CN114017940A - Integral heat pump heat recovery type fresh air dehumidifier and control method thereof - Google Patents
Integral heat pump heat recovery type fresh air dehumidifier and control method thereof Download PDFInfo
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- CN114017940A CN114017940A CN202111233521.8A CN202111233521A CN114017940A CN 114017940 A CN114017940 A CN 114017940A CN 202111233521 A CN202111233521 A CN 202111233521A CN 114017940 A CN114017940 A CN 114017940A
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- 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
- F25B13/00—Compression machines, plants or systems, with reversible cycle
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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
- 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
- F24F11/65—Electronic processing for selecting an operating mode
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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
- 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
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- 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]
- Y02B30/56—Heat recovery units
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Abstract
The invention relates to an integral heat pump heat recovery type fresh air dehumidifier and a control method thereof, wherein the dehumidifier comprises an air flow path and a refrigerant loop, the air flow path comprises an exhaust air duct and an air supply duct, the two ends of the exhaust air duct are provided with an air return air inlet and an air exhaust air inlet, the two ends of the air supply duct are provided with an air supply air inlet and an air inlet, and the integrated heat pump heat recovery type fresh air dehumidifier is characterized in that an inclined air mixing air door capable of communicating the exhaust air duct and the air supply duct is arranged between the exhaust air duct and the air supply duct; the refrigerant loop comprises a compressor, a four-way reversing valve, an exhaust coil, an air return coil, a first one-way valve, an air supply coil, a first throttling device, a second throttling device and an air inlet coil which are connected in sequence. Compared with the prior art, the invention can deeply dehumidify air while ensuring the air outlet temperature, can meet the supply requirements of fresh air in different seasons so as to cover various working conditions all the year around, and can effectively avoid the absorption of heat in the fresh air fed by the air supply coil pipe in heating and internal circulation modes.
Description
Technical Field
The invention relates to a fresh air dehumidifier, in particular to an integral heat pump heat recovery type fresh air dehumidifier and a control method thereof.
Background
The heat pump type exhaust air heat recovery technology utilizes indoor exhaust air to condense or evaporate a refrigerant in a heat exchanger so as to complete the recovery of energy in the exhaust air, and is one of important means for energy conservation of modern buildings. The heat pump heat recovery type fresh air dehumidifier adopting the technology can reduce the energy consumption of a compressor of a unit, can avoid cross infection caused by a traditional exhaust heat recovery mode, saves energy and improves the indoor air quality.
However, as the new air blower is continuously expanded in the field of household market, in order to further standardize product energy efficiency and improve user comfort, the new national standard provides higher requirements for the filtration, refrigeration (heating), dehumidification and the like of the household fresh air dehumidifier, which undoubtedly brings more challenges to the design of the new air blower.
The chinese patent with application number 201810585463.7 proposes an integral heat pump heat recovery type fresh air dehumidifier with an internal circulation mode, which realizes three modes of internal circulation, refrigeration dehumidification and heating through control design. But the summer dehumidification working conditions are not carefully distinguished, the coping modes under different loads are lacked, and meanwhile, the fresh air is directly sent into the room after being cooled and dehumidified by the evaporator, so that the summer air supply temperature is lower, the standard that the summer air supply temperature is not lower than 22 ℃ specified in the new national standard is difficult to achieve, and the comfort level of a user is poor.
To this end, chinese patent application No. 202011216770.1 proposes an all-duty heat pump heat recovery type fresh air fan with multiple reheating modes, which has multiple reheating modes such as supercooling reheating, condensation reheating, and semi-condensation reheating, and can be selected by the unit under different loads of dehumidification mode, and can ensure that the outlet air temperature is higher than the set value. The setting of reheat coil and variable reheat mode in this patent has ensured the air-out temperature under the dehumidification mode forcefully, but under the heating mode, the existence of reheat coil can make the air cooling after the heating on the contrary, causes unnecessary heat energy loss. In the heating mode, the reheating disc manages to continuously heat the air coming out of the air supply coil (as in the cooling and dehumidifying mode), but actually, the temperature of the refrigerant in the reheating coil is lower than that of the inlet air, and the air flowing through the reheating coil is cooled.
Disclosure of Invention
The invention aims to overcome the defects of the prior art and provide an integral heat pump heat recovery type fresh air dehumidifier and a control method thereof, which can deeply dehumidify air while ensuring the air outlet temperature, can meet the fresh air supply requirements in different seasons so as to cover various working conditions all the year around, and can effectively avoid the absorption of heat in the fresh air fed by an air supply coil pipe in a heating and internal circulation mode.
The applicant found that the root cause of the problem in chinese patent 202011216770.1 is that when the two modes of cooling and dehumidifying are switched, the refrigerant flow path is switched in reverse, and the air flow direction is always unchanged. The concrete expression is as follows: in a summer refrigeration dehumidification mode, the coil pipe is used as an evaporator, and a refrigerant and air need to be arranged in a concurrent heat exchange mode, so that the evaporation temperature is prevented from being reduced, and the energy efficiency is improved; however, in the heating mode, the coil serves as a condenser with the refrigerant flow path reversed, and the refrigerant and air become a counterflow heat exchange arrangement. This results in the outlet refrigerant having been cooled by the inlet air to around 16 c (see fig. 1(a)) although the coil heats the air to a higher temperature in excess of 30 c. Further, the temperature of the refrigerant (about 16 ℃) entering the reheat coil is already lower than the air temperature (more than 30 ℃), causing heat loss in which the supply air is heated by the supply coil and then cooled by the reheat coil.
The invention is particularly additionally provided with a bypass pipeline which is connected with the air supply coil in parallel, and the refrigerant flowing out of the air inlet coil does not flow through the air supply coil in the heating and internal circulation modes, thereby effectively avoiding the loss of heat in air supply (see figure 1 (b)). Meanwhile, the invention enables the design of the product to be more compact and the occupied space to be smaller by changing the placing mode of the corresponding internal components.
The invention aims to protect an integral heat pump heat recovery type fresh air dehumidifier which comprises an air flow path and a refrigerant loop, wherein the air flow path comprises an exhaust air duct and an air supply duct, the two ends of the exhaust air duct are provided with an air return air inlet and an air exhaust air inlet, the two ends of the air supply duct are provided with an air supply air inlet and an air inlet, and an inclined air mixing air door capable of communicating the exhaust air duct and the air supply duct is arranged between the exhaust air duct and the air supply duct;
the refrigerant loop comprises a compressor, a four-way reversing valve, an exhaust coil, an air return coil, a first one-way valve, an air supply coil, a first throttling device, a second throttling device and an air inlet coil which are sequentially connected.
Further, a first bypass circuit is arranged in the refrigerant loop;
and a stop valve is arranged on the first bypass loop, one end of the stop valve is connected to a connecting pipe between an exhaust port of the compressor and the four-way reversing valve, and the other end of the stop valve is connected to a connecting pipe between an outlet of the first one-way valve and the air supply coil pipe.
Further, a second bypass circuit is arranged in the refrigerant loop;
the second bypass loop is provided with a second one-way valve, and the second one-way valve is connected with the first one-way valve, the air supply coil and the first throttling device in parallel;
one end of the second one-way valve is connected to a connecting pipe between the air return coil and the first one-way valve, and the other end of the second one-way valve is connected to a connecting pipe between the first throttling device and the second throttling device.
Furthermore, an air exhaust side water tray is arranged in the air exhaust duct;
the exhaust coil and the return coil are respectively arranged in the exhaust side water tray in an inclined manner at a certain angle.
Furthermore, the first one-way valve, the air supply coil pipe, the first throttling device, the second throttling device, the air inlet coil pipe, the first bypass loop and a stop valve thereon, the second bypass loop and a second one-way valve thereon, the four-way reversing valve and the compressor are arranged in the air supply duct.
Furthermore, an air supply side water tray is arranged in the air supply duct, and the air supply coil pipe and the air inlet coil pipe are arranged in the air supply side water tray;
a connector which can connect the air exhaust side water disc and the air supply side water disc is arranged between the air exhaust side water disc and the air supply side water disc, and a water outlet is arranged on the air exhaust side water disc.
Furthermore, four interfaces of the four-way reversing valve are respectively connected with the exhaust coil pipe, the air suction port of the compressor, the air inlet coil pipe and the exhaust port of the compressor.
Furthermore, the conducting direction of the first one-way valve is consistent with the flow direction of the refrigerant in the dehumidification mode, namely the refrigerant is allowed to flow into the air supply coil from the air return coil and is reversely cut off;
the conducting direction of the second one-way valve is consistent with the flowing direction of the refrigerant in the heating mode and the internal circulation mode, namely, the refrigerant is allowed to flow to the return air coil from a connecting pipe between the first throttling device and the second throttling device and is cut off reversely.
Furthermore, the return air inlet and the air supply inlet are respectively provided with a return air sensor and an air supply temperature and humidity sensor. Wherein the return air sensor can measure the temperature, humidity and CO in the return air2The concentration is detected, and the air supply temperature and humidity sensor can detect the temperature and the humidity in air supply.
Further, an air exhaust fan is arranged at an air exhaust port of the air exhaust duct;
and an air supply fan is arranged at the inclined air mixing air door in the air supply air duct.
Furthermore, a humidifier is arranged between the air supply coil and the air supply outlet, and the humidifier can be a wet film humidifier, an electrode type humidifier, an electric heating type humidifier or an ultrasonic humidifier and is used for humidifying the air supply which does not meet the humidity requirement in the heating mode.
Furthermore, an air filter is arranged in front of the air inlet coil pipe, a replacement opening is reserved in the air filter, and the replacement opening is arranged on the side face or the bottom.
The first throttling device and the second throttling device in the technical scheme are one of capillary tubes, throttling short tubes or electronic expansion valves, and the electronic expansion valves are preferably selected in the technical scheme in order to facilitate the realization of automatic control.
The stop valve in the technical scheme is preferably an electromagnetic valve, is suitable for the high-temperature and high-pressure environment of the exhaust port of the compressor, and is favorable for realizing automatic control of the fresh air fan.
In the technical scheme, the inclined air mixing air door is a servo driving air door, and servo driving air doors are arranged on the air exhaust opening and the air inlet opening.
The second purpose of the invention is to protect the control method of the integral heat pump heat recovery type fresh air dehumidifier, according to different loads under refrigeration and dehumidification in summer, through the opening and closing of each air door and the change of a flow path, a reheating mode of supercooling reheating or condensation reheating is selected, so that the air supply temperature can reach or be higher than the minimum air supply temperature of 22 ℃;
by opening the bypass pipeline at the air supply coil, the refrigerant flowing out through the air inlet coil in the heating and internal circulation modes does not flow through the air supply coil, so that the loss of heat in air supply is avoided.
Furthermore, in a dehumidification mode, the series-parallel connection relation between the exhaust coil and the return coil and the air supply coil is changed through the opening and closing of the first bypass circuit, so that the state of a refrigerant at the inlet of the air supply coil is adjusted, the proportion of condensation reheating and supercooling reheating in the heat exchange quantity of the first bypass circuit and air is changed, and the required air supply temperature can be ensured in different air inlet states;
in the heating mode, high-temperature and high-pressure refrigerant gas is sent into the air supply coil pipe through the first bypass circuit, so that the air supply coil pipe is connected with a refrigerant flow path of the air inlet coil pipe in parallel, the air is subjected to step heating, and the energy efficiency is improved at the same air supply temperature;
under the heating and internal circulation mode, the air supply coil has reheating capacity in summer, and meanwhile, the absorption of heat in the supplied fresh air by the air supply coil under the heating and internal circulation mode is avoided through the bypass effect of the second one-way valve on the second bypass loop.
Through air door switching and flow path switching, the following 6 operation modes can be mainly realized by the technical scheme:
1. a dehumidification mode: the air return air port, the air exhaust air port, the air supply air port and the air inlet air port are all opened, and the inclined air mixing air door is opened. The air exhaust fan and the air supply fan are both started. The air exhaust coil pipe in the four-way reversing valve is communicated with the flow path of the air exhaust port of the compressor, and the air intake coil pipe is communicated with the air suction port of the compressorThe flow paths of the ports are communicated. The first one-way valve is in a conducting state, the second one-way valve is in a stopping state, and the first throttling device is in a full-open state. The shut-off valve is closed. The humidifier is not operated. In the mode, the second throttling device controls the superheat degree of the system, controls the indoor return air humidity through the frequency adjustment of the compressor, and adjusts the air supply quantity through the air supply fan to adjust the indoor CO2The concentration is controlled, and the return air volume is controlled by the exhaust fan, so that the return air volume of the system is ensured to be between 80% and 90% of the supply air volume all the time.
2. Dehumidification mode (low ambient conditions): the air return air port, the air exhaust air port, the air supply air port and the air inlet air port are all opened, and the inclined air mixing air door is closed. The air exhaust fan and the air supply fan are both started. The air exhaust coil pipe in the four-way reversing valve is communicated with the flow path of the air exhaust port of the compressor, and the air inlet coil pipe is communicated with the flow path of the air suction port of the compressor. The first one-way valve is in a conducting state, the second one-way valve is in a stopping state, the first throttling device is in a full-open state, the stopping valve is opened, and the humidifier does not work. In this mode, the control strategy of the second throttle device, the air supply fan, and the air exhaust fan is the same as that in the dehumidification mode. The compressor controls the indoor return air humidity preferentially through frequency adjustment, and when the indoor return air humidity meets the requirement, the compressor controls the air supply temperature.
3. Heating mode 1: the air return air port, the air exhaust air port, the air supply air port and the air inlet air port are all opened, and the inclined air mixing air door is closed. The air exhaust fan and the air supply fan are both started. The air inlet coil pipe in the four-way reversing valve is communicated with the flow path of the air outlet of the compressor, and the air outlet coil pipe is communicated with the flow path of the air suction port of the compressor. The first one-way valve is in a cut-off state, and the second one-way valve is in a conducting state. The shut-off valve is closed. The humidifier starts to operate. In this mode, the control strategy of the second throttle device, the air supply fan, and the air exhaust fan is the same as that in the dehumidification mode. The air supply temperature is controlled by adjusting the frequency of the compressor, and the return air humidity is controlled by adjusting the water flow of the water supply through the humidifier.
4. Heating mode 2: the states of the air port, the air door, the fan, the four-way reversing valve, the one-way valve and the humidifier are consistent with the heating mode 1. And the stop valve is opened. In this mode, the first throttling device controls the flow ratio of the refrigerant in the flow path of the air supply coil and the flow path of the air inlet coil, and the control strategies of the second throttling device, the air supply fan, the air exhaust fan, the compressor and the humidifier are the same as those in the heating mode 1.
5. An internal circulation mode: the air exhaust air port and the air inlet air port are closed, the air return air port and the air supply air port are opened, and the middle inclined air mixing air door is opened. The air exhaust fan is closed, and the air supply fan is opened. The air inlet coil pipe in the four-way reversing valve is communicated with the flow path of the air outlet of the compressor, and the air outlet coil pipe is communicated with the flow path of the air suction port of the compressor. The first one-way valve is in a cut-off state, and the second one-way valve is in a conducting state. The shut-off valve is closed. The humidifier is not operated. In this mode, the second throttle controls the superheat of the system and controls the indoor return air humidity by compressor frequency regulation. The air supply fan keeps running at a constant speed.
6. Take the inner loop mode of new trend: the air inlet is closed, the air return air inlet, the air exhaust air inlet and the air supply air inlet are opened, and the inclined air mixing air door is opened. The air exhaust fan is closed, and the air supply fan is opened. The air inlet coil pipe in the four-way reversing valve is communicated with the flow path of the air outlet of the compressor, and the air outlet coil pipe is communicated with the flow path of the air suction port of the compressor. The first one-way valve is in a cut-off state, and the second one-way valve is in a conducting state. The shut-off valve is closed. The humidifier is turned off. In the mode, the control strategy of the second throttling device and the compressor is the same as that in the internal circulation mode, and the air supply fan adjusts the air supply quantity to indoor CO2The concentration is controlled.
In the technical scheme, in a dehumidification mode, a refrigerant in an air inlet coil pipe evaporates and absorbs heat to become refrigerant gas, the refrigerant gas is sucked by a suction inlet of a compressor through a four-way reversing valve and compressed into high-temperature and high-pressure refrigerant gas, the refrigerant is condensed and released in an air exhaust coil pipe through the four-way reversing valve, further subcooled in an air return coil pipe and an air supply coil pipe, throttled by a first throttling device and a second throttling device to become a gas-liquid two-phase state, and returned to the air inlet coil pipe. Outdoor fresh air enters the air supply duct from the air inlet and takes away compressor powderThe partial heat of hair is divided into two parts by the fresh air: one part enters the air exhaust duct through the inclined air mixing damper; one part of the air is continuously in the air supply duct, is filtered by the air filter, is cooled and dehumidified by the air inlet coil, is reheated by the air supply coil and then enters the room from the air supply air inlet. Indoor return air enters the exhaust air duct from the return air inlet, firstly passes through the return air coil to absorb heat, then is mixed with part of fresh air entering the exhaust air duct to flow through the exhaust coil to absorb heat, and finally is exhausted outdoors from the exhaust air inlet through the exhaust fan. In this mode, the second throttle device controls the degree of superheat of the system, and when the degree of superheat of the system is low, the opening degree of the second throttle device is decreased, otherwise, the opening degree is increased. The compressor controls the indoor return air humidity through frequency adjustment, when the indoor return air humidity is larger than a set value, the frequency of the compressor is increased, and when the indoor return air humidity is lower than the set value, the frequency of the compressor is reduced. The air supply fan adjusts the air supply quantity to indoor CO2Controlling the concentration of CO in room2When the concentration is higher, the rotating speed of the air supply fan is increased, the air supply quantity is increased, and otherwise, the rotating speed is reduced. The air exhaust fan controls the return air volume of the system by adjusting the rotating speed, when the air supply volume of the air supply fan is increased, the air exhaust fan increases the return air volume by increasing the rotating speed, and when the air supply volume of the air supply fan is reduced, the air exhaust fan needs to reduce the rotating speed to reduce the return air volume. By the mode, the return air volume of the system is ensured to be between 80% and 90% of the supply air volume all the time.
In the technical scheme, under a dehumidification mode (low environment working condition), a refrigerant in an air inlet coil pipe is evaporated and absorbs heat to become refrigerant gas, and a high-temperature high-pressure gas refrigerant at the outlet of a compressor is divided into two parts: one part flows to the air supply coil pipe through the stop valve, and the other part flows to the air supply coil pipe after the condensation heat release of the exhaust coil pipe and the supercooling of the return coil pipe through the four-way reversing valve. The two parts of refrigerants are converged in an inlet pipeline of the air supply coil, condensed or further supercooled in the air supply coil, throttled by the first throttling device and the second throttling device to be in a gas-liquid two-phase state together, and returned to the air inlet coil. Outdoor fresh air enters the air supply duct from the air inlet, is filtered by the air filter after taking away partial heat emitted by the compressor, and then enters the room from the air supply duct after being cooled and dehumidified by the air inlet coil and reheated by the air supply coil. Indoor return air enters the exhaust air duct from the return air inlet, firstly passes through the return air coil and the exhaust coil to absorb heat, and then is exhausted outdoors from the exhaust air inlet through the exhaust fan. In this mode, the control methods of the second throttle device, the air-supply fan, and the air-discharge fan are the same as in the dehumidification mode. The compressor controls the indoor return air humidity preferentially through frequency adjustment, when the indoor return air humidity is larger than a set value, the frequency of the compressor is increased, and when the indoor return air humidity is lower than the set value, the frequency of the compressor is reduced. When the indoor return air humidity meets the requirement, the compressor controls the air supply temperature, when the air supply temperature is lower, the frequency of the compressor is increased, and when the air supply temperature is higher, the frequency of the compressor is reduced.
In the technical scheme, under a heating mode 1, refrigerants in a return air coil and an exhaust coil are evaporated and absorb heat to become refrigerant gas, the refrigerant gas is sucked by a suction inlet of a compressor through a four-way reversing valve and compressed into high-temperature and high-pressure refrigerant gas, the refrigerant gas is condensed in an air inlet coil through the four-way reversing valve to release heat, and the refrigerant gas is throttled by a second throttling device to become a gas-liquid two-phase state and returns to the return air coil through a second one-way valve. Outdoor fresh air enters the air supply duct from the air inlet, takes away partial heat emitted by the compressor, is filtered by the air filter, is heated by the air inlet coil pipe, and is humidified by the humidifier and then is sent into the room. Indoor return air enters the exhaust air duct from the return air inlet, is cooled by the return air coil and the exhaust coil, and is exhausted outdoors from the exhaust air inlet through the exhaust fan. In this mode, the control methods of the second throttle device, the air-supply fan, and the air-discharge fan are the same as in the dehumidification mode. The compressor controls the temperature of the supplied air through frequency adjustment, and when the temperature of the supplied air is lower, the frequency of the compressor is increased, and when the temperature of the supplied air is higher, the frequency of the compressor is reduced. The humidifier controls the return air humidity by adjusting the water flow rate of water supplied by the humidifier, reduces the water supply flow rate when the return air humidity is larger than a set value, and increases the water supply flow rate in the humidifier when the return air humidity is lower than the set value.
In the technical scheme, under a heating mode 2, refrigerants in an air return coil and an air exhaust coil are evaporated and absorb heat to become refrigerant gas, the refrigerant gas is sucked by a suction inlet of a compressor through a four-way reversing valve and compressed into high-temperature and high-pressure refrigerant gas, and then the refrigerant gas is divided into two parts: one part of the air flows into the air supply coil pipe through the electromagnetic valve for condensation and heat release, and is throttled in the first throttling device; the other part is condensed in the air inlet coil pipe through a four-way reversing valve to release heat and is throttled by a second throttling device. The gas-liquid two-phase refrigerant respectively throttled by the first throttling device and the second throttling device returns to the air return coil pipe through the second one-way valve. Outdoor fresh air enters the air supply duct from the air inlet, takes away partial heat emitted by the compressor, is filtered by the air filter, is heated by the air inlet coil pipe and the air supply coil pipe, and is finally humidified by the humidifier and then is sent into a room. Indoor return air enters the exhaust air duct from the return air inlet, is cooled by the return air coil and the exhaust coil, and is exhausted outdoors from the exhaust air inlet through the exhaust fan. In this mode, the control methods of the second throttle device, the air-supply fan, the air-discharge fan, the compressor, and the humidifier are the same as those in the heating mode 1. On the premise that the second throttling device controls the superheat degree, the first throttling device controls the flow proportion of the refrigerant in the air supply coil and the air inlet coil, the opening degree of the first throttling device is increased when the flow in the air supply coil is less, and the opening degree of the first throttling device is reduced when the flow in the air supply coil is more.
In the technical scheme, under an internal circulation mode, a refrigerant in a return coil pipe evaporates and absorbs heat to become refrigerant gas, the refrigerant gas is sucked by a suction inlet of a compressor through an exhaust coil pipe and a four-way reversing valve and compressed into high-temperature and high-pressure refrigerant gas, the refrigerant gas is condensed in an air inlet coil pipe through the four-way reversing valve to release heat, and the refrigerant gas is throttled by a second throttling device to become a gas-liquid two-phase state and returns to the return coil pipe through a second one-way valve. Indoor return air enters the exhaust air duct from the return air inlet, is cooled and dehumidified through the return air coil, enters the air supply duct through the inclined air mixing air door, is filtered by the air filter, and enters the room from the air supply inlet after absorbing heat through the air inlet coil. In this mode, the second throttling device and the control method of the compressor are the same as in the dehumidification mode. The air supply fan keeps running at a constant speed.
In the technical scheme, under an internal circulation mode with fresh air, refrigerants in a return air coil and an exhaust coil are evaporated and absorb heat to become refrigerant gas, the refrigerant gas is sucked by a suction inlet of a compressor through a four-way reversing valve and compressed into high-temperature and high-pressure refrigerant gas, the refrigerant gas is condensed in an air inlet coil through the four-way reversing valve to release heat, and the refrigerant gas is throttled by a second throttling device to become a gas-liquid two-phase state and returns to the return air coil through a second one-way valve. Indoor return air enters the exhaust air duct from the return air inlet, is cooled and dehumidified through the return air coil, meanwhile, enters a small amount of outdoor fresh air through the exhaust air inlet in the exhaust air duct, emits heat through the exhaust air coil, is mixed with the outdoor fresh air through the inclined air mixing air door and enters the air supply duct, is filtered by the air filter, and enters the indoor from the air supply inlet after being heated through the air inlet coil. In this mode, the control method of the second throttle device, the compressor, and the blower fan is the same as that in the dehumidification mode.
The invention relates to an integral heat pump heat recovery type fresh air dehumidifier and a control method thereof, which have the following characteristics and innovation points in structure:
1. a first bypass loop is provided: in a dehumidification mode, the series-parallel connection relation of the exhaust coil, the return coil and the air supply coil is changed through the opening and closing of the loop, so that the state of a refrigerant at the inlet of the air supply coil is adjusted, the proportion of condensation reheating and supercooling reheating in the heat exchange quantity of the refrigerant and air is changed, and the required air supply temperature can be ensured in different air inlet states; in the heating mode, high-temperature and high-pressure refrigerant gas can be sent into the air supply coil by means of the first bypass loop, so that the air supply coil and the refrigerant flow path of the air inlet coil are connected in parallel, the air is heated in a gradient manner, and the energy efficiency is improved at the same air supply temperature.
2. The second bypass loop is arranged, so that the air supply coil has reheating capacity in summer, and can be bypassed by the second one-way valve on the second bypass loop in a heating and internal circulation mode, and the heat loss caused by the absorption of the air supply coil on the heat in the fresh air in the heating and internal circulation mode is effectively avoided (see fig. 1).
3. The air supply fan is arranged on the inclined air mixing air door opening in the air supply air duct, on one hand, positive pressure can be always kept near the air supply side water disc, negative pressure can be always kept near the air exhaust side water disc, condensate water in the air exhaust side water disc can flow into the air supply side water disc through the connecting opening, and therefore the integral condensate water of the unit can be better discharged through the water outlet. On the other hand, the air supply fan can reduce the noise of the unit through the shielding of parts such as an air filter, an air inlet coil pipe, an air supply coil pipe and a humidifier, and the user experience feeling is better.
4. The unit is newly increased and is taken the inner loop mode of new trend, on the basis of transition season inner loop mode, will exhaust air the air door and open, can introduce the new trend when filtering the dehumidification to the room air.
5. The setting of exhaust side water tray and air feed side water tray not only is favorable to the drainage, and the comdenstion water in the water tray can play the cooling effect to placing coil pipe wherein under the air flow moreover, can reduce condensation temperature under certain condition to promote unit wholeness ability.
6. The air return coil and the air exhaust coil are respectively obliquely arranged in the water tray of the air exhaust duct at a certain angle, so that the width of the air duct is reduced, the size of the whole unit is effectively reduced, and the whole structure of the unit is more compact.
7. The indoor temperature and humidity can be automatically maintained at set values through the control method of related components, and the unit is more efficient and convenient to use.
The purpose of the invention can be realized by the following technical scheme:
compared with the prior art, the invention has the following advantages:
1. the air supply coil and the first bypass loop which are additionally arranged in the technical scheme have effects in dehumidification and heating modes. In summer, different loads of the summer dehumidification working condition can be matched with an appropriate reheating mode by controlling the opening and closing of the stop valve, so that the summer air supply temperature always meets the requirement, particularly the requirement of the new national standard on the minimum air supply temperature of 22 ℃. Under the heating mode, also can make high temperature refrigerant flow in air supply coil pipe through opening the stop valve, realize the reheating to the new trend, promote the unit efficiency. The setting of this stop valve utilizes simple part to combine ingenious structural design to reach and is showing the effect, has greatly richened new fan's use scene, and is not only economical but also effective.
2. Set up the second bypass return circuit to air supply coil pipe department among this technical scheme, through the unilateral effect of switching on of first check valve and second check valve for the refrigerant does not flow through air supply coil pipe under heating and the inner loop mode, can effectively avoid the loss of heat in the air supply coil pipe department in the air supply, more is fit for the needs of family formula new trend supply all the year.
3. The air supply fan sets up the slope in the air supply wind channel and mixes wind door mouth among this technical scheme, not only is favorable to the whole drainage of unit, can reduce the noise of unit moreover to a certain extent for user experience feels better.
4. The technical scheme is that the exhaust side water tray and the air supply side water tray are arranged, the air return coil and the air exhaust coil are obliquely arranged in the exhaust side water tray, and the air supply coil and the air inlet coil are arranged in the air supply side water tray. The condensed water formed in the water tray at the air exhaust side and the water tray at the air supply side can cool the heat exchanger piece placed in the water tray through the blowing action of air when the unit runs, so that the condensation temperature of the unit can be reduced, and the overall performance of the unit is improved.
5. The inclined arrangement of the exhaust coil and the return coil in the technical scheme reduces the size of the unit, and meanwhile, as the unit box body is not provided with excessive air valves or air duct steering assemblies, the structure of the unit is simpler and more compact than that of the like products.
6. The adjustable mode of unit is many among this technical scheme to all can make indoor humiture keep the setting value all the time through the mutual control between each part, promoted user's comfort level when convenience of customers uses.
Drawings
FIG. 1 is a schematic diagram illustrating the flow direction and temperature changes of refrigerant and air in the blowing coil and the reheating coil in the heating mode of the invention 202011216770.1 and the invention;
FIG. 2 is a schematic structural diagram of a heat pump heat recovery type fresh air dehumidifier in the present invention;
fig. 3 to 8 are schematic flow diagrams of the heat pump heat recovery type fresh air dehumidifier in a dehumidification mode, a dehumidification mode (low environmental condition), a heating mode 1, a heating mode 2, an internal circulation mode and an internal circulation mode with fresh air according to the present invention;
fig. 9 is a schematic view of a structural arrangement mode of the heat pump heat recovery type fresh air dehumidifier of the present invention.
In the figure: 1-an air exhaust duct; 2-air supply duct; 3-return air inlet; 4-air exhaust port; 5-air supply port; 6-air inlet; 7-inclined air mixing damper; 8-10-blast gate; 11-a wind-discharging side water tray; 12-air supply side water pan; 13-return air coil pipe; 14-exhaust coil pipe; 15-a first one-way valve; 16-air supply coil pipe; 17-a first throttling means; 18-a second throttling means; 19-air intake coil pipe; 20-an air filter; a 21-four-way reversing valve; 22-a compressor; 23-an exhaust fan; 24-an air supply fan; 25-a stop valve; 26-a second one-way valve; 27-a humidifier; 28-return air sensor; 29-air supply temperature and humidity sensor; 30-connecting port; 31-a water outlet; 32-47 connecting pipes.
Detailed Description
The invention is described in detail below with reference to the figures and specific embodiments. In the technical scheme, the features such as component model, material name, connection structure, control method, algorithm and the like which are not explicitly described are all regarded as common technical features disclosed in the prior art.
Example 1
The structure of the integrated heat pump heat recovery type fresh air dehumidifier in the embodiment is shown in fig. 2, and the main structure comprises an exhaust air duct 1, an air supply duct 2, an air return air inlet 3, an exhaust air inlet 4, an air supply air inlet 5, an air inlet 6, an inclined air mixing air door 7, air valves 8-10, an exhaust side water tray 11, an air supply side water tray 12, an air return coil 13, an exhaust coil 14, a first one-way valve 15, an air supply coil 16, a first throttling device 17, a second throttling device 18, an air inlet coil 19, an air filter 20, a four-way reversing valve 21, a compressor 22, an exhaust fan 23, an air supply fan 24, a stop valve 25, a second one-way valve 26, a humidifier 27, an air return air sensor 28, an air supply temperature and humidity sensor 29, a connecting port 30, a water outlet 31 and connecting pipelines 32-47.
In this embodiment, the compressor 22, the connection pipes 42 and 43, the four-way reversing valve 21, the connection pipe 32, the exhaust coil 14, the connection pipe 33, the return coil 13, the connection pipes 34 and 35, the first check valve 15, the air supply coil 16, the connection pipe 36, the first throttling device 17, the connection pipes 37 and 38, the second throttling device 18, the connection pipe 39, the exhaust coil 19, the connection pipe 40, the four-way reversing valve 21, and the connection pipe 41 are sequentially connected to form a refrigerant loop. The interface A of the four-way reversing valve 21 is connected with the connecting pipe 40, the interface B is connected with the connecting pipe 41, the interface C is connected with the connecting pipe 32, and the interface D is connected with the connecting pipe 43.
The refrigerant loop in this embodiment is further provided with a first bypass circuit and a second bypass circuit, the first bypass circuit is composed of a connecting pipe 44, a stop valve 25 and a connecting pipe 45, one end of the first bypass circuit is connected with the compressor exhaust connecting pipe 42 through the connecting pipe 44, and the other end of the first bypass circuit is connected with a pipeline between the first check valve 15 and the air supply coil 16 through the connecting pipe 45. The second bypass circuit is composed of a connecting pipe 46, a second check valve 26 and a connecting pipe 47, is connected with the first check valve 15 and the air supply coil 16 in parallel, and has one end communicated with the inlet connecting pipe 35 of the first check valve 15 through the connecting pipe 46 and the other end communicated with the connecting pipes 37 and 38 between the first throttling device 17 and the second throttling device 18 through the connecting pipe 47.
The unit can realize the following 6 operation modes through air door opening and closing and flow path switching:
first, dehumidification mode (see fig. 3)
In the dehumidification mode, the unit of this embodiment has the following component states: the air return air inlet 3, the air exhaust air inlet 4, the air supply air inlet 5 and the air inlet 6 are all opened, and the inclined air mixing air door 7 is opened. The exhaust fan 23 and the supply fan 24 are both turned on. The AB interface and the CD interface of the four-way reversing valve 21 are communicated. The first check valve 15 is in the on state, the second check valve 26 is in the off state, the first throttle device 17 is in the fully open state, the shutoff valve 25 is closed, and the humidifier 27 does not operate.
In the dehumidification mode of the unit of the embodiment, the states of the refrigerant flow paths are as follows: the refrigerant in the air intake coil 19 evaporates and absorbs heat to become refrigerant gas, the refrigerant gas is sucked by the suction inlet of the compressor 22 through the four-way reversing valve 21 and compressed into high-temperature and high-pressure refrigerant gas, the refrigerant is condensed and released heat in the exhaust coil 14 through the four-way reversing valve 21, the refrigerant is further supercooled in the air return coil 13 and the air supply coil 16, and the refrigerant is throttled by the first throttling device 17 and the second throttling device 18 to become a gas-liquid two-phase state and returns to the air intake coil 19.
In the dehumidification mode of the unit of this embodiment, the air flow path state is: outdoor new trend gets into air supply duct 2 from air inlet 6, takes away the partial heat that compressor 22 gived off, and the new trend divide into two parts afterwards: one part enters the air exhaust duct 1 through the inclined air mixing damper 7; one part of the air continues in the air supply duct 2, is filtered by the air filter 20, is cooled and dehumidified by the air inlet coil 19, is reheated by the air supply coil 16, and then enters the room from the air supply air inlet 5. Indoor return air enters the exhaust air duct 1 from the return air inlet 3, firstly absorbs heat through the return air coil 13, then is mixed with part of fresh air entering the exhaust air duct 1, flows through the exhaust coil 14 to absorb heat, and finally is exhausted outdoors from the exhaust air inlet 4 through the exhaust fan 23.
In the dehumidification mode, the control strategy of the unit of this embodiment is as follows: the second throttling device 18 controls the degree of superheat of the system, and when the degree of superheat of the system is low, the opening degree of the second throttling device 18 is reduced, otherwise, the opening degree is increased. The compressor 22 controls the indoor return air humidity by frequency modulation, increasing the frequency of the compressor 22 when the indoor return air humidity is greater than the set point, and decreasing the frequency of the compressor 22 when the indoor return air humidity is less than the set point. The air supply fan 24 adjusts the air supply quantity to indoor CO2Controlling the concentration of CO in room2When the concentration is higher, the rotating speed of the air supply fan 24 is increased, the air supply quantity is increased, and converselyThe rotational speed is reduced. The exhaust fan 23 controls the amount of return air of the system by adjusting the rotation speed, when the air supply amount of the air supply fan 24 increases, the exhaust fan 23 increases the amount of return air by increasing the rotation speed, and when the air supply amount of the air supply fan 24 decreases, the exhaust fan 23 needs to decrease the rotation speed to decrease the amount of return air. By the mode, the return air volume of the system is ensured to be between 80% and 90% of the supply air volume all the time.
Second, dehumidification mode (Low ambient conditions) (see FIG. 4)
In the dehumidification mode (low environment condition), the unit of the embodiment has the following component states: the air return air inlet 3, the air exhaust air inlet 4, the air supply air inlet 5 and the air inlet 6 are all opened, and the inclined air mixing air door 7 is closed. The exhaust fan 23 and the supply fan 24 are both turned on. The AB interface and the CD interface of the four-way reversing valve 21 are communicated. The first check valve 15 is in a conducting state, the second check valve 26 is in a blocking state, the first throttle device 17 is in a fully open state, the shutoff valve 25 is opened, and the humidifier 27 does not operate.
In the dehumidification mode (low-environment working condition), the refrigerant flow path state of the unit of the embodiment is as follows: the refrigerant in the air intake coil 19 evaporates and absorbs heat to become refrigerant gas, and the high-temperature high-pressure gas refrigerant at the outlet of the compressor 22 is divided into two parts: one part flows to the air supply coil 16 through the stop valve 25, and the other part flows to the air supply coil 16 through the four-way reversing valve 21 after being condensed and released heat in the exhaust coil 14 and supercooled in the return air coil 13. The two parts of refrigerant are merged in the inlet pipeline of the air supply coil 16, condensed or further supercooled in the air supply coil 16, throttled by the first throttling device 17 and the second throttling device 18 to be in a gas-liquid two-phase state, and returned to the air inlet coil 19.
In the dehumidification mode (low environment condition), the air flow path state of the unit of the embodiment is as follows: outdoor fresh air enters the air supply duct 2 from the air inlet 6, takes away partial heat emitted by the compressor 22, is filtered by the air filter 20, is cooled and dehumidified by the air inlet coil 19, is reheated by the air supply coil 16, and then enters the room from the air supply inlet 5. Indoor return air enters the exhaust air duct 1 from the return air inlet 3, firstly passes through the return air coil 13 and the exhaust coil 14 to absorb heat, and then is exhausted outdoors from the exhaust air inlet 4 through the exhaust fan 23.
In the dehumidification mode (low environment condition), the control strategy of the unit of this embodiment is as follows: the control method of the second throttle device 18, the supply fan 24, and the exhaust fan 23 is the same as that in the dehumidification mode. The compressor 22 preferably controls the indoor return air humidity by frequency modulation, with the compressor 22 increasing in frequency when the indoor return air humidity is greater than the set point and decreasing in frequency when the indoor return air humidity is less than the set point. When the indoor return air humidity reaches the requirement, the compressor 22 controls the air supply temperature, when the air supply temperature is lower than the dew point temperature corresponding to the indoor return air state (or the minimum air supply temperature 22 ℃ specified in the new national standard), the frequency of the compressor 22 is increased, and when the air supply temperature is higher than the dew point temperature corresponding to the indoor return air state (or the minimum air supply temperature 22 ℃ specified in the new national standard), the frequency of the compressor 22 is reduced.
This embodiment unit is under dehumidification mode (low environmental condition), and structural feature and regulation and control beneficial effect do: under this mode, because the unit is equipped with first bypass return circuit, through opening solenoid valve 25, adjust the state of reheat coil inlet refrigerant, change the proportion of condensation reheat and subcooling reheat in the reheat coil (the condensation reheat is higher than subcooling reheat heat transfer volume), make the unit can satisfy the requirement of air-out temperature all the time when carrying out the degree of depth dehumidification.
Heating mode 1 (see fig. 5)
In the heating mode 1 of the unit of the embodiment, the component states are as follows: the air return air inlet 3, the air exhaust air inlet 4, the air supply air inlet 5 and the air inlet 6 are all opened, and the inclined air mixing air door 7 is closed. The exhaust fan 23 and the supply fan 24 are both turned on. The AD interface of the four-way reversing valve 21 is communicated with the BC interface. The first check valve 15 is in the blocking state, the second check valve 26 is in the conducting state, the blocking valve 25 is closed, and the humidifier 27 starts to operate.
In the heating mode 1 of the unit of the present embodiment, the states of the refrigerant flow path are as follows: the refrigerants in the air return coil 13 and the exhaust coil 14 are evaporated to absorb heat to become refrigerant gas, the refrigerant gas passes through the four-way reversing valve 21, is sucked by the suction port of the compressor 22 and is compressed into high-temperature and high-pressure refrigerant gas, the refrigerant gas passes through the four-way reversing valve 21, is condensed and releases heat in the air inlet coil 19, is throttled by the second throttling device 18 to become a gas-liquid two-phase state, and returns to the air return coil 13 through the second one-way valve 26.
In the heating mode 1 of the unit of the embodiment, the air flow path state is as follows: outdoor fresh air enters the air supply duct 2 from the air inlet 6, takes away part of heat emitted by the compressor 22, is filtered by the air filter 20, is heated by the air inlet coil 19, and is humidified by the humidifier 27 and then is sent into the room. Indoor return air enters the exhaust air duct 1 from the return air inlet 3, is cooled by the return air coil 13 and the exhaust coil 14, and is exhausted outdoors from the exhaust air inlet 4 through the exhaust fan 23.
In the unit of this embodiment, in the heating mode 1, the control strategy is as follows: the control method of the second throttle device 18, the supply fan 24, and the exhaust fan 23 is the same as that in the dehumidification mode. The compressor 22 controls the supply air temperature by frequency modulation, increasing the compressor 22 frequency when the supply air temperature is low, and decreasing the compressor 22 frequency when the supply air temperature is high. The humidifier 27 controls the return air humidity by adjusting the water flow rate of the water supplied by the humidifier 27, when the return air humidity is higher than a set value, the humidifier 27 reduces the water flow rate of the water supplied, and when the return air humidity is lower than the set value, the water flow rate of the water supplied in the humidifier 27 is increased.
Under heating mode 1, the unit of this embodiment, structural feature and regulation and control beneficial effect are: in this mode, because the unit is provided with the second bypass circuit at the air supply coil 16, the refrigerant does not flow through the air supply coil 16 under this mode through the cut-off of the first check valve 15 and the conduction of the second check valve 26, so that the heat exchange process that the refrigerant with a lower temperature absorbs heat to the air supply in the air supply coil 16 is well avoided, and the loss of heat at the air supply coil 16 in the air supply can be effectively prevented (see fig. 1).
Heating mode 2 (see fig. 6)
In the heating mode 2 of the unit of the embodiment, the component states are as follows: the air return air inlet 3, the air exhaust air inlet 4, the air supply air inlet 5 and the air inlet 6 are all opened, and the inclined air mixing air door 7 is closed. The exhaust fan 23 and the supply fan 24 are both turned on. The AD interface of the four-way reversing valve 21 is communicated with the BC interface. The first check valve 15 is in the blocking state and the second check valve 26 is in the conducting state. The cut-off valve 25 is opened.
In the heating mode 2 of the unit of the present embodiment, the states of the refrigerant flow path are as follows: the refrigerants in the return coil 13 and the exhaust coil 14 are evaporated and absorb heat to become refrigerant gas, and the refrigerant gas is sucked by the suction port of the compressor 22 through the four-way reversing valve 21 and compressed into high-temperature and high-pressure refrigerant gas, and then divided into two parts: a part of the condensed heat is discharged through the electromagnetic valve 25 flowing into the air supply coil 16 and throttled in the first throttling device 17; the other part is condensed and released in the air inlet coil 19 through the four-way reversing valve 21 and throttled by the second throttling device 18. The gas-liquid two-phase refrigerant throttled by the first and second throttling devices 17 and 18 is returned to the return air coil 13 through the second check valve 26.
In the heating mode 2 of the unit of the present embodiment, the air flow path state is as follows: outdoor fresh air enters the air supply duct 2 from the air inlet 6, takes away part of heat emitted by the compressor 22, is filtered by the air filter 20, is heated by the air inlet coil 19 and the air supply coil 16, and is finally humidified by the humidifier 27 and then is sent into the room. Indoor return air enters the exhaust air duct 1 from the return air inlet 3, is cooled by the return air coil 13 and the exhaust coil 14, and is exhausted outdoors from the exhaust air inlet 4 through the exhaust fan 23.
In the heating mode 2 of the unit of this embodiment, the control strategy is as follows: the control methods of the second throttle device 18, the blower fan 24, the exhaust fan 23, the compressor 22, and the humidifier 27 are the same as those in the heating mode 1. On the premise that the second throttling device 18 controls the superheat degree, the first throttling device 17 controls the flow ratio of the refrigerants in the air supply coil 16 and the air inlet coil 19, when the flow in the air supply coil 16 is small, the opening degree of the first throttling device 17 is increased, and when the flow in the air supply coil 16 is large, the opening degree of the first throttling device 17 is decreased.
Under heating mode 2, the unit of this embodiment, structural feature and regulation and control beneficial effect are: in this mode, the unit opens the stop valve 25 based on the heating mode 1, and allows the high-temperature refrigerant to flow into the air-supply coil 16 through the first bypass circuit. When possessing the advantage of heating mode 1, further utilized the heat of condensation in the air supply coil 16 to realize the reheating to the new trend, can promote the unit efficiency.
Five, inner circulation mode (see fig. 7)
In the internal circulation mode of the unit of this embodiment, the component states are: the air exhaust port 4 and the air inlet port 6 are closed, the air return port 3 and the air supply port 5 are opened, and the middle inclined air mixing air door 7 is opened. The exhaust fan 23 is turned off and the supply fan 24 is turned on. The AD interface of the four-way reversing valve 21 is communicated with the BC interface. The first check valve 15 is in the blocking state and the second check valve 26 is in the conducting state. The shut-off valve 25 is closed. The humidifier 27 is turned off.
In the internal circulation mode of the unit of the present embodiment, the states of the refrigerant flow paths are as follows: the refrigerant in the return air coil 13 evaporates and absorbs heat to become refrigerant gas, which is sucked by the suction inlet of the compressor 22 through the exhaust coil 14 and the four-way reversing valve 21 and compressed into high-temperature and high-pressure refrigerant gas, which is condensed and released in the intake coil 19 through the four-way reversing valve 21, throttled by the second throttling device 18 to become a gas-liquid two-phase state, and returned to the return air coil 13 through the second one-way valve 26.
In the internal circulation mode of the unit of this embodiment, the air flow path state is: indoor return air enters the exhaust air duct 1 from the return air inlet 3, is cooled and dehumidified through the return air coil 13, enters the air supply duct 2 through the inclined air mixing damper 7, is filtered by the air filter 20, and enters the room from the air supply inlet 5 after absorbing heat through the air inlet coil 19.
In the internal circulation mode of the unit of this embodiment, the control strategy is as follows: the control method of the second throttling device 18 and the compressor 22 is the same as in the dehumidification mode. The air supply fan keeps running at a constant speed.
Sixthly, an internal circulation mode with fresh air (see figure 8)
In the internal circulation mode with fresh air, the unit of this embodiment has the following component states: the air inlet 6 is closed, the air return 3, the air exhaust 4 and the air supply 5 are opened, and the inclined air mixing door 7 is opened. The exhaust fan 23 is turned off and the supply fan 24 is turned on. The AD interface of the four-way reversing valve 21 is communicated with the BC interface. The first check valve 15 is in the blocking state and the second check valve 26 is in the conducting state. The shut-off valve 25 is closed. The humidifier 27 is turned off.
In the internal circulation mode with fresh air, the refrigerant flow path state of the unit of this embodiment is as follows: the refrigerants in the air return coil 13 and the exhaust coil 14 are evaporated to absorb heat and become refrigerant gas, the refrigerant gas is sucked by the suction inlet of the compressor 22 through the four-way reversing valve 21 and compressed into high-temperature and high-pressure refrigerant gas, the refrigerant gas is condensed and released heat in the air inlet coil 19 through the four-way reversing valve 21, the refrigerant gas is throttled by the second throttling device 18 to become a gas-liquid two-phase state, and the refrigerant gas returns to the air return coil 13 through the second one-way valve 26.
In the internal circulation mode with fresh air, the air flow path state of the unit of this embodiment is as follows: indoor return air enters the exhaust air duct 1 from the return air inlet 3, is cooled and dehumidified through the return air coil 13, simultaneously enters a small amount of outdoor fresh air through the exhaust air inlet 4 in the exhaust air duct 1, emits heat through the exhaust coil 14, is mixed with the outdoor fresh air through the inclined air mixing air door 7 and enters the air supply duct 2, is filtered by the air filter 20, and enters the indoor from the air supply air inlet 5 after being heated through the air inlet coil 19.
In the internal circulation mode with fresh air, the control strategy of the unit of this embodiment is as follows: the second throttle device 18, the compressor 22, and the blower fan 24 are controlled in the same manner as in the dehumidification mode.
Under the inner loop mode of this embodiment unit area new trend, structural feature and regulation and control beneficial effect are: under this mode, the unit will be opened air outlet 4 on the basis of inner loop mode, can introduce the new trend when filtering the dehumidification to the room air, and user experience is better.
Referring to fig. 9, this compact design occupies a small space and is very convenient for installation. It should be understood that other arrangements, which are within the spirit of the invention, are also within the scope of the invention.
The terms "first," "second," and the like are used herein to define components, as one skilled in the art would know: the use of the words "first", "second", etc. is merely for convenience in describing the differences between the components. Unless otherwise stated, the above words have no special meaning.
The embodiments described above are described to facilitate an understanding and use of the invention by those skilled in the art. It will be readily apparent to those skilled in the art that various modifications to these embodiments may be made, and the generic principles described herein may be applied to other embodiments without the use of the inventive faculty. Therefore, the present invention is not limited to the above embodiments, and those skilled in the art should make improvements and modifications within the scope of the present invention based on the disclosure of the present invention.
Claims (10)
1. An integral heat pump heat recovery type fresh air dehumidifier comprises an air flow path and a refrigerant loop, wherein the air flow path comprises an exhaust air channel and an air supply air channel, the two ends of the exhaust air channel are provided with an air return air inlet and an air exhaust air inlet, and the two ends of the air supply air channel are provided with an air supply air inlet and an air inlet;
the refrigerant loop comprises a compressor, a four-way reversing valve, an exhaust coil, an air return coil, a first one-way valve, an air supply coil, a first throttling device, a second throttling device and an air inlet coil which are sequentially connected.
2. The integrated heat pump heat recovery type fresh air dehumidifier as claimed in claim 1, wherein a first bypass circuit is further provided in the refrigerant loop;
and a stop valve is arranged on the first bypass loop, one end of the stop valve is connected to a connecting pipe between an exhaust port of the compressor and the four-way reversing valve, and the other end of the stop valve is connected to a connecting pipe between an outlet of the first one-way valve and the air supply coil pipe.
3. The integrated heat pump heat recovery type fresh air dehumidifier as claimed in claim 1, wherein a second bypass circuit is further arranged in the refrigerant loop;
the second bypass loop is provided with a second one-way valve, and the second one-way valve is connected with the first one-way valve, the air supply coil and the first throttling device in parallel;
one end of the second one-way valve is connected to a connecting pipe between the air return coil and the first one-way valve, and the other end of the second one-way valve is connected to a connecting pipe between the first throttling device and the second throttling device.
4. The integrated heat pump heat recovery type fresh air dehumidifier as claimed in claim 1, wherein a discharge side water tray is arranged in the discharge air duct;
the exhaust coil and the return coil are respectively arranged in the exhaust side water tray in an inclined manner at a certain angle.
5. The integrated heat pump heat recovery type fresh air dehumidifier of claim 1, wherein the first one-way valve, the air supply coil, the first throttling device, the second throttling device, the air inlet coil, the first bypass loop and a stop valve thereon, the second bypass loop and a second one-way valve thereon, the four-way reversing valve and the compressor are arranged in the air supply duct.
6. The integrated heat pump heat recovery type fresh air dehumidifier as claimed in claim 4, wherein an air supply side water tray is arranged in the air supply duct, and the air supply coil and the air inlet coil are arranged in the air supply side water tray;
a connector which can connect the air exhaust side water disc and the air supply side water disc is arranged between the air exhaust side water disc and the air supply side water disc, and a water outlet is arranged on the air exhaust side water disc.
7. The integrated heat pump heat recovery type fresh air dehumidifier of claim 1, wherein four ports of the four-way reversing valve are respectively connected with the exhaust coil, the air suction port of the compressor, the air intake coil and the air exhaust port of the compressor.
8. The integrated heat pump heat recovery type fresh air dehumidifier as claimed in claim 3, wherein the conducting direction of the first one-way valve is consistent with the flow direction of the refrigerant in the dehumidification mode, namely, the refrigerant is allowed to flow into the air supply coil from the return coil and is reversely cut off;
the conducting direction of the second one-way valve is consistent with the flowing direction of the refrigerant in the heating mode and the internal circulation mode, namely, the refrigerant is allowed to flow to the return air coil from a connecting pipe between the first throttling device and the second throttling device and is cut off reversely.
9. A control method of the integrated heat pump heat recovery type fresh air dehumidifier as claimed in any one of claims 1 to 8, characterized in that according to different loads under refrigeration and dehumidification in summer, through the opening and closing of each air door and the change of flow paths, a reheating mode of supercooling reheating or condensation reheating is selected, so that the temperature of the supplied air can reach or be higher than the minimum temperature of the supplied air by 22 ℃;
by opening the bypass pipeline at the air supply coil, the refrigerant flowing out through the air inlet coil in the heating and internal circulation modes does not flow through the air supply coil, so that the loss of heat in air supply is avoided.
10. The control method of the integrated heat pump heat recovery type fresh air dehumidifier as claimed in claim 9, wherein in the dehumidification mode, the series-parallel connection relationship between the exhaust coil and the return coil and the air supply coil is changed by opening and closing the first bypass circuit, so as to adjust the state of the refrigerant at the inlet of the air supply coil, change the ratio of condensation reheating and supercooling reheating between the first bypass circuit and the air heat exchange quantity, and ensure the required air supply temperature under different air inlet states;
in the heating mode, high-temperature and high-pressure refrigerant gas is sent into the air supply coil pipe through the first bypass circuit, so that the air supply coil pipe is connected with a refrigerant flow path of the air inlet coil pipe in parallel, the air is subjected to step heating, and the energy efficiency is improved at the same air supply temperature;
under the heating and internal circulation mode, the air supply coil has reheating capacity in summer, and meanwhile, the absorption of heat in the supplied fresh air by the air supply coil under the heating and internal circulation mode is avoided through the bypass effect of the second one-way valve on the second bypass loop.
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| CN114811907B (en) * | 2022-03-14 | 2024-01-26 | 青岛海信日立空调***有限公司 | Air conditioner control method and air conditioner |
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| Publication number | Publication date |
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| CN114017940B (en) | 2022-09-09 |
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