CN217209606U - Temperature and humidity double-control heat pump fresh air dehumidifier with deep total heat recovery - Google Patents

Abstract

The utility model discloses a temperature and humidity double-control heat pump fresh air dehumidifier with deep total heat recovery, which comprises an air flow path and a refrigerant circulation flow path, wherein the air flow path comprises an air supply flow path and an air exhaust flow path; a total heat exchanger is arranged at the intersection of the air supply flow path and the air exhaust flow path; the refrigerant circulating flow path comprises a compressor, a four-way reversing valve, an exhaust coil branch throttling device, a second air supply coil branch throttling device and a first air supply coil which are sequentially connected. Compared with the prior art, the utility model discloses carry out pertinence, match comprehensively to indoor operating mode, can realize dehumidification, heat, operational mode such as heat exchange, bypass, more be fit for the needs that family formula new trend dehumidification was supplied with all the year.

Description

Temperature and humidity double-control heat pump fresh air dehumidifier with deep total heat recovery

Technical Field

The utility model relates to a new trend dehumidifier especially relates to a wet two accuse heat pump new trend dehumidifier of temperature of full heat recovery of degree of depth.

Background

The recovery of energy in the exhaust air for fresh air pretreatment has become one of the important energy-saving means of modern buildings. The common devices comprise a sensible heat or total heat exchanger and a heat pump heat recovery fresh air dehumidifier. The former has obvious effect when the difference between indoor and outdoor states is large (such as hot working condition in summer and cold working condition in winter), and realizes heat/humidity transfer by utilizing the indoor and outdoor temperature difference/humidity difference, thereby effectively reducing the fresh air and humidity load brought into the room (but the fresh air and humidity load cannot be completely eliminated, and the indoor self humidity load cannot be removed in addition). The latter can realize larger dehumidification amount by means of the refrigeration heat pump circulating system.

In the prior art, a total heat exchanger and a heat pump dehumidification system are combined for use, and a common structure is that fresh air flows through the total heat exchanger to exchange heat and humidity with return air, then flows through a heat pump dehumidification module to be dehumidified, is reheated and then is sent indoors (see patent publications CN111637578A and CN 110986213A). The main defects are as follows: (1) all condensation heat of the heat pump dehumidification module is brought to the indoor, and the air supply temperature cannot be controlled. If the dehumidification amount is large, the temperature of the air supply is likely to be high, and the heat load of the indoor air conditioning system is increased. (2) The heat pump dehumidification module and the total heat exchanger are independent modules/systems and are not organically combined. The heat recovery of the indoor return air is completed in the total heat exchanger, and the heat pump system does not participate. In fact, the return air often has a considerable heat recovery potential after flowing through the total heat exchanger. (3) The heat pump dehumidification module has a limited amount of added dehumidification. If the dehumidification capacity is improved in the current structure, the condenser bears higher heat exchange amount, and the problems of overhigh condensation temperature and the like are easily caused.

SUMMERY OF THE UTILITY MODEL

The utility model aims at providing a two accuse heat pump new trend dehumidifiers of temperature and humidity of the full heat recovery of degree of depth exactly in order to overcome above-mentioned prior art's defect.

The utility model discloses a realize through following technical scheme:

the temperature and humidity double-control heat pump fresh air dehumidifier with deep total heat recovery comprises an air flow path and a refrigerant circulation flow path, wherein the air flow path comprises an air supply flow path and an air exhaust flow path;

the two ends of the air supply flow path are provided with an air inlet and an air supply port;

the two ends of the air exhaust flow path are provided with an air return air port and an air exhaust air port;

a total heat exchanger is arranged at the intersection of the air supply flow path and the air exhaust flow path;

the refrigerant circulating flow path comprises a compressor, a four-way reversing valve, an exhaust coil branch throttling device, a second air supply coil branch throttling device and a first air supply coil which are connected in sequence;

the four-way reversing valve, the exhaust coil branch throttling device, the second air supply coil branch throttling device and the first air supply coil are all arranged in an air supply flow path;

the compressor and the exhaust coil are both arranged in an exhaust flow path.

The utility model has the preferred proposal that the air inlet section of the air supply flow path is provided with an air inlet sensor for monitoring the temperature and the humidity of inlet air;

and the air return section of the exhaust air flow path is provided with an air return sensor for monitoring the temperature, the humidity and the carbon dioxide concentration of the return air.

The utility model discloses an optimal scheme does, the air inlet section of air supply flow path and the return air section of the flow path of airing exhaust are equipped with air supply fan respectively and the fan of airing exhaust, air supply fan with the fan of airing exhaust is adjustable speed's variable frequency fan.

The utility model discloses an optimal scheme does, the bypass wind gap is left to full heat exchanger bottom, the bypass wind gap is located air supply flow path direction.

The utility model has the preferred proposal that the air supply flow path is respectively provided with an air inlet filter and an air supply filter at the front and the back of the total heat exchanger;

and the air exhaust flow path is provided with an air return filter at the air return section.

The utility model discloses an optimal scheme does, the return air section of the flow path of airing exhaust and the air supply section of air supply flow path meet the department and still be provided with return air inner loop air door.

The utility model discloses an optimal scheme does, four interfaces of four-way reversing valve link to each other with the induction port of first air supply coil pipe, air exhaust coil pipe, second air supply coil pipe, compressor and the gas vent of compressor respectively, wherein, air exhaust coil pipe and second air supply coil pipe are connected on the same interface of four-way reversing valve.

The utility model discloses a preferred scheme does, and exhaust coil place branch road and second air supply coil place branch road connect in parallel the setting on the refrigerant flow path, and one end is connected to the interface C of four-way reversing valve, and the other end is connected to first air supply coil through exhaust coil branch road throttling arrangement and second air supply coil branch road throttling arrangement respectively.

The utility model discloses an optimal scheme does, exhaust coil pipe branch road throttling arrangement and second air supply coil pipe branch road throttling arrangement are one of capillary, throttle sleeve or electron throttling arrangement.

The technical scheme has the following operation modes by switching the air flow path and the refrigerant circulating flow path:

1. dehumidification mode (full fresh air): the air supply to the indoor is all composed of outdoor fresh air, the outdoor fresh air is filtered, cooled, dehumidified and reheated and then is sent to the indoor, and the indoor air conditioner is suitable for hot and humid working conditions in summer;

2. dehumidification mode (internal cycle): the majority of the air supply to the indoor is the internal circulation of the return air, a small amount of fresh air is supplied at the same time, the return air is mixed with a small amount of filtered outdoor fresh air, and then the mixture is cooled, dehumidified and reheated and then sent to the indoor, so that the indoor air conditioner is suitable for extremely humid working conditions such as Huangmeitian and the like;

3. heating mode: the air supply to the indoor is all composed of outdoor fresh air, the outdoor fresh air is filtered and heated and then is sent to the indoor, and the indoor air conditioner is suitable for cold working conditions in winter;

4. a heat exchange mode: the air supply to the indoor is composed of outdoor fresh air, the outdoor fresh air is filtered and subjected to heat exchange and then is sent to the indoor, and the indoor air supply system is suitable for low-environment working conditions (such as an air inlet state at 16 ℃/14 ℃) in transitional seasons;

5. bypass mode: the indoor air supply is composed of outdoor fresh air, the outdoor fresh air is filtered and then is sent to the indoor environment, and the indoor environment-friendly fresh air system is suitable for the suitable working condition in the transition season, namely the outdoor fresh air is suitable for being directly introduced into the indoor environment.

Further, the component states of the unit in each operation mode are as follows:

1. dehumidification mode (full fresh air): and the air supply fan and the air exhaust fan are started. The return air internal circulation air door is closed. And closing the bottom bypass air port. The port E of the four-way reversing valve is connected with the port S, so that the first air supply coil is communicated with an air suction port of the compressor; the port D is connected with the port C, so that the exhaust port of the compressor is communicated with the exhaust coil/the second air supply coil. And throttling devices on the exhaust coil branch and the second air supply coil branch adjust the opening degrees as required.

2. Dehumidification mode (internal cycle): on the basis of a dehumidification mode (full fresh air), an air return internal circulation air door is opened, the rotating speed of an air supply fan is reduced, and the states of other components are kept unchanged.

3. A heating mode: and the air supply fan and the air exhaust fan are started. The return air internal circulation air door is closed. And closing the bottom bypass air port. The port C of the four-way reversing valve is connected with the port S, so that the exhaust coil is communicated with an air suction port of the compressor; the port D is connected with the port E, so that an exhaust port of the compressor is communicated with the first air supply coil pipe. The branch throttling device of the exhaust coil pipe is adjusted as required, the opening degree of the branch throttling device of the second air supply coil pipe is set to be 0, and the flow path is in a closed state.

4. A heat exchange mode: the heat pump system is shut down. The air supply fan and the air exhaust fan are started. The return air internal circulation air door is closed. And closing the bottom bypass air port.

5. Bypass mode: the heat pump system is shut down. The air supply fan is started, and the air exhaust fan is closed. The return air internal circulation air door is closed. And opening the bottom bypass air port.

Further, the air flow path state in the unit under each operation mode is as follows:

1. dehumidification mode (full fresh air): the outdoor fresh air is introduced from the air inlet, and is driven by the air supply fan to sequentially pass through the air inlet air filter for filtration and purification, the total heat exchanger and return air heat and humidity exchange, the air supply air filter for deep purification, the first air supply coil for cooling and dehumidification and the second air supply coil for reheating, and then is sent to the indoor from the air supply inlet. The indoor return air is introduced from the return air inlet, flows through the return air filter for filtration and purification, the total heat exchanger and the fresh air heat and humidity exchange in sequence under the drive of the exhaust fan, takes away the condensation heat through the exhaust coil pipe, and is exhausted to the outside from the exhaust air inlet.

2. Dehumidification mode (internal cycle): outdoor fresh air is introduced from the air inlet, and is sequentially filtered and purified by the air inlet air filter, the total heat exchanger and a small amount of return air for heat and humidity exchange, deeply purified by the air supply air filter, cooled and dehumidified by the first air supply coil and reheated by the second air supply coil under the driving of the air supply fan, and then is sent to the indoor space from the air supply inlet. The indoor return air is introduced from a return air inlet and is divided into two parts under the drive of an exhaust fan, and a small part of the indoor return air flows through a return air filter for filtration and purification, a total heat exchanger and fresh air heat and humidity exchange in sequence, and an exhaust coil pipe takes away condensation heat and then is exhausted to the outside from an exhaust air inlet; in addition, most of the fresh air is mixed with the fresh air after the air supply filter from the return air internal circulation air door, and then is cooled, dehumidified and reheated together and then is sent to the indoor.

3. Heating mode: outdoor fresh air is introduced from the air inlet, and is driven by the air supply fan to sequentially pass through the air inlet air filter for preliminary purification, the total heat exchanger and return air heat and humidity exchange, the air supply air filter for deep purification and the first air supply coil for heating, and then is sent into a room through the air supply air inlet. The indoor return air is introduced from the return air inlet, and is driven by the exhaust fan to sequentially pass through the return air filter for filtration and purification, the total heat exchanger and the fresh air heat and humidity exchange, and the exhaust coil pipe is used for recovering exhaust heat and then exhausting the heat to the outdoor from the exhaust air inlet.

4. A heat exchange mode: the outdoor fresh air is introduced from the air inlet, and is driven by the air supply fan to sequentially pass through the air inlet air filter for preliminary purification, the total heat exchanger and the return air heat and humidity exchange, and the air supply air filter for deep purification, and then is sent into the room through the air supply air inlet. The indoor return air is introduced from the return air inlet, passes through the return air filter for filtration and purification and the total heat exchanger for heat and moisture exchange with the fresh air in sequence under the drive of the exhaust fan, and is exhausted to the outside from the exhaust air inlet.

5. Bypass mode: outdoor fresh air is introduced from the air inlet, and is driven by the air supply fan to sequentially pass through the air inlet air filter for preliminary purification, the bypass air inlet at the bottom of the total heat exchanger and the air supply air filter for deep purification, and then is sent into a room through the air supply air inlet.

Further, the states of the refrigerant circulation flow paths in the unit in each operation mode are as follows:

1. dehumidification mode (full fresh air): the refrigerant evaporates and absorbs heat in the first air supply coil pipe to form low-pressure steam, the low-pressure steam is sucked by the compressor through the four-way reversing valve and compressed into high-temperature high-pressure refrigerant gas, the high-temperature high-pressure refrigerant gas flows through the four-way reversing valve and then is divided into two branches connected in parallel, one branch flows through the air exhaust coil pipe to exhaust air and dissipate heat, the other branch flows through the second air supply coil pipe to be used for reheating low-temperature fresh air after deep dehumidification, the refrigerants flowing out of the air exhaust coil pipe and the second air supply coil pipe are respectively throttled by throttling devices of the branches to form low-temperature low-pressure two-phase state refrigerants, the low-temperature low-pressure two-phase state refrigerants are mixed and then return to the first air supply coil pipe, and the refrigerant circulation is continued.

2. Dehumidification mode (internal cycle): the state of the refrigerant circulation flow path is consistent with the dehumidification mode (fresh air).

3. Heating mode: the refrigerant loop reverses direction, reversing the direction of flow from dehumidification mode. The refrigerant evaporates and absorbs heat in the exhaust coil pipe to form low-pressure steam, is sucked by the compressor through the four-way reversing valve, is compressed to form high-temperature high-pressure refrigerant gas, flows through the four-way reversing valve, enters the first air supply coil pipe for condensation, heats fresh air flowing through, dissipates heat to form low-temperature high-pressure refrigerant liquid, flows out of the first air supply coil pipe, is throttled by the exhaust coil pipe branch throttling device, becomes low-temperature low-pressure refrigerant again, returns to the exhaust coil pipe, and continues the refrigerant circulation.

4. A heat exchange mode: the heat pump system is closed and the refrigerant circulation flow path is not opened.

5. Bypass mode: the heat pump system is closed and the refrigerant circulation flow path is not opened.

Further, the control method in each operation mode is as follows:

1. dehumidification mode (full fresh air): (1) the dehumidification capacity is adjusted by changing the rotating speed of the compressor, when the current indoor return air humidity measured by the return air sensor is higher than a user set value, the rotating speed of the compressor is increased, and otherwise, the rotating speed is reduced. And (2) controlling the superheat degree of an air suction port of the compressor through the branch throttling device of the exhaust coil pipe, increasing the opening degree of the throttling device when the superheat degree of air suction is higher than a set value, and otherwise, reducing the opening degree. (3) And the refrigerant distribution proportion of the parallel branch where the second air supply coil and the air exhaust coil are located is controlled through the linkage of the second air supply coil branch throttling device and the air exhaust coil branch throttling device, so that the air supply temperature is controlled. Specifically, when the air supply temperature is higher, the opening degree of a branch throttling device of the second air supply coil pipe is reduced, the resistance of the branch is increased, and the flow of the refrigerant distributed by the branch is reduced; and conversely, when the reheating temperature of the air supply is lower, the opening degree of the branch throttling device of the second air supply coil is increased, the resistance of the branch is reduced, and the flow of the refrigerant distributed by the branch is increased. And (4) adjusting the indoor air quality through the air supply fan, increasing the rotating speed of the air supply fan to increase the fresh air volume when the indoor carbon dioxide concentration is higher than a set value, and otherwise, reducing the rotating speed. (5) The air exhaust fan is linked with the air supply fan, so that the air exhaust amount is always maintained at 80-90% of the air intake amount, and the indoor positive pressure of an air-conditioning room is controlled.

2. Dehumidification mode (internal cycle): the control method is consistent with the dehumidification mode (fresh air).

3. Heating mode: the heating capacity is adjusted by changing the rotating speed of the compressor, when the air supply temperature is lower than a set value of a user, the rotating speed of the compressor is increased, otherwise, the rotating speed is reduced. The control strategies of the exhaust coil branch throttling device, the air supply fan and the exhaust fan are consistent with the dehumidification mode (full fresh air). The remaining components need not be controlled.

The unit may face the risk of frosting under the heating mode, and the following adjustment is carried out on the control: (1) when the temperature of the inlet air is low and the frosting risk is common, a bypass air door at the bottom of the total heat exchanger is opened, most of fresh air is directly bypassed without carrying out heat and humidity exchange with the return air, so that the temperature of the return air entering the exhaust coil is high, the evaporation temperature of a refrigerant in the exhaust coil is increased, and the frosting possibility is reduced. (2) When the air inlet temperature is further reduced and the frosting risk is serious, the throttling device of the second air supply coil branch is opened, so that the second air supply coil becomes a refrigerant evaporator connected with the air exhaust coil in parallel, the heat exchange quantity of the air exhaust coil is reduced, the evaporation temperature is increased, and the frosting risk is reduced.

4. A heat exchange mode: the control strategy of the air supply fan and the air exhaust fan is consistent with the dehumidification mode (full fresh air). The remaining components need not be controlled.

5. Bypass mode: the control strategy of the air supply fan is consistent with the dehumidification mode (full fresh air). The remaining components need not be controlled.

The utility model discloses a two accuse heat pump new trend dehumidifiers of warm and humid of full heat recovery of degree of depth, compare with prior art:

1. temperature and humidity double control: the scheme that the second air supply coil and the exhaust coil are in parallel connection is adopted, and the flow distribution of the refrigerants in the two branches is realized through the adjustment of the opening degree of the throttling devices of the respective branches, so that the indoor return air humidity can be controlled to ensure the required dehumidification capacity in the dehumidification mode, the air supply temperature of fresh air can be controlled, and the increase of indoor heat load/reduction of thermal comfort of personnel due to overhigh air supply temperature or air pipe condensation caused by low air supply temperature is avoided;

2. deep total heat recovery: besides the total heat exchanger, a heat pump system is integrated, and a heat exchanger is reasonably replaced. An exhaust coil pipe for heat recovery is arranged at the tail end of the exhaust flow path, and in a dehumidification mode, after the primary heat recovery is realized by the heat and moisture exchange between the return air and the fresh air, the cold energy of the return air is further recycled by using a heat pump system, so that the system efficiency is improved; meanwhile, excessive condensation heat is prevented from being directly discharged indoors. In the heating mode, after the return air in the total heat exchanger is primarily recovered by fresh air, the residual waste heat of the return air is further recovered and utilized in the exhaust coil by utilizing a heat pump, so that the overall energy utilization efficiency of the unit is improved;

3. the return air internal circulation air door is arranged and controlled to be opened and closed, and under the condition that the refrigerant flow path is not changed, the switching between the full fresh air mode and the internal circulation mode in the dehumidification mode is easy to realize. Under the working conditions of high fresh air humidity load such as greengage, the indoor dehumidification can be realized rapidly;

4. the bottom of the total heat exchanger is provided with a bypass air door, and the bypass air door is opened when the inlet air temperature is low in a heating mode, so that the effect of shielding total heat exchange is achieved greatly, and the frosting risk of a heat pump system is reduced. Under the bypass mode, the air conditioner is started under the proper working condition in the transition season, and only fresh air is allowed to be filtered and then introduced, so that the effect similar to mechanical bypass is realized, and the reduction of operation energy consumption is facilitated;

5. the full heat exchanger can independently operate, and can be sent into indoors after utilizing return air to heat fresh air under the condition that outdoor humidity is not high, the temperature is on the low side, and the high-efficient silence of this mode strengthens user experience.

Drawings

FIG. 1 is a schematic structural view of a fresh air dehumidifier of the present invention;

FIG. 2 is a schematic diagram of the fresh air dehumidifier of the present invention in the dehumidification mode (fresh air);

FIG. 3 is a schematic diagram of the new air dehumidifier of the present invention in the dehumidification mode (inner circulation);

fig. 4 is a schematic view of the connection relationship between the refrigerant circulation flow paths of the fresh air dehumidifier in the dehumidification mode (fresh air) and the dehumidification mode (internal circulation);

FIG. 5 is a schematic view of the heating mode of the fresh air dehumidifier of the present invention;

FIG. 6 is a schematic view of the connection relationship between the refrigerant circulation flow paths in the heating mode of the fresh air dehumidifier of the present invention;

FIG. 7 is a schematic diagram of the fresh air dehumidifier of the present invention in the heat exchange mode;

FIG. 8 is a schematic diagram of the fresh air dehumidifier of the present invention in the bypass mode;

FIG. 9 is a schematic diagram showing the positional relationship between the total heat exchanger and the bottom bypass tuyere in a horizontal side view along the air supply flow path.

Fig. 10 is a schematic view of the connection relationship of the refrigerant circulation flow paths of the fresh air dehumidifier of the present invention in the dehumidification mode;

fig. 11 is a schematic view of the connection relationship of the refrigerant circulation flow paths in the heating mode of the fresh air dehumidifier of the present invention.

In the figure: 0-total heat exchanger; 1-a compressor; a 2-four-way reversing valve; 3-an exhaust coil pipe; 4-a second air supply coil; 5-branch throttling device of exhaust coil pipe; 6-a second air supply coil branch throttling device; 7-a first air supply coil; 10-air inlet; 11-air supply port; 12-return air inlet; 13-air exhaust port; 14-an air supply fan; 15-an exhaust fan; 16-return air internal circulation air door; 17-an air intake sensor; 18-return air sensor; 19-air intake air filter; 20-air supply air filter; 21-return air filter; 22-an electric control cabinet; 23-bottom bypass tuyere.

Detailed Description

The technical solution of the present invention is further explained by the following embodiments with reference to the accompanying drawings.

Wherein the showings are for the purpose of illustration only and are shown by way of illustration only and not in actual form, and are not to be construed as limiting the present patent; for a better understanding of the embodiments of the present invention, some parts of the drawings may be omitted, enlarged or reduced, and do not represent the size of an actual product; it will be understood by those skilled in the art that certain well-known structures in the drawings and descriptions thereof may be omitted.

The same or similar reference numerals in the drawings of the embodiments of the present invention correspond to the same or similar parts; in the description of the present invention, it should be understood that if the terms "upper", "lower", "left", "right", "inner", "outer", etc. are used to indicate the orientation or positional relationship based on the orientation or positional relationship shown in the drawings, it is only for convenience of description and simplification of description, but it is not indicated or implied that the device or element referred to must have a specific orientation, be constructed in a specific orientation, and be operated, and therefore, the terms describing the positional relationship in the drawings are used only for illustrative purposes and are not to be construed as limiting the present patent, and the specific meaning of the terms will be understood by those skilled in the art according to the specific circumstances.

Example 1

The temperature and humidity double-control heat pump fresh air dehumidifier with deep total heat recovery in the embodiment has a structure shown in fig. 1, and mainly comprises a total heat exchanger 0, an air inlet 10, an air supply outlet 11, a return air outlet 12, an air exhaust outlet 13, an air supply fan 14, an air exhaust fan 15, a return air internal circulation air door 16, an air inlet sensor 17, a return air sensor 18, an air inlet filter 19, an air supply filter 20, a return air filter 21, an electric control cabinet 22, a bottom bypass air outlet 23, a compressor 1, a four-way reversing valve 2, an air exhaust coil 3, an air exhaust coil branch throttling device 5, a second air supply coil 4, a second air supply coil branch throttling device 6 and a first air supply coil 7. It should be noted that the electric control cabinet 22 is prior art, and a person skilled in the art can select the electric control cabinet according to actual needs, and in addition, the electric control cabinet 22 is arranged in the air supply flow path.

The temperature and humidity double-control heat pump fresh air dehumidifier with deep total heat recovery in the embodiment structurally comprises an air flow path and a refrigerant circulating flow path.

The air flow path of the embodiment is a bidirectional flow, which comprises an air supply flow path and an air exhaust flow path, wherein an air inlet 10 and an air supply 11 are arranged at two ends of the air supply flow path, an air return 12 and an air exhaust 13 are arranged at two ends of the air exhaust flow path, an air inlet sensor 17 is arranged at an air inlet section of the air supply flow path and is used for monitoring the temperature and the humidity of inlet air, an air return sensor 18 is arranged at an air return section of the air exhaust flow path and is used for monitoring the temperature, the humidity, the carbon dioxide concentration and other parameters of return air, an air supply fan 14 and an air exhaust fan 15 are respectively arranged at the air inlet section of the air supply flow path and the air return section of the air exhaust flow path, both variable-frequency fans can be adjusted, a total heat exchanger 0 is arranged at the intersection of the air supply flow path and the air exhaust flow path, an air inlet air filter 19 and an air supply filter 20 are respectively arranged at the front and back of the total heat exchanger 0 of the air supply flow path, and an air return air filter 21 is arranged at the air exhaust flow path, the joint of the return air section of the exhaust air flow path and the air supply section of the air supply flow path is also provided with a return air internal circulation air door 16, the bottom of the total heat exchanger 0 is provided with a bypass air opening 23, and the bottom bypass air opening 23 is positioned in the flow path direction of the air supply (see figure 9).

The refrigerant circulation flow path (see fig. 4 and 6) of the present embodiment is composed of a compressor 1, a four-way selector valve 2, an exhaust coil 3, an exhaust coil bypass throttle device 5, a second air-blowing coil 4, a second air-blowing coil bypass throttle device 6, and a first air-blowing coil 7. Wherein, the interface E of the four-way reversing valve 2 is connected with the first air supply coil pipe 7, the interface C is connected with the air exhaust coil pipe 3 and the second air supply coil pipe 4, and the interface S and the interface D are respectively connected with the air suction port and the air exhaust port of the compressor 1. The branch where the exhaust coil 3 is located and the branch where the second air supply coil 4 is located are connected in parallel on the refrigerant flow path, one end of the branch is connected to a connector C of the four-way reversing valve 2, and the other end of the branch is connected to a first air supply coil 7 through an exhaust coil branch throttling device 5 and a second air supply coil branch throttling device 6 respectively.

By switching the components in the air flow path and the refrigerant circulation flow path, the present embodiment has the following operation modes:

1. dehumidification mode (full fresh air). Referring to fig. 2, the refrigerant circulation flow path is connected as shown in fig. 4.

The air supply to the indoor in the mode is completely composed of outdoor fresh air. And (4) filtering, cooling, dehumidifying and reheating the outdoor fresh air, and then sending the fresh air to the indoor. Is suitable for hot and humid working conditions in summer.

The unit of this embodiment is under dehumidification mode (full new trend), and the part state is: the supply fan 14 and the exhaust fan 15 are turned on. The return air internal circulation damper 16 is closed. The bottom bypass tuyere 23 is closed. The port E of the four-way reversing valve 2 is connected with the port S, so that the first air supply coil 7 is communicated with an air suction port of the compressor 1; the port D is connected with the port C, so that an exhaust port of the compressor 1 is communicated with the exhaust coil 3 and the second air supply coil 4. The throttle devices 5 and 6 adjust the opening degree as required.

In the dehumidification mode (fresh air), the air flow path state of the unit of the embodiment is as follows: outdoor fresh air is introduced from an air inlet 10, and is driven by an air supply fan 14 to sequentially pass through an air inlet filter 19 for filtration and purification, a total heat exchanger 0 and return air heat and humidity exchange, an air supply filter 20 for deep purification, a first air supply coil 7 for cooling and dehumidification, a second air supply coil 4 for reheating and then is sent to the indoor from an air supply air inlet 11. The indoor return air is introduced from the return air inlet 12, and is sequentially filtered and purified by the return air filter 21, subjected to the total heat exchanger 0 and the fresh air heat and humidity exchange, and subjected to condensation heat removal by the exhaust coil 3 under the drive of the exhaust fan 15, and then is exhausted to the outside from the exhaust air inlet 13.

In the dehumidification mode (fresh air), the refrigerant loop state of the unit of the embodiment is as follows: the refrigerant evaporates and absorbs heat in the first air supply coil 7 to be low-pressure steam, the low-pressure steam is sucked by the compressor 1 through the four-way reversing valve 2 and compressed to be high-temperature high-pressure refrigerant gas, the high-temperature high-pressure refrigerant gas flows through the four-way reversing valve 2 and then is divided into two branches connected in parallel, one branch flows through the air exhaust coil 3 to exhaust air and dissipate heat, the other branch flows through the second air supply coil 4 to reheat low-temperature fresh air subjected to deep dehumidification, the refrigerants flowing out of the air exhaust coil 3 and the second air supply coil 4 are respectively throttled by the throttling devices 5 and 6 of the branches to be low-temperature low-pressure two-phase state refrigerants, the refrigerants are mixed and then return to the first air supply coil 7, and the refrigerant circulation is continued.

In the dehumidification mode (full fresh air), the control method of the unit of the embodiment is as follows: (1) the dehumidification capacity is adjusted by changing the rotating speed of the compressor 1, when the current indoor return air humidity measured by the return air sensor 18 is higher than a user set value, the rotating speed of the compressor 1 is increased, otherwise, the rotating speed is reduced. (2) The superheat degree of an air suction port of the compressor is controlled by the throttling device 5, when the superheat degree of the air suction port is higher than a set value, the opening degree of the throttling device 5 is increased, and otherwise, the opening degree is reduced. (3) The refrigerant distribution proportion of the parallel branch where the second air supply coil 4 and the exhaust coil 3 are located is controlled through the linkage of the throttling device 6 and the throttling device 5, and then the air supply temperature is controlled. Specifically, when the air supply temperature is higher, the opening degree of the throttling device 6 is reduced, the resistance of the branch is increased, and the flow rate of the refrigerant distributed by the branch is reduced; on the other hand, when the supply air reheating temperature is low, the opening degree of the throttle device 6 is increased, the branch resistance is decreased, and the refrigerant flow rate distributed to the branch is increased. (4) The indoor air quality is adjusted through the air supply fan 14, when the indoor carbon dioxide concentration is higher than a set value, the rotating speed of the air supply fan 14 is increased, the fresh air quantity is increased, and otherwise, the rotating speed is reduced. (5) The exhaust fan 15 is linked with the air supply fan 14 to ensure that the exhaust air volume is always maintained at 80-90% of the intake air volume so as to control the indoor positive pressure of the air-conditioning room.

The unit of this embodiment is under dehumidification mode (full new trend), and structural feature and the beneficial effect who obtains are: (1) the branch circuits of the second air supply coil pipe 4 and the exhaust coil pipe 3 are connected in parallel, and the distribution of the flow of the refrigerants of the two branch circuits is realized through the adjustment of the opening degrees of the branch circuit throttling devices 6 and 5, so that the air supply temperature of fresh air can be controlled. The increase of indoor heat load or the reduction of thermal comfort of people caused by overhigh temperature of the supplied air is avoided. (2) An exhaust coil is arranged at the tail end of the exhaust flow path, and after the primary heat recovery is realized by the heat and moisture exchange between the return air and the fresh air, the cold energy of the return air is further recycled by using a heat pump system, so that the system efficiency is improved; meanwhile, excessive condensation heat is prevented from being directly discharged to the indoor space.

2. Dehumidification mode (internal circulation). Referring to fig. 3, the refrigerant circulation flow path is connected as shown in fig. 4.

Most of the air supply to the indoor space in the mode is the internal circulation of return air, and a small amount of fresh air is supplied at the same time. The return air is mixed with a small amount of filtered outdoor fresh air, and then the mixture is cooled, dehumidified and reheated and sent to the indoor. Is suitable for the indoor very humid working conditions such as Huangmei day and the like.

The unit of this embodiment can be regarded as a special case of the dehumidification mode (full fresh air) in the dehumidification mode (internal circulation). On the basis of a dehumidification mode (full fresh air), the return air internal circulation air door 16 is opened, the rotating speed of the air supply fan 14 is reduced, and the states of other components are kept unchanged. In the air flow path, the air supply consists of most indoor return air and a small amount of fresh air introduced from an air inlet. The refrigerant circulation flow path state and the control method are not changed.

The unit of the embodiment has the following structural characteristics and beneficial effects in a dehumidification mode (internal circulation): by arranging the return air internal circulation air door 16 and controlling the opening and closing of the return air internal circulation air door, the switching between the full fresh air mode and the internal circulation mode in the dehumidification mode is easily realized under the condition that the refrigerant flow path is not changed. Under the working conditions of high fresh air humidity load such as greengage, the indoor dehumidification can be realized quickly.

3. And (4) heating mode. Referring to fig. 5, the refrigerant circulation flow path is connected as shown in fig. 6.

The air supply to the indoor in the mode is completely composed of outdoor fresh air. And filtering and heating the fresh outdoor air, and then sending the fresh outdoor air to the indoor environment. Is suitable for winter cold working conditions.

In the heating mode of the unit of the embodiment, the states of the components are as follows: the supply fan 14 and the exhaust fan 15 are turned on. The return air internal circulation damper 16 is closed. The bottom bypass tuyere 23 is closed. The port C of the four-way reversing valve 2 is connected with the port S, so that the exhaust coil 3 is communicated with an air suction port of the compressor 1; the port D is connected with the port E, so that the exhaust port of the compressor 1 is communicated with the first air supply coil 7. The throttling device 5 of the exhaust coil branch is adjusted as required, the opening degree of the throttling device 6 of the second air supply coil branch is set to be 0, and the flow path is in a closed state.

In the heating mode of the unit of this embodiment, the air flow path state is: outdoor fresh air is introduced from an air inlet 10, and is driven by an air supply fan 14 to sequentially pass through an air inlet air filter 19 for preliminary purification, a total heat exchanger 0 and return air heat and humidity exchange, an air supply air filter 20 for deep purification, and a first air supply coil 7 for heating, and then is sent into a room through an air supply air inlet 11. The indoor return air is introduced from the return air inlet 12, and is driven by the exhaust fan 15 to sequentially pass through the return air filter 21 for filtration and purification, the total heat exchanger 0 and the fresh air heat and humidity exchange, and the exhaust coil 3 for recovering exhaust heat, and then is exhausted from the exhaust air inlet 13 to the outdoor.

In the heating mode of the unit of the embodiment, the states of the refrigerant loop are as follows: the refrigerant loop reverses direction, reversing the direction of flow from dehumidification mode. The refrigerant evaporates and absorbs heat in the exhaust coil 3 to be low-pressure steam, is sucked by the compressor 1 through the four-way reversing valve 2, is compressed to be high-temperature high-pressure refrigerant gas, then flows through the four-way reversing valve 2, enters the first air supply coil 7 to be condensed, heats fresh air flowing through, dissipates heat to be low-temperature high-pressure refrigerant liquid, flows out of the first air supply coil 7, is throttled by the throttling device 5, becomes low-temperature low-pressure refrigerant again, returns to the exhaust coil 3, and continues the refrigerant circulation.

In the heating mode of the unit of the embodiment, the control method comprises the following steps: the heating capacity is adjusted by changing the rotating speed of the compressor 1, when the air supply temperature is lower than a set value of a user, the rotating speed of the compressor 1 is increased, otherwise, the rotating speed is reduced. The control strategies of the exhaust coil branch throttling device 5, the air supply fan 14 and the exhaust fan 15 are consistent with the dehumidification mode (full fresh air).

The unit of the embodiment may face the risk of frosting in the heating mode, and is adjusted in control as follows: (1) when the temperature of the inlet air is low and the frosting risk is common, the bypass air door 23 at the bottom of the total heat exchanger 0 is opened, so that most of the fresh air is directly bypassed without carrying out heat and humidity exchange with the return air, the temperature of the return air entering the exhaust coil 3 is high, the evaporation temperature of the refrigerant in the exhaust coil 3 is increased, and the frosting possibility is reduced. (2) When the air inlet temperature is further reduced and the frosting risk is serious, the throttling device 6 of the second air supply coil branch is opened, so that the second air supply coil 6 becomes a refrigerant evaporator connected with the air exhaust coil 3 in parallel, the heat exchange quantity of the air exhaust coil 3 is reduced, the evaporation temperature is increased, and the frosting risk is reduced.

Under the heating mode of this embodiment unit, structural feature and the beneficial effect who obtains are: (1) the tail end of the air exhaust flow path is provided with an air exhaust coil 3, after the return air in the total heat exchanger 0 is primarily recovered by fresh air, the residual waste heat of the return air is further recovered and utilized in the air exhaust coil 3 by utilizing a heat pump, so that the overall energy utilization efficiency of the unit is improved; (2) the bottom of the total heat exchanger 0 is provided with a bypass air door which is opened when the inlet air temperature is lower, so that the effect of shielding total heat exchange is achieved greatly, and the frosting risk of the heat pump system is reduced.

4. Heat exchange pattern, see FIG. 7

The air supply to the indoor in the mode is completely composed of outdoor fresh air. And (4) filtering and heat exchanging the outdoor fresh air and then sending the fresh air to the indoor. Is suitable for the low environmental working condition (such as the air inlet state at 16 ℃/14 ℃) in the transition season.

In the heat exchange mode, the unit of the embodiment has the following component states: the heat pump system is shut down. The supply fan 14 and the exhaust fan 15 are turned on. The return air internal circulation damper 16 is closed. The bottom bypass tuyere 23 is closed.

In the heat exchange mode of the unit of the embodiment, the air flow path state is as follows: outdoor fresh air is introduced from the air inlet 10, passes through the air inlet filter 19 for preliminary purification, the total heat exchanger 0 and the return air heat and humidity exchange and the air inlet filter 20 for deep purification in sequence under the drive of the air supply fan 14, and is sent into the room through the air inlet 11. The indoor return air is introduced from the return air inlet 12, passes through the return air filter 21 for filtration and purification, the total heat exchanger 0 for heat and moisture exchange with the fresh air in sequence under the drive of the exhaust fan 15, and is exhausted to the outside from the exhaust air inlet 13.

In the heat exchange mode of the unit of the embodiment, the control method comprises the following steps: (1) the indoor air quality is adjusted through the air supply fan 14, when the indoor carbon dioxide concentration is higher than a set value, the rotating speed of the air supply fan 14 is increased, the fresh air volume is increased, and otherwise, the rotating speed is reduced. (2) The exhaust fan 15 is linked with the air supply fan 14, so that the exhaust air volume is always maintained at 80-90% of the intake air volume, and the indoor positive pressure of the air-conditioned room is controlled.

This embodiment unit is under the heat exchange mode, and structural feature and the beneficial effect who obtains are: the total heat exchanger can operate independently, and fresh air can be heated by return air and then sent into a room under the conditions of low outdoor humidity and low temperature. The mode is efficient in muting, and user experience is enhanced.

5. Bypass mode, see FIG. 8

The air supply to the indoor in the mode is completely composed of outdoor fresh air. The fresh air outside is filtered and then sent to the indoor. Suitable operating mode in transition season, outdoor new trend is fit for directly letting in indoor promptly.

In the bypass mode, the unit of this embodiment has the following component states: the heat pump system is shut down. The blowing fan 14 is turned on and the exhaust fan 15 is turned off. The return air internal circulation damper 16 is closed. The bottom bypass tuyere 23 is opened.

In the bypass mode of the unit of this embodiment, the air flow path state is: outdoor fresh air is introduced from the air inlet 10, and is driven by the air supply fan 14 to sequentially pass through the air inlet filter 19 for preliminary purification, the bypass air inlet 23 at the bottom of the total heat exchanger 0 and the air supply filter 20 for deep purification, and then is sent into the room through the air supply air inlet 11.

In the bypass mode of the unit of this embodiment, the control method is as follows: the indoor air quality is adjusted through the air supply fan 14, when the indoor carbon dioxide concentration is higher than a set value, the rotating speed of the air supply fan 14 is increased, the fresh air quantity is increased, and otherwise, the rotating speed is reduced.

The unit of this embodiment is under bypass mode, and structural feature and the beneficial effect who obtains are: by arranging the bypass air opening 23 at the bottom of the total heat exchanger 0 and opening in the mode, the fresh air is allowed to be introduced after being filtered, and the effect similar to mechanical bypass is realized. The mode is switched to under the suitable working condition in the transition season, so that the reduction of the operation energy consumption is facilitated.

Example 2

The structural arrangement of the embodiment 2 is similar to that of the embodiment 1, and the different modes and functions are similar. The main difference is the arrangement of the refrigerant circulation flow path.

Referring to fig. 10 and 11, the exhaust coil 3 and the second blowing coil 4 in embodiment 2 are in series, so that only one throttling device 5 is needed. The exhaust coil 3 and the second blowing coil 4 in the embodiment 1 are connected in parallel, and two branches are respectively controlled by a throttling device.

The parallel connection of the exhaust coil 3 and the second air supply coil 4 in the embodiment 1 has the advantages that the accurate control of the air supply temperature can be realized in the dehumidification mode, the second air supply coil 4 can be selectively shielded in the heating mode, and the unit performance is improved under the working condition of no frosting. And the advantage of the series connection of the exhaust coil 3 and the second air supply coil 4 in the embodiment 2 lies in that the cold energy of fresh air after being cooled and dehumidified by the first air supply coil 7 can be utilized to the maximum under the dehumidification mode, the supercooling degree of the heat pump cycle is larger, and the system dehumidification capacity is strong. And in the heating mode, if the heat pump is started, the high evaporation temperature is always kept, and frosting is avoided.

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 terms first, second, etc. are merely used to descriptively distinguish one element from another. Unless otherwise stated, the above words have no special meaning.

In the above-mentioned embodiment not show all parts in refrigerant circulation and wind channel completely, in the implementation, set up common refrigeration auxiliaries such as high-pressure reservoir, vapour and liquid separator, oil separator, filter, desicator in the refrigerant return circuit, set up air treatment auxiliaries such as silencer, humidifier, heater, sterilizing equipment in the wind channel, choose different air supply spouts and return air grid for use, change the fan position, or do not deviate from the utility model discloses technical scheme's spirit increases heat exchanger, and fan and blast gate etc. all can not be regarded as right the utility model discloses carried out substantive improvement, should belong to the utility model discloses protection scope.

It is noted that, herein, relational terms such as first and second, and the like may be used solely to distinguish one entity or action from another entity or action without necessarily requiring or implying any actual such relationship or order between such entities or actions. Also, the terms "comprises," "comprising," or any other variation thereof, are intended to cover a non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements does not include only those elements but may include other elements not expressly listed or inherent to such process, method, article, or apparatus. Without further limitation, an element defined by the phrase "comprising an … …" does not exclude the presence of other identical elements in a process, method, article, or apparatus that comprises the element.

Claims (9)

1. The temperature and humidity double-control heat pump fresh air dehumidifier with deep total heat recovery is characterized by comprising an air flow path and a refrigerant circulating flow path, wherein the air flow path comprises an air supply flow path and an air exhaust flow path;

the two ends of the air supply flow path are provided with an air inlet (10) and an air supply outlet (11);

two ends of the air exhaust flow path are provided with an air return air inlet (12) and an air exhaust air inlet (13);

a total heat exchanger (0) is arranged at the intersection of the air supply flow path and the air exhaust flow path;

the refrigerant circulating flow path comprises a compressor (1), a four-way reversing valve (2), an exhaust coil (3), an exhaust coil branch throttling device (5), a second air supply coil (4), a second air supply coil branch throttling device (6) and a first air supply coil (7) which are connected in sequence;

the four-way reversing valve (2), the exhaust coil branch throttling device (5), the second air supply coil (4), the second air supply coil branch throttling device (6) and the first air supply coil (7) are all arranged in an air supply flow path;

the compressor (1) and the exhaust coil (3) are both arranged in an exhaust flow path.

2. The temperature and humidity double-control heat pump fresh air dehumidifier for deep total heat recovery according to claim 1, wherein an air inlet air sensor (17) is arranged at an air inlet section of the air supply flow path and used for monitoring the temperature and humidity of inlet air;

and the return air section of the exhaust air flow path is provided with a return air sensor (18) for monitoring the temperature, the humidity and the carbon dioxide concentration of return air.

3. The temperature and humidity double-control heat pump fresh air dehumidifier with deep total heat recovery according to claim 2, wherein an air supply fan (14) and an air exhaust fan (15) are respectively arranged at the air inlet section of the air supply flow path and the air return section of the air exhaust flow path, and the air supply fan (14) and the air exhaust fan (15) are variable-frequency fans with adjustable speed.

4. The temperature and humidity double-control heat pump fresh air dehumidifier with deep total heat recovery according to claim 1, wherein a bypass air port (23) is reserved at the bottom of the total heat exchanger (0), and the bypass air port (23) is located in the direction of an air supply flow path.

5. The temperature and humidity double-control heat pump fresh air dehumidifier with deep total heat recovery according to claim 1, wherein the air supply flow path is respectively provided with an air inlet filter (19) and an air supply filter (20) at the front and the rear of the total heat exchanger (0);

the air exhaust flow path is provided with a return air filter (21) at the return air section.

6. The temperature and humidity double-control heat pump fresh air dehumidifier for deep total heat recovery according to claim 1, wherein a return air internal circulation air door (16) is further arranged at the joint of the return air section of the exhaust air flow path and the air supply section of the air supply flow path.

7. The temperature and humidity double-control heat pump fresh air dehumidifier with deep total heat recovery according to claim 1, wherein four interfaces of the four-way reversing valve (2) are respectively connected with a first air supply coil (7), an air exhaust coil (3), a second air supply coil (4), an air suction port of the compressor (1) and an air exhaust port of the compressor (1), wherein the air exhaust coil (3) and the second air supply coil (4) are connected to the same interface of the four-way reversing valve (2).

8. The temperature and humidity double-control heat pump fresh air dehumidifier for deep total heat recovery according to claim 7, wherein a branch where the exhaust coil (3) is located and a branch where the second air supply coil (4) is located are arranged in parallel on a refrigerant flow path, one end of the branch is connected to a connector C of the four-way reversing valve (2), and the other end of the branch is connected to the first air supply coil (7) through the exhaust coil branch throttling device (5) and the second air supply coil branch throttling device (6) respectively.

9. The temperature and humidity double-control heat pump fresh air dehumidifier with deep total heat recovery according to claim 8, wherein the exhaust coil branch throttling device (5) and the second supply coil branch throttling device (6) are both one of capillary tubes, throttling short pipes or electronic throttling devices.

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