CN116293959A - Heat pump heat recovery type fresh air dehumidifier with total heat exchanger and control method thereof - Google Patents
Heat pump heat recovery type fresh air dehumidifier with total heat exchanger and control method thereof Download PDFInfo
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- CN116293959A CN116293959A CN202211102618.XA CN202211102618A CN116293959A CN 116293959 A CN116293959 A CN 116293959A CN 202211102618 A CN202211102618 A CN 202211102618A CN 116293959 A CN116293959 A CN 116293959A
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- 238000011084 recovery Methods 0.000 title claims abstract description 40
- 238000000034 method Methods 0.000 title claims abstract description 19
- 238000002156 mixing Methods 0.000 claims abstract description 31
- 238000007791 dehumidification Methods 0.000 claims abstract description 25
- 238000005192 partition Methods 0.000 claims abstract description 23
- 238000009833 condensation Methods 0.000 claims abstract description 14
- 230000005494 condensation Effects 0.000 claims abstract description 14
- 230000001276 controlling effect Effects 0.000 claims description 7
- 230000003247 decreasing effect Effects 0.000 claims description 4
- 230000001105 regulatory effect Effects 0.000 claims description 4
- 230000008878 coupling Effects 0.000 claims description 3
- 238000010168 coupling process Methods 0.000 claims description 3
- 238000005859 coupling reaction Methods 0.000 claims description 3
- 238000001914 filtration Methods 0.000 claims description 2
- 238000000926 separation method Methods 0.000 claims 1
- 230000000694 effects Effects 0.000 abstract description 3
- 239000003507 refrigerant Substances 0.000 description 12
- 238000004378 air conditioning Methods 0.000 description 7
- 230000008569 process Effects 0.000 description 4
- 238000010586 diagram Methods 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 239000007788 liquid Substances 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 238000005057 refrigeration Methods 0.000 description 2
- 230000007704 transition Effects 0.000 description 2
- 230000002776 aggregation Effects 0.000 description 1
- 238000004220 aggregation Methods 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000005265 energy consumption Methods 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
- 230000036541 health Effects 0.000 description 1
- 238000000746 purification Methods 0.000 description 1
- 238000009423 ventilation Methods 0.000 description 1
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Classifications
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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
- F24F3/1405—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 in which the humidity of the air is exclusively affected by contact with the evaporator of a closed-circuit cooling system or heat pump circuit
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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
- F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
- F24F11/46—Improving electric energy efficiency or saving
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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
- F24F11/64—Electronic processing using pre-stored data
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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
- F24F11/70—Control systems characterised by their outputs; Constructional details thereof
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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
- F24F12/00—Use of energy recovery systems in air conditioning, ventilation or screening
- F24F12/001—Use of energy recovery systems in air conditioning, ventilation or screening with heat-exchange between supplied and exhausted air
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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
- F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
- F24F13/08—Air-flow control members, e.g. louvres, grilles, flaps or guide plates
- F24F13/10—Air-flow control members, e.g. louvres, grilles, flaps or guide plates movable, e.g. dampers
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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
- F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
- F24F13/30—Arrangement or mounting of heat-exchangers
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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
- F24F2110/00—Control inputs relating to air properties
- F24F2110/10—Temperature
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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
- F24F2110/00—Control inputs relating to air properties
- F24F2110/20—Humidity
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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
- F24F2110/00—Control inputs relating to air properties
- F24F2110/50—Air quality properties
- F24F2110/65—Concentration of specific substances or contaminants
- F24F2110/70—Carbon dioxide
Abstract
The invention relates to a heat pump heat recovery type fresh air dehumidifier with a total heat exchanger and a control method thereof, wherein the invention comprises a shell, a heat pump heat recovery system and a total heat exchanger, wherein the heat pump heat recovery system and the total heat exchanger are arranged in the shell; an air supply fan is arranged at the air supply air port, and an air exhaust fan is arranged at the air exhaust air port; the total heat exchanger is connected with the shell through 4 partition plates, and 4 exchange ports of the total heat exchanger can be coupled with an exhaust flow path and an air supply flow path; part of return air enters the air supply flow path through the air mixing air door and is mixed with fresh air passing through the evaporator of the heat pump heat recovery system, so that the air supply quantity is increased, the condensation temperature and the air supply temperature are reduced, and the energy efficiency and the dehumidification quantity of the system are improved. Compared with the prior art, the air mixing damper achieves a remarkable effect by means of simple components combined with ingenious structural design, and solves the problems of limited air supply quantity, low energy efficiency, less dehumidification quantity, high air supply temperature and the like of the existing fresh air system, and is economical and effective.
Description
Technical Field
The invention relates to a fresh air dehumidifier, in particular to an integral heat pump heat recovery type fresh air dehumidifier with a total heat exchanger and a control method thereof.
Background
Fresh air is fed indoors, and the fresh air supply device has important significance for human health. Modern many buildings, especially residential buildings, are beginning to incorporate fresh air conditioning systems to improve indoor air quality. However, if the fresh air is directly sent to the air conditioning area without any treatment, the load of the air conditioning system is necessarily increased. In order to increase little or no indoor load, the fresh air is sent to the air conditioning area after a certain treatment, so that a fresh air fan is generated.
The total heat recovery fresh air blower performs total heat recovery (namely temperature and humidity exchange) on the introduced outdoor fresh air and the discharged indoor return air, and the indoor exhaust temperature is used for preheating or precooling the outdoor fresh air to reduce the cold and hot load of the fresh air, so that the effect of reducing the indoor load is achieved. The technology is widely focused by people with the advantages of no pollution, low energy consumption, wide application range and the like. However, with the further expansion of the market of the new fan in the household field, the housing and urban and rural construction department draw forth the relevant national standard of the household type new fan dehumidifier, namely the household type new fan dehumidifier (request opinion manuscript). The new national standard puts higher demands on the dehumidifying capacity and the air supply temperature of the household fresh air machine.
In recent years, heat pump technology has been proposed for use in fresh air machines. The heat pump type fresh air fan is used for carrying out deep cooling and dehumidification treatment on the fresh air after precooling of the total heat exchanger. Therefore, compared with the traditional fresh air machine, the heat pump type fresh air machine improves the dehumidification capacity of the system. However, the existing heat pump type fresh air fan has some defects, and the fresh air quantity passing through the condenser is smaller after the evaporator is cooled and dehumidified due to the limitation of the air quantity of the supplied air. The air quantity passing through the condenser is smaller under the refrigeration working condition, condensation heat is gathered, the condensation temperature is higher, the air supply temperature is also improved, and a larger heat and humidity load is brought indoors. Meanwhile, when the condensing temperature is too high, the compressor can start high-pressure protection, so that the current heat pump type fresh air machine is insufficient in dehumidification capability, high in air supply temperature and particularly incapable of operating normally in summer at high temperature.
Disclosure of Invention
The invention aims to provide a heat pump heat recovery type fresh air dehumidifier with a total heat exchanger and a control method thereof, so that the air is deeply dehumidified while the air outlet temperature is ensured.
The aim of the invention can be achieved by the following technical scheme:
the first object of the invention is to provide a heat pump heat recovery type fresh air dehumidifier with a total heat exchanger, which comprises a shell, a heat pump heat recovery system and the total heat exchanger, wherein the heat pump heat recovery system and the total heat exchanger are arranged in the shell;
an air supply air port and an air return air port are arranged on one side of the shell, and an air exhaust air port and an air inlet air port are arranged on the other side of the shell, so that an air flow path of the coupling heat pump heat recovery system respectively forms an air exhaust flow path and an air supply flow path;
an air supply fan is arranged at the air supply air port, and an air exhaust fan is arranged at the air exhaust air port;
the total heat exchanger is connected with the shell through 4 partition plates, and 4 exchange ports of the total heat exchanger can be coupled with an exhaust flow path and an air supply flow path;
among the 4 division boards, the first division board is provided with an openable air mixing air door, partial return air enters an air supply flow path through the air mixing air door and is mixed with fresh air passing through an evaporator of the heat pump heat recovery system, and the air supply air quantity is increased, so that the condensation temperature and the air supply temperature are reduced, and the energy efficiency and the dehumidification capacity of the system are improved.
Further, in the 4 division plates, a bypass air door capable of being opened and closed is arranged on the second division plate, and outdoor fresh air is directly fed into a room through the bypass air door without passing through the total heat exchanger, so that the power consumption of the fan is reduced.
Further, the 4 exchange ports of the total heat exchanger are respectively inclined towards the air supply port, the air return port, the air inlet port and the air exhaust port.
Further, among the 4 partition plates, the first partition plate, the second partition plate, the third partition plate and the fourth partition plate are distributed counterclockwise, so that 4 exchange ports of the total heat exchanger are separated.
Further, the heat pump heat recovery system comprises a compressor, a condenser, a throttling device and an evaporator which are connected in sequence.
Further, an openable return air door is arranged at the return air port;
further, the return air port and the supply air port are respectively provided with a return air sensor and a supply air temperature and humidity sensor. Wherein the return air sensor can detect the temperature, humidity and CO in the return air 2 The concentration is detected, and the temperature and humidity in the air supply can be detected by the air supply temperature and humidity sensor.
Further, a wind mixing air door which can be communicated with the air return air port of the exhaust flow path and the air supply port of the air supply flow path is arranged between the air return air port and the air supply port of the air supply flow path;
a bypass air door which can be communicated with the air return opening of the air exhaust flow path and the air inlet opening of the air supply flow path is arranged between the air return opening and the air inlet opening of the air supply flow path.
Further, an exhaust fan and an air supply fan are respectively arranged at the exhaust air port of the exhaust flow path and the air supply air port of the air supply flow path.
Further, the refrigerant loop comprises a compressor, a condenser, a throttling device and an evaporator which are connected in sequence.
Further, the throttling device can be a refrigerating system throttling device such as a capillary tube, a short tube or an electronic expansion valve;
the return air port, the exhaust fan and the exhaust air port are arranged in the exhaust flow path.
Further, the air inlet, the air filter, the evaporator, the condenser, the compressor, the throttling device, the air supply fan and the air supply port are arranged in the air supply flow path.
Further, a total heat exchanger is arranged at the intersection of the exhaust flow path and the air supply flow path.
Further, the air filters are respectively arranged at the positions in the air supply flow path before the total heat exchanger and at the air supply port.
Further, in the technical scheme, the air mixing air door and the bypass air door are servo driving air doors.
Further, the automatic control system also comprises a controller which is respectively and electrically connected with the controllable components such as the air door, the sensor, the fan, the compressor and the like, thereby being used for an automatic control process.
Further, the controller is a single chip microcomputer or one of an x86 architecture, an ARM architecture and a RISC-V architecture processor.
The second object of the present invention is to provide a control method of the heat pump heat recovery type fresh air dehumidifier with a total heat exchanger, comprising: under the dehumidification working condition, the dehumidification capacity is adjusted by changing the rotation speed of the compressor, when the humidity measured at the return air port is higher than a set value, the rotation speed of the compressor is increased, and otherwise, the rotation speed of the compressor is reduced.
Further, the method further comprises the steps of controlling the air suction superheat degree through the throttling device, and increasing the opening of the throttling device when the air suction superheat degree is higher than a set value, otherwise, decreasing the opening;
the indoor air quality is regulated by an air supply fan, and when the indoor CO is measured 2 When the concentration or VOC concentration is higher than the set value, the rotating speed of the air supply fan is increased to improve the fresh air quantity, otherwise, the rotating speed of the air supply fan is decreased to reduce the fresh air quantity.
Further, the indoor positive pressure of the air-conditioning room is controlled by linking the air exhaust fan with the air supply fan, so that the air exhaust amount is 80% -90% of the fresh air amount, and the condensation temperature is reduced and the dehumidifying energy efficiency is improved by the fact that the ratio of the air return amount of the air mixing door to the fresh air amount is about 1:1.
Further, the method also comprises the steps of closing the compressor, the exhaust fan and the return air door under the working conditions that the temperature difference between the inside and the outside is smaller than the threshold value and the dehumidification load is smaller than the threshold value in transitional seasons, opening the air supply fan, the air mixing air door and the bypass air door, and directly sending outdoor fresh air into a room after filtering without passing through the total heat exchanger through the bypass air door.
Specifically, the main working process of the technical scheme is as follows: under the dehumidifying working condition, the refrigerant in the evaporator evaporates and absorbs heat to be low-pressure steam, is sucked by the compressor, compressed into high-temperature and high-pressure refrigerant gas, enters the condenser to be condensed into low-temperature and high-pressure refrigerant, is throttled by the throttling device, becomes low-temperature and low-pressure refrigerant liquid again, and returns to the evaporator. The indoor return air is divided into two parts after being introduced from the return air opening, one part is arranged in the total heat exchanger through an exhaust flow path and is exhausted to the outside from the exhaust air opening under the driving of an exhaust fan after heat-moisture exchange with outdoor fresh air. And the other part of the fresh air enters the air supply flow path from the air mixing air door and is mixed with the fresh air after being purified by the filter, subjected to heat-moisture exchange by the total heat exchanger and deeply dehumidified by the evaporator, and the fresh air with proper temperature is sent into a room from the air supply air port after the excessive condensation heat of the refrigerant is taken away by the condenser under the driving of the air supply fan. At this time, the air quantity through the condenser is increased compared with that of the fresh air which is singly used, and the condensation temperature can be effectively reduced.
Specifically, the main control method of the technical scheme comprises the following steps: under the dehumidification working condition, the dehumidification capacity is adjusted by changing the rotation speed of the compressor, when the humidity measured at the return air port is higher than a set value, the rotation speed of the compressor is increased, and otherwise, the rotation speed of the compressor is reduced. And controlling the air suction superheat degree through the throttling device, and increasing the opening of the throttling device when the air suction superheat degree is higher than a set value, otherwise, reducing the opening. The indoor air quality is regulated by an air supply fan, and when the indoor CO is measured 2 The concentration or VOC concentration is higher than the set value, the rotating speed of the air supply fan is increased to improve the fresh air quantity, otherwise, the rotating speed of the air supply fan is reduced to reduce the fresh air quantity. The air exhaust fan is linked with the air supply fan to ensure that the air exhaust quantity is 80% -90% of the fresh air quantity so as to control the indoor positive pressure of an air-conditioning room, and the ratio of the air return quantity to the fresh air quantity through the air mixing door is about 1:1 so as to reduce the air return quantityLow condensing temperature, improved dehumidifying energy efficiency and reaching the aim of dehumidifying. Under the working condition, an air supply fan, an air exhaust fan and a compressor in the unit are all started, the air mixing air door and the air return air door are opened, and the bypass air door is closed. Under variable conditions, control can be achieved by changing the state of the component. For example, under the low environment working condition (the temperature of the air inlet dry bulb is 16 ℃/wet bulb is 14 ℃), the compressor, the air mixing air door and the bypass air door can be closed, outdoor fresh air is introduced from the air inlet, and is filtered through the air filter under the driving of the air supply fan, heat and humidity exchange is carried out between the fresh air and return air in the total heat exchanger, and after the fresh air is cooled and dehumidified, the fresh air is sent into a room through the air supply air inlet. In the transition season, when the temperature difference between the inside and the outside is not large and the dehumidification load is low, the compressor, the exhaust fan and the return air door can be closed, the air supply fan, the air mixing door and the bypass door are opened, and outdoor fresh air is directly fed into a room after being filtered through the bypass door without a total heat exchanger.
The core innovation features of the invention are as follows:
1. the air mixing air door is arranged, and by opening the air mixing air door, a part of return air can enter the air supply flow path through the air mixing air door and is mixed with fresh air passing through the evaporator and then is sent into a room. The problems of low energy efficiency and high air supply temperature of the system due to condensation heat aggregation are avoided.
2. The air conditioner is provided with a bypass air door, and the introduced outdoor fresh air can directly pass through the bypass air door without a total heat exchanger by opening the air supply fan, the air mixing air door and the bypass air door, and is filtered and then sent into a room to purify indoor air.
Compared with the prior art, the invention has the following technical advantages:
1. the air mixing air door is arranged in the technical scheme, and part of return air can enter the air supply flow path through the air mixing air door and is mixed with fresh air passing through the evaporator, so that the air supply quantity is increased, the condensation temperature and the air supply temperature are reduced, and the energy efficiency and the dehumidification quantity of the system are improved. The setting of this air mixing air door utilizes simple part to combine ingenious structural design to have reached showing the effect, has solved current fresh air system air supply amount of wind limited, and the energy efficiency is lower, and the dehumidification volume is less, and air supply temperature is higher scheduling problem, both economical and effective.
2. According to the technical scheme, the fresh air dehumidifying unit has a bypass function, and free refrigeration and ventilation are carried out when the transition season and the outdoor working condition are proper.
Drawings
FIG. 1 is a schematic diagram of the structure of an integral heat pump heat recovery type fresh air dehumidifier with a total heat exchanger;
FIGS. 2-4 are schematic flow diagrams of the integral heat pump heat recovery type fresh air dehumidifier with the total heat exchanger in the invention under the dehumidifying working condition, the low-environment working condition and the bypass mode respectively;
in the figure: 1-a compressor; a 2-condenser; 3-an evaporator; 4-throttling means; 5-an air supply fan; 6-an exhaust fan; 7-a total heat exchanger; 8-9-an air filter; 10-an air inlet; 11-an exhaust air port; 12-an air supply port; 13-an air return port; 14-a return air door; 15-a wind mixing air door; 16-bypass damper; 17-an air supply temperature and humidity sensor; 18-a return air sensor; 19-an air supply flow path; 20-an exhaust flow path; 21-24-connecting pipe.
Detailed Description
The invention will now be described in detail with reference to the drawings and specific examples. In the technical scheme, the characteristics such as the names of structures/modules, control modes, algorithms, process procedures or composition ratios and the like which are not explicitly described are regarded as common technical characteristics disclosed in the prior art.
In specific implementation, the heat pump heat recovery type fresh air dehumidifier with the total heat exchanger comprises a shell, a heat pump heat recovery system and a total heat exchanger 7, wherein the heat pump heat recovery system and the total heat exchanger 7 are arranged in the shell; one side of the machine shell is provided with an air supply air port 12 and an air return air port 13, and the other side is provided with an air exhaust air port 11 and an air inlet air port 10, so that an air flow path of the coupling heat pump heat recovery system respectively forms an air exhaust flow path 20 and an air supply flow path 19.
The structure and flow path are as shown in fig. 2, and the main structure comprises a shell, a compressor 1, a condenser 2, an evaporator 3, a throttling device 4, an air supply fan 5, an air exhaust fan 6, a total heat exchanger 7, air filters 8-9, an air inlet 10, an air exhaust opening 11, an air supply opening 12, an air return opening 13, an air return opening 14, an air mixing opening 15, a bypass opening 16, an air supply temperature and humidity sensor 17, an air return air sensor 18, an air supply flow path 19, an air exhaust flow path 20 and connecting pipes 21-24.
An air supply fan 5 is arranged at the air supply air port 12, and an air exhaust fan 6 is arranged at the air exhaust air port 11; the total heat exchanger 7 is connected with the shell through 4 partition plates, and 4 exchange ports of the total heat exchanger 7 can be coupled with an exhaust flow path 20 and an air supply flow path 19; among the 4 division plates, the first division plate is provided with an openable air mixing air door 15, part of return air enters an air supply flow path 19 through the air mixing air door 15 and is mixed with fresh air passing through an evaporator of the heat pump heat recovery system, so that the air supply quantity is increased, the condensation temperature and the air supply temperature are reduced, and the energy efficiency and the dehumidification capacity of the system are improved.
In the 4 partition plates, a bypass air door 16 capable of being opened and closed is arranged on the second partition plate, and outdoor fresh air is directly fed into a room through the bypass air door 16 without passing through the total heat exchanger 7, so that the power consumption of a fan is reduced. The 4 exchange ports of the total heat exchanger 7 are respectively inclined towards the air supply port 12, the air return port 13, the air inlet port 10 and the air exhaust port 11. Among the 4 partition plates, the first partition plate, the second partition plate, the third partition plate and the fourth partition plate are distributed counterclockwise, so that the 4 exchange ports of the total heat exchanger 7 are separated.
The heat pump heat recovery system comprises a compressor 1, a condenser 2, a throttling device 4 and an evaporator 3 which are connected in sequence. The air return air inlet 13 is provided with an openable air return air door 14; the return air port 13 and the supply air port 12 are respectively provided with a return air sensor 18 and a supply air temperature and humidity sensor 17.
The main working process (see fig. 2) of the unit of this embodiment is that under the dehumidification condition:
the refrigerant flow path state is: the refrigerant in the evaporator 3 absorbs heat to be low-pressure steam by evaporation, is sucked by the compressor 1, is compressed into high-temperature high-pressure refrigerant gas, enters the condenser 2 to be condensed into low-temperature high-pressure refrigerant, is throttled by the throttling device 4, is changed into low-temperature low-pressure refrigerant liquid again, and returns to the evaporator 3.
The air flow path state is: the indoor return air is led in from the return air door 14 and then is divided into two parts, one part is in the total heat exchanger 7 through the exhaust flow path 20, and is discharged to the outside from the exhaust air port 11 under the drive of the exhaust fan 6 after heat-moisture exchange with the outdoor fresh air. The other part of the fresh air enters the air supply flow path 19 from the air mixing air door 15, is mixed with the fresh air after the heat and humidity exchange of the air filter purification 8 and the total heat exchanger 7 and the deep dehumidification of the evaporator 3, and is driven by the air supply fan 5 to take away the superfluous condensation heat of the refrigerant through the condenser 2, and then the fresh air with proper temperature is sent into a room from the air supply air port 12. At this time, the air quantity through the condenser 2 is increased compared with that of the fresh air alone, so that the condensing temperature can be effectively reduced.
In the dehumidification mode, the main control method of the unit is as follows:
under the dehumidification working condition, the dehumidification capacity is adjusted by changing the rotation speed of the compressor 1, when the humidity measured at the return air door 14 is higher than a set value, the rotation speed of the compressor 1 is increased, and otherwise, the rotation speed of the compressor 1 is reduced.
The suction superheat degree is controlled by the throttling device 4, and when the suction superheat degree is higher than a set value, the opening of the throttling device 4 is increased, and otherwise, the opening is reduced.
The indoor air quality is regulated by the air supply fan 5, and when the indoor CO is measured 2 The concentration or VOC concentration is higher than the set value, the rotation speed of the air supply fan 5 is increased to improve the fresh air quantity, and otherwise, the rotation speed of the air supply fan 5 is reduced to reduce the fresh air quantity.
The air exhaust fan 6 is linked with the air supply fan 5 to ensure that the air exhaust quantity is 80% -90% of the fresh air quantity so as to control the indoor positive pressure of an air-conditioning room, and the ratio of the air return quantity to the fresh air quantity through the air mixing door is about 1:1 so as to reduce the condensation temperature, improve the dehumidifying energy efficiency and achieve the aim of dehumidifying.
Under the working condition, the air supply fan 5, the air exhaust fan 6 and the compressor 1 in the unit are all opened, the air mixing damper 15 and the air return damper 14 are opened, and the bypass damper 16 is closed. Under variable conditions, control can be achieved by changing the state of the component.
For example, under the low environment working condition (the air inlet dry bulb temperature is 16 ℃/wet bulb temperature is 14 ℃), the state of the unit components and the state of the flow path are shown in fig. 3, the compressor 1, the air mixing air door 15 and the bypass air door 16 can be closed, outdoor fresh air is introduced from the air inlet 10, is purified by the air filter 8 under the driving of the air supply fan 5, performs heat-humidity exchange with return air in the total heat exchanger 7, and is sent into a room through the air supply air port 12 after the fresh air is cooled and dehumidified.
In the transitional season, under the working conditions of small temperature difference between the inside and the outside and low dehumidification load, the state of the unit components and the state of the flow path are shown in fig. 4, the compressor 1, the exhaust fan 6 and the return air door 14 can be closed, the air supply fan 5, the air mixing door 15 and the bypass air door 16 are opened, and outdoor fresh air is directly sent into a room after being filtered through the bypass air door 16 without passing through the total heat exchanger 7.
The previous description of the embodiments is provided to facilitate a person of ordinary skill in the art in order to make and use the present invention. It will be apparent to those skilled in the art that various modifications can be readily made to these embodiments 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-described embodiments, and those skilled in the art, based on the present disclosure, should make improvements and modifications without departing from the scope of the present invention.
Claims (10)
1. The heat pump heat recovery type fresh air dehumidifier with the total heat exchanger is characterized by comprising a shell, a heat pump heat recovery system and a total heat exchanger (7), wherein the heat pump heat recovery system and the total heat exchanger are arranged in the shell;
an air supply air port (12) and an air return air port (13) are arranged on one side of the shell, and an air exhaust air port (11) and an air inlet air port (10) are arranged on the other side of the shell, so that an air flow path of the coupling heat pump heat recovery system respectively forms an air exhaust flow path (20) and an air supply flow path (19);
an air supply fan (5) is arranged at the air supply air port (12), and an air exhaust fan (6) is arranged at the air exhaust air port (11);
the total heat exchanger (7) is connected with the shell through 4 partition plates, and 4 exchange ports of the total heat exchanger (7) can be coupled with an exhaust flow path (20) and an air supply flow path (19);
among the 4 division boards, be equipped with on the first division board and mix wind air door (15) that can open and shut, part return air gets into air supply flow path (19) through mix wind air door (15), mixes with the new trend through heat pump heat recovery system evaporimeter, increases the air supply amount of wind to this reduces condensation temperature and air supply temperature, improves system efficiency and dehumidification volume.
2. The heat pump heat recovery type fresh air dehumidifier with the total heat exchanger according to claim 1, wherein the second partition plate of the 4 partition plates is provided with a bypass air door (16) which can be opened and closed, and outdoor fresh air is directly sent into a room through the bypass air door (16) without passing through the total heat exchanger (7), so that the power consumption of a fan is reduced.
3. The heat pump heat recovery type fresh air dehumidifier with the total heat exchanger according to claim 2, wherein the 4 exchange ports of the total heat exchanger (7) are respectively inclined towards the air supply port (12), the air return port (13), the air inlet port (10) and the air exhaust port (11).
4. A heat pump heat recovery type fresh air dehumidifier with a total heat exchanger according to claim 3, wherein among 4 partition plates, the first partition plate, the second partition plate, the third partition plate and the fourth partition plate are distributed counterclockwise, thereby realizing the separation of 4 exchange ports of the total heat exchanger (7).
5. The heat pump heat recovery type fresh air dehumidifier with the total heat exchanger according to claim 4, wherein the heat pump heat recovery system comprises a compressor (1), a condenser (2), a throttling device (4) and an evaporator (3) which are connected in sequence.
6. The heat pump heat recovery type fresh air dehumidifier with total heat exchanger according to claim 4, wherein the return air inlet (13) is provided with an openable return air door (14);
the return air port (13) and the air supply port (12) are respectively provided with a return air sensor (18) and an air supply temperature and humidity sensor (17).
7. A control method of a heat pump heat recovery type fresh air dehumidifier with a total heat exchanger according to any one of claims 1 to 6, comprising: under the dehumidification working condition, the dehumidification capacity is adjusted by changing the rotating speed of the compressor (1), when the humidity measured at the return air inlet (13) is higher than a set value, the rotating speed of the compressor is increased, and otherwise, the rotating speed of the compressor is reduced.
8. The method for controlling a heat pump heat recovery type fresh air dehumidifier with a total heat exchanger according to claim 7, further comprising controlling a suction superheat degree through a throttle device (4), increasing an opening degree of the throttle device (4) when the suction superheat degree is higher than a set value, and decreasing the opening degree in the opposite direction;
the indoor air quality is regulated by an air supply fan (5), and the indoor CO is measured 2 When the concentration or VOC concentration is higher than the set value, the rotating speed of the air supply fan (5) is increased to increase the fresh air quantity, otherwise, the rotating speed of the air supply fan (5) is decreased to decrease the fresh air quantity.
9. The control method of a heat pump heat recovery type fresh air dehumidifier with a total heat exchanger according to claim 7, further comprising the steps of controlling the indoor positive pressure of an air-conditioned room by linking an exhaust fan (6) with an air supply fan (5) so that the exhaust air quantity is 80% -90% of the fresh air quantity, and reducing the condensation temperature and improving the dehumidifying energy efficiency by controlling the ratio of the return air quantity of an air mixing door to the fresh air quantity to be about 1:1.
10. The method for controlling a heat pump heat recovery type fresh air dehumidifier with a total heat exchanger according to claim 7, further comprising closing the compressor (1), the exhaust fan (6) and the return air door (14) and opening the supply fan (5), the air mixing door (15) and the bypass door (16) under the working conditions that the temperature difference between the inside and the outside is smaller than a threshold value and the dehumidification load is smaller than the threshold value in a transitional season, and directly passing outdoor fresh air through the bypass door (16) without passing through the total heat exchanger (7), and filtering the fresh air into a room.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202211102618.XA CN116293959A (en) | 2022-09-09 | 2022-09-09 | Heat pump heat recovery type fresh air dehumidifier with total heat exchanger and control method thereof |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202211102618.XA CN116293959A (en) | 2022-09-09 | 2022-09-09 | Heat pump heat recovery type fresh air dehumidifier with total heat exchanger and control method thereof |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN116518701A (en) * | 2023-07-05 | 2023-08-01 | 中建环能科技股份有限公司 | Method for improving dehumidification performance of evaporator of heat pump low-temperature drying equipment and electronic equipment |
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2022
- 2022-09-09 CN CN202211102618.XA patent/CN116293959A/en active Pending
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN116518701A (en) * | 2023-07-05 | 2023-08-01 | 中建环能科技股份有限公司 | Method for improving dehumidification performance of evaporator of heat pump low-temperature drying equipment and electronic equipment |
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