CN114087743B

CN114087743B - Heat pipe fresh air machine, control method thereof and computer readable storage medium

Info

Publication number: CN114087743B
Application number: CN202111406496.9A
Authority: CN
Inventors: 杜顺开; 黄剑云; 高卓贤; 刘步东; 徐振坤; 李金波
Original assignee: GD Midea Air Conditioning Equipment Co Ltd; Midea Group Wuhan Refrigeration Equipment Co Ltd
Current assignee: GD Midea Air Conditioning Equipment Co Ltd; Midea Group Wuhan Refrigeration Equipment Co Ltd
Priority date: 2021-11-24
Filing date: 2021-11-24
Publication date: 2024-01-23
Anticipated expiration: 2041-11-24
Also published as: CN114087743A

Abstract

The invention discloses a control method of a heat pipe fresh air machine, wherein the heat pipe fresh air machine comprises a fresh air duct, an exhaust air duct, a heat exchange module and a dehumidification module, the heat exchange module comprises a first loop, 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, the first heat exchanger is arranged 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, and the dehumidification module is independent of the first loop, and the method comprises the following steps: acquiring a characteristic temperature, wherein the characteristic temperature characterizes the temperature regulation requirement of fresh air; determining target control parameters of the heat exchange module according to the characteristic temperature; and controlling the heat exchange module to operate according to the target control parameters so as to enable the heat exchange quantity of the second heat exchanger to be matched with the temperature regulation requirement. The invention also discloses a heat pipe fresh air machine and a readable storage medium. The invention improves the accuracy of fresh air outlet temperature regulation, reduces the fluctuation of fresh air outlet temperature and improves the comfort of indoor users.

Description

Heat pipe fresh air machine, 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 heat pipe fresh air machine, the heat pipe 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 heat pipe fresh air machine is characterized in that heat pipe heat exchangers are arranged in front of and behind a cold source, fresh air is subjected to heat absorption and temperature reduction through a heat pipe evaporator, then is subjected to further dehumidification and temperature reduction through the cold source, and is heated and heated through a heat pipe condenser to be sent into a room. The heat pipe evaporator absorbs heat from the high-temperature fresh air to change the liquid refrigerant into the gaseous refrigerant, the gaseous refrigerant enters the heat pipe condenser under the pressure difference, the dehumidified and cooled low-temperature fresh air is condensed into the liquid refrigerant, and the liquid refrigerant flows into the heat pipe evaporator to complete the heat pipe circulation under the siphon effect generated by the flowing of the throttling component.

However, in the process of dehumidifying and reheating fresh air by the existing heat pipe fresh air machine, the fresh air is generally heated according to preset fixed parameters, so that the heating capacity of the heat pipe fresh air machine is easily excessively large or small, the fluctuation of the air outlet temperature of the heat pipe fresh air machine is large, and the indoor user comfort is influenced.

Disclosure of Invention

The invention mainly aims to provide a control method of a heat pipe fresh air machine, the heat pipe fresh air machine and a computer readable storage medium, and aims to improve the accuracy of fresh air outlet temperature adjustment, reduce the outlet temperature fluctuation of the heat pipe fresh air machine and improve the indoor user comfort.

In order to achieve the above object, the present invention provides a control method of a heat pipe fresh air machine, the heat pipe fresh air machine 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, the control method of the heat pipe fresh air machine includes the following steps:

acquiring a characteristic temperature, wherein the characteristic temperature characterizes the temperature regulation requirement of fresh air;

determining target control parameters of the heat exchange module according to the characteristic temperature;

and controlling the heat exchange module to operate according to the target control parameter so as to enable the heat exchange quantity of the second heat exchanger to be matched with the temperature regulation requirement.

Optionally, the step of determining the target control parameter of the heat exchange module according to the characteristic temperature includes:

when the characteristic temperature is greater than or equal to a first set temperature, determining a first control parameter as the target control parameter; the first control parameter is used for stopping heat exchange of the second heat exchanger;

when the characteristic temperature is larger than a second set temperature and smaller than the first set temperature, determining a second control parameter as the target control parameter; the second control parameter is used for reducing the heat exchange amount of the second heat exchanger, and the second set temperature is smaller than the first set temperature;

and when the characteristic temperature is smaller than the second set temperature, determining a third control parameter as the target control parameter, wherein the third control parameter is used for increasing the heat exchange amount of the second heat exchanger.

Optionally, the heat exchange module further includes the 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, and the first control parameter includes one of the following parameters:

Closing the compressor and closing the first throttling means;

the compressor is closed and the solenoid valve is opened.

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:

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 third 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 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, and the control method of the heat pipe fresh air machine further includes:

when the dehumidification reheating mode is started, controlling the dehumidification module to be started, controlling the compressor to be closed, controlling the electromagnetic valve to be closed, and controlling the first throttling device to be opened; and

executing the step of acquiring the characteristic temperature when the dehumidification module is in an on state, the compressor is in an off state, the electromagnetic valve is in an off state, and the first throttling device is in an on state; or alternatively

When the dehumidification reheating mode is started, controlling the dehumidification module to be started, controlling the compressor to be started, controlling the electromagnetic valve to be started, and controlling the first throttling device to be started; and

and executing the step of acquiring the characteristic temperature when the dehumidification module is in an open state, the compressor is in an open state, the electromagnetic valve is in an open state and the first throttling device is in an open state.

Optionally, the step of obtaining the characteristic temperature includes:

acquiring the fresh air outlet temperature of the heat pipe fresh air machine, wherein the characteristic temperature comprises the fresh air outlet temperature;

or, obtaining the ambient temperature of the heat pipe fresh air machine acting space, wherein the characteristic temperature comprises the ambient temperature;

or, obtaining the exhaust temperature of the heat pipe fresh air machine, wherein the characteristic temperature comprises the exhaust temperature;

or, obtaining a coil temperature of the second heat exchanger, wherein the characteristic temperature comprises the coil temperature.

In addition, in order to realize above-mentioned purpose, this application still provides a new fan of heat pipe, new fan of heat pipe 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 method comprises the steps of a memory, a processor and a control program of the heat pipe fresh air machine, wherein the control program is stored in the memory and can run on the processor, and the control program of the heat pipe fresh air machine is executed by the processor to realize the control method of the heat pipe fresh air machine.

Optionally, the heat pipe fresh air machine further includes:

the first one-way valve is arranged between the refrigerant outlet of the third heat exchanger and the refrigerant inlet of the first heat exchanger;

a compressor connected in parallel with the first check valve; and

a solenoid valve in series with the compressor;

and/or, the heat pipe fresh air machine further comprises an exhaust fan, and the exhaust fan is arranged in the exhaust air duct.

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 heat pipe fresh air machine is stored, which when executed by a processor, implements the steps of the control method of a heat pipe fresh air machine as set forth in any one of the above.

According to the control method of the heat pipe 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 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 heat pipe fresh air machine, the method adjusts target control parameters of the heat exchange module based on the characteristic temperature required by actual heating of the fresh air, rather than adjusting fresh air heating quantity of the heat exchange module according to preset fixed parameters, so that the refrigerant flowing into the second heat exchanger after the sensible heat recovery in the heat exchange module comprising the first loop can be accurately matched with the actual temperature adjustment requirement of the fresh air, the accuracy of fresh air temperature adjustment is improved, the fresh air outlet temperature adjustment is reduced, and the indoor comfort of a user is improved.

Drawings

FIG. 1 is a schematic diagram of a heat pipe fresh air machine according to an embodiment of the present invention;

FIG. 2 is a schematic diagram of another embodiment of a heat pipe fresh air machine according to the present invention;

FIG. 3 is a schematic view of a heat pipe fresh air machine according to another embodiment of the present invention;

FIG. 4 is a schematic view of a heat pipe fresh air machine according to another embodiment of the present invention;

FIG. 5 is a schematic diagram of a hardware architecture involved in the operation of an embodiment of the heat pipe fresh air machine of the present invention;

FIG. 6 is a flow chart of an embodiment of a method for controlling a heat pipe fresh air machine according to the present invention;

FIG. 7 is a flow chart of another embodiment of a method for controlling a heat pipe fresh air machine according to the present invention;

fig. 8 is a flowchart of a control method of a heat pipe fresh air machine according to another embodiment of the present invention.

Reference numerals illustrate:

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: based on a new fan of heat pipe, a control method is proposed, new fan of heat pipe includes new wind channel, the wind channel of airing exhaust, heat transfer module and dehumidification module, the heat transfer module includes first return circuit, first return circuit includes 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 the dehumidification module and the second heat exchanger are in the new wind channel is followed the new wind flow path and is arranged in proper order, the dehumidification module is independent of first return circuit, and this method includes: acquiring a characteristic temperature, wherein the characteristic temperature characterizes the temperature regulation requirement of fresh air; determining target control parameters of the heat exchange module according to the characteristic temperature; and controlling the heat exchange module to operate according to the target control parameter so as to enable the heat exchange quantity of the second heat exchanger to be matched with the temperature regulation requirement.

In the prior art, in the process of dehumidifying and reheating fresh air by the existing heat pipe fresh air machine, the fresh air is generally heated according to preset fixed parameters, so that the heating capacity of the heat pipe fresh air machine is easily excessively large or small, the fluctuation of the air outlet temperature of the heat pipe fresh air machine is large, and the indoor user comfort is influenced.

The invention provides the solution, which aims to improve the accuracy of fresh air outlet temperature regulation, reduce the outlet temperature fluctuation of the heat pipe fresh air machine and improve the indoor user comfort.

The embodiment of the invention provides a novel heat pipe fan.

Referring to fig. 1, in an embodiment of the present invention, a heat pipe 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 heat pipe fresh air machine starts a heat pipe heat recovery cycle, and simultaneously, 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 heat pipe fresh air machine 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 heat pipe fresh air machine to different working conditions is improved, the energy conservation of the heat pipe fresh air machine can be guaranteed when the fresh air temperature is low or high, and the temperature and the 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 heat pipe 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 heat pipe fresh air machine starts to perform heat pump heat recovery cycle, and simultaneously 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, and the heat pipe fresh air machine starts the heat pipe heat recovery cycle, and simultaneously the dehumidification module 8 is started.

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 heat pipe fresh air machine starts to perform 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 heat pipe fresh air machine 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 heat pipe fresh air machine further includes a sixth heat exchanger 10, a second compressor 17, and a second throttling device 13, where 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 heat pipe fresh air machine can dehumidify fresh air, 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 for a hybrid heat exchanger, so that the change of the humidity caused by the 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 heat pipe 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 heat pipe fresh air machine 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 heat pipe fresh air fan. The temperature detection module 03 can be used for detecting relevant humidity data required by the operation regulation of the heat pipe fresh air fan. 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 heat pipe 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 heat pipe 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 for a heat pipe 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 heat pipe fresh air machine stored in a memory 1002 and perform the relevant step operations of the control method of the heat pipe fresh air machine in the following embodiments.

The embodiment of the invention also provides a control method of the heat pipe fresh air machine, which is applied to control the heat pipe fresh air machine.

Referring to fig. 6, an embodiment of a method for controlling a heat pipe fresh air machine is provided. In this embodiment, the control method of the heat pipe fresh air machine includes:

Step S10, obtaining a characteristic temperature, wherein the characteristic temperature represents the temperature regulation requirement of fresh air;

the characteristic temperature can be the air temperature detected on the heat pipe fresh air machine or the air temperature detected by the indoor environment acted by the heat pipe fresh air machine.

In an embodiment, a fresh air outlet temperature of the heat pipe fresh air machine is obtained, and the characteristic temperature includes the fresh air outlet temperature.

In another embodiment, the ambient temperature of the heat pipe fresh air machine working space is obtained, and the characteristic temperature comprises the ambient temperature.

In yet another embodiment, an exhaust temperature of the heat pipe fresh air machine is obtained, and the characteristic temperature includes the exhaust temperature.

In yet another embodiment, a coil temperature of the second heat exchanger is obtained, the characteristic temperature comprising the coil temperature.

In yet another embodiment, at least two of the fresh air outlet temperature, the ambient temperature, the exhaust air temperature, and the coil temperature are obtained as target temperatures, and the characteristic temperature herein is calculated from the at least two target temperatures.

Any of the characteristic temperatures mentioned herein can achieve an accurate characterization of the fresh air temperature regulation requirement. The higher the characteristic temperature is, the smaller the fresh air temperature regulation requirement is; conversely, the lower the characteristic temperature, the greater the fresh air temperature regulation requirement is characterized.

Step S20, determining target control parameters of the heat exchange module according to the characteristic temperature;

the target control parameters are specifically operation control parameters of relevant parts of the heat pipe fresh air fan for regulating and controlling fresh air heating quantity of the heat exchange module.

The target control parameter may be a target temperature value of a relevant component for temperature adjustment of the fresh air (for example, a target value of a coil temperature of the second heat exchanger or a minimum temperature value allowed by a coil temperature of the third heat exchanger, etc.), and may be an operation parameter of a relevant component for temperature adjustment of the fresh air, for example, an operation rotation speed of a fan affecting temperature 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 necessary to ensure that the heat exchange amount supplied by the second heat exchanger is accurately matched with the actual temperature adjustment requirement of the current fresh air when the operation of the heat exchange module is controlled according to the target control parameter.

The different target control parameters of characteristic temperature, the different target control parameters are the heat exchange module and are supplied the different heat of new trend in the new trend wind channel. Specifically, a corresponding relation between the characteristic temperature and the target control parameter may be established in advance, and the control parameter corresponding to the current characteristic temperature is determined as the target control parameter according to the corresponding relation. For example, the target temperature of the corresponding characteristic temperature can be determined based on the indoor comfort requirement, the characteristic temperature is divided into at least two preset temperature intervals based on the target temperature, different target control parameters can be correspondingly set in the preset temperature intervals of different characteristic temperatures, the adjustment directions of the heat exchange amounts of the second heat exchangers corresponding to different target control parameters are different, based on the adjustment directions, the temperature interval where the characteristic temperature is located is determined, the control parameter corresponding to the temperature interval can be obtained as the target control parameter, and the heat exchange amount of the second heat exchanger can be changed according to the adjustment directions of the corresponding heat exchange amounts in the operation process of the heat exchange module controlled by the obtained target control parameter; 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 a characteristic temperature and the operation parameter of the fresh air temperature adjusting component in the heat exchange module can be established in advance, and when more than one component is provided, each component corresponds to one quantity relation, and the operation parameter of the corresponding fresh air temperature adjusting component can be calculated based on the current characteristic temperature.

And step S30, controlling the heat exchange module to operate according to the target control parameter so as to enable the heat exchange quantity of the second heat exchanger to be matched with the temperature regulation requirement.

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 heated by the second heat exchanger after dehumidification by the dehumidification module, and the fresh air heated by the second heat exchanger can be directly or further heated and then is sent into the indoor environment. When the heat pipe fresh air machine 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.

The heat exchange amount of the second heat exchanger matched with the temperature adjustment requirement can be understood as follows: when the temperature regulation requirement is smaller (i.e. the characteristic temperature is higher, for example, the characteristic temperature is higher than the second set temperature or higher than the first set temperature), the heat exchange amount of the second heat exchanger is reduced, and at the moment, the heat exchange amount of the second heat exchanger is matched with the temperature regulation requirement; when the temperature adjustment requirement is larger (i.e. the characteristic temperature is lower, for example, the characteristic temperature is smaller than the second set temperature), the heat exchange amount of the second heat exchanger is increased, and at this time, the heat exchange amount of the second heat exchanger is matched with the temperature adjustment requirement.

According to the control method of the heat pipe 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 of air exhaust 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 fresh air, based on the heat pipe fresh air machine, the method adjusts target control parameters of the heat exchange module based on characteristic temperature required by actual heating of the fresh air, rather than adjusting fresh air heating quantity of the heat exchange module according to preset fixed parameters, so that the heat exchange quantity of the refrigerant flowing into the second heat exchanger after the sensible heat recovery in the air exhaust duct in the heat exchange module comprising the first loop can be accurately matched with actual temperature adjustment requirements, the accuracy of temperature adjustment of the air outlet temperature is improved, the fresh air temperature adjustment is reduced, the fresh air temperature fluctuation of the fresh air machine is improved, and indoor comfort of a user is improved.

Further, based on any one of the above embodiments, another embodiment of a method for controlling a heat pipe fresh air machine is provided. In this embodiment, referring to fig. 7, the step of determining the target control parameter of the heat exchange module according to the characteristic temperature includes:

step S21, when the characteristic temperature is greater than or equal to a first set temperature, determining a first control parameter as the target control parameter; the first control parameter is used for stopping heat exchange of the second heat exchanger;

in this embodiment, the heat exchange module further includes the electromagnetic valve, a compressor, and a first check valve disposed between the refrigerant outlet of the second heat exchanger and the refrigerant inlet of the third heat exchanger, the compressor is connected in parallel with the first check valve, the electromagnetic valve is connected in series with the compressor, and the first control parameter includes one of the following parameters:

closing the compressor and closing the first throttling means;

the compressor is closed and the solenoid valve is opened.

Specifically, when the compressor and the first throttling device are both closed, the closing of the first throttling device blocks the refrigerant from circulating in the first loop, and the second heat exchanger stops heating the fresh air. In addition, when the compressor is closed and the electromagnetic valve is opened, the pressure difference of two sides of the first one-way valve is 0, the refrigerant stops flowing from one side of the first one-way valve to the other side, the refrigerant in the first loop stops circulating flow, and the second heat exchanger cannot further heat fresh air.

In other embodiments, the first control parameter may also include closing the first throttle device when the compressor and its solenoid valve in series are not present.

Here when the characteristic temperature is greater than first settlement temperature, indicate that current new trend air-out temperature is serious to be higher or new trend does not have the heating demand, according to first control parameter control heat transfer module operation this moment, be favorable to new trend temperature to reduce fast to avoid indoor temperature too high, realize the effective improvement of indoor user's travelling comfort under the new trend mode.

Step S22, when the characteristic temperature is larger than a second set temperature and smaller than the first set temperature, determining a second control parameter as the target control parameter; the second control parameter is used for reducing the heat exchange amount of the second heat exchanger, and the second set temperature is smaller than the first set temperature;

the second set 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 temperature deviation between the first set temperature and the second set temperature is greater than the set threshold. The heat exchange amount of the second heat exchanger represents the heat exchange amount of the second heat exchanger and the air in unit volume, and under the same condition, the larger the heat exchange amount of the second heat exchanger is, the larger the temperature rise of the air passing through the second heat exchanger is; under the same conditions, the smaller the heat exchange amount of the second heat exchanger, the smaller the temperature rise of the air passing through 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 second control parameter includes at least one of the following parameters:

parameter 1, improving the running rotating speed of the exhaust fan;

parameter 2, 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 3, 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 second control parameter may be parameter 1, parameter 2 or parameter 3; the second control parameter may also be parameter 1 and parameter 3; the second control parameter may also be parameter 1 and parameter 2.

The operation speed of the exhaust fan in the parameter 1 can be increased according to a preset fixed adjustment parameter, and the operation speed of the exhaust fan can also be increased according to an adjustment parameter determined by the actual operation condition of the heat pipe 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 improvement of the running rotating speed of the exhaust fan can improve the heat exchange quantity of the first heat exchanger, effectively reduce the reheat quantity of the second heat exchanger, and further realize the reduction of the fresh air outlet temperature.

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 heat pipe fresh air fan is in a heat pump circulation 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 heat pipe 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 exchange amount of the second heat exchanger under the heat pump cycle is larger than that of the second heat exchanger under the heat pipe cycle.

The parameter 2 is specifically a control parameter for converting the heat pipe fresh air machine from a heat pump cycle to a heat pipe cycle. Specifically, when the compressor is currently in an open state, the solenoid valve is currently in an open state, and the first throttling device is currently in an open state, the parameter 2 may be determined to be a second control parameter.

The parameter 3 is specifically a control parameter for converting the heat pipe fresh air machine from heat pipe circulation to the second heat exchanger to stop heat exchange. 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 3 may be determined to be the second control parameter. When the compressor is 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 exchanging heat to the fresh air in the fresh air duct.

In other embodiments, the second control parameter may also include the first throttle increasing the opening, and so on, when the compressor is currently in the heat pump cycle.

Here when the characteristic temperature is greater than the second settlement temperature and is less than or equal to first settlement temperature, indicate that current new trend air-out temperature is higher, according to second control parameter control heat transfer module operation this moment, reduce second heat exchanger heat exchange volume in order to reduce new trend air-out temperature, guarantee that new trend air-out temperature can reach the comfortable state of indoor demand.

And S23, when the characteristic temperature is smaller than the second set temperature, determining a third control parameter as the target control parameter, wherein the third control parameter is used for increasing the heat exchange amount of 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:

parameters 4, reducing the running rotating speed of the exhaust fan;

a parameter 5 controlling the compressor to switch from a closed state to an open state, controlling the solenoid valve to switch from a closed state to an open state, and controlling the first throttling device to maintain the open state;

Parameter 6, 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;

and a parameter 7, controlling the compressor to maintain a closed state, controlling the electromagnetic valve to maintain a closed state, and controlling the first throttling device to switch from the closed state to the open state.

Specifically, the third control parameter may be parameter 4, parameter 5, parameter 6 or parameter 7; the third control parameter may also be parameter 4 and parameter 5; the third control parameter may also be parameter 4 and parameter 6; the third control parameters may also be parameter 4 and parameter 7.

The operation rotation speed of the exhaust fan in the parameter 4 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 by the actual operation condition of the heat pipe 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 exchange quantity of the first heat exchanger and effectively improve the reheat quantity of the second heat exchanger, thereby realizing the improvement of the fresh air outlet temperature.

The parameter 5 is specifically a control parameter for converting the heat pipe 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 throttling device is currently in the open state, the parameter 5 may be determined to be the third control parameter.

Parameters 6 and 7 are specifically control parameters for turning the stop of the heat exchange 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 opened, the parameter 6 may be determined to be a third control parameter; alternatively, parameter 7 may be determined to be the third 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 exchange amount of the second heat exchanger is increased.

In other embodiments, the third 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.

Here when the characteristic temperature is less than the second settlement temperature, indicate that current new trend air-out temperature is lower, according to the operation of third control parameter control heat transfer module this moment, increase second heat exchanger heat exchange volume in order to improve new trend air-out temperature, guarantee that new trend air-out temperature can reach the comfortable state of indoor demand.

In this embodiment, the characteristic temperature adopts different control parameters to control the operation of heat exchange module when in different temperature intervals to realize being adapted to actual new trend temperature regulation demand and accurately adjust second settlement temperature with new trend air-out temperature, guarantee that new trend air-out temperature can satisfy indoor comfortable demand.

Further, based on any one of the above embodiments, another embodiment of a method for controlling a heat pipe fresh air machine is provided. 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, and referring to fig. 8, the control method of the heat pipe fresh air fan further includes:

Step S01, when a dehumidification reheating mode is started, controlling the dehumidification module to be started, controlling the compressor to be closed, controlling the electromagnetic valve to be closed and controlling the first throttling device to be opened;

step S02, executing the step of obtaining the characteristic temperature when the dehumidification module is in an on state, the compressor is in an off state, the electromagnetic valve is in an off state, and the first throttling device is in an on state.

The dehumidifying and reheating mode is specifically an air conditioner operation mode of firstly cooling and dehumidifying fresh air and then reheating the cooled and dehumidified fresh air.

In this embodiment, when the dehumidification reheating mode is started, the above-mentioned mode is operated, so that the heat pipe fresh air machine can firstly implement reheating dehumidification of fresh air in an energy-saving manner in a heat pipe circulation mode, and therefore when the characteristic temperature under the heat pipe circulation cannot meet the comfort requirement, the fresh air outlet temperature can be regulated and controlled in other manners, and the fresh air outlet temperature can be ensured to accurately meet the indoor comfort requirement, and meanwhile, the consumed energy of the heat pipe fresh air machine can be further reduced.

In other embodiments, the method for controlling the heat pipe fresh air machine further includes: when the dehumidification reheating mode is started, controlling the dehumidification module to be started, controlling the compressor to be started, controlling the electromagnetic valve to be started, and controlling the first throttling device to be started; and executing the step of acquiring the characteristic temperature when the dehumidification module is in an open state, the compressor is in an open state, the electromagnetic valve is in an open state and the first throttling device is in an open state. The dehumidifying and reheating mode is specifically an air conditioner operation mode of firstly cooling and dehumidifying fresh air and then reheating the cooled and dehumidified fresh air. Here when dehumidification reheat mode starts, earlier through heat pump cycle's mode with providing great heat exchange volume and reheat dehumidification to the new trend to guarantee that new trend can reach enough high air-out temperature and satisfy indoor temperature comfortable demand, still further carry out accurate regulation and control to new trend air-out temperature through other modes when the characteristic temperature can't satisfy comfortable demand under heat pump cycle, thereby guarantee new trend air-out temperature and indoor comfortable demand accurate matching.

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 heat pipe fresh air machine, and the control program of the heat pipe fresh air machine realizes the relevant steps of any embodiment of the control method of the heat pipe 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, including several instructions for causing a terminal device (which may be a mobile phone, a computer, a server, a hot-pipe fan, 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

1. The control method of the heat pipe fresh air machine is characterized in that the heat pipe fresh air machine comprises a fresh air duct, an exhaust air duct, a heat exchange module and a dehumidification module, the heat exchange module comprises a first loop, 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, the first heat exchanger is arranged 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, the heat exchange module further comprises an electromagnetic valve, a compressor, an exhaust air machine arranged in the exhaust air duct and a first one-way valve arranged 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 one-way valve, the electromagnetic valve is connected with the compressor in series, and the control method of the heat pipe fresh air machine comprises the following steps:

controlling the heat exchange module to operate according to the target control parameter so as to enable the heat exchange quantity of the second heat exchanger to be matched with the temperature regulation requirement;

the step of determining the target control parameter of the heat exchange module according to the characteristic temperature comprises the following steps:

when the characteristic temperature is greater than or equal to a first set temperature, determining a first control parameter as the target control parameter; the first control parameter is used for stopping heat exchange of the second heat exchanger, and comprises one of closing the compressor and closing the first throttling device, closing the compressor and opening the electromagnetic valve;

when the characteristic temperature is larger than a second set temperature and smaller than the first set temperature, determining a second control parameter as the target control parameter; the second control parameter is used for reducing the heat exchange amount of the second heat exchanger, the second set temperature is smaller than the first set temperature, the second control parameter comprises increasing the operation rotating speed of the exhaust fan, the rotating speed increasing amplitude of the operation of the exhaust fan is 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 according to the determined rotating speed increasing amplitude; the second control parameter further comprises a control unit for 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; or, controlling the compressor to maintain a closed state, controlling the electromagnetic valve to switch from a closed state to an open state or controlling the first throttling device to switch from an open state to a closed state;

When the characteristic temperature is smaller than the second set temperature, determining a third control parameter as the target control parameter, wherein the third control parameter is used for increasing the heat exchange amount of the second heat exchanger;

the step of obtaining the characteristic temperature comprises the following steps:

2. The method of claim 1, wherein the third control parameter comprises at least one of:

reducing the running rotating speed of the exhaust fan;

3. The method of controlling a heat pipe fresh air machine according to any one of claims 1 to 2, further comprising:

4. The utility model provides a new fan of heat pipe which characterized in that, new fan of heat pipe includes:

fresh air duct;

an exhaust air duct;

a compressor connected in parallel with the first check valve; and

a solenoid valve in series with the compressor;

the heat pipe fresh air machine further comprises an exhaust fan, and the exhaust fan is arranged in the exhaust air duct;

the heat exchange module and the dehumidification module are both connected with the control device, and the control device comprises: a memory, a processor and a control program of a heat pipe 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 heat pipe fresh air machine according to any one of claims 1 to 3.

5. A computer readable storage medium, characterized in that the computer readable storage medium has stored thereon a control program of a heat pipe fresh air machine, which when executed by a processor, implements the steps of the control method of a heat pipe fresh air machine according to any one of claims 1 to 3.