this embodiment, through improving the running rotational speed of fan of airing exhaust, increase the heat of condensation that the airing exhaust was taken away, reduce the reheat of second heat exchanger to the new trend, can improve the evaporating temperature of third heat exchanger through improving the compressor rotational speed or reducing first throttling arrangement aperture to increase the dehumidification volume, based on this, realize that new fan can be with the humiture regulation of new trend air-out to satisfying indoor comfortable demand under the current operating mode.
In other embodiments, when the heat exchange module does not include the compressor and the electromagnetic valve, the rotation speed of the exhaust fan may be increased while the opening degree of the first throttling device is reduced as the first control parameter.
Further, referring to fig. 7, step S20 further includes:
and S22, when the humidity characteristic parameter is larger than a preset humidity parameter, if the characteristic temperature is smaller than the target comfort temperature, determining a second control parameter as the target control parameter, wherein the second control parameter is used for increasing the heating capacity of the heat exchange module to fresh air and increasing the dehumidifying capacity of the heat exchange module to the fresh air.
The humidity characteristic parameter is greater than when predetermineeing humidity parameter and indicates that new trend dehumidification demand is great, if the characteristic temperature is less than the comfortable temperature of target this moment, and new trend has the intensification demand, through second control parameter control heat transfer module operation this moment to realize that heat transfer module improves new trend dehumidification volume and improves the reheat volume to the new trend after dehumidification simultaneously, make the humiture of new trend air-out can satisfy indoor comfortable demand.
Specifically, the second control parameters include a third sub-control parameter for increasing the dehumidification amount of the third heat exchanger and a fourth sub-control parameter for increasing the reheat amount of the second heat exchanger.
In this embodiment, the heat exchange module further includes a solenoid valve, a compressor, and a first check valve disposed between the refrigerant outlet of the third heat exchanger and the refrigerant inlet of the first heat exchanger, the compressor is connected in parallel with the first check valve, the solenoid valve is connected in series with the compressor, the heat exchange module further includes an exhaust fan disposed in the exhaust air duct, and the second control parameter includes at least one of the following parameters:
parameter 3, opening the compressor, opening the electromagnetic valve, reducing the rotating speed of the exhaust fan and reducing the opening of the first throttling device;
and 4, opening the compressor, opening the electromagnetic valve, reducing the rotating speed of the exhaust fan, and increasing the frequency of the compressor.
In particular, the second control parameter may comprise parameter 3 or parameter 4. The second control parameters may also include parameter 3 and parameter 4.
The exhaust fan is in an open state in the operation process of the fresh air fan, and based on the open state, the rotating speed of the exhaust fan can be reduced according to the parameter 3 or the parameter 4. Specifically, when the first throttle device is currently in an on state, determining the first control parameter includes parameter 3, for example, when the fresh air machine is currently in a heat pump cycle state (compressor on, solenoid valve on, first throttle device on) or a heat pipe cycle state (compressor off, solenoid valve off, first throttle device on) may determine the first control parameter includes parameter 3. Determining the first control parameter includes parameter 4 when the compressor is currently on, e.g., determining the first control parameter includes parameter 4 when the fresh air mover is currently in a heat pump cycle state.
The running speed of the exhaust fan can be reduced according to a preset fixed adjustment parameter, and the running speed of the exhaust fan can be reduced according to an adjustment parameter determined by the actual running condition of the fresh air fan. In this embodiment, the rotation speed reduction range can be determined according to the exhaust temperature, the fresh air temperature, the first coil temperature of the first heat exchanger, the second coil temperature of the second heat exchanger and the second set temperature, and the exhaust fan is controlled to reduce the operation rotation speed according to the determined rotation speed reduction range. The reduction of the running rotating speed of the exhaust fan can reduce the heat dissipation capacity of the first heat exchanger, effectively improve the reheat capacity of the second heat exchanger, and further improve the fresh air outlet temperature.
The opening adjustment parameters (such as opening adjustment amplitude, opening adjustment rate, etc.) in the opening reduction process of the first throttling device and/or the frequency adjustment parameters (such as frequency adjustment amplitude, frequency adjustment rate, etc.) in the frequency raising process of the compressor can be fixed adjustment parameters set in advance, and can also be adjustment parameters determined according to the current characteristic temperature and humidity characteristic parameters. In particular, the opening adjustment parameter and/or the frequency adjustment parameter may be determined here in combination with the characteristic temperature, the humidity characteristic parameter, the current condensation temperature of the second heat exchanger and the current evaporation temperature of the third heat exchanger.
The compressor is opened, the electromagnetic valve is opened, the first throttling device is opened, the fresh air machine is in a heat pump circulation state, high-temperature and high-pressure refrigerant is discharged from an exhaust port of the compressor in the heat pump circulation state and sequentially flows through the first heat exchanger and the second heat exchanger to exchange heat, sensible heat in outdoor air discharged indoors can be recovered by the first heat exchanger to achieve energy conservation, the refrigerant releases heat in the second heat exchanger to heat fresh air in a fresh air duct, the refrigerant flowing out of the second heat exchanger is throttled by the first throttling device to form a low-temperature refrigerant, the low-temperature refrigerant enters the third heat exchanger to evaporate to dehumidify the fresh air, and the evaporated low-temperature refrigerant flows back to an air return port of the compressor through the electromagnetic valve to be recompressed.
In this embodiment, by reducing the operation speed of the exhaust fan, reducing the condensation heat taken away by exhaust, improving the reheat of the fresh air by the second heat exchanger, and by increasing the speed of the compressor or reducing the opening of the first throttling device, the evaporation temperature of the third heat exchanger can be reduced, thereby increasing the dehumidification amount.
In other embodiments, when the heat exchange module does not include the compressor and the electromagnetic valve, the rotation speed of the exhaust fan may be reduced and the opening degree of the first throttling device may be reduced as the second control parameter.
Further, based on any one of the above embodiments, another embodiment of the control method of the fresh air machine is provided. In this embodiment, referring to fig. 8, the step S20 includes:
step S23, when the humidity characteristic parameter is smaller than or equal to a preset humidity parameter, if the characteristic temperature is larger than a target comfort temperature, determining a third control parameter as the target control parameter; the third control parameter is used for reducing the heating capacity of the heat exchange module to fresh air;
the preset humidity parameter in the present embodiment is the same concept as that in the above embodiment, and will not be described herein.
When the humidity characteristic parameter is smaller than or equal to the preset humidity parameter, the fresh air dehumidification requirement is smaller or the fresh air dehumidification requirement does not exist, and at the moment, if the characteristic temperature is larger than the target comfortable temperature, the fresh air has the cooling requirement, and the heat exchange module is controlled to operate through the third control parameter, so that the reheating quantity of the dehumidified fresh air is reduced by the heat exchange module, and the indoor comfortable requirement can be met by the temperature and humidity of the fresh air outlet.
The target comfort temperature is specifically a target temperature value required to be reached by the characteristic temperature required by the indoor comfort state in the fresh air mode.
The third control parameter is specifically a sub-control parameter for reducing the reheating amount of the dehumidified fresh air by the second heat exchanger.
In this embodiment, the heat exchange module further includes an electromagnetic valve, a compressor, and a first check valve disposed between the refrigerant outlet of the third heat exchanger and the refrigerant inlet of the first heat exchanger, the compressor is connected in parallel with the first check valve, the electromagnetic valve is connected in series with the compressor, the heat exchange module further includes an exhaust fan disposed in the exhaust air duct, and the third control parameter includes at least one of the following parameters:
a parameter 5, increasing the running rotating speed of the exhaust fan;
parameter 6, controlling the compressor to switch from an open state to a closed state, controlling the electromagnetic valve to switch from the open state to the closed state, and controlling the first throttling device to maintain the open state;
and a parameter 7, controlling the compressor to maintain a closed state, controlling the electromagnetic valve to switch from the closed state to the open state or controlling the first throttling device to switch from the open state to the closed state.
Specifically, the third control parameter may be parameter 5, parameter 6 or parameter 7; the third control parameter may also be parameter 5 and parameter 7; the third control parameters may also be parameter 5 and parameter 6.
The operation rotation speed of the exhaust fan in the parameter 5 can be increased according to a preset fixed adjustment parameter, and the operation rotation speed of the exhaust fan can also be increased according to an adjustment parameter determined according to the actual operation condition of the fresh air fan. In this embodiment, the rotational speed increasing range may be determined according to the exhaust temperature, the fresh air temperature, the first coil temperature of the first heat exchanger, the second coil temperature of the second heat exchanger, and the second set temperature, and the exhaust fan may be controlled to increase the operation rotational speed according to the determined rotational speed increasing range. The heat dissipation capacity of the first heat exchanger can be improved by improving the running rotating speed of the exhaust fan, and the reheat capacity of the second heat exchanger is effectively reduced, so that the reduction of the fresh air outlet temperature is realized.
Specifically, when the compressor is currently in an open state, the electromagnetic valve is currently in an open state, and the first throttling device is currently in an open state, the fresh air fan is in a heat pump cycle state: the high-temperature and high-pressure refrigerant is discharged from the exhaust port of the compressor and sequentially flows through the first heat exchanger and the second heat exchanger to exchange heat, wherein the first heat exchanger can recover sensible heat in indoor outdoor air discharged to realize energy conservation, the refrigerant releases heat in the second heat exchanger to heat fresh air in the fresh air duct, and the refrigerant flowing out of the second heat exchanger sequentially flows through the first throttling device and the third heat exchanger and then flows back to the return port of the compressor through the electromagnetic valve. When the compressor is in a closed state, the electromagnetic valve is in a closed state, and the first throttling device is in an open state, the fresh air fan is in a heat pipe circulation state: the refrigerant in the first loop is not compressed in the compressor any more due to the closing of the compressor and the electromagnetic valve, a certain pressure difference is formed at two sides of the first one-way valve due to the closing of the electromagnetic valve, the refrigerant flows from one side of the first one-way valve to the other side of the first one-way valve under the driving of the certain pressure difference, the refrigerant circularly flows in the first loop, and the refrigerant heats fresh air in the fresh air duct when flowing into the second heat exchanger. The heat dissipation capacity of the second heat exchanger under the heat pump cycle is greater than the heat dissipation capacity of the second heat exchanger under the heat pipe cycle.
The parameter 6 is in particular a control parameter for converting the fresh air machine from a heat pump cycle to a heat pipe cycle. Specifically, when the compressor is currently in the on state, the solenoid valve is currently in the on state, and the first throttling device is currently in the on state, the parameter 6 may be determined to be the third control parameter.
The parameter 7 is specifically a control parameter for converting the fresh air machine from the heat pipe circulation to the second heat exchanger to stop heat radiation. Specifically, when the compressor is currently in the closed state, the solenoid valve is currently in the closed state, and the first throttling device is currently in the open state, the parameter 7 may be determined to be the third control parameter. When the compressor is kept closed, the electromagnetic valve is switched from closed to open, so that the pressure difference between two ends of the first one-way valve is 0, the refrigerant cannot flow through the first one-way valve under the action of no pressure difference, and the refrigerant in the first loop cannot flow circularly; when the compressor is closed, the first throttling device is closed, the flow of the refrigerant in the first loop is blocked, and the refrigerant in the first loop cannot circulate. Under the two conditions, the second heat exchanger stops radiating the fresh air in the fresh air duct.
In other embodiments, the third control parameter may also include the first throttle increasing the opening, and so on, when the compressor is currently in the heat pump cycle.
Further, the step S20 further includes:
and S24, when the humidity characteristic parameter is smaller than or equal to a preset humidity parameter, determining a fourth control parameter as the target control parameter if the characteristic temperature is smaller than the target comfort temperature, wherein the fourth control parameter is used for increasing the heating amount of the heat exchange module to fresh air.
When the humidity characteristic parameter is smaller than or equal to the preset humidity parameter, the fresh air dehumidification requirement is smaller or the fresh air dehumidification requirement does not exist, and at the moment, if the characteristic temperature is smaller than the target comfortable temperature, the fresh air has the heating requirement, and the heat exchange module is controlled to operate through the fourth control parameter, so that the reheating quantity of the dehumidified fresh air is improved by the heat exchange module, and the indoor comfortable requirement can be met by the temperature and the humidity of the fresh air outlet.
The fourth control parameter is specifically a sub-control parameter for increasing the reheating amount of the dehumidified fresh air by the second heat exchanger.
In this embodiment, the heat exchange module further includes an electromagnetic valve, a compressor, and a first check valve disposed between the refrigerant outlet of the third heat exchanger and the refrigerant inlet of the first heat exchanger, the compressor is connected in parallel with the first check valve, the electromagnetic valve is connected in series with the compressor, the heat exchange module further includes an exhaust fan disposed in the exhaust air duct, and the fourth control parameter includes at least one of the following parameters:
The parameter 8 is used for reducing the running rotating speed of the exhaust fan;
parameter 9, controlling the compressor to switch from a closed state to an open state, controlling the electromagnetic valve to switch from the closed state to the open state, and controlling the first throttling device to maintain the open state;
parameter 10, controlling the compressor to maintain a closed state, controlling the electromagnetic valve to switch from an open state to a closed state, and controlling the first throttling device to maintain an open state;
parameter 11, controlling the compressor to maintain a closed state, controlling the solenoid valve to maintain a closed state, and controlling the first throttle device to switch from a closed state to an open state.
Specifically, the fourth control parameter may be parameter 8, parameter 9, parameter 10 or parameter 11; the fourth control parameter may also be parameter 8 and parameter 9; the fourth control parameter may also be parameter 8 and parameter 10; the fourth control parameter may also be parameter 8 and parameter 11.
The operation rotation speed of the exhaust fan in the parameter 8 can be reduced according to a preset fixed adjustment parameter, and the operation rotation speed of the exhaust fan can be reduced according to an adjustment parameter determined according to the actual operation condition of the fresh air fan. In this embodiment, the rotation speed reduction range can be determined according to the exhaust temperature, the fresh air temperature, the first coil temperature of the first heat exchanger, the second coil temperature of the second heat exchanger and the second set temperature, and the exhaust fan is controlled to reduce the operation rotation speed according to the determined rotation speed reduction range. The heat dissipation capacity of the first heat exchanger can be reduced due to the reduction of the running rotating speed of the exhaust fan, and the reheat capacity of the second heat exchanger is effectively improved, so that the fresh air outlet temperature is improved.
The parameter 9 is in particular a control parameter for switching the fresh air machine from a heat pipe cycle to a heat pump cycle. Specifically, when the compressor is currently in the closed state, the solenoid valve is currently in the closed state, and the first throttle device is currently in the open state, it may be determined that the parameter 9 is the fourth control parameter.
Parameters 10 and 11 are specifically control parameters for converting the stopping of the heat dissipation of the second heat exchanger into a heat pipe cycle. Specifically, when the compressor is currently in the closed state, the solenoid valve is currently in the open state, and the first throttling device is open, the parameter 10 may be determined to be a fourth control parameter; alternatively, parameter 11 may be determined to be the fourth control parameter when the compressor is currently in the off state, the first throttle is closed, and the solenoid valve is closed. When the compressor is closed, the electromagnetic valve is switched from open to closed, so that the pressure difference between two ends of the first one-way valve is 0 and is switched to a certain pressure difference, and the refrigerant is driven to flow through the first one-way valve under the action of the certain pressure difference to drive the refrigerant in the first loop to circularly flow; when the compressor is turned off, the first throttle device is switched from off to on, and the solenoid valve maintains a closed state, allowing the refrigerant to circulate in the first circuit. In both cases, the refrigerant in the first circuit can be switched from the stopped flow state to the heat pipe circulation state, and the heat dissipation capacity of the second heat exchanger can be increased.
In other embodiments, the fourth control parameter may also be determined to be opening the compressor, closing the solenoid valve, and opening the first restriction when the compressor is off.
It should be noted that, in the practical application process, the step S20 may include at least one of the steps S21 to S24.
In addition, the embodiment of the invention also provides a computer readable storage medium, wherein the computer readable storage medium is stored with a control program of the fresh air machine, and the control program of the fresh air machine realizes the relevant steps of any embodiment of the control method of the fresh air machine when being executed by a processor.
It should be noted that, in this document, the terms "comprises," "comprising," or any other variation thereof, are intended to cover a non-exclusive inclusion, such that a process, method, article, or system that comprises a list of elements does not include only those elements but may include other elements not expressly listed or inherent to such process, method, article, or system. Without further limitation, an element defined by the phrase "comprising one … …" does not exclude the presence of other like elements in a process, method, article, or system that comprises the element.
The foregoing embodiment numbers of the present invention are merely for the purpose of description, and do not represent the advantages or disadvantages of the embodiments.
From the above description of the embodiments, it will be clear to those skilled in the art that the above-described embodiment method may be implemented by means of software plus a necessary general hardware platform, but of course may also be implemented by means of hardware, but in many cases the former is a preferred embodiment. Based on this understanding, the technical solution of the present invention may be embodied essentially or in a part contributing to the prior art in the form of a software product stored in a storage medium (such as ROM/RAM, magnetic disk, optical disk) as described above, comprising instructions for causing a terminal device (which may be a mobile phone, a computer, a server, a fresh air machine, or a network device, etc.) to perform the method according to the embodiments of the present invention.
The foregoing description is only of the preferred embodiments of the present invention, and is not intended to limit the scope of the invention, but rather is intended to cover any equivalents of the structures or equivalent processes disclosed herein or in the alternative, which may be employed directly or indirectly in other related arts.

Claims (7)

1. The utility model provides a control method of new fan, its characterized in that, new fan includes new wind channel, the wind channel of airing exhaust, heat transfer module and dehumidification module, heat transfer module includes first return circuit, first return circuit includes first heat exchanger, second heat exchanger, first throttling arrangement and third heat exchanger that connect gradually, the wind channel of airing exhaust is located to first heat exchanger, third heat exchanger dehumidification module and second heat exchanger are in the new wind channel is arranged in proper order along the new wind flow path, dehumidification module is independent of first return circuit setting, first heat exchanger is used for cooling down the refrigerant that will flow through first heat exchanger based on the wind of airing exhaust wind channel, the third heat exchanger is used for cooling down dehumidification operation to the new wind, new fan's control method includes the following steps:
acquiring humidity characteristic parameters and characteristic temperatures; the humidity characteristic parameter represents the dehumidification requirement of the fresh air, and the characteristic temperature represents the heating requirement of the fresh air;
determining a target control parameter of the heat exchange module according to the humidity characteristic parameter and the characteristic temperature, wherein the target control parameter is used for controlling at least one of the heat dissipation capacity of the first heat exchanger on the refrigerant flowing through the first heat exchanger, the heating capacity of the second heat exchanger on the fresh air and the dehumidifying capacity of the third heat exchanger on the fresh air, so that the heat exchange module adjusts the characteristic temperature of the fresh air and the humidity characteristic parameter of the fresh air;
Controlling the heat exchange module to operate according to the target control parameters so that the fresh air outlet temperature and the fresh air outlet humidity of the fresh air fan reach target comfort states;
the step of determining the target control parameter of the heat exchange module according to the humidity characteristic parameter and the characteristic temperature comprises the following steps:
when the humidity characteristic parameter is larger than a preset humidity parameter, if the characteristic temperature is larger than a target comfort temperature, determining a first control parameter as the target control parameter; the first control parameter is used for reducing the heating capacity of the heat exchange module to fresh air and increasing the dehumidifying capacity of the heat exchange module to the fresh air;
if the characteristic temperature is smaller than the target comfort temperature, determining a second control parameter as the target control parameter, wherein the second control parameter is used for increasing the heating capacity of the heat exchange module on fresh air and increasing the dehumidifying capacity of the heat exchange module on the fresh air;
the heat exchange module further comprises an electromagnetic valve, a compressor and a first one-way valve arranged between the refrigerant outlet of the third heat exchanger and the refrigerant inlet of the first heat exchanger, the compressor is connected with the first one-way valve in parallel, the electromagnetic valve is connected with the compressor in series, the heat exchange module further comprises an exhaust fan arranged in the exhaust air duct, and the first control parameter comprises at least one of the following parameters:
Opening the compressor, opening the electromagnetic valve, increasing the rotating speed of the exhaust fan, and reducing the opening of the first throttling device;
opening the compressor, opening the electromagnetic valve, increasing the rotating speed of the exhaust fan, and increasing the frequency of the compressor;
the second control parameter includes at least one of the following:
opening the compressor, opening the electromagnetic valve, reducing the rotating speed of the exhaust fan and reducing the opening of the first throttling device;
and opening the compressor, opening the electromagnetic valve, reducing the rotating speed of the exhaust fan, and increasing the frequency of the compressor.
2. The method of controlling a fresh air machine according to claim 1, wherein the step of determining a target control parameter based on the humidity characteristic parameter and the characteristic temperature comprises:
when the humidity characteristic parameter is smaller than or equal to a preset humidity parameter, if the characteristic temperature is larger than a target comfort temperature, determining a third control parameter as the target control parameter; the third control parameter is used for reducing the heating capacity of the heat exchange module to fresh air;
and if the characteristic temperature is smaller than the target comfort temperature, determining a fourth control parameter as the target control parameter, wherein the fourth control parameter is used for increasing the heating amount of the heat exchange module to the fresh air.
3. The method of claim 2, wherein the heat exchange module further comprises a solenoid valve, a compressor, and a first check valve disposed between a refrigerant outlet of the third heat exchanger and a refrigerant inlet of the first heat exchanger, the compressor is connected in parallel with the first check valve, the solenoid valve is connected in series with the compressor, the heat exchange module further comprises an exhaust fan disposed in the exhaust duct, and the third control parameter comprises at least one of:
the running rotating speed of the exhaust fan is increased;
controlling the compressor to switch from an open state to a closed state, controlling the electromagnetic valve to switch from an open state to a closed state, and controlling the first throttling device to maintain the open state;
and controlling the compressor to maintain a closed state, controlling the electromagnetic valve to switch from the closed state to the open state or controlling the first throttling device to switch from the open state to the closed state.
4. The method of claim 2, wherein the heat exchange module further comprises a solenoid valve, a compressor, and a first check valve disposed between a refrigerant outlet of the third heat exchanger and a refrigerant inlet of the first heat exchanger, the compressor is connected in parallel with the first check valve, the solenoid valve is connected in series with the compressor, the heat exchange module further comprises an exhaust fan disposed in the exhaust duct, and the fourth control parameter comprises at least one of:
Reducing the running rotating speed of the exhaust fan;
controlling the compressor to switch from a closed state to an open state, controlling the electromagnetic valve to switch from the closed state to the open state, and controlling the first throttling device to maintain the open state;
controlling the compressor to maintain a closed state, controlling the electromagnetic valve to switch from an open state to a closed state, and controlling the first throttling device to maintain an open state;
the compressor is controlled to maintain a closed state, the solenoid valve is controlled to maintain a closed state, and the first throttle device is controlled to switch from a closed state to an open state.
5. The method of controlling a fresh air machine according to any one of claims 1 to 4, wherein the step of acquiring the humidity characteristic parameter includes:
acquiring the exhaust temperature and the exhaust humidity of the fresh air fan;
calculating the exhaust moisture content according to the exhaust temperature and the exhaust humidity, wherein the humidity characteristic parameter comprises the exhaust moisture content;
or, acquiring the fresh air outlet temperature and the fresh air outlet humidity of the fresh air fan;
calculating the wind moisture content according to the fresh air outlet temperature and the fresh air outlet rheumatism, wherein the humidity characteristic parameters comprise the wind moisture content;
Or, obtaining the fresh air temperature of the air outlet side of the dehumidification module;
and calculating the fresh air moisture content according to the fresh air temperature, wherein the humidity characteristic parameter comprises the fresh air moisture content.
6. A new fan, characterized in that it comprises:
fresh air duct;
an exhaust air duct;
the heat exchange module comprises a first loop, wherein the first loop comprises a first heat exchanger, a second heat exchanger, a first throttling device and a third heat exchanger which are sequentially connected, and the first heat exchanger is arranged in an exhaust air duct;
the dehumidification module is independent of the first loop, and the third heat exchanger, the dehumidification module and the second heat exchanger are sequentially arranged in the fresh air duct along a fresh air flow path;
the heat exchange module and the dehumidification module are both connected with the control device, and the control device comprises: memory, a processor and a control program of a fresh air machine stored on the memory and operable on the processor, which when executed by the processor, implements the steps of the method of controlling a fresh air machine according to any one of claims 1 to 5.
7. A computer-readable storage medium, characterized in that the computer-readable storage medium has stored thereon a control program of a fresh air machine, which when executed by a processor, implements the steps of the control method of a fresh air machine according to any one of claims 1 to 5.
CN202111407967.8A 2021-11-24 2021-11-24 New fan, control method thereof and computer readable storage medium Active CN114110884B (en)

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