CN112377998A

CN112377998A - All-condition heat pump heat recovery type fresh air fan with multiple reheating modes

Info

Publication number: CN112377998A
Application number: CN202011216770.1A
Authority: CN
Inventors: 曹祥; 成家豪; 张春路
Original assignee: Tongji University
Current assignee: Tongji University
Priority date: 2020-11-04
Filing date: 2020-11-04
Publication date: 2021-02-19
Anticipated expiration: 2040-11-04
Also published as: CN112377998B

Abstract

The invention relates to a full-working-condition heat pump heat recovery type fresh air fan with multiple reheating modes, wherein a reheating coil and a bypass pipeline are specially arranged in the fresh air fan, the fresh air can be reheated by using the condensation heat and/or the supercooling heat of a refrigerant in a steam compression cycle through opening and closing of an air door and flow path conversion, and multiple reheating modes such as supercooling reheating, condensation reheating, semi-condensation reheating and the like are provided for a unit to select under different loads of a refrigeration and dehumidification mode in summer, so that the outlet air temperature can be ensured to be higher than a set value. Compared with the prior art, the air outlet temperature of the fresh air dehumidifier can be adjusted as required under different loads in summer, and the requirement on the air outlet temperature can be always met, particularly the requirement that the air outlet temperature of the fresh air dehumidifier is not lower than 22 ℃ in the new national standard; the heat pump heat recovery type fresh air fan can carry out pertinence and comprehensive matching on the annual working condition, can realize up to 14 operation modes including refrigeration and dehumidification in summer, heating in winter and internal circulation in transition seasons, and is more suitable for the requirement of household type annual fresh air supply.

Description

All-condition heat pump heat recovery type fresh air fan with multiple reheating modes

Technical Field

The invention relates to an integral fresh air fan, in particular to an all-working-condition heat pump heat recovery type fresh air fan with a multi-reheating mode.

Background

Many modern buildings, especially residential buildings, are beginning to introduce new air conditioning systems to improve indoor air quality. With the further expansion of the new fans in the household market, the housing and urban and rural construction departments have involved making up the relevant national standards of the household fresh air dehumidifier, namely, "household fresh air dehumidifier (request for comments and drawings"). The new national standard puts higher requirements on the household new fan in the aspects of fresh air filtration, refrigeration (heating), dehumidification and the like, and especially provides that the air supply temperature in summer is not lower than 22 ℃. The current products on the market can hardly meet the standard.

A heat pump type fresh air heat recovery technology is a novel active heat recovery technology, limited electric energy is used in the technology, and cold (heat) quantity of exhaust air is recovered through thermodynamic circulation of a refrigerant. The heat pump heat recovery type fresh air machine can improve the indoor air quality and simultaneously reduce the energy consumption of an air conditioning system, and is a fresh air dehumidifier with energy conservation and economy.

The new national standard also provides numerous challenges to the design of new fan when standardizing the product efficiency, promoting user's comfort level, and the ubiquitous problem of new fan of heat recovery type of present heat pump lies in: (1) the working conditions are limited, most of the working conditions provide simple fresh air and dehumidification modes, and the full coverage of the working conditions of fresh air refrigeration, heating, dehumidification and internal circulation crossing different seasons is difficult to realize; (2) the comfort level is not good enough, the air supply temperature is low in summer, and the temperature is difficult to be ensured to be over 22 ℃. Meanwhile, different loads are not distinguished, and the air supply temperature is too low under the condition of low load for a unit designed for high load. If auxiliary electric heating is adopted, the structure is complex, the cost is increased, and the energy efficiency is reduced.

To solve the above problem (1), for example, patent CN201911412579.1 discloses an integrated fresh air dehumidifier, in which a refrigeration cycle is provided with three coils of a dehumidification evaporator, a dehumidification condenser and a balance condenser, and a fresh air mode and a dehumidification mode can be realized by switching flow channels, but there is no corresponding working mode in transitional seasons and winter, and it is not suitable for fresh air supply all the year round.

To solve the above problem (2), for example, patent CN202010522451.7 discloses a total heat fresh air dehumidification and purification integrated machine, in which two coils of an evaporator and a condenser are arranged in a refrigeration cycle, and three modes of fresh air dehumidification, fresh air dehumidification and internal circulation can be realized by switching flow channels; patent CN109000312A proposes an integral heat pump heat recovery type fresh air dehumidifier with an internal circulation mode, in which a refrigeration cycle is provided with three coils of an air supply coil, an air exhaust coil and a supercooling coil, and the dehumidifier can have an internal circulation mode, a refrigeration dehumidification mode and a heating mode by switching channels; patent CN201910949050.7 has proposed a kind of exhaust heat recovery type new trend dehumidifier, is equipped with three coil pipes of evaporimeter, first condenser and second condenser in the refrigeration cycle, can have dehumidification and heating mode through the runner switching. The above-mentioned patent does not all distinguish different loads under the dehumidification operating mode in summer, and the new trend directly sends into indoor after the evaporimeter cooling dehumidification. This practice results in the supply air temperature not meeting the new national standard requirements of no less than 22 c when the indoor load is low in summer. The lower new trend of temperature gets into indoor easily to cause the sensation of blowing, and human travelling comfort is relatively poor.

Disclosure of Invention

The invention aims to overcome the defects of the prior art and provide the full-working-condition heat pump heat recovery type fresh air fan with a multi-reheating mode, so that different requirements of refrigeration and dehumidification in summer, heating in winter and internal circulation in transition seasons are met, fresh air supply in different seasons is realized, and various working conditions in the whole year are covered.

The invention is characterized in that a reheating coil and a bypass pipeline are also specially arranged outside the air supply coil, the air exhaust coil and the supercooling coil, the fresh air can be reheated by selecting the condensation heat and/or the supercooling heat of the refrigerant in the steam compression cycle through the opening and closing of the air door and the conversion of the flow path, and the invention has various reheating modes such as supercooling reheating, condensation reheating, semi-condensation reheating and the like, is used for selecting the units under different loads of a refrigeration and dehumidification mode in summer, and can ensure that the air outlet temperature is higher than a set value (for example, 22 ℃ of the new national standard).

The purpose of the invention can be realized by the following technical scheme:

the invention relates to a full-working-condition heat pump heat recovery type fresh air fan with a multi-reheating mode, which comprises a first air duct, a second air duct and a refrigerant loop;

the first air duct is provided with an air return air port and an air exhaust air port;

an air supply port and a fresh air port are arranged on the second air duct;

a wind mixing air door capable of communicating the first air duct and the second air duct is arranged between the first air duct and the second air duct;

an air exhaust fan and an air supply fan are respectively arranged at the air exhaust air port of the first air duct and the air supply air port of the second air duct;

the refrigerant loop comprises a compressor, a four-way reversing valve, an exhaust coil, a supercooling coil, a first throttling device, a reheating coil, a second throttling device and an air supply coil which are connected in sequence;

the refrigerant loop is also provided with a first bypass loop and a second bypass loop, and a first stop valve and a second stop valve are respectively arranged on the first bypass loop and the second bypass loop;

the first bypass loop is connected with the exhaust coil and the supercooling coil in parallel, one end of the first bypass loop is communicated with an exhaust port of the compressor through a four-way reversing valve, and the other end of the first bypass loop is communicated with the reheating coil through a first throttling device;

the second bypass circuit is connected with the supercooling coil in parallel, one end of the second bypass circuit is communicated with a refrigerant outlet of the exhaust coil, and the other end of the second bypass circuit is communicated with the reheating coil through a first throttling device;

the exhaust coil, the supercooling coil, the first bypass loop, the second bypass loop and the first stop valve and the second stop valve on the first bypass loop are arranged in the first air channel;

the first throttling device, the reheating coil, the second throttling device, the air supply coil, the four-way reversing valve and the compressor are arranged in the second air channel.

Furthermore, four interfaces of the four-way reversing valve are respectively connected with the exhaust coil, the air suction port of the compressor, the air supply coil and the exhaust port of the compressor.

The first throttling device and the second throttling device in the technical scheme are both one of a capillary tube, a throttling short pipe or an electronic expansion valve, and the electronic expansion valve is preferably selected in the technical scheme, so that the automatic control is favorably realized.

The first stop valve and the second stop valve in the technical scheme are preferably electromagnetic valves, are suitable for a high-temperature exhaust environment, and are favorable for realizing automatic control.

In the technical scheme, the first air duct and the second air duct are equal-diameter and equal-length air ducts which are arranged in parallel;

the air return air inlet and the air exhaust air inlet are respectively arranged at two ends of the first air duct;

and the air supply air port and the fresh air port are respectively arranged at two ends of the second air channel.

In the technical scheme, the air mixing air door is arranged in the middle of the first air channel and the second air channel.

Further, the air mixing damper is a servo driving damper.

Furthermore, servo-driven air doors are arranged on the air return air port, the air exhaust air port, the air supply air port and the fresh air port.

Through the opening and closing of the air door and the switching of the flow path, the technical scheme can realize the following 14 operation modes (table 1):

1. summer refrigeration dehumidification mode (mixed wind-supercooled reheat): the air return air port, the air exhaust air port, the air supply air port and the fresh air port are all opened, and the air mixing air door is opened. The air exhaust fan and the air supply fan are both started. The first throttle device is kept normally open (equivalent to a connecting pipe), and the second throttle device is used for throttling. 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 supply coil pipe is communicated with the flow path of the air suction port of the compressor. First, the second stop valve is all closed, and the reheat coil pipe import is refrigerant liquid, adopts the hot reheat new trend of subcooling, adopts the subcooling reheat mode promptly.

2. Summer refrigeration dehumidification mode (mixed wind-condensation reheating): the states of the air port, the fan, the throttling device and the four-way reversing valve are consistent with a summer refrigeration and dehumidification mode (air mixing-supercooling reheating). The first stop valve is opened, and the second stop valve is closed, and the inlet of reheating coil pipe is refrigerant gas, adopts the hot new trend of condensation reheat, adopts the condensation reheat mode promptly.

3. Summer refrigeration dehumidification mode (mixed wind-semi-condensation reheating): the states of the air port, the fan, the throttling device and the four-way reversing valve are consistent with a summer refrigeration and dehumidification mode (air mixing-supercooling reheating). The second stop valve is opened, the first stop valve is opened or closed as required, the inlet of the reheating coil is in a refrigerant two-phase state, and the condensing heat and the supercooling heat reheating fresh air are adopted, namely, a semi-condensing reheating mode is adopted.

4. Summer refrigeration dehumidification mode (full return air-subcooling reheating): the air return air port, the air exhaust air port, the air supply air port and the fresh air port are all opened, and the air mixing air door is closed. The air exhaust fan and the air supply fan are both started. The first throttle device is kept normally open (equivalent to a connecting pipe), and the second throttle device is used for throttling. 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 supply coil pipe is communicated with the flow path of the air suction port of the compressor. The first and second stop valves are both closed.

5. Summer refrigeration dehumidification mode (full return air-condensation reheating): the states of the air port, the fan, the throttling device and the four-way reversing valve are consistent with a refrigeration and dehumidification mode (full return air-supercooling reheating) in summer. The first stop valve is opened and the second stop valve is closed.

6. Summer refrigeration dehumidification mode (full return air-semi-condensation reheating): the states of the air port, the fan, the throttling device and the four-way reversing valve are consistent with a refrigeration and dehumidification mode (full return air-supercooling reheating) in summer. The second stop valve is opened, and the first stop valve is opened or closed as required.

7. Summer refrigeration dehumidification mode (fresh air-supercooling reheating): the air return air port is closed, the air exhaust air port, the air supply air port and the fresh air port are all opened, and the air mixing air door is opened. The air exhaust fan and the air supply fan are both started. The first throttle device is kept normally open (equivalent to a connecting pipe), and the second throttle device is used for throttling. 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 supply coil pipe is communicated with the flow path of the air suction port of the compressor. The first and second stop valves are both closed.

8. Summer refrigeration dehumidification mode (fresh air-condensation reheating): the states of the air port, the fan, the throttling device and the four-way reversing valve are consistent with a summer refrigeration and dehumidification mode (fresh air-supercooling reheating). The first stop valve is opened and the second stop valve is closed.

9. Summer refrigeration dehumidification mode (full fresh air-semi-condensation reheating): the states of the air port, the fan, the throttling device and the four-way reversing valve are consistent with a summer refrigeration and dehumidification mode (fresh air-supercooling reheating). The second stop valve is opened, and the first stop valve is opened or closed as required.

10. Summer cooling dehumidification mode (single duct-condensing reheat): and the air return air port and the air exhaust air port are closed, the air supply air port and the fresh air port are opened, and the air mixing air door is closed. The air exhaust fan is closed, and the air supply fan is opened. The first throttle device is kept normally open (equivalent to a connecting pipe), and the second throttle device is used for throttling. 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 supply coil pipe is communicated with the flow path of the air suction port of the compressor. The first and second stop valves are both closed.

11. Winter heating mode (wind mixing): the air return air port, the air exhaust air port, the air supply air port and the fresh air port are all opened, and the air mixing air door is opened. The air exhaust fan and the air supply fan are both started. The first throttling device is used for throttling, and the second throttling device is kept normally open (equivalent to a connecting pipe). The air supply 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 exhaust coil pipe is communicated with the flow path of the air suction port of the compressor. The first and second stop valves are both closed.

12. Winter heating mode (full return air): the air return air port, the air exhaust air port, the air supply air port and the fresh air port are all opened, and the air mixing air door is closed. The states of the fan, the throttling device, the four-way reversing valve and the stop valve are consistent with the heating mode (mixed air) in winter.

13. Winter heating mode (full fresh air): the air return air port is closed, the air exhaust air port, the air supply air port and the fresh air port are all opened, and the air mixing air door is opened. The states of the fan, the throttling device, the four-way reversing valve and the stop valve are consistent with the heating mode (mixed air) in winter.

14. Transition season internal circulation mode: and the air exhaust air port and the fresh air port are closed, the air return air port and the air supply air port are opened, and the air mixing air door is opened. The air exhaust fan is closed, and the air supply fan is opened. The first throttling device is used for throttling, and the second throttling device is kept normally open (equivalent to a connecting pipe). The air supply 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 exhaust coil pipe is communicated with the flow path of the air suction port of the compressor. The first and second stop valves are both closed.

The 14 operating modes of the present solution are summarized in the following table.

TABLE 1

In the technical scheme, under a summer refrigeration and dehumidification mode (air mixing-supercooling reheating), a refrigerant in an air supply coil is evaporated 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 gas is condensed and released in an exhaust coil through the four-way reversing valve, further supercooled in a supercooling coil and a reheating coil, and throttled by a second throttling device to become a gas-liquid two-phase state and returns to the air supply coil. Outdoor new trend gets into the second wind channel from the new trend wind gap, takes away the partial heat that the compressor gived off, and the new trend divide into two parts afterwards: one part enters the first air channel through the air mixing damper; and one part of the air enters the room from the air supply port through the air supply fan after being cooled and dehumidified by the air supply coil and reheated by the reheating coil in the second air duct. Indoor return air enters the first air channel from the return air inlet, passes through the supercooling coil pipe, is mixed with part of fresh air entering the first air channel, and is exhausted outdoors from the exhaust air inlet through the exhaust fan after the heat is absorbed by the exhaust coil pipe.

In the technical scheme, under a summer refrigeration and dehumidification mode (air mixing-condensation reheating), a refrigerant in an air supply coil is evaporated 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 gas is shunted after passing through the four-way reversing valve, part of the refrigerant gas is condensed in an air exhaust coil and a supercooling coil, part of the refrigerant gas is condensed in the reheating coil to release heat, and refrigerant liquid coming out of the reheating coil is throttled by a second throttling device to become a gas-liquid two-phase state and returns to the air supply coil. The air flow form is consistent with a summer refrigeration and dehumidification mode (mixed air-supercooling reheating).

In the technical scheme, under a summer refrigeration dehumidification mode (mixed air-semi-condensation reheating), a refrigerant in an air supply coil is evaporated and absorbs heat to be changed into 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, all or part of the refrigerant gas flows through an air exhaust coil to become gas-liquid two-phase refrigerant and then is divided through the four-way reversing valve, part of the refrigerant gas is condensed in a supercooling coil, part of the refrigerant gas enters a reheating coil to be condensed and supercooled to release heat, and refrigerant liquid coming out of the reheating coil is throttled by a second throttling device to be changed into a gas-liquid two-phase state and returns to the air supply coil. The air flow form is consistent with a summer refrigeration and dehumidification mode (mixed air-supercooling reheating).

In the technical scheme, the all-working-condition heat pump heat recovery type fresh air fan with the multiple reheating modes has the advantages that under a summer refrigeration dehumidification mode (full return air-supercooling reheating), the flowing form of a refrigerant is consistent with that of the summer refrigeration dehumidification mode (mixed air-supercooling reheating). Outdoor new trend gets into the second wind channel from the new trend wind gap, takes away the partial heat that the compressor gived off, through air supply coil cooling dehumidification, through reheat coil reheat back, gets into indoorly from the air supply wind gap via air supply fan. Indoor return air enters the first air channel from the return air inlet, passes through the supercooling coil and the exhaust coil to absorb heat, and is exhausted outdoors from the exhaust air inlet through the exhaust fan.

In the technical scheme, the all-condition heat pump heat recovery type fresh air fan with the multiple reheating modes has the advantages that under a summer refrigeration dehumidification mode (full return air-condensation reheating), the flowing form of a refrigerant is consistent with the summer refrigeration dehumidification mode (mixed air-condensation reheating). The air flow pattern is consistent with the summer cooling and dehumidifying mode (full return air-overcooled reheating).

In the technical scheme, the all-condition heat pump heat recovery type fresh air fan with the multiple reheating modes has the advantages that under a summer refrigeration dehumidification mode (full return air-semi-condensation reheating), the flowing form of a refrigerant is consistent with the summer refrigeration dehumidification mode (mixed air-semi-condensation reheating). The air flow pattern is consistent with the summer cooling and dehumidifying mode (full return air-overcooled reheating).

In the technical scheme, the all-working-condition heat pump heat recovery type fresh air fan with the multiple reheating modes has the advantages that under a summer refrigeration and dehumidification mode (fresh air-supercooling reheating), the flowing form of a refrigerant is consistent with that of the summer refrigeration and dehumidification mode (mixed air-supercooling reheating). Outdoor new trend gets into the second wind channel from the new trend wind gap, takes away the partial heat that the compressor gived off, and the new trend divide into two parts afterwards: and one part of the air enters the room from the air supply port through the air supply fan after being cooled and dehumidified by the air supply coil and reheated by the reheating coil in the second air duct. One part enters the first air channel through the air mixing air door, absorbs heat through the exhaust coil pipe, and is exhausted outdoors from the exhaust air port through the exhaust fan.

In the technical scheme, the all-working-condition heat pump heat recovery type fresh air fan with the multiple reheating modes has the advantages that under a summer refrigeration and dehumidification mode (fresh air-condensation reheating), the flowing form of a refrigerant is consistent with the summer refrigeration and dehumidification mode (mixed air-condensation reheating). The air flow form is consistent with a summer refrigeration and dehumidification mode (fresh air-supercooling reheating).

In the technical scheme, the all-condition heat pump heat recovery type fresh air fan with the multiple reheating modes has the advantages that under a summer refrigeration dehumidification mode (full fresh air-semi-condensation reheating), the flowing form of a refrigerant is consistent with the summer refrigeration dehumidification mode (mixed air-semi-condensation reheating). The air flow form is consistent with a summer refrigeration and dehumidification mode (fresh air-supercooling reheating).

In the technical scheme, under a summer refrigeration and dehumidification mode (single air channel-condensation reheating), a refrigerant in an air supply coil is evaporated 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 gas flows through an exhaust coil and a supercooling coil through the four-way reversing valve, enters a reheating coil to be condensed and release heat, and is throttled by a second throttling device to become a gas-liquid two-phase state and returns to the air supply coil. Outdoor new trend gets into the second wind channel from the new trend wind gap, takes away the partial heat that the compressor gived off, through air supply coil cooling dehumidification, through reheat coil reheat back, gets into indoorly from the air supply wind gap via air supply fan.

In the technical scheme, under a winter heating mode (air mixing), refrigerants in a supercooling 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 and released in an air supply coil and a reheating coil through the four-way reversing valve, and the refrigerant gas is throttled by a first throttling device to become a gas-liquid two-phase state and returns to the supercooling coil. Outdoor new trend gets into the second wind channel from the new trend wind gap, takes away the partial heat that the compressor gived off, and the new trend divide into two parts afterwards: one part enters the first air channel through the air mixing damper; and one part of the air enters the room from the air supply port through the air supply fan after being heated continuously in the second air duct through the air supply coil and the reheating coil. Indoor return air enters the first air channel from the return air inlet, passes through the supercooling coil pipe, is mixed with part of fresh air entering the first air channel, is cooled by the exhaust coil pipe, and is exhausted outdoors from the exhaust air inlet through the exhaust fan.

In the technical scheme, the all-condition heat pump heat recovery type fresh air fan with the multiple reheating modes has the advantages that the flowing form of a refrigerant is consistent with that of a winter heating mode (mixed air) in the winter heating mode (full return air). Outdoor fresh air enters the second air channel from the fresh air inlet, takes away partial heat emitted by the compressor, and is heated by the air supply coil and the reheating coil and then is sent into a room. Indoor return air enters the first air channel from the return air inlet, is cooled by the supercooling coil and the exhaust coil, and is exhausted outdoors from the exhaust air inlet through the exhaust fan.

In the technical scheme, the all-condition heat pump heat recovery type fresh air fan with the multiple reheating modes has the advantages that the flowing form of the refrigerant is consistent with that of a winter heating mode (mixed air) in the winter heating mode (all fresh air). Outdoor new trend gets into the second wind channel from the new trend wind gap, takes away the partial heat that the compressor gived off, and the new trend divide into two parts afterwards: and one part of the air enters the room from the air supply port through the air supply fan after being heated continuously in the second air duct through the air supply coil and the reheating coil. One part enters the first air duct through the air mixing air door, is cooled through the exhaust coil and is exhausted outdoors from the exhaust air port through the exhaust fan.

In the technical scheme, under a transition season internal circulation mode, a refrigerant in a supercooling coil is evaporated and absorbs heat to become refrigerant gas, the refrigerant gas is sucked by a suction inlet of a compressor and compressed into high-temperature and high-pressure refrigerant gas through an exhaust coil and a four-way reversing valve, the refrigerant gas is condensed and released in an air supply coil and a reheating coil through the four-way reversing valve, and the refrigerant gas is throttled by a first throttling device to become a gas-liquid two-phase state and returns to the supercooling coil. Indoor return air enters the first air channel from the return air inlet, is cooled and dehumidified through the supercooling coil, enters the second air channel through the air mixing air door, and enters the room from the air supply inlet through the air supply fan after absorbing heat through the air supply coil and the reheating coil.

The invention relates to a full-working-condition heat pump heat recovery type fresh air fan with a multi-reheating mode, which structurally has the following characteristics and innovation points:

1. the four coils of the air supply coil, the air exhaust coil, the supercooling coil and the reheating coil are arranged, particularly the arrangement of the reheating coil distinguishes the working conditions of the whole year, particularly the summer working conditions in detail, the four coils can be used in summer, winter and transition seasons through flow channel switching, and the requirements of various fresh air supply of the whole working conditions of the whole season are met.

2. The refrigerant bypass loop is arranged, so that various reheating modes such as supercooling reheating, condensation reheating, semi-condensation reheating and the like are realized, the adjustment is carried out according to needs under different loads in summer, and the requirement on the air outlet temperature can be always met, particularly the requirement that the air outlet temperature of the fresh air dehumidifier in the new national standard is not lower than 22 ℃.

Compared with the prior art, the invention has the following advantages:

1. this technical scheme realizes matching different reheat modes and reheating the new trend after cooling dehumidification through addding reheat coil pipe and refrigerant bypass circuit under the dehumidification operating mode in summer when the load changes for supply air temperature in summer satisfies the requirement to minimum supply air temperature in the new national standard, has improved human travelling comfort, reduces the sense of blowing.

2. According to the technical scheme, the heat pump heat recovery type fresh air fan can be used for pertinently and comprehensively matching the annual working conditions, up to 14 operation modes including summer refrigeration dehumidification, winter heating and transition season internal circulation can be realized, and the requirement of household type annual fresh air supply is met.

3. The arrangement of the first bypass loop, the second bypass loop and the stop valve on the first bypass loop is limited in added components, simple in form, but obvious in effect, provides various reheating forms which can be selected, and greatly widens the applicability of the fresh air machine.

4. The first throttling device and the second throttling device are arranged on two sides of the reheating coil pipe, so that the requirements of throttling processes in steam compression circulation under different mode switching are met, and the switching of various modes can be completed without additionally arranging pipelines.

The heat pump heat recovery type fresh air fan in the technical scheme is an integral fresh air dehumidifier, excessive air valves or air duct steering assemblies are not arranged in the box body, and the heat pump heat recovery type fresh air fan is compact in structure and small in occupied area compared with similar products and is more suitable for household installation requirements.

Drawings

Fig. 1 is a schematic structural view of a heat pump heat recovery type fresh air machine according to the present invention.

Fig. 2 to 14 are schematic flow diagrams of the heat pump heat recovery type fresh air fan in the refrigeration and dehumidification mode according to the present invention, which correspond to: fig. 2 is a mixed air-supercooling reheating mode, fig. 3 is a mixed air-condensation reheating mode, fig. 4 and 5 are mixed air-semi-condensation reheating modes, fig. 6 is a full return air-supercooling reheating mode, fig. 7 is a full return air-condensation reheating mode, fig. 8 and 9 are full return air-semi-condensation reheating modes, fig. 10 is a full fresh air-supercooling reheating mode, fig. 11 is a full fresh air-condensation reheating mode, fig. 12 and 13 are full fresh air-semi-condensation reheating modes, and fig. 14 is a single air duct-condensation reheating mode.

Fig. 15 to 17 are schematic flow diagrams of the heat pump heat recovery type fresh air fan in the heating mode of the invention, which respectively correspond to: fig. 15 shows a mixed air mode, fig. 16 shows a full return air mode, and fig. 17 shows a full fresh air mode.

FIG. 18 is a schematic view showing the flow of the heat pump heat recovery type fresh air fan in the internal circulation mode according to the present invention

In the figure: 1-a first air duct; 2-a second air duct; 3-return air inlet; 4-air supply port; 5-air exhaust port; 6-fresh air port; 7-air mixing damper; 8-an exhaust fan; 9-an air supply fan; 10-a super-cooling coil; 11-an exhaust coil pipe; 12-a first throttling device; 13-a reheat coil; 14-a second throttling device; 15 air supply coil pipe; a 16-four-way reversing valve; 17-a compressor; 18-34-connecting pipe; 35-a first stop valve; 36-second stop valve.

Detailed Description

The invention is described in detail below with reference to the figures and specific embodiments.

Example 1

In this embodiment, an all-condition heat pump heat recovery type fresh air fan with multiple reheating modes has a structure shown in fig. 1, and the main structure includes a first air duct 1, a second air duct 2, a return air inlet 3, an air supply inlet 4, an air exhaust inlet 5, a fresh air inlet 6, an air mixing air door 7, an air exhaust fan 8, an air supply fan 9, a supercooling coil 10, an air exhaust coil 11, a first throttling device 12, a reheating coil 13, a second throttling device 14, an air supply coil 15, a four-way reversing valve 16, a compressor 17, connecting pipelines 18-34, a first stop valve 35 and a second stop valve 36.

In the present embodiment, the compressor 17, the connection pipe 19, the four-way selector valve 16, the

connection pipes

21 and 22, the refrigerant passage of the discharge coil 11, the

connection pipes

23 and 24, the refrigerant passage of the supercooling coil 10, the

connection pipes

25 and 26, the first throttle device 12, the connection pipe 27, the refrigerant passage of the reheating coil 13, the connection pipe 28, the second throttle device 14, the connection pipe 29, the refrigerant passage of the air blowing coil 15, and the connection pipe 18 are connected in this order to form a refrigerant loop. The interface A of the four-way reversing valve 16 is connected with a connecting pipe 21, the interface B is connected with a connecting pipe 20, the interface C is connected with a connecting pipe 18, and the interface D is connected with a connecting pipe 19.

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 connection pipe 32, a first stop valve 35, a connection pipe 33, and a connection pipe 34, and is connected in parallel with the exhaust coil 11 and the supercooling coil 10, one end of the first bypass circuit is communicated with the exhaust of the compressor 17 through the connection pipe 21, and the other end of the first bypass circuit is communicated with the reheating coil 13 through the connection pipe 26, the first throttle device 12, and the connection pipe 27. The second bypass circuit is composed of a connection pipe 30, a second stop valve 36, a connection pipe 31 and a connection pipe 34, and is connected in parallel with the supercooling coil 10, one end of the second bypass circuit is communicated with the exhaust coil 11 through the connection pipe 23, and the other end of the second bypass circuit is communicated with the reheating coil 13 through the connection pipe 26, the first throttling device 12 and the connection pipe 27.

In a cooling and dehumidifying mode (air mixing-supercooling reheating) in summer, as shown in fig. 2, the return air port 3, the exhaust air port 5, the supply air port 4 and the fresh air port 6 are all opened, and the air mixing door 7 is opened. The exhaust fan 8 and the air supply fan 9 are both started. The first throttle device 12 is kept normally open and the second throttle device 14 is used for throttling. The AD interface of the four-way reversing valve 16 is communicated with the BC interface. The first and

second cutoff valves

35 and 36 are closed. The refrigerant in the air supply coil 15 absorbs heat through evaporation to become refrigerant gas, the refrigerant gas is sucked by a suction inlet of a compressor 17 through a four-way reversing valve 16 and compressed into high-temperature and high-pressure refrigerant gas, the refrigerant gas is condensed and released heat in an exhaust coil 11 through the four-way reversing valve 16, is further supercooled in a supercooling coil 10 and a reheating coil 13, is throttled by a second throttling device 14 to become a gas-liquid two-phase state, and returns to the air supply coil 15. Outdoor new trend gets into second wind channel 2 from new trend wind gap 6, takes away the partial heat that compressor 17 gived off, and the new trend is divided into two parts afterwards: one part enters the first air duct 1 through the air mixing damper 7; and a part of the air continues to be cooled and dehumidified in the second air duct 2 through the air supply coil 15, is heated through the reheating coil 13, and then enters the room from the air supply air inlet 4 through the air supply fan 9. The return air enters the first air channel 1 from the return air inlet 3, passes through the supercooling coil 10, is mixed with part of fresh air entering the first air channel 1, absorbs heat through the exhaust coil 11, and is exhausted outdoors from the exhaust air inlet 5 by the exhaust fan 8.

In the cooling and dehumidifying mode in summer (mixing air-condensing reheating), as shown in fig. 3, the states of the air inlet, the fan, the throttling device and the four-way reversing valve are consistent with the cooling and dehumidifying mode in summer (mixing air-subcooling reheating). The first cut-off valve 35 is opened and the second cut-off valve 36 is closed. The refrigerant in the air supply coil 15 is evaporated to absorb heat and changed into refrigerant gas, the refrigerant gas is sucked by a suction inlet of the compressor 17 through the four-way reversing valve 16 and compressed into high-temperature and high-pressure refrigerant gas, the refrigerant gas is shunted after passing through the four-way reversing valve 16, part of the refrigerant gas is condensed in the exhaust coil 11 and the supercooling coil 10, part of the refrigerant gas is condensed in the reheating coil 13 to release heat, and the refrigerant liquid coming out of the reheating coil 13 is throttled by the second throttling device 14 and changed into a gas-liquid two-phase state and returns to the air supply. The air flow form is consistent with a summer refrigeration and dehumidification mode (mixed air-supercooling reheating).

In the cooling and dehumidifying mode in summer (mixed air-semi-condensation reheating), as shown in fig. 4 and 5, the states of the air inlet, the fan, the throttling device and the four-way reversing valve are consistent with the cooling and dehumidifying mode in summer (mixed air-super-cooling reheating). The second cut-off valve 36 is opened and the first cut-off valve 35 is opened or closed as required. The refrigerant in the air supply coil 15 absorbs heat through evaporation and becomes refrigerant gas, the refrigerant gas is sucked by a suction inlet of the compressor 17 through the four-way reversing valve 16 and is compressed into high-temperature and high-pressure refrigerant gas, then the refrigerant gas passes through the four-way reversing valve 16, all/part of the refrigerant gas flows through the air exhaust coil 11 to become gas-liquid two-phase refrigerant and then is divided, part of the refrigerant gas is condensed in the supercooling coil 10, part of the refrigerant gas enters the reheating coil 13 to be condensed and supercooled to release heat, and the refrigerant liquid coming out of the reheating coil 13 is throttled by the second throttling device 14 to become a gas-. The air flow form is consistent with a summer refrigeration and dehumidification mode (mixed air-supercooling reheating).

In the cooling and dehumidifying mode (full return air-supercooling reheating) in summer, as shown in fig. 6, the return air inlet 3, the exhaust air inlet 5, the supply air inlet 4 and the fresh air inlet 6 are all opened, and the mixed air door 7 is closed. The exhaust fan 8 and the air supply fan 9 are both started. The first throttle device 12 is kept normally open and the second throttle device 14 is used for throttling. The AD interface of the four-way reversing valve 16 is communicated with the BC interface. The first and

second cutoff valves

35 and 36 are closed. The refrigerant flow pattern is consistent with the summer refrigeration and dehumidification mode (mixed air-supercooling reheating). Outdoor fresh air enters the second air duct 2 from the fresh air inlet 6, takes away partial heat emitted by the compressor 17, is cooled and dehumidified by the air supply coil 15, is reheated by the reheating coil 13, and enters the room from the air supply inlet 4 through the air supply fan 9. Indoor return air enters the first air duct 1 from the return air inlet 3, passes through the supercooling coil 10 and the exhaust coil 11 to absorb heat, and is exhausted outdoors from the exhaust air inlet 5 through the exhaust fan 8.

In the cooling and dehumidifying mode in summer (full return air-condensation reheating), as shown in fig. 7, the states of the air inlet, the fan, the throttling device and the four-way reversing valve are consistent with those in the cooling and dehumidifying mode in summer (full return air-supercooling reheating). The first cut-off valve 35 is opened and the second cut-off valve 36 is closed. The refrigerant flow pattern is consistent with the summer cooling and dehumidifying mode (mixed air-condensation reheating). The air flow pattern is consistent with the summer cooling and dehumidifying mode (full return air-overcooled reheating).

In the cooling and dehumidifying mode in summer (full return air-semi-condensation reheating), as shown in fig. 8 and 9, the states of the air inlet, the fan, the throttling device and the four-way reversing valve are consistent with the cooling and dehumidifying mode in summer (full return air-supercooling reheating). The second cut-off valve 36 is opened and the first cut-off valve 35 is opened or closed as required. The refrigerant flow form is consistent with a summer refrigeration and dehumidification mode (mixed air-semi-condensation reheating). The air flow pattern is consistent with the summer cooling and dehumidifying mode (full return air-overcooled reheating).

In the cooling and dehumidifying mode in summer (fresh air-supercooling and reheating), as shown in fig. 10, the return air port 3 is closed, the exhaust air port 5, the supply air port 4 and the fresh air port 6 are all opened, and the mixed air door 7 is opened. The exhaust fan 8 and the air supply fan 9 are both started. The first throttle device 12 is kept normally open and the second throttle device 14 is used for throttling. The AD interface of the four-way reversing valve 16 is communicated with the BC interface. The first and

second cutoff valves

35 and 36 are closed. The refrigerant flow pattern is consistent with the summer refrigeration and dehumidification mode (mixed air-supercooling reheating). Outdoor new trend gets into second wind channel 2 from new trend wind gap 6, takes away the partial heat that compressor 17 gived off, and the new trend is divided into two parts afterwards: and a part of the air continues to be cooled and dehumidified in the second air duct 2 through the air supply coil 15, is reheated through the reheating coil 13, and then enters the room from the air supply air inlet 4 through the air supply fan 9. One part enters the first air duct 1 through the air mixing damper 7, absorbs heat through the exhaust coil 11, and is exhausted out of the room through the exhaust air outlet 5 through the exhaust fan 8.

In the summer cooling and dehumidifying mode (fresh air-condensation reheating), as shown in fig. 11, the states of the air inlet, the fan, the throttling device and the four-way reversing valve are consistent with the summer cooling and dehumidifying mode (fresh air-supercooling reheating). The first cut-off valve 35 is opened and the second cut-off valve 36 is closed. The refrigerant flow pattern is consistent with the summer cooling and dehumidifying mode (mixed air-condensation reheating). The air flow form is consistent with a summer refrigeration and dehumidification mode (fresh air-supercooling reheating).

In the summer cooling and dehumidifying mode (full fresh air-semi-condensation reheating), as shown in fig. 12 and 13, the states of the air port, the fan, the throttling device and the four-way reversing valve are consistent with the summer cooling and dehumidifying mode (full fresh air-super-cooling reheating). The second cut-off valve 36 is opened and the first cut-off valve 35 is opened or closed as required. The refrigerant flow form is consistent with a summer refrigeration and dehumidification mode (mixed air-semi-condensation reheating). The air flow form is consistent with a summer refrigeration and dehumidification mode (fresh air-supercooling reheating).

In the cooling and dehumidifying mode (single duct-condensation reheating) in summer, as shown in fig. 14, the return air inlet 3 and the exhaust air inlet 5 are closed, the supply air inlet 4 and the fresh air inlet 6 are opened, and the mixed air door 7 is closed. The exhaust fan 8 is turned off and the supply fan 9 is turned on. The first throttle device 12 is kept normally open and the second throttle device 14 is used for throttling. The AD interface of the four-way reversing valve 16 is communicated with the BC interface. The first and

second cutoff valves

35 and 36 are closed. The refrigerant in the air supply coil 15 absorbs heat through evaporation and becomes refrigerant gas, the refrigerant gas is sucked by a suction inlet of the compressor 17 through the four-way reversing valve 16 and is compressed into high-temperature and high-pressure refrigerant gas, the refrigerant gas flows through the exhaust coil 11 and the supercooling coil 10 through the four-way reversing valve 16, enters the reheating coil 13 to be condensed and release heat, is throttled by the second throttling device 14 to become a gas-liquid two-phase state, and returns to the air supply coil 15. Outdoor fresh air enters the second air duct 2 from the fresh air inlet 6, takes away partial heat emitted by the compressor 17, is cooled and dehumidified by the air supply coil 15, is reheated by the reheating coil 13, and enters the room from the air supply inlet 4 through the air supply fan 9.

In the winter heating mode (air mixing), as shown in fig. 15, the return air port 3, the exhaust air port 5, the supply air port 4, and the fresh air port 6 are all opened, and the air mixing damper 7 is opened. The exhaust fan 8 and the air supply fan 9 are both started. The first throttle device 12 is used for throttling and the second throttle device 14 is kept normally open. The AB port and the CD port of the four-way reversing valve 16 are communicated. The first and

second cutoff valves

35 and 36 are closed. The refrigerants in the supercooling coil 10 and the exhaust coil 11 are evaporated to absorb heat and become refrigerant gas, the refrigerant gas is sucked by a suction inlet of the compressor 17 through the four-way reversing valve 16 and compressed into high-temperature and high-pressure refrigerant gas, the refrigerant gas is condensed and released in the air supply coil 15 and the reheating coil 13 through the four-way reversing valve 16, and the refrigerant gas is throttled by the first throttling device 12 to become a gas-liquid two-phase state and returns to the supercooling coil 10. Outdoor new trend gets into second wind channel 2 from new trend wind gap 6, takes away the partial heat that compressor 17 gived off, and the new trend is divided into two parts afterwards: one part enters the first air duct 1 through the air mixing damper 7; after a part of the air continues to be heated in the second air duct 2 through the air supply coil 15 and the reheating coil 13, the air enters the room from the air supply port 4 through the air supply fan 9. Indoor return air enters the first air channel 1 from the return air inlet 3, passes through the supercooling coil 10, is mixed with part of fresh air entering the first air channel 1, is cooled by the exhaust coil 11, and is exhausted outdoors from the exhaust air inlet 5 through the exhaust fan 8.

In the winter heating mode (full return air), as shown in fig. 16, the return air inlet 3, the exhaust air inlet 5, the supply air inlet 4 and the fresh air inlet 6 are all opened, and the mixed air door 7 is closed. The states of the fan, the throttling device, the four-way reversing valve and the stop valve are consistent with the heating mode (mixed air) in winter. The refrigerant flow pattern is consistent with the winter heating mode (air mixing). Outdoor fresh air enters the second air channel 2 from the fresh air inlet 6, takes away part of heat emitted by the compressor 17, and is heated by the air supply coil 15 and the reheating coil 13 and then is sent to the indoor. Indoor return air enters the first air channel 1 from the return air inlet 3, is cooled by the supercooling coil 10 and the exhaust coil 11, and is exhausted outdoors from the exhaust air inlet 5 through the exhaust fan 8.

In the winter heating mode (full fresh air), as shown in fig. 17, the return air port 3 is closed, the exhaust air port 5, the supply air port 4 and the fresh air port 6 are all opened, and the mixed air door 7 is opened. The states of the fan, the throttling device, the four-way reversing valve and the stop valve are consistent with the heating mode (mixed air) in winter. The refrigerant flow pattern is consistent with the winter heating mode (air mixing). Outdoor new trend gets into second wind channel 2 from new trend wind gap 6, takes away the partial heat that compressor 17 gived off, and the new trend is divided into two parts afterwards: after a part of the air continues to be heated in the second air duct 2 through the air supply coil 15 and the reheating coil 13, the air enters the room from the air supply port 4 through the air supply fan 9. One part enters the first air duct 1 through the air mixing damper 7, is cooled through the exhaust coil 11, and is discharged out of the room from the exhaust air port 5 through the exhaust fan 8.

In the transition season internal circulation mode, as shown in fig. 18, the exhaust air port 5 and the fresh air port 6 are closed, the return air port 3 and the supply air port 4 are opened, and the mixed air door 7 is opened. The exhaust fan 8 is turned off and the supply fan 9 is turned on. The first throttle device 12 is used for throttling and the second throttle device 14 is kept normally open. The AB port and the CD port of the four-way reversing valve 16 are communicated. The first and

second cutoff valves

35 and 36 are closed. The refrigerant in the supercooling coil 10 evaporates and absorbs heat to become refrigerant gas, the refrigerant gas is sucked by a suction inlet of a compressor 17 through an exhaust coil 11 and a four-way reversing valve 16 and compressed into high-temperature and high-pressure refrigerant gas, the refrigerant gas is condensed and released in an air supply coil 15 and a reheating coil 13 through the four-way reversing valve 16, and the refrigerant gas is throttled by a first throttling device 12 to become a gas-liquid two-phase state and returns to the supercooling coil 10. Indoor return air enters the first air channel from the return air inlet 3, is cooled and dehumidified through the supercooling coil 10, enters the second air channel 2 through the air mixing air door 7, absorbs heat through the air supply coil 15 and the reheating coil 13, and then enters the indoor space from the air supply inlet 4 through the air supply fan 9.

Comparative example 1

Compared with the technical schemes in patents CN109000312A and CN201910949050.7, the technical scheme is as follows:

(1) the reheating coil is structurally added, so that the air supply temperature can be increased, and the requirements of new national standards are met. Meanwhile, the fresh air requirement that 14 operation modes cover all working conditions all the year around is formed, particularly 10 refrigeration dehumidification modes in summer, and the comfort in different load working conditions in summer is obviously improved. The switching of different working modes is realized through the switching of air door and valve, and is convenient and reliable.

(2) The bypass pipeline is further added on the basis of the step (1), so that various reheating modes of supercooling reheating, condensation reheating and semi-condensation reheating can be realized, and different loads under refrigeration and dehumidification in summer are matched. When the load is high, the reheating coil in the prior art uses the condensation heat of the condenser for reheating, and this way has low heat recovery efficiency, and cannot realize multiple mode switching or the system is very complex, which causes great technical obstacles for the skilled in the art. The innovative core of the technical scheme is that the supercooling heat is utilized for reheating, so that the supercooling degree of the refrigeration cycle is further improved, and the air supply temperature is increased. The prior art cannot operate in this mode when the load is low. The innovative core of the technical scheme is that the refrigerant is allowed to be switched to utilize all or part of the refrigerant condensation heat for reheating at the moment so as to ensure the requirement of the outlet air temperature.

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

1. A full-working-condition heat pump heat recovery type fresh air fan with a multi-reheating mode is characterized by comprising a first air duct (1), a second air duct (2) and a refrigerant loop;

the first air duct (1) is provided with an air return air inlet (3) and an air exhaust air inlet (5);

an air supply port (4) and a fresh air port (6) are arranged on the second air duct (2);

a wind mixing air door (7) capable of communicating the first air duct (1) and the second air duct (2) is arranged between the first air duct and the second air duct;

the refrigerant loop comprises a compressor (17), a four-way reversing valve (16), an exhaust coil (11), a supercooling coil (10), a first throttling device (12), a reheating coil (13), a second throttling device (14) and an air supply coil (15) which are connected in sequence;

the refrigerant loop is also provided with a first bypass circuit and a second bypass circuit, and the first bypass circuit and the second bypass circuit are respectively provided with a first stop valve (35) and a second stop valve (36);

the first bypass loop is simultaneously connected with the exhaust coil (11) and the supercooling coil (10) in parallel;

the second bypass circuit is connected in parallel with the subcooling coil (10);

and an exhaust fan (8) and an air supply fan (9) are respectively arranged at the exhaust air port (5) and the air supply air port (4).

2. The all-condition heat pump heat recovery type fresh air fan with multiple reheating modes according to claim 1, wherein one end of the first bypass circuit is communicated with an exhaust port of a compressor (17) through a four-way reversing valve (16), and the other end of the first bypass circuit is communicated with a reheating coil (13) through a first throttling device (12).

3. The all-operating-condition heat pump heat recovery type fresh air fan with multiple reheating modes according to claim 2, wherein one end of the second bypass circuit is communicated with a refrigerant outlet of the exhaust coil (11), and the other end of the second bypass circuit is communicated with the reheating coil (13) through a first throttling device (12).

4. The all-operating-condition heat pump heat recovery type fresh air fan with multiple reheating modes according to claim 3, wherein the exhaust coil (11), the supercooling coil (10), the first bypass circuit, the second bypass circuit, the first stop valve (35) and the second stop valve (36) are arranged in the first air duct (1).

5. The all-condition heat pump heat recovery type fresh air fan with multiple reheating modes according to claim 3, wherein the first throttling device (12), the reheating coil (13), the second throttling device (14), the air supply coil (15), the four-way reversing valve (16) and the compressor (17) are arranged in the second air duct (2).

6. The all-condition heat pump heat recovery type fresh air fan with multiple reheating modes according to claim 1, wherein four interfaces of the four-way reversing valve (16) are respectively connected with an exhaust coil (11), an air suction port of a compressor (17), an air supply coil (15) and an air exhaust port of the compressor (17).

7. The all-condition heat pump heat recovery type fresh air fan with multiple reheating modes according to claim 1, wherein the first throttling device (12) and the second throttling device (14) are both one of capillary tubes, throttling short pipes or electronic expansion valves;

the first stop valve (35) and the second stop valve (36) are both solenoid valves.

8. The all-condition heat pump heat recovery type fresh air fan with multiple reheating modes according to claim 1, wherein the first air duct (1) and the second air duct (2) are parallel air ducts with equal diameter and equal length;

the air return air inlet (3) and the air exhaust air inlet (5) are respectively arranged at two ends of the first air channel (1);

the air supply air port (4) and the fresh air port (6) are respectively arranged at two ends of the second air duct (2);

the air mixing damper (7) is arranged in the middle of the first air channel (1) and the second air channel (2).

9. The all-condition heat pump heat recovery type fresh air fan with multiple reheating modes according to claim 1, wherein the air mixing damper (7) is a servo driving damper;

and servo-driven air doors are arranged on the return air inlet (3), the exhaust air inlet (5), the air supply inlet (4) and the fresh air inlet (6).

10. The all-condition heat pump heat recovery type fresh air fan with multiple reheating modes as claimed in claim 1, wherein the all-condition heat pump heat recovery type fresh air fan can realize a summer cooling and dehumidifying mode of mixed air-supercooling reheating, a summer cooling and dehumidifying mode of mixed air-condensing reheating, a summer cooling and dehumidifying mode of mixed air-semi-condensing reheating, a summer cooling and dehumidifying mode of full return air-supercooling reheating, a summer cooling and dehumidifying mode of full return air-condensing reheating, a summer cooling and dehumidifying mode of full return air-semi-condensing reheating, and a summer cooling and dehumidifying mode of single air duct-condensing reheating, The winter heating mode is the switching of mixed air, the winter heating mode is the full return air, the winter heating mode is the full new trend, the transition season internal circulation mode.