CN219640473U

CN219640473U - Air conditioning system

Info

Publication number: CN219640473U
Application number: CN202320335631.3U
Authority: CN
Inventors: 张自庆
Original assignee: Zhejiang Dunan Electro Mechanical Technology Co Ltd
Current assignee: Zhejiang Dunan Electro Mechanical Technology Co Ltd
Priority date: 2023-02-16
Filing date: 2023-02-16
Publication date: 2023-09-05
Anticipated expiration: 2033-02-16

Abstract

The utility model provides an air conditioning system, and relates to the technical field of air conditioners. The air conditioning system comprises a first heat exchanger, a second heat exchanger, a third heat exchanger, a first throttling element, a regulating valve and a second throttling element, wherein the second heat exchanger is positioned on the first side of the first heat exchanger; the first throttling element is connected between the second heat exchanger and the third heat exchanger, and the second heat exchanger can be communicated with the third heat exchanger through the first throttling element; the regulating valve is connected between the second heat exchanger and the third heat exchanger, the second heat exchanger can be communicated with the third heat exchanger through the regulating valve, and the regulating valve is arranged in parallel with the first throttling element. The second heat exchanger is additionally arranged, and through the parallel connection of the first throttling element and the regulating valve, working condition switching can be performed at different temperatures, effective frost suppression is realized, heat exchange efficiency of the first heat exchanger is ensured, and heating circulation is promoted.

Description

Air conditioning system

Technical Field

The utility model relates to the technical field of air conditioners, in particular to an air conditioning system.

Background

When the air conditioner heats in winter, the frost layer is easily condensed on the surface of the evaporator because of low ambient temperature and high humidity, so that the heat exchange efficiency of the evaporator is reduced, the refrigerating capacity is reduced, and the heating cycle of the system is affected. In the related art, the air conditioner is operated in a reversing manner, so that the high-temperature and high-pressure refrigerant discharged by the compressor is used for defrosting the evaporator, and the air conditioner continues to perform heating operation after defrosting and frosting. However, if the frost layer is condensed faster, frequent repeated defrosting is easy to affect the heating efficiency and the indoor temperature.

Disclosure of Invention

Based on this, it is necessary to provide an air conditioning system that can effectively suppress frost, which is advantageous for reducing frost formation.

An air conditioning system comprising a first heat exchanger, a second heat exchanger, a third heat exchanger, a first throttling element, a regulating valve and a second throttling element, wherein the second heat exchanger is positioned on a first side of the first heat exchanger, the second throttling element is connected between the first heat exchanger and the second heat exchanger, and the first heat exchanger can be communicated with the second heat exchanger through the second throttling element; the first throttling element is connected between the second heat exchanger and the third heat exchanger, and the second heat exchanger can be communicated with the third heat exchanger through the first throttling element; the regulating valve is connected between the second heat exchanger and the third heat exchanger, the second heat exchanger can be communicated with the third heat exchanger through the regulating valve, and the regulating valve is arranged in parallel with the first throttling element.

It will be appreciated that when the air conditioning system is in the heating mode, the third heat exchanger is primarily used to cool the refrigerant and simultaneously produce hot water, and the first heat exchanger is beneficial to the refrigerant to absorb heat from the ambient air and evaporate back into the compressor. The provision of the second throttling element enables the throttling and depressurization of the refrigerant between the first heat exchanger and the second heat exchanger. The second heat exchanger is additionally arranged, so that under the working condition of lower temperature, the air humidity is higher, the regulating valve is opened, and the first throttling element is closed, so that the medium-temperature refrigerant in the third heat exchanger after heat exchange directly flows into the second heat exchanger, the second heat exchanger can release heat to the outside air to increase the temperature of the air, the relative humidity of the air is reduced, and frosting is further inhibited; under the working condition of extremely low temperature, the air humidity is smaller, and the opening of the first throttling element has the throttling and depressurization effects on the refrigerant, so that the refrigerant flowing into the second heat exchanger is low-temperature and low-pressure refrigerant, the second heat exchanger and the first heat exchanger are promoted to absorb heat in the air together, and the evaporating temperature is increased to inhibit frosting. The first throttling element and the regulating valve are arranged in parallel, so that working conditions can be switched at different temperatures, effective frost inhibition is realized, heat exchange efficiency of the first heat exchanger is ensured, and heating circulation is promoted.

In one embodiment, the air conditioning system further comprises a temperature sensor, and the regulator valve and the first throttling element are configured to adjust on-off in response to a temperature signal of the temperature sensor.

It can be understood that setting up temperature sensor can detect ambient temperature, select different operating modes to restrain frosting through ambient temperature's change, can improve and restrain frosting efficiency.

In one embodiment, when the temperature signal of the temperature sensor is greater than a first temperature threshold value in a heating mode, the regulating valve is opened, the first throttling element is closed, and the second throttling element is opened; when the temperature signal of the temperature sensor is smaller than a first temperature threshold value, the regulating valve is closed, the first throttling element is opened, and the second throttling element is opened.

It can be understood that the setting of the first temperature threshold can accurately and efficiently inhibit frost.

In one embodiment, the first heat exchanger has an air inlet side, the first side being the air inlet side; along the first direction, the second heat exchanger and the first heat exchanger are arranged opposite to each other, and the projection area of the second heat exchanger is not smaller than that of the first heat exchanger.

It will be appreciated that the provision of the air inlet side enables the second heat exchanger to heat the inlet air of the first heat exchanger to a greater extent, facilitating an increase in air temperature to reduce air humidity. In the heating mode, under the working condition that the temperature signal of the temperature sensor is greater than or equal to the first temperature threshold value, the projection area of the second heat exchanger is arranged, so that the contact area between the second heat exchanger and air can be increased, the air temperature can be increased in a large range, the relative humidity of the air can be reduced, and the frost suppression can be promoted; under the working condition that the temperature signal of the temperature sensor is smaller than the first temperature threshold, the heat conduction area of the second heat exchanger to the first heat exchanger can be increased, and frost suppression is enhanced; in the defrosting mode, the area of the second heat exchanger for heat conduction to the first heat exchanger can be increased, and defrosting is promoted.

In one embodiment, the air conditioning system further comprises a one-way valve connected between the first heat exchanger and the second heat exchanger, wherein the first heat exchanger can be in one-way communication with the second heat exchanger through the one-way valve, and the one-way valve and the second throttling element are arranged in parallel.

It will be appreciated that the arrangement of the one-way valve allows one-way flow of refrigerant between the first heat exchanger and the second heat exchanger.

In one embodiment, in a cooling or defrost mode, the one-way valve and the first throttling element are respectively configured in an open state, and the regulating valve and the second throttling element are respectively configured in a closed state.

It can be understood that in the refrigeration mode, the refrigerant is supercooled by the arrangement, so that the external heat exchange efficiency can be improved, and the refrigeration effect can be improved. In the defrosting mode, the refrigerant in the first heat exchanger can only flow into the second refrigerant through the one-way valve, so that the refrigerant can defrost the first heat exchanger and the second heat exchanger, and the heat exchange efficiency of the first heat exchanger and the second heat exchanger is improved.

In one embodiment, the air conditioning system further comprises a four-way valve and a compressor, wherein a first port of the four-way valve can be communicated with an inlet of the compressor, a second port of the four-way valve can be communicated with the first heat exchanger, a third port of the four-way valve can be communicated with the third heat exchanger, and a fourth port of the four-way valve can be communicated with an outlet of the compressor; in a heating mode, the first port is communicated with the second port, and the third port is communicated with the fourth port; in the refrigeration or defrosting mode, the first port is communicated with the third port, and the second port is communicated with the fourth port.

It will be appreciated that the four-way valve is configured to change the flow direction of the refrigerant discharged from the compressor to facilitate switching between cooling and heating of the air conditioning system.

In one embodiment, the air conditioning system further comprises a fan located on a side of the first heat exchanger facing away from the first side; the fan is configured to be in an open state when the second heat exchanger is in a heating or cooling mode; the fan is configured to be off when the second heat exchanger is in a defrost mode.

It can be appreciated that the arrangement of the fan promotes the air flow, which is beneficial to improving the heat exchange efficiency of the air and the first heat exchanger.

In one embodiment, the air conditioning system further comprises a gas-liquid separator connected between the first port of the four-way valve and the inlet of the compressor.

It is understood that the gas-liquid separator is arranged to separate the refrigerant into gas and liquid, so that only gaseous refrigerant can enter the compressor, and the occurrence of liquid impact phenomenon is prevented.

In one embodiment, the first and second heat exchangers are provided as fin heat exchangers; the first heat exchanger comprises a plurality of refrigerant loops, and the refrigerant loops are independent from each other.

It can be appreciated that the heat exchange area of the first heat exchanger and the second heat exchanger and the air can be increased by the arrangement, and the heat exchange efficiency is improved.

Drawings

In order to more clearly illustrate the technical solutions of the embodiments or the conventional techniques of the present utility model, the drawings required for the descriptions of the embodiments or the conventional techniques will be briefly described below, and it is apparent that the drawings in the following descriptions are only some embodiments of the present utility model, and other drawings may be obtained according to the drawings without inventive effort for those skilled in the art.

Fig. 1 is a schematic diagram of an air conditioning system provided by the present utility model in a heating mode;

fig. 2 is a schematic diagram of an air conditioning system according to the present utility model in a cooling mode or a defrosting mode.

Reference numerals: 100. an air conditioning system; 11. a first heat exchanger; 111. a first side; 12. a second heat exchanger; 13. a third heat exchanger; 20. a compressor; 31. a first throttling element; 32. a second throttling element; 40. a regulating valve; 50. a one-way valve; 60. a blower; 70. a four-way valve; 80. a gas-liquid separator.

Detailed Description

In order that the above objects, features and advantages of the utility model will be readily understood, a more particular description of the utility model will be rendered by reference to the appended drawings. In the following description, numerous specific details are set forth in order to provide a thorough understanding of the present utility model. The present utility model may be embodied in many other forms than described herein and similarly modified by those skilled in the art without departing from the spirit of the utility model, whereby the utility model is not limited to the specific embodiments disclosed below.

It will be understood that when an element is referred to as being "mounted" or "disposed" on another element, it can be directly on the other element or intervening elements may also be present. When a component is considered to be "connected" to another component, it can be directly connected to the other component or intervening components may also be present. The terms "vertical", "horizontal", "upper", "lower", "left", "right" and the like are used in the description of the present utility model for the purpose of illustration only and do not represent the only embodiment.

Furthermore, the terms "first," "second," and the like, are used for descriptive purposes only and are not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defining "a first" or "a second" may explicitly or implicitly include at least one such feature. In the description of the present utility model, the meaning of "plurality" means at least two, for example, two, three, etc., unless specifically defined otherwise.

In the present utility model, unless expressly stated or limited otherwise, a first feature "up" or "down" on a second feature may be that the first feature is in direct contact with the second feature, or that the first feature and the second feature are in indirect contact through intermedial media. Moreover, a first feature being "above," "over" and "on" a second feature may be a first feature being directly above or obliquely above the second feature, or simply indicating that the first feature is higher in level than the second feature. The first feature being "under", "below" and "beneath" the second feature may be the first feature being directly under or obliquely under the second feature, or simply indicating that the first feature is less level than the second feature.

Unless defined otherwise, all technical and scientific terms used in the specification of the present utility model have the same meaning as commonly understood by one of ordinary skill in the art to which this utility model belongs. The terminology used in the description of the utility model herein is for the purpose of describing particular embodiments only and is not intended to be limiting of the utility model. The term "and/or" as used in the description of the present utility model includes any and all combinations of one or more of the associated listed items.

Referring to fig. 1 to 2, the present utility model provides an air conditioning system 100, which includes a compressor 20, a first heat exchanger 11, a second heat exchanger 12, a third heat exchanger 13, a first throttling element 31, a regulating valve 40 and a second throttling element 32; the first heat exchanger 11 is communicated with the compressor 20, the first heat exchanger 11 is provided with a first side 111, and the second heat exchanger 12 is positioned on the first side 111 of the first heat exchanger 11; the second throttling element 32 is connected between the first heat exchanger 11 and the second heat exchanger 12, the first heat exchanger 11 being able to communicate with the second heat exchanger 12 through the second throttling element 32; the first throttling element 31 is connected between the second heat exchanger 12 and the third heat exchanger 13, and the second heat exchanger 12 can be communicated with the third heat exchanger 13 through the first throttling element 31; the regulating valve 40 is connected between the second heat exchanger 12 and the third heat exchanger 13, the second heat exchanger 12 can communicate with the third heat exchanger 13 through the regulating valve 40, and the regulating valve 40 is disposed in parallel with the first throttling element 31. In the present utility model, the communication may include direct communication or indirect communication.

In this way, the compressor 20 can compress the refrigerant into a high-temperature and high-pressure refrigerant; in the heating mode, the high-temperature and high-pressure refrigerant in the compressor 20 flows into the third heat exchanger 13, exchanges heat with the heat exchange medium in the third heat exchanger 13, and becomes a medium-temperature refrigerant. In the embodiment of the present utility model, the heat exchange medium in the third heat exchanger 13 is set as cold water, and hot water can be formed to flow out of the third heat exchanger 13 through heat exchange with a high-temperature refrigerant to heat the external environment.

The refrigerant discharged from the compressor 20 has different flow directions according to the cooling or heating requirements, so as to realize the switching of the flow directions of the refrigerant; thus, in some embodiments, the air conditioning system 100 further comprises a four-way valve 70, a first port of the four-way valve 70 is capable of communicating with an inlet of the compressor 20, a second port of the four-way valve 70 is capable of communicating with the first heat exchanger 11, a third port of the four-way valve 70 is capable of communicating with the third heat exchanger 13, and a fourth port of the four-way valve 70 is capable of communicating with an outlet of the compressor 20. In this way, the four-way valve 70 can switch the flow path of the refrigerant to achieve the heating or cooling effect. Specifically, when the air conditioning system 100 heats, as shown in fig. 1, the four-way valve 70 can communicate the outlet of the compressor 20 with the inlet of the third heat exchanger 13, i.e., the third port of the four-way valve 70 with the fourth port, and the inlet of the compressor 20 with the outlet of the first heat exchanger 11, i.e., the first port of the four-way valve 70 with the second port; when the air conditioning system 100 is cooling, the four-way valve 70 can communicate the outlet of the compressor 20 with the inlet of the first heat exchanger 11 (the fourth port communicates with the second port), and the inlet of the compressor 20 with the third heat exchanger 13 (the first port communicates with the third port).

In the heating mode, during the process of flowing the medium-temperature refrigerant from the third heat exchanger 13 into the first heat exchanger 11, the second heat exchanger 12 is additionally arranged, and the working state of the second heat exchanger 12 is changed by switching different working conditions through the parallel connection of the regulating valve 40 and the first throttling element 31, so that condensation of a frost layer on the surface of the first heat exchanger 11 can be inhibited. Wherein the second heat exchanger 12 has a first operating condition and a second operating condition.

Specifically, as shown in fig. 1, under the first working condition, the regulating valve 40 is configured to be in an open state, the first throttling element 31 is configured to be in a closed state, the medium-temperature refrigerant is directly passed through the second heat exchanger 12 from the third heat exchanger 13, the second heat exchanger 12 serves as a condenser, the medium-temperature refrigerant exchanges heat with ambient air in the second heat exchanger 12, the medium-temperature refrigerant is condensed again to be cooled, then flows out of the second heat exchanger 12, throttled and depressurized by the second throttling element 32, flows into the first heat exchanger 11, absorbs the heat of the ambient air, evaporates into a gaseous refrigerant, returns to the compressor 20 through the four-way valve 70, and continues to circulate under the first working condition.

In this process, the second heat exchanger 12 can raise the temperature of the ambient air through the process of releasing heat from the air by the medium-temperature refrigerant, so that when the ambient air exchanges heat with the second heat exchanger 12 and then exchanges heat with the first heat exchanger 11, the condensation of moisture in the air can be reduced, and the formation of frost is suppressed. Meanwhile, since the medium temperature refrigerant in the second heat exchanger 12 is high in temperature, the second heat exchanger 12 can transfer heat to the first heat exchanger 11 by means of heat radiation, and formation of frost on the first heat exchanger 11 is suppressed. In addition, the second heat exchanger 12 is also beneficial to ensuring the supercooling degree of the refrigerant before throttling, and promoting the heating effect while suppressing frost.

As shown in fig. 1, under the second working condition, the regulating valve 40 is configured to be in a closed state, the first throttling element 31 is configured to be in an open state, so that the medium-temperature refrigerant flows out of the third heat exchanger 13, throttles and reduces pressure through the first throttling element 31 to become low-temperature low-pressure refrigerant, then enters the second heat exchanger 12, the second heat exchanger 12 exchanges heat with the outside through the low-temperature low-pressure refrigerant for one time, absorbs heat of the outside air, the refrigerant flows out of the second heat exchanger 12, throttles for the second time through the second throttling element 32, then enters the first heat exchanger 11, further absorbs heat of the outside air, becomes high-temperature gaseous refrigerant, returns to the compressor 20 through the four-way valve 70, and continues to circulate under the second working condition. Like this, first heat exchanger 11 and second heat exchanger 12 are as the evaporimeter to the external air heat absorption jointly, can increase evaporation area, and then improve evaporating temperature for first heat exchanger 11 surface temperature is high, is difficult for becoming the frost layer, reaches and presses down the frost effect. In addition, as the evaporation area under the second working condition is increased, more liquid refrigerant can be changed into gaseous refrigerant, more refrigerant is promoted to enter the heating cycle, the flow of the refrigerant is increased, and the heating effect is promoted while the frost is suppressed.

The switching of the first and second conditions is dependent on the ambient temperature, and in order to achieve a precise switching of the conditions to increase the frost suppression efficiency, in a preferred embodiment the air conditioning system 100 further comprises a temperature sensor, the regulator valve 40 and the first throttling element 31 being configured to adjust the on-off in response to the temperature signal of the temperature sensor. Specifically, the air conditioning system 100 further includes a controller connected to the temperature sensor and also connected to the regulator valve 40 and the first throttling element 31. In this way, the temperature sensor transmits a temperature signal to the controller after detecting the outside ambient temperature, and the controller receives the temperature sensor signal and then controls the opening and closing of the regulator valve 40 and the first throttle element 31, respectively.

In a specific embodiment, when the temperature signal of the temperature sensor is greater than or equal to the first temperature threshold, the regulator valve 40 is opened, and the first throttling element 31 is closed, that is, the air conditioning system 100 is operated under the first working condition; when the temperature signal of the temperature sensor is less than the first temperature threshold, the regulator valve 40 is closed and the first throttling element 31 is opened, that is, the air conditioning system 100 is operated in the second operating condition.

This is because the relative humidity of the air having the ambient temperature equal to or higher than the first temperature threshold is far higher than or equal to the first temperature threshold, that is, when the ambient temperature is equal to or higher than the first temperature threshold, the relative humidity of the air is relatively high, and a thick frost layer is easily formed on the surface of the first heat exchanger 11, so that the adjusting valve 40 is opened and the first throttling element 31 is closed, the second heat exchanger 12 can be placed in the first working condition, the second heat exchanger 12 can raise the air temperature, and the air humidity is further reduced, thereby suppressing the frost layer. However, since the temperature of the refrigerant in the second heat exchanger 12 decreases after heat exchange with air, i.e. the condensation temperature is low, so that the condensation pressure decreases, when the ambient temperature is less than the first temperature threshold (i.e. the extremely low ambient temperature and the relative humidity of air is small), the two ends of the second throttling element 32 cannot obtain a sufficient pressure drop, and it is difficult to provide a suitable amount of refrigerant to the first heat exchanger 11, which affects the heating cycle of the air conditioning system 100, so that the first working condition cannot be performed at the extremely low ambient temperature, so that the condensation temperature is not too low, which affects the operation of the air conditioning system 100. Therefore, when the ambient temperature is less than the first temperature threshold, the regulating valve 40 is closed, the first throttling element 31 is opened, so that the refrigerant in the second heat exchanger 12 absorbs the heat of the external air under the second working condition, and the frost formation is suppressed by increasing the evaporation area, and at this time, the condensation temperature is the condensation temperature in the third heat exchanger 13, so that the normal operation of the heating cycle of the air conditioning system 100 can be ensured.

In a more specific embodiment, the first temperature threshold is set at-7 ℃. In other embodiments, the first temperature threshold may also be selected to be a specific temperature value according to the actual situation.

As shown in fig. 1, in a preferred embodiment, the first heat exchanger 11 has an air inlet side, and the second heat exchanger 12 is disposed on the air inlet side of the first heat exchanger 11. That is, in this embodiment, the first side 111 is the air inlet side, so that, under the first working condition, the air temperature on the periphery side of the first heat exchanger 11 raised by the second heat exchanger 12 is the air temperature on the air inlet side of the first heat exchanger 11, which further raises the temperature of the air exchanging heat with the first heat exchanger 11, reduces the relative humidity of the air, and improves the frost suppression efficiency.

Further, along the first direction, the second heat exchanger 12 and the first heat exchanger 11 are disposed opposite to each other, and the projected area of the second heat exchanger 12 is not smaller than the projected area of the first heat exchanger 11. Therefore, the second heat exchanger 12 can shield the air exchanging heat with the first heat exchanger 11 along the first direction, so that the air along the first direction can exchange heat with the first heat exchanger 11 after exchanging heat with the second heat exchanger 12, the air exchanging area with the second heat exchanger 12 can be increased under the first working condition, the air temperature is improved to a greater extent, the relative humidity of the air is reduced, and frosting is inhibited. The heat conduction area of the second heat exchanger 12 relative to the first heat exchanger 11 can be increased under other working conditions, the increase of the surface temperature of the first heat exchanger 11 is promoted, and the frost suppression or defrosting effect is promoted.

It should be added that the above-mentioned opposite arrangement, i.e. the heat exchange tubes in the first heat exchanger 11 and the heat exchange tubes in the second heat exchanger 12 are arranged in parallel; the first direction is set to be perpendicular to the direction of the heat exchange tubes in the first heat exchanger 11, and the first direction is also perpendicular to the gravitational direction of the first heat exchanger 11.

In a preferred embodiment, the first heat exchanger 11 and the second heat exchanger 12 are provided as fin heat exchangers; so set up, the fin can increase the area of contact of first heat exchanger 11 and second heat exchanger 12 with the air, and then can increase heat transfer area, improves heat exchange efficiency.

Further, the first heat exchanger 11 includes a plurality of refrigerant circuits, and the plurality of refrigerant circuits are independent from each other. Thus, the heat exchange path of the refrigerant can be prolonged, and the refrigerant can exchange heat with the outside air sufficiently.

As shown in fig. 1 and 2, in a preferred embodiment, the air conditioning system 100 further includes a check valve 50, wherein the check valve 50 is connected between the first heat exchanger 11 and the second heat exchanger 12, and the first heat exchanger 11 can be in unidirectional communication with the second heat exchanger 12 through the check valve 50, and the check valve 50 and the second throttling element 32 are disposed in parallel. In this way, the check valve 50 ensures that refrigerant fluid can only flow from the first heat exchanger 11 to the second heat exchanger 12. Typically, the check valve 50 and the second throttling element 32 are alternatively opened, such as when the check valve 50 is in a closed state and the second throttling element 32 is in an open state during the first and second conditions.

As shown in fig. 2, when the air conditioning system 100 is in the defrost mode based on the arrangement of the check valve 50, the check valve 50 and the first throttling element 31 are respectively configured in an open state, the regulating valve 40 and the second throttling element 32 are respectively configured in a closed state, the fourth port of the four-way valve 70 is in communication with the second port, the first port is in communication with the third port, and the second heat exchanger 12 is for exchanging heat with the first heat exchanger 11. In this way, the high-temperature and high-pressure refrigerant in the compressor 20 flows into the first heat exchanger 11 through the four-way valve 70, and can exchange heat with the frost layer in the first heat exchanger 11, so that the frost layer is melted. The refrigerant directly flows from the first heat exchanger 11 into the second heat exchanger 12 through the check valve 50, further melting the frost layer. The refrigerant turns into medium temperature refrigerant after the second heat exchanger 12 exchanges heat, turns into low temperature low pressure refrigerant after throttling and depressurization through the first throttling element 31, flows into the third heat exchanger 13, absorbs the heat of the medium in the third heat exchanger 13, evaporates into gaseous refrigerant and flows back into the compressor 20 through the four-way valve 70, and continues to circulate in the defrosting mode.

In this process, since the plurality of refrigerant circuits are disposed in the first heat exchanger 11, in the process of defrosting the refrigerant, the situation that the defrosting conditions of the refrigerant circuits are inconsistent is easy to occur, for example, part of the refrigerant circuits have fewer frost layers and part of the refrigerant circuits have more frost layers, so that part of the refrigerant circuits with fewer frost layers firstly complete the defrosting of the part, and the part of the refrigerant circuits do not have the effect of cooling the subsequent high-temperature refrigerant any more, thereby leading to faster pressure rise of the refrigerant. The second heat exchanger 12 is arranged, so that the refrigerant in the first heat exchanger 11 flows out of the first heat exchanger 11, flows into the second heat exchanger 12 after being mixed, and defrost the second heat exchanger 12, and the second heat exchanger 12 can further cool the refrigerant, so that the speed of the pressure rise of the refrigerant is slowed down. In addition, the temperature of the second heat exchanger 12 rises after defrosting, and heat can be transferred to the first heat exchanger 11 through the effect of heat radiation, so that the first heat exchanger 11 can be promoted to be fully defrosted.

Of course, the air conditioning system 100 of the present utility model is also capable of cooling. As shown in fig. 2, in a preferred embodiment, in the cooling mode, the check valve 50 and the first throttling element 31 are respectively configured in an open state, the second throttling element 32 and the regulating valve 40 are respectively configured in a closed state, the fourth port of the four-way valve 70 is communicated with the second port, the first port is communicated with the third port, the refrigerant in the compressor 20 flows into the first heat exchanger 11 through the four-way valve 70 to exchange heat, the second heat exchanger 12 performs secondary cooling on the refrigerant after heat exchange by the first heat exchanger 11, and the subsequent process is similar to the defrosting mode and is not repeated. In this way, the circulation process of the air conditioning system 100 in the defrosting mode is substantially the same as that in the cooling mode, except that the defrosting mode is aimed at defrosting, and when a certain frost layer is left on the first heat exchanger 11 and the second heat exchanger 12 after the heating mode is operated for a period of time, the defrosting mode is turned on to defrost the first heat exchanger 11 and the second heat exchanger 12, and the heating mode is continued after the frost layer is melted. The purpose of the refrigeration mode is to cool the refrigerant, which is generally performed in summer, the ambient temperature in summer is high, and the frost layer is not easy to form, so in the refrigeration mode, the second heat exchanger 12 can cool the refrigerant after the first heat exchanger 11 cools the refrigerant, so as to promote supercooling of the refrigerant, increase the temperature difference between the refrigerant and the medium inside the third heat exchanger 13, promote the liquid refrigerant to absorb heat sufficiently in the third heat exchanger 13 and evaporate the liquid refrigerant into the gaseous refrigerant, further improve the refrigerating capacity, and promote the refrigeration cycle. Besides, the heat exchange area is increased by the second heat exchanger 12, so that the loop through which the refrigerant flows is increased, the pressure of the refrigerant is reduced, the condensation temperature is reduced, the refrigerant liquefaction is promoted thoroughly, the refrigerating capacity is improved, and the power consumption of the compressor 20 is reduced, so that the operation energy efficiency of the air conditioning system 100 is improved.

As shown in fig. 1 and 2, in a preferred embodiment, the air conditioning system 100 further includes a gas-liquid separator 80, the gas-liquid separator 80 being connected between the first port of the four-way valve 70 and the inlet of the compressor 20. In this way, the gas-liquid separator 80 can ensure that the refrigerant flowing back into the compressor 20 is in a gaseous state, so as to avoid liquid impact caused by the liquid refrigerant entering into the compressor 20 as much as possible, and is beneficial to maintaining the stable operation of the compressor 20.

As shown in fig. 1 and 2, in a specific embodiment, the air conditioning system 100 further includes a fan 60, where the fan 60 is located on a side of the first heat exchanger 11 facing away from the first side 111; the fan 60 is configured to be in an on state when the second heat exchanger 12 is in a heating or cooling mode; when the second heat exchanger 12 is in the defrost mode, the fan 60 is configured to be off. In this way, the fan 60 can increase air flow during heating or cooling modes, and continuously promote heat exchange between ambient air and the first heat exchanger 11, which is beneficial to improving heat exchange efficiency. The fan 60 is turned off in the defrosting mode, so that the fan 60 can be prevented from interfering with the defrosting process, and the defrosting process can be smoothly performed.

In a specific embodiment, the regulating valve 40 may be provided as a solenoid valve, and the first and second throttle elements 31 and 32 may be provided as electronic expansion valves. In other embodiments, other elements may be provided to achieve the above-described effects. In addition, it is to be appreciated that the connections described above include both indirect and direct connections.

The technical features of the above-described embodiments may be arbitrarily combined, and all possible combinations of the technical features in the above-described embodiments are not described for brevity of description, however, as long as there is no contradiction between the combinations of the technical features, they should be considered as the scope of the description.

The above examples illustrate only a few embodiments of the utility model, which are described in detail and are not to be construed as limiting the scope of the claims. It should be noted that it will be apparent to those skilled in the art that several variations and modifications can be made without departing from the spirit of the utility model, which are all within the scope of the utility model. Accordingly, the scope of the utility model should be determined from the following claims.

Claims

1. An air conditioning system, characterized by comprising a first heat exchanger (11), a second heat exchanger (12), a third heat exchanger (13), a first throttling element (31), a regulating valve (40) and a second throttling element (32), the second heat exchanger (12) being located at a first side (111) of the first heat exchanger (11), the second throttling element (32) being connected between the first heat exchanger (11) and the second heat exchanger (12), the first heat exchanger (11) being capable of communicating with the second heat exchanger (12) through the second throttling element (32);

the first throttling element (31) is connected between the second heat exchanger (12) and the third heat exchanger (13), and the second heat exchanger (12) can be communicated with the third heat exchanger (13) through the first throttling element (31);

the regulating valve (40) is connected between the second heat exchanger (12) and the third heat exchanger (13), the second heat exchanger (12) can be communicated with the third heat exchanger (13) through the regulating valve (40), and the regulating valve (40) and the first throttling element (31) are arranged in parallel.

2. The air conditioning system according to claim 1, wherein the air conditioning system (100) further comprises a temperature sensor, the regulator valve (40) and the first throttling element (31) being configured to adjust on-off in response to a temperature signal of the temperature sensor.

3. An air conditioning system according to claim 2, characterized in that, when in heating mode, the temperature signal of the temperature sensor is equal to or higher than a first temperature threshold value, the regulating valve (40) is opened, the first throttling element (31) is closed, and the second throttling element (32) is opened;

when the temperature signal of the temperature sensor is smaller than a first temperature threshold value, the regulating valve (40) is closed, the first throttling element (31) is opened, and the second throttling element (32) is opened.

4. An air conditioning system according to claim 1, characterized in that the first heat exchanger (11) has an air inlet side, the first side being the air inlet side;

along a first direction, the second heat exchanger (12) and the first heat exchanger (11) are arranged opposite to each other, and the projection area of the second heat exchanger (12) is not smaller than that of the first heat exchanger (11).

5. An air conditioning system according to any of claims 1-4, characterized in that the air conditioning system (100) further comprises a non-return valve (50), the non-return valve (50) being connected between the first heat exchanger (11) and the second heat exchanger (12), the first heat exchanger (11) being capable of being in non-return communication with the second heat exchanger (12) through the non-return valve (50), the non-return valve (50) and the second throttling element (32) being arranged in parallel.

6. An air conditioning system according to claim 5, characterized in that in the cooling or defrost mode, the one-way valve (50) and the first throttling element (31) are configured in an open state, respectively, and the regulating valve (40) and the second throttling element (32) are configured in a closed state, respectively.

7. The air conditioning system according to claim 6, characterized in that the air conditioning system (100) further comprises a four-way valve (70) and a compressor (20), a first port of the four-way valve (70) being communicable with an inlet of the compressor (20), a second port of the four-way valve (70) being communicable with the first heat exchanger (11), a third port of the four-way valve (70) being communicable with the third heat exchanger (13), a fourth port of the four-way valve (70) being communicable with an outlet of the compressor (20);

in a heating mode, the first port is communicated with the second port, and the third port is communicated with the fourth port;

in the refrigeration or defrosting mode, the first port is communicated with the third port, and the second port is communicated with the fourth port.

8. The air conditioning system according to claim 7, characterized in that the air conditioning system (100) further comprises a fan (60), the fan (60) being located on a side of the first heat exchanger (11) facing away from the first side (111);

-the fan (60) is configured to be in an open state when the second heat exchanger (12) is in a heating or cooling mode; the fan (60) is configured to be off when the second heat exchanger (12) is in a defrost mode.

9. The air conditioning system according to claim 8, wherein the air conditioning system (100) further comprises a gas-liquid separator (80), the gas-liquid separator (80) being connected between the first port of the four-way valve (70) and the inlet of the compressor (20).

10. An air conditioning system according to claim 1, characterized in that the first heat exchanger (11) and the second heat exchanger (12) are provided as fin heat exchangers; the first heat exchanger (11) comprises a plurality of refrigerant circuits, and the refrigerant circuits are independent from each other.