CN107676902B

CN107676902B - Air conditioning system

Info

Publication number: CN107676902B
Application number: CN201711021470.6A
Authority: CN
Inventors: 石文星; 宋波; 杨絮霏; 李艳杰; 陈炜; 王宝龙; 丁连锐
Original assignee: Guoanrui Beijing Technology Co ltd; Tsinghua University
Current assignee: National Security (beijing) Technology Co Ltd; Tsinghua University
Priority date: 2017-10-27
Filing date: 2017-10-27
Publication date: 2020-06-16
Anticipated expiration: 2037-10-27
Also published as: CN107676902A

Abstract

The application provides an air conditioning system, this air conditioning system includes: the fresh air module comprises a compressor, a condenser and an evaporator which are in fluid connection, and the evaporator is used for regulating and controlling the temperature and/or the humidity of fresh air; and the flow path of the temperature module is in heat exchange with the flow path of the fresh air module but is not communicated with the flow path of the fresh air module, the temperature module is used for regulating and controlling the temperature of a use side, and the temperature module comprises: the heat exchanger is used for exchanging heat with the fresh air module; a heat radiator connected to the heat exchanger to form a closed flow path; a pump connected in series in the closed flow path; wherein the fresh air module comprises a bidirectional flash evaporator connected to the condenser, the evaporator and the heat exchanger respectively. According to the air conditioning system, the temperature and the humidity can be independently controlled on the basis of energy conservation.

Description

Air conditioning system

Technical Field

The present application relates to the field of environmental protection, and more particularly, to an air conditioning system capable of controlling temperature and humidity relatively independently.

Background

Currently, people have higher requirements for living or living environments, and therefore, more and more spaces are equipped with multi-split air conditioning systems to improve the comfort of people in the activity space. In order to obtain higher environmental comfort, not only the temperature of the environment but also the humidity of the environment need to be regulated. Therefore, how to independently control the temperature and humidity becomes a technical problem to be solved for the air conditioning system.

Disclosure of Invention

The application aims to provide a technical scheme capable of independently regulating and controlling temperature and humidity.

In order to achieve the object of the present application, there is provided an air conditioning system including: the fresh air module comprises a compressor, a condenser and an evaporator which are in fluid connection, and the evaporator is used for regulating and controlling the temperature and/or the humidity of fresh air; and the flow path of the temperature module is in heat exchange with the flow path of the fresh air module but is not communicated with the flow path of the fresh air module, the temperature module is used for regulating and controlling the temperature of a use side, and the temperature module comprises: the heat exchanger is used for exchanging heat with a flow path of the fresh air module, which passes through the heat exchanger; a heat radiator located in the use side and connected to the heat exchanger to form a closed flow path; a pump connected in series in the closed flow path; wherein the new trend module includes two-way flash vessel, and this two-way flash vessel includes: the first connecting pipe is communicated with the condenser and extends into the lower part of the flash evaporator; the second connecting pipe is communicated with the evaporator and extends into the lower part of the flash evaporator; and the first connecting port is positioned at the lower part of the flash evaporator, the second connecting port is positioned at the upper part of the flash evaporator, the first connecting port is connected to the water inlet of the heat exchanger through a first one-way valve, and the water outlet of the heat exchanger is connected to the second connecting port through an electromagnetic valve.

Preferably, the temperature module comprises a fresh air processor, and the fresh air processor is connected with the heat radiator in parallel and used for regulating and controlling the temperature and/or the humidity of the fresh air.

Preferably, the fresh air processor and/or the heat exchanger are connected with a regulating valve in series.

Preferably, the compressor comprises a first compressor and a second compressor connected in series, and a four-way valve is connected to each of the first compressor and the second compressor to selectively deliver the fluid medium to the condenser or the evaporator.

Preferably, the upper part of the bidirectional flash evaporator is provided with a gas phase outlet which is connected to a flow path between the first compressor and the second compressor.

Preferably, the condenser and the evaporator are connected in series with a first and a third throttle valve, respectively.

Preferably, the air conditioning system includes a heat exchange bypass connected in parallel to the evaporator and passing through the heat exchanger to enable heat exchange.

Preferably, a second check valve and/or a second throttling valve are/is connected in series in the heat exchange bypass.

Preferably, in the flow direction of the fresh air, the fresh air processor and the evaporator are arranged from upstream to downstream in sequence.

In the technical scheme of this application, because the new trend module is mainly responsible for the regulation and control of temperature and/or humidity, and the temperature module that does not communicate in the new trend module is used for being responsible for the regulation and control of temperature, relatively independent between the two, consequently, the temperature regulation of user side can be realized to the temperature module, and the new trend module can carry out humidity (and/or temperature) to the new trend and adjust, and temperature module and new trend module are relatively independent to can eliminate cold and hot offset phenomenon, improve the unit performance.

Drawings

The accompanying drawings, which are incorporated in and constitute a part of this application, illustrate embodiments of the application and, together with the description, serve to explain the application and are not intended to limit the application. In the drawings:

fig. 1a is a schematic view of a connection structure of an air conditioning system according to a first embodiment of the present application;

FIG. 1b is a schematic diagram illustrating operation of the air conditioning system of FIG. 1a during summer conditions;

FIG. 1c is a pressure-enthalpy diagram showing the change in refrigerant state during operation in summer conditions;

FIG. 1d is a schematic diagram illustrating the operation of the air conditioning system of FIG. 1a during winter conditions;

FIG. 1e is a pressure-enthalpy diagram showing the change in refrigerant state during operation in winter conditions;

fig. 2a is a schematic view of a connection structure of an air conditioning system according to a second embodiment of the present application;

FIG. 2b is a schematic diagram of the operation of the air conditioning system shown in FIG. 2a during summer conditions;

FIG. 2c is a schematic diagram of the air conditioning system of FIG. 2a operating in winter conditions;

fig. 3a is a schematic view of a connection structure of an air conditioning system according to a third embodiment of the present application;

FIG. 3b is a schematic diagram illustrating operation of the air conditioning system shown in FIG. 3a during summer conditions;

FIG. 3c is a schematic diagram of the air conditioning system of FIG. 3a operating in winter conditions;

fig. 4a is a schematic view of a connection structure of an air conditioning system according to a fourth embodiment of the present application;

FIG. 4b is a schematic diagram illustrating operation of the air conditioning system of FIG. 4a during summer conditions;

FIG. 4c is a schematic diagram of the air conditioning system of FIG. 4a operating in winter conditions;

fig. 4d is a schematic diagram according to another embodiment of the present application.

Detailed Description

The following detailed description describes specific embodiments of the present application. In addition, the features of the embodiments and the respective embodiments in the present application may be combined with each other without conflict.

As shown in the drawings, the present application provides an air conditioning system comprising: the fresh air module comprises a compressor, a condenser 11 and an evaporator 12 which are in fluid connection, and the evaporator 12 is used for regulating and controlling the temperature and/or the humidity of fresh air; and the temperature module is used for regulating and controlling the temperature of the use side.

The fresh air module is used for introducing purified outdoor fresh air into the room, so that the indoor air is kept to have sufficient cleanliness. In order to ensure a good comfort of the indoor environment, the temperature and/or the humidity of the fresh air (fresh air flow) introduced is controlled by means of a fresh air module (as an air conditioning unit) which essentially comprises a compressor, a condenser and an evaporator. Of course, in order to realize the function of the air conditioner, the fresh air module may also include other auxiliary components, such as a throttle valve, a refrigerant storage, etc., which are not described in detail herein, and may be realized by using the composition structure and operation principle of the conventional air conditioner. Because the air conditioning function of new trend module can regulate and control the temperature and/or the humidity of new trend, especially can regulate and control the humidity of new trend to realize the regulation and control of the humidity in the space.

Simultaneously, still be provided with the temperature module among the technical scheme of this application, mainly regulate and control the temperature of user side, the flow path of this temperature module and the flow path of new trend module do not communicate but can carry out the heat exchange each other to the regulation and control to temperature in the user side space. By use-side is meant a space where temperature and/or humidity is to be regulated, such as a building space, a conference room or the like where people live, in particular a room(s) and/or end(s) within the space.

In a conventional air conditioning system, in order to meet the requirement of dehumidification, the evaporation temperature needs to be lowered; on the other hand, in order to satisfy the temperature requirement, the air supply temperature needs to be increased by reheating. Therefore, the performance of the air conditioning system is reduced due to the low evaporation temperature, and a cold and heat offset phenomenon is generated, so that energy is wasted.

And in the technical scheme of this application, because the new trend module is mainly responsible for the regulation and control of temperature and/or humidity, and the temperature module that does not communicate in the new trend module is used for being responsible for the regulation and control of temperature, relatively independent between the two, consequently, higher evaporating temperature can be realized to the temperature module to adjust the temperature, the new trend module can realize that low evaporating temperature carries out humidity (and/or temperature) and adjusts, in order to eliminate cold and hot offset phenomenon, improves the unit performance. That is to say, in the technical scheme of this application, can realize the independent control of temperature and humidity on the basis of energy-conservation.

Each of the modules of the air conditioning system of the present application will be described in detail below.

A,Temperature module

As shown in the drawings, the temperature module includes: a heat exchanger 20, the heat exchanger 20 being for heat exchange with a flow path of the fresh air module passing through the heat exchanger; a heat radiator 21, the heat radiator 21 being located inside the use side and connected to the heat exchanger 20 to form a closed flow path; and a pump 22, the pump 22 being connected in series in the closed flow path.

The heat exchanger 20 may be a heat exchanger selected as appropriate according to the operating conditions, such as a plate heat exchanger. In the heat exchanger 20, the flow path of the fresh air module and the flow path of the temperature module are arranged adjacent to each other, but are not communicated with each other, so that heat exchange is realized. Thus, in the following, when the fresh air module is described with reference to the heat exchanger 20, it is generally understood as the flow path of the fresh air module through the heat exchanger 20; when reference is made to the heat exchanger 20 in describing the temperature module, it is understood that the flow path of the temperature module through the heat exchanger. Of course, the heat exchanger 20 is referred to herein as an integral means of effecting heat exchange.

The pump 22 is used to provide a driving force for the refrigerant (which may be a cold/hot carrier, as will be understood hereinafter) in the flow path of the temperature module, so that the fluid medium (such as refrigerant or water) in the flow path of the temperature module can be kept flowable in a predetermined state. On the one hand, the heat exchanger 20 can exchange heat with the flow path of the fresh air module, and on the other hand, the heat-exchanged medium can flow to the heat radiator 20. The pump 22 may be selected from any suitable industrial parameter, such as a gear pump, a plunger pump, etc., depending on the operating conditions.

The heat radiator 21 is located in the use side, and since the heat radiator, the pump and the heat exchanger 20 are connected to form a closed flow path, when the medium after heat exchange flows to the heat radiator 20, the space on the use side can be temperature-controlled by the heat radiator 20, so that the temperature in the use side can be increased or decreased to reach a predetermined temperature level. The heat radiator 20 may be a cold radiation ceiling or a dry fan coil, etc.

In order to control the operating parameters of the temperature module by means of the flow state of the medium, a valve device for throttling or switching can be provided in the flow path of the temperature module. Alternatively, the flow rate of the pump 22 may be adjustable.

As described above, the main function of the fresh air device is to regulate and control the temperature and/or humidity of the fresh air, but under the preferable condition, the temperature module can also be used to regulate and control the temperature of the fresh air. As shown in the accompanying drawings, the temperature module comprises a fresh air processor 23, and the fresh air processor 23 is connected in parallel with the heat radiator 21 and is used for regulating and controlling the temperature and/or humidity of the fresh air.

Because the fresh air processor 23 is connected with the heat radiator 12 in parallel, when the medium is subjected to heat exchange, one path of medium flows to the heat radiator 21, so that the temperature of the use side is regulated and controlled; and the other path of medium enters the fresh air processor 23 to regulate and control the temperature of the fresh air. The two media then converge again toward the pump 22. Preferably, in order to adapt the temperature module to different working conditions, as shown in the figure, the fresh air processor 23 and/or the heat exchanger 20 are connected in series with regulating valves. The fresh air processor 23 may be a surface air cooler or a radiator, etc. The temperature modules can be relatively independent through the cooperation of valves in the air conditioning system.

The connection relationship and the basic operation process of the temperature module are described in detail above. The operation under different conditions will be described in detail with reference to the drawings.

II,Fresh air module

As described above, the main function of the fresh air module is to regulate and control the temperature and/or humidity of fresh air by using the air conditioning device. In the technical scheme of the application, besides the adoption of the traditional air conditioning device, different implementation modes are provided for the fresh air module, as shown in each drawing. The conventional air conditioning device will not be described in detail, and various embodiments of the fresh air module and corresponding various embodiments of the entire air conditioning system will be described in detail with reference to the accompanying drawings. In addition, it should be noted that the temperature module described above is applicable to all the following embodiments.

2.1 embodiment one

Fig. 1a to 1e illustrate a first embodiment of the present invention.

As shown in fig. 1a, 1b and 1d, the fresh air module comprises a compressor, a condenser 11 and an evaporator 12 which are in fluid connection, i.e. in fluid communication with each other directly and/or indirectly. In a first embodiment, the fresh air module further includes a bidirectional flash evaporator 13, and the bidirectional flash evaporator 13 includes: a first connection pipe 131, wherein the first connection pipe 131 is communicated with the condenser 11 and extends into the lower part of the flash evaporator 13; a second connection pipe 132, wherein the second connection pipe 132 is communicated with the evaporator 12 and extends into the lower part of the flash evaporator 13; and a first connection port 133 and a second connection port 134, the first connection port 133 being located at a lower portion of the flash evaporator 13, the second connection port 134 being located at an upper portion of the flash evaporator 13, the first connection port 133 being connected to an inlet of the heat exchanger 20 through a first check valve 139, and an outlet of the heat exchanger 20 being connected to the second connection port 134 through a solenoid valve 140.

The bidirectional means that the first connection pipe and the second connection pipe can be used as an input pipe and an output pipe, and therefore, the refrigerant medium can be conveyed in two directions through the first connection pipe and the second connection pipe.

After the liquid refrigerant medium under a certain pressure enters the two-way flash evaporator 13 through one of the first connecting pipe and the second connecting pipe, flash evaporation is carried out due to the change of the pressure, so that medium steam is formed at the top of the inner cavity of the two-way flash evaporator 13, and medium liquid is accumulated at the bottom. Subsequently, the liquid medium flows out of the two-way flash evaporator through the other of the first connecting pipe and the second connecting pipe.

In the case of the lower first connection 133, the liquid medium can be conducted to the heat exchanger 20 via the first non-return valve 139 via the first connection 133. After heat exchange between the heat exchanger and the flow path of the temperature module is completed, the heat is returned to the bidirectional flash evaporator through the second connection port 134. As shown in fig. 1a and 1b, an electromagnetic valve 140 is connected in series to the second connection port 134 to control the opening and closing of the flow path at the second connection port 134. First one-way valve 139 only allows liquid medium to flow out of bi-directional flash vessel 13 and does not allow fluid to flow to the bi-directional flash vessel. The function of the valve 140 and the first check valve 139 is also sufficient to adapt the flow path of the first embodiment to different operating conditions, which will be described in detail below.

The compressor may be one or more, but preferably, as shown in fig. 1a, 1b and 1d, the compressor comprises a first compressor 101 and a second compressor 102 connected in series, and a four-way valve is connected to each of the first compressor 101 and the second compressor 102 to selectively deliver a fluid medium (such as heat transfer medium/refrigerant) to the condenser 11 or the evaporator 12.

The four-way valve is used for conveying a pressure medium to the condenser 11 or the evaporator 12 by the aid of the first compressor and the second compressor which are connected in series under different working conditions. For example, when performing a cooling operation, the medium from the evaporator 12 needs to be compressed and then sent to the condenser 11; when heating is performed, the medium from the condenser 11 needs to be compressed and sent to the evaporator 12. The different modes of operation will be described in detail below. The four-way valve can be selected from common structural forms and is not described in detail here.

The first and second compressors may be selected for a range of suitable industrial parameters depending on operating conditions. Preferably, the first compressor and the second compressor have different industrial parameters, such as volume, flow rate, suction pressure, discharge pressure, etc. Preferably, the first compressor is rated for a power rating greater than the second compressor.

By the design of the double compressors, the refrigerant medium can be conveniently compressed to more physical states, so that a good working effect is obtained.

Preferably, as shown in fig. 1a and 1b, the upper portion of the bi-directional flash evaporator 13 is provided with a gas phase outlet 135, and the gas phase outlet 135 is connected to the flow path between the first compressor 101 and the second compressor 102, so that the gaseous medium can be supplemented into the main flow path under predetermined conditions.

Preferably, as shown in fig. 1a and 1b, the condenser 11 and the evaporator 12 are connected in series with a first throttle EEV1 and a third throttle EEV3, respectively. The throttle valve serves to control the flow of the refrigerant medium and at the same time to regulate the physical state of the refrigerant medium, e.g. to control the pressure of the refrigerant medium and thus the enthalpy.

Preferably, the air conditioning system includes a heat exchange bypass in which the heat exchanger 20 is connected in series, so that the heat exchanger 20 is connected in parallel to the evaporator 12. Further preferably, a second check valve 136 and/or a second throttle EEV2 are connected in series in the heat exchange bypass to control the flow direction and amount of refrigerant medium.

The working principle of the technical solution of the first embodiment under different working conditions is described below.

Summer working condition of a

In summer working conditions, the main realized function is independent temperature and humidity control, not only meets the setting requirement of indoor environment, but also can improve the performance of the system and reduce energy consumption. Wherein the use side in the system can be the ends of a plurality of rooms.

As shown in fig. 1b and 1c, the low-pressure refrigerant gas is compressed to the intermediate state point 2 by the second compressor 102, then mixed with the medium-pressure refrigerant gas (state point 6') from the two-way flash evaporator to the state point 3, and then compressed to the state point 4 by the first compressor, and the high-temperature and high-pressure refrigerant gas is output.

The high temperature, high pressure refrigerant gas passes through condenser 11, condenses to a high pressure refrigerant liquid, throttles to intermediate state point 6 via EEV1, and enters bi-directional flash evaporator 13.

In the bi-directional flash vessel 13, the upper portion collects refrigerant gas at an intermediate pressure and the lower portion collects refrigerant liquid at an intermediate pressure. The refrigerant liquid in the lower part of the bidirectional flash evaporator is divided into two parts: one feed liquid is supplied to the heat exchanger 20 through the first one-way valve 139 by means of gravity feed liquid through the first connecting port 133, high-temperature cold water is prepared at a higher evaporation temperature (intermediate temperature), and saturated refrigerant gas generated after evaporation flows back to the bidirectional flash evaporator 13 through the second connecting port 134; the other stream enters the evaporator 12 (indoor heat exchanger) through the secondary throttling of the throttling valve EEV3, dehumidifies the outdoor fresh air at a lower evaporation temperature, and then returns to the compressor through the four-way valve.

The medium-pressure refrigerant gas in the upper half part of the bidirectional flash evaporator is supplemented to the compressor and compressed into high-temperature and high-pressure gaseous refrigerant.

One part of the high-temperature cold water prepared by the heat exchanger 20 flows to the fresh air processor 23 for reheating the dehumidified fresh air, and the other part of the high-temperature cold water enters the indoor heat radiator 21 for cooling the indoor space, so that a plurality of rooms and/or a plurality of tail ends can work simultaneously.

According to the description, in summer working conditions, the high-temperature cold water is prepared by adopting the temperature module and is supplied to the heat radiator to cool the indoor; meanwhile, the evaporator 12 is used to dehumidify the fresh outdoor air. Therefore, the temperature and the humidity are independently controlled by adopting double evaporation temperatures, and the performance of an air conditioning system (such as a multi-split refrigeration system) is improved substantially.

B winter conditions

In winter working conditions, the air conditioning system mainly achieves the function of rapidly enabling indoor temperature to reach heating set requirements and improving comfort level experience of users. And meanwhile, the running performance of the air conditioning system can be improved.

As shown in fig. 1d and 1e, the low-pressure refrigerant gas is compressed to the intermediate state point 2 by the first compressor 101, then mixed with the intermediate-pressure (state point 6') refrigerant gas from the two-way flash evaporator to the state point 3, and then compressed to the state point 4 by the second compressor 102, and the high-temperature and high-pressure refrigerant gas is discharged.

The high-temperature high-pressure refrigerant gas is divided into two streams: one of the fresh air used for preheating entering the room reaches a state point 5, and then is throttled to a state point 6 through an EEV 3; the other stream enters a heat exchanger 20 to prepare hot water for radiation heating to a state point 5, then is throttled to a state point 6 through a throttle valve EEV2, is mixed with the refrigerant of the other path, and enters a bidirectional flash evaporator 13.

The upper portion of the bi-directional flash evaporator 13 collects refrigerant gas at intermediate pressure and the lower portion collects refrigerant liquid at intermediate pressure. The middle pressure refrigerant gas in the upper half part is supplemented to the compressor through a pipeline to be used as middle air supplement of two-stage compression. The refrigerant liquid in the bidirectional flash evaporator is throttled for the second time by the throttle valve EEV1 and then enters the condenser 11 to be evaporated, and then returns to the compressor to complete the primary cycle.

A small part of the prepared hot water for heating flows to the fresh air processor 23 and is used for reheating outdoor fresh air, and the other part of the prepared hot water enters the indoor heat radiator 21, so that the temperature in a room can quickly reach the heating requirement.

As can be seen from the above description, the air conditioning system according to the first embodiment first performs fluorine air heat exchange and water air heat exchange through, for example, a fan coil at the evaporator, and preheats fresh air, so that the fresh air entering the room is at a higher temperature; the heat radiator 21 is also used to directly heat the indoor air at the end of radiation, enabling the indoor temperature to be quickly reached. Compared with the traditional heating only by adopting the conventional radiation, the time from the system starting to operate to the indoor heating requirement is greatly shortened. Moreover, as can be seen from the operation principle of winter working conditions, the cycle of the system is single condensation temperature and evaporation temperature, but the pressure ratio is reduced compared with the conventional single-stage compression due to the adoption of the double-stage compression system, so that the performance of the system is improved.

2.2 embodiment two

Fig. 2a to 2c illustrate a second embodiment of the present application.

As shown in fig. 2a to 2c, a four-way valve is connected to the compressor 30 to selectively deliver the fluid medium to the condenser 11 or the evaporator 12. Similar to the first embodiment, the four-way valve serves to allow the compressor to deliver pressure medium to the condenser 11 or the evaporator 12 using the four-way valve under different operating conditions.

In the second embodiment, when the compressor 30 feeds the condenser 11, the heat exchanger 20 is connected in parallel with the evaporator 12; and in the case where the compressor is supplied to the evaporator 12, the compressor is connected to the condenser 11 through the heat exchanger 20, and the evaporator 12 is connected in parallel with a flow path between the heat exchanger 20 and the condenser 11.

When the compressor 30 delivers high pressure refrigerant medium to the condenser 11, the condensed medium is heat exchanged through the heat exchanger 20, thereby bringing the medium in the temperature module into a desired physical state. Meanwhile, the fresh air can be dehumidified by the evaporator 12. When the compressor 30 delivers the medium to the evaporator 12, the pressure medium is first subjected to a heat exchange process by means of the heat exchanger 20 in order to meet the requirements of the temperature module. One part of the medium flowing out of the heat exchanger 20 flows to the condenser 11, and the other part flows to the evaporator 12 to regulate the temperature and/or humidity of the fresh air. The above-described operating conditions will be described in detail below.

As shown in fig. 2a to 2c, preferably, a reheater 14 is connected in series upstream of the evaporator 12, and the reheater 14 is used for regulating and controlling the temperature of the fresh air, so that the fresh air can be subjected to more precise temperature control by using the reheater 14. Preferably, in order to adapt the solution of the second embodiment to different working conditions, as shown in the figure, two upstream check valves 137, 137 'are connected in series upstream of the reheater 14, which allow the fluid from the condenser 11 to flow to the reheater only, and the fluid from the heat exchanger 20 to flow to the reheater only, and two downstream check valves 138, 138' are connected in series downstream of the evaporator 12, which allow the fluid from the evaporator 12 to flow to the compressor and the condenser only. The two pairs of check valves can control the flow direction of the refrigerant medium, so that the system is allowed to be suitable for different working conditions.

Preferably, the heat exchanger 20 is connected in series with a first throttle EEV1 and a third throttle EEV 3; and/or a second throttle EEV2 is connected in series upstream of the evaporator 12 to control the flow direction and amount of refrigerant medium. Also preferably, as shown, the flow path between the evaporator 12 and the reheater 14 is connected to the flow path between the first and third throttle valves EEV1, EEV3 via valve 141. The air conditioning system can be selectively enabled to perform a dehumidifying function by the control of the valve 141.

The connection structure of the second embodiment is described above in detail, and the working principle of the technical solution of the second embodiment under different working conditions is described below.

Summer working condition of a

As shown in fig. 2b, the high-temperature and high-pressure refrigerant discharged from the compressor 30 passes through the four-way valve, enters the condenser 11 (outdoor air-cooled heat exchanger) to be cooled into low-temperature and high-pressure liquid, and then is divided into two paths: one path of low-temperature high-pressure refrigerant liquid enters the reheater 14 through an upstream check valve 137 to heat the dehumidified fresh air, then the refrigerant enters the evaporator 12 to cool and dehumidify the outdoor fresh air after being throttled and expanded by the throttle valve EEV2, and the evaporated low-pressure gaseous refrigerant flows back to the compressor through a downstream check valve 138 through the four-way valve; the excess refrigerant flows through the valve 141 along the bypass line (via the solenoid valve 2) into the outlet end of the first throttle EEV 1. The other path of refrigerant is mixed with the refrigerant flowing into the outlet end of the first throttle valve EEV1, and then is expanded and throttled by the EEV3, enters the heat exchanger 20, and then is subjected to heat exchange with the temperature control module to prepare high-temperature cold water, so that the fresh air handling unit precools fresh air through the fresh air processor 23, and the temperature of the indoor tail end is reduced through the heat radiator 21. The other refrigerant then flows back to the compressor through the four-way valve, completing the cycle.

The valve 141 (e.g., a solenoid valve) is opened and closed to switch between the dehumidification mode and the non-dehumidification mode, and the opening of the first throttle EEV1 is adjusted to adjust the flow rates of the refrigerant passing through the reheater 14 and the refrigerant on the main line, so as to satisfy different reheating requirements.

As can be seen from the above description, in summer, the heat exchanger 20 directly prepares high-temperature cold water to supply the radiation cooling in the room; and (4) dehumidifying the outdoor fresh air by using a low-temperature evaporator through heat exchange of fluorine air. The temperature and humidity are independently controlled, and the energy consumption of the system is relatively low.

B winter Condition

In the technical scheme of the second embodiment, the winter working condition has two sub-modes: a heating and dehumidifying mode and a separate heating mode.

1) Heating and dehumidifying mode

The high-temperature and high-pressure gaseous refrigerant discharged from the compressor 30 enters the heat exchanger 20 through the four-way valve, and low-temperature hot water for heating is prepared through heat exchange.

The condensed high-pressure liquid refrigerant is divided into two paths: one path of refrigerant enters the reheater 14 through another upstream check valve 137' to heat the dehumidified fresh air, and meanwhile, the supercooling degree of the refrigerant is further increased; after that, a part of the refrigerant is collected to an outlet pipe of the third throttle valve EEV3 through a bypass of the valve 141, and a part of the refrigerant enters the evaporator 12 to cool and dehumidify the fresh outdoor air after being throttled and expanded by the second throttle valve EEV2, and returns to an outlet of the first throttle valve EEV1 through another downstream check valve 138', and joins the gas-liquid two-phase refrigerant in the main loop after being throttled by the first throttle valve EEV 1. Meanwhile, the other path of high-pressure liquid refrigerant flowing out of the heat exchanger 20 is slightly decompressed by the third throttle EEV3, then is mixed with the refrigerant passing through the reheater bypass, then is subjected to expansion throttling by the first throttle EEV1, and then is mixed with the gaseous refrigerant returning from the dehumidification evaporator 12 through the other downstream check valve 138', and then enters the condenser 12 (outdoor side air-cooled heat exchanger), and then returns to the compressor through the four-way valve and the gas-liquid separator, thus completing the primary cycle.

The third throttle EEV3 with different opening degrees is adjusted to adjust the flow rates of the refrigerant passing through the reheater 14 and the refrigerant on the main line, so as to meet different reheating requirements. Through the heat exchanger 20, the hot water for heating prepared by the temperature module is divided into two paths, one path is conveyed to the heat radiator 21, so that the temperature of the tail end is directly regulated; and the other path of the air is conveyed to a fresh air processor 23 (a surface air cooler) in the fresh air unit to preheat fresh air.

2) Heating mode alone

The second throttle EEV2 and the valve 141 are closed, while the third throttle EEV3 is kept fully open. At this time, since the second throttle EEV2 is closed, no refrigerant flows through the evaporator 12, and thus there is no dehumidification function. Moreover, only low-temperature hot water can be used for heating fresh air in the fresh air processor 23 (surface air cooler). When the second throttle EEV2 is closed and the valve 141 is open, the high-pressure refrigerant in the supercooled state can be used to further heat the fresh air by the reheater 14.

As can be seen from the above description, in the winter mode, the second embodiment can preheat fresh air, and can also directly heat the indoor air at the radiation end by using the heat radiator 21, so as to quickly reach the required temperature in the room.

2.3 embodiment III

Fig. 3a to 3c illustrate a third embodiment.

As shown in fig. 3a to 3c, a four-way valve is connected to the compressor 30 to selectively supply the fluid medium to the condenser 11 or the evaporator 12. Similarly, the four-way valve serves to make it possible for the compressor to deliver pressure medium to the condenser 11 or the evaporator 12 in different operating states. In the third embodiment, the condenser 11 and the heat exchanger 20 are connected in series, the evaporator 12 is connected in parallel with the condenser 11 and the heat exchanger 20 connected in series, and an inlet of the evaporator 12 is connected to a flow path between an exhaust port of the compressor 30 and the four-way valve.

Preferably, as shown in the figure, a reheater 14 is connected in series upstream of the evaporator 12, and the reheater 14 is used for regulating and controlling the temperature of the fresh air, so that the temperature of the fresh air can be regulated and controlled more flexibly.

As shown, a valve 142 is connected in series upstream of the reheater 14; and/or a second throttle EEV2 is connected in series between the reheater 14 and the evaporator 12, so that on the one hand the flow of the refrigerant medium can be regulated, and at the same time the solution of the third embodiment can be adapted to different operating conditions, which will be described in detail below. Still preferably, the condenser 11 is connected in series with a first throttle EEV1, and the heat exchanger 20 is connected in series with a third throttle EEV 3.

The connecting structure of the third embodiment is described above in detail, and the working principle of the technical solution of the third embodiment under different working conditions is described below.

Summer working condition of a

During summer conditions, the first throttle EEV1 is fully open. The high-temperature and high-pressure refrigerant discharged from the compressor 30 is divided into two paths, one path enters the four-way valve, and the other path (bypass branch) enters the reheater 14 to reheat the dehumidified air. The refrigerant flow (i.e., reheat) of the bypass branch is regulated by a valve 142 (e.g., a solenoid valve). The refrigerant passing through the reheater 14 is expanded and throttled by the second throttle valve EEV2, and then enters the dehumidification evaporator 12 to cool and dehumidify the fresh outdoor air. (ii) a The high-temperature and high-pressure refrigerant entering the four-way valve enters the condenser 11 to be cooled, becomes low-temperature and high-pressure liquid, is expanded and throttled by the third throttle valve EEV3, and enters the heat exchanger 20 to prepare high-temperature cold water. Finally, the two refrigerants are collected before the gas-liquid separator and then enter the compressor 30 to complete one cycle.

In the temperature module, one part of the prepared high-temperature cold water bypasses the surface air cooler to preheat fresh air, and the other part of the prepared high-temperature cold water enters the heat radiator 21 to adjust the indoor temperature at the tail end.

As can be seen from the above description, under summer working conditions, the radiation cooling in the high-temperature cold water supply room can be directly prepared by the heat exchanger; meanwhile, the low-temperature evaporator 12 dehumidifies the outdoor fresh air through heat exchange of the fluorine air. Therefore, independent control of the temperature and the humidity can be realized, and the energy consumption of the system is relatively low.

B winter conditions

In winter conditions, when dehumidification operation is required, the third throttle EEV3 is fully open. The high-temperature and high-pressure refrigerant discharged from the compressor bypasses one path to the reheater 14 before entering the four-way valve, and the dehumidified air is reheated. The refrigerant flow (i.e. reheat) of the bypass branch is adjusted by the valve 142, and enters the dehumidification evaporator 12 for cooling and dehumidifying the outdoor fresh air after being expanded and throttled by the second throttle valve EEV 2.

The other path of high-temperature and high-pressure refrigerant passes through the four-way valve and then enters the heat exchanger to prepare hot water for heating. The refrigerant is expanded and throttled by the first throttle EEV1, enters the condenser 11, is changed into a low-pressure gas refrigerant, is collected with the refrigerant of the dehumidification evaporator before the gas-liquid separator, and returns to the compressor, thereby completing one cycle.

During winter conditions when separate heating is required, both the second throttle EEV2 and the valve 142 are closed and no refrigerant passes through the reheater 14 and the evaporator 12. At this time, only the high-temperature and high-pressure refrigerant is heat-exchanged by the heat exchanger 20 to prepare hot water for heating.

Because reheater and evaporimeter are as the equipment to the dehumidification processing of new trend, lie in with the biggest difference of the VRV system on the market: the high-pressure gas pipe which can be connected from the exhaust port of the compressor does not pass through the four-way valve but can pass through the reheater and the evaporator and then be connected to the low-pressure gas pipe which is connected with the suction port of the compressor, so that the dehumidification requirement in winter and summer can be met. Meanwhile, the scheme greatly reduces the use of valves, simplifies the control and makes the system easier to realize.

As can be seen from the above description, in the winter mode, the third embodiment of the present invention can preheat fresh air, and can also directly heat the indoor air at the radiation end by using the heat radiator 21, so as to quickly reach the required indoor temperature.

Further, by cooperation of the valve 142 and the second throttle EEV2, selection of the dehumidification function can be achieved.

2.4 embodiment four

Fig. 4a to 4c depict a technical solution of a fourth embodiment of the present application.

As shown in fig. 4a to 4c, a four-way valve is connected to the compressor 30 to selectively supply the fluid medium to the condenser 11 or the evaporator 12. Similar to the first embodiment, the four-way valve serves to allow the compressor to deliver pressure medium to the condenser 11 or the evaporator 12 using the four-way valve under different operating conditions.

In the fourth embodiment, the inlet of the evaporator 12 is connected to the flow path between the condenser 11 and the heat exchanger 20, and the outlet of the evaporator 20 is connected to the suction port of the compressor 30. Thus, when the compressor 30 delivers the medium to the condenser 11, the medium flowing through the condenser 11 will be diverted to the evaporator 12 and the heat exchanger 20; while the compressor 30 delivers the medium to the heat exchanger 20, the medium will be diverted to the evaporator 12 and the condenser 11. This operating condition will be described in more detail below.

As shown in the drawing, it is preferable that the air conditioning system includes a reheater 14, an inlet of the reheater 14 is connected to a flow path between the discharge port of the compressor 30 and the four-way valve, and an outlet of the reheater 14 is connected to a flow path between the condenser 11 and the heat exchanger 20. Because the reheater 14 is arranged, the temperature of the fresh air can be more reliably regulated. In addition, since the inlet of the reheater 14 is connected to the exhaust of the compressor 30, the fluid medium delivered by the compressor 30 will be branched to the four-way valve and the reheater 14.

In order to meet the requirements of controlling the medium flow direction and adapting to different working conditions, the condenser 11 is preferably connected with a first throttle valve EEV1 in series; the evaporator 12 is connected with a second throttle valve EEV2 in series; the heat exchanger 20 is connected with a third throttle valve EEV3 in series; and/or the reheater 14 is connected in series with a fourth throttle EEV 4. The use of these throttles also enables the regulation of the physical state of the medium, such as pressure and flow.

The connection structure of the fourth embodiment is described in detail above, and the working principle of the technical solution of the fourth embodiment under different working conditions is described below.

Summer working condition of a

In the summer cooling dehumidification condition, the first throttle EEV1 is fully open. The high-temperature and high-pressure refrigerant discharged from the compressor 30 bypasses one path to the reheater 14 before entering the four-way valve, and the dehumidified air is reheated. The refrigerant flow (i.e., reheat) of the bypass branch is regulated by the fourth throttle EEV 4. The other path of refrigerant passing through the four-way valve enters the condenser 11 to be cooled into low-temperature high-pressure liquid, and the low-temperature high-pressure liquid is collected with the refrigerant from the reheater 14 and then divided into two paths. The first path of refrigerant enters the dehumidification evaporator 12 to cool and dehumidify the outdoor fresh air after being expanded and throttled by the second throttle valve EEV 2; the second refrigerant path is expanded and throttled by the third throttle EEV3, and enters the heat exchanger 20 to prepare high-temperature cold water. And finally, the two paths of refrigerants are converged in front of the gas-liquid separator and enter the compressor to complete one cycle.

According to the description, under the working condition of summer, the high-temperature cold water is directly prepared by the heat exchanger to supply the radiation cooling in the room; the low-temperature evaporator 12 dehumidifies the fresh outdoor air by heat exchange with the fluorine air. Therefore, independent temperature and humidity control is realized, and the energy consumption of the system is relatively low.

B winter conditions

In the winter heating and dehumidifying mode, the third throttle EEV3 is fully opened. The high-temperature and high-pressure refrigerant discharged from the compressor 30 bypasses one path to the reheater 14 before entering the four-way valve, and the dehumidified air is reheated. The refrigerant flow (i.e., reheat) of the bypass branch is regulated by the fourth throttle EEV 4. The other path of high-temperature and high-pressure refrigerant passing through the four-way valve enters a heat exchanger to prepare hot water for heating. Then, the air is divided into two paths, wherein one path of air enters the dehumidification evaporator 12 for cooling and dehumidification after passing through the expansion and throttling of the second throttling valve EEV 2; the other path is collected with the refrigerant from the reheater 14, expanded and throttled by the first throttle EEV1, collected with the refrigerant of the dehumidification evaporator 12 before the gas-liquid separator, and returned to the compressor, thereby completing the primary cycle.

In the winter heating only mode, the valves EEV2, 4 are closed and the reheater 14 and evaporator 12 are free of refrigerant. The high-temperature and high-pressure refrigerant discharged from the compressor 30 does not flow to the reheater 14 any more, but flows only to the heat exchanger 20.

Because the reheater and the evaporator are used as equipment for dehumidifying fresh air, the flow path direction of the refrigerant in winter and summer is not changed, and the biggest difference of the scheme is that: the high-pressure gas pipe connected from the exhaust port of the compressor is connected to the low-pressure gas pipe connected with the suction port of the compressor after passing through the reheater and the evaporator without passing through the four-way valve, so that the dehumidification requirement in winter and summer can be met. Meanwhile, the scheme greatly reduces the use of valves, simplifies the control and makes the system easier to realize. Further, the refrigerant flow rates of the reheater 14 and the dehumidification evaporator 12 can be adjusted independently of each other, and accurate control of the air parameter can be achieved.

As can be seen from the above description, in the winter mode, the fourth embodiment of the present invention can preheat fresh air, and can also directly heat the indoor air at the radiation end by using the heat radiator 21, so as to quickly reach the required indoor temperature.

The connection structure of different embodiments and the operation process and principle thereof under different working conditions are respectively described above. Features of the different embodiments described above may be combined with or referred to one another without technical conflicts or inconsistencies and will not be described again here. For example, as shown in the drawings, the fresh air processor 23, the evaporator 12 and the reheater 14 (the reheater 14 may be omitted in some embodiments) are arranged in sequence from upstream to downstream in the flow direction of the fresh air, so as to more reliably and accurately adjust the temperature and/or humidity of the fresh air.

According to the arrangement, when the refrigeration and dehumidification operation is carried out in summer, for example, outdoor high-temperature and high-humidity air firstly passes through the evaporator 23, the temperature of the refrigerant introduced into the evaporator 23 is the same as that of the radiator, generally 16-18 ℃, the fresh air is precooled and cooled by the fresh air processor 23 introduced with the refrigerant of 16-18 ℃, the temperature and the humidity are reduced to about 20-23 ℃, and the air passes through the evaporator 12 after the humidity is nearly saturated. At the moment, a refrigerant with the temperature of 0-8 ℃ is introduced into the evaporator 12, the fresh air is further cooled through the evaporator 12, the air is close to saturation after passing through the evaporator 23, the air is further cooled after passing through the evaporator 12, and meanwhile, a large amount of saturated water in the air is separated out to form a good dehumidification effect. The dehumidified fresh air is heated by the reheater 14, the temperature of the cold/heat carrying medium in the reheater 14 is 30-60 ℃, the fresh air is reheated to 20 ℃ by the reheater and then sent into the room, and the process enables the outdoor air to be subjected to the processes of cooling, dehumidifying and heating, and the air can be accurately adjusted by the design of hardware and the control of software, so that the state required by the system is achieved.

Through the mode of arranging in order, the new trend can be through the flow of longer time to fully and carry out cold and hot exchange between the heat exchanger, provide very big facility to the accurate regulation of air.

The arrangement order is not limited to this, and the fresh air processor 23, the evaporator 12, and the reheater 14 may have another arrangement order.

In addition, an improvement is made on the basis of the fourth embodiment, so that an embodiment as shown in fig. 4d can be obtained, wherein the fresh air processor 23 can be omitted. In the first to third embodiments, the fresh air processor 23 may be optionally omitted. In the embodiment shown in fig. 4d, the operation principle and process of the summer and winter conditions can be referred to the fourth embodiment, and the defrosting mode can be implemented, and the operation principle and process thereof can be referred to fig. 4d and will not be described in detail herein.

In addition, as shown in the drawing, an oil separator (i.e., an oil separator) may be provided in the air conditioning system to separate the lubricating oil in the refrigerant medium, thereby ensuring reliable operation of the system.

The above description is only for the purpose of illustrating the preferred embodiments of the present application and is not to be construed as limiting the present application, and any modifications, equivalents, improvements, etc. made within the spirit and principle of the present application should be included in the scope of the present application.

Claims

1. Air conditioning system, characterized in that, this air conditioning system includes:

the fresh air module comprises a compressor, a condenser (11) and an evaporator (12) which are in fluid connection, and the evaporator (12) is used for regulating and controlling the temperature and/or the humidity of fresh air; and

the flow path of the temperature module is in heat exchange with the flow path of the fresh air module but is not communicated with the flow path of the fresh air module, the temperature module is used for regulating and controlling the temperature of a use side, and the temperature module comprises:

a heat exchanger (20), the heat exchanger (20) being for heat exchange with a flow path of the fresh air module through the heat exchanger;

a heat radiator (21), the heat radiator (21) being located inside the use side and connected to the heat exchanger (20) to form a closed flow path;

a pump (22), the pump (22) being connected in series in the closed flow path;

wherein the fresh air module further comprises a bidirectional flash evaporator (13), the bidirectional flash evaporator (13) comprising:

a first connecting pipe (131), wherein the first connecting pipe (131) is communicated with the condenser (11) and extends into the lower part of the flash evaporator (13);

a second connecting pipe (132), wherein the second connecting pipe (132) is communicated with the evaporator (12) and extends into the lower part of the flash evaporator (13); and

a first connection port (133) and a second connection port (134), the first connection port (133) being located at a lower portion of the flash evaporator (13), the second connection port (134) being located at an upper portion of the flash evaporator (13), the first connection port (133) being connected to an inlet port of the heat exchanger (20) through a first check valve (139), and an outlet port of the heat exchanger (20) being connected to the second connection port (134) through a solenoid valve (140).

2. Air conditioning system according to claim 1, wherein the temperature module comprises a fresh air processor (23), which fresh air processor (23) is connected in parallel with the heat radiator (21) for regulating the temperature and/or humidity of the fresh air.

3. Air conditioning system according to claim 2, characterized in that the fresh air processor (23) and/or the heat exchanger (20) are connected in series with a regulating valve.

4. Air conditioning system according to claim 1, characterized in that the compressor comprises a first compressor (101) and a second compressor (102) connected in series, a four-way valve being connected to each of the first compressor (101) and the second compressor (102) for selectively feeding a fluid medium to the condenser (11) or the evaporator (12).

5. Air conditioning system according to claim 4, characterized in that the upper part of the bi-directional flash evaporator (13) is provided with a gas phase outlet (135), which gas phase outlet (135) is connected to the flow path between the first compressor (101) and the second compressor (102).

6. Air conditioning system according to claim 1, characterized in that the condenser (11) and the evaporator (12) are connected in series with a first and a third throttle valve (EEV1, EEV3), respectively.

7. Air conditioning system according to claim 1, characterized in that it comprises a heat exchange bypass connected in parallel to said evaporator (12) and passing through said heat exchanger (20) to enable heat exchange.

8. The air conditioning system of claim 7, wherein a second check valve (136) and/or a second throttle valve (EEV2) are connected in series in the heat exchange bypass.

9. Air conditioning system according to claim 2, wherein the fresh air processor (23) and the evaporator (12) are arranged in sequence from upstream to downstream in the flow direction of the fresh air.