CN215930202U - Supercooling air return device and air conditioning system - Google Patents
Supercooling air return device and air conditioning system Download PDFInfo
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- CN215930202U CN215930202U CN202122355441.1U CN202122355441U CN215930202U CN 215930202 U CN215930202 U CN 215930202U CN 202122355441 U CN202122355441 U CN 202122355441U CN 215930202 U CN215930202 U CN 215930202U
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Abstract
The utility model provides a supercooling air return device and an air conditioning system, wherein the supercooling air return device comprises an air return pipe and a supercooling assembly, and the supercooling assembly is arranged in the air return pipe; the first port of the air return pipe is used for being connected with a four-way valve in an air conditioning system, and the second port of the air return pipe is used for being connected with an air return port of a compressor in the air conditioning system; the first port of the supercooling assembly is used for being connected with an outdoor heat exchanger in the air conditioning system, and the second port of the supercooling assembly is used for being connected with an indoor heat exchanger in the air conditioning system. By arranging the supercooling air return device in the air conditioning system, on one hand, the liquefaction degree of the refrigerant entering the indoor heat exchanger can be effectively improved when the air conditioning system operates in a refrigeration mode; on the other hand, the refrigerant in the muffler and the refrigerant in the supercooling assembly are utilized to exchange heat, so that the heat exchange efficiency of the supercooling assembly can be improved, the temperature of the gaseous refrigerant flowing back to the compressor is improved, and the energy consumption of the compressor is reduced.
Description
Technical Field
The utility model relates to the technical field of air conditioners, in particular to a supercooling air return device and an air conditioning system.
Background
At present, the air conditioning system takes refrigeration energy efficiency as an energy efficiency grade evaluation standard. In the related art, in order to further improve the energy efficiency of the air conditioning system in the refrigeration mode, a supercooling structure is often arranged at the bottom of the outdoor unit heat exchanger, and the supercooling structure is used for prolonging the flow path of the high-temperature refrigerant in the heat exchanger, so that the supercooling degree of the refrigerant is improved, and the refrigerant with lower temperature is obtained. However, the lower temperature of the refrigerant is obtained by only relying on the heat exchange between the cooling structure and the air, and the heat exchange efficiency is low.
In addition, the return air temperature of the compressor in the air conditioning system is relatively low, and generally, when the return air temperature of the compressor is too low, the working efficiency of the compressor is also lowered, and even the risk of liquid impact is faced. Higher discharge temperatures require higher electrical power consumption, which results in higher compressor power consumption.
SUMMERY OF THE UTILITY MODEL
The utility model mainly aims to provide a supercooling air return device and an air conditioning system, which can improve the heat exchange efficiency of a supercooling structure and simultaneously improve the air return temperature of a compressor.
In a first aspect, embodiments of the present invention provide a supercooling air returning device, including an air returning pipe and a supercooling assembly, wherein,
the supercooling assembly is arranged inside the air return pipe;
the first port of the air return pipe is used for being connected with a four-way valve in an air conditioning system, and the second port of the air return pipe is used for being connected with an air return port of a compressor in the air conditioning system;
the first port of the supercooling assembly is used for being connected with an outdoor heat exchanger in the air conditioning system, and the second port of the supercooling assembly is used for being connected with an indoor heat exchanger in the air conditioning system.
The supercooling air return device provided by the embodiment of the utility model at least has the following beneficial technical effects:
through setting the subcooling subassembly in the inside of muffler, when air conditioning system operation refrigeration mode, the high temperature high pressure gaseous state refrigerant of following compressor exhaust carries out the heat transfer through outdoor heat exchanger and outdoor air after, enters into the subcooling subassembly, because the refrigerant that flows out from outdoor heat exchanger probably has some not liquefied gaseous state refrigerant, this part gaseous state refrigerant can carry out the heat transfer with the lower refrigerant of temperature in the muffler in the subcooling subassembly, make the gaseous state refrigerant liquefaction of flowing out from outdoor heat exchanger, make the refrigerant temperature reduce, reach the refrigerant subcooling purpose. According to the scheme of the embodiment of the utility model, on one hand, the liquefaction degree of the refrigerant entering the indoor heat exchanger can be effectively improved; on the other hand, the refrigerant in the muffler and the refrigerant in the supercooling assembly are utilized to exchange heat, so that the heat exchange efficiency of the supercooling assembly can be improved, and meanwhile, the temperature of the gaseous refrigerant flowing back to the compressor can be improved, and the energy consumption of the compressor is reduced.
According to some embodiments of the supercooling return air device of the present invention, the supercooling assembly includes a throttling capillary tube, and the high temperature liquid refrigerant and the low temperature gaseous refrigerant in the return pipe fully exchange heat in the throttling capillary tube, thereby further realizing throttling.
According to some embodiments of the supercooling return air device, the supercooling assembly further comprises at least one of a first supercooling pipe and a second supercooling pipe, wherein the first supercooling pipe is used for connecting the throttling capillary tube and the outdoor heat exchanger, and the second supercooling pipe is used for connecting the throttling capillary tube and the indoor heat exchanger.
In a second aspect, an embodiment of the present invention further provides an air conditioning system, including: a compressor, a four-way valve, an outdoor heat exchanger, an indoor heat exchanger and a supercooling air return device, wherein,
the supercooling air return device comprises an air return pipe and a supercooling assembly, and the supercooling assembly is arranged inside the air return pipe;
the compressor has a discharge port and a return port;
a first port of the four-way valve is connected with the exhaust port, a second port of the four-way valve is connected with a first port of the outdoor heat exchanger, a third port of the four-way valve is connected with a first port of the indoor heat exchanger, and a fourth port of the four-way valve is connected with a first port of the muffler;
the second port of the air return pipe is connected with the air return port;
the second port of the outdoor heat exchanger is connected with the first port of the supercooling assembly;
the second port of the indoor heat exchanger is connected with the second port of the supercooling assembly.
The air conditioning system provided by the embodiment of the utility model at least has the following beneficial technical effects: through setting the subcooling subassembly in the inside of muffler, when air conditioning system operation refrigeration mode, the high temperature high pressure gaseous state refrigerant of following compressor exhaust carries out the heat transfer through outdoor heat exchanger and outdoor air after, enters into the subcooling subassembly, because the refrigerant that flows out from outdoor heat exchanger probably has some not liquefied gaseous state refrigerant, this part gaseous state refrigerant can carry out the heat transfer with the lower refrigerant of temperature in the muffler in the subcooling subassembly, make the gaseous state refrigerant liquefaction of flowing out from outdoor heat exchanger, make the refrigerant temperature reduce, reach the refrigerant subcooling purpose. According to the scheme of the embodiment of the utility model, on one hand, the liquefaction degree of the refrigerant entering the indoor heat exchanger can be effectively improved; on the other hand, the refrigerant in the muffler and the refrigerant in the supercooling assembly are utilized to exchange heat, so that the heat exchange efficiency of the supercooling assembly can be improved, and meanwhile, the temperature of the gaseous refrigerant flowing back to the compressor can be improved, and the energy consumption of the compressor is reduced.
According to some embodiments of the air conditioning system of the present invention, the supercooling assembly includes a throttling capillary tube, and the high-temperature liquid refrigerant exchanges heat with the low-temperature gaseous refrigerant in the return pipe in the throttling capillary tube sufficiently, so as to further realize throttling.
According to the air conditioning system of some embodiments of the present invention, the supercooling assembly further includes at least one of a first supercooling pipe and a second supercooling pipe, wherein the first supercooling pipe is used for connecting the throttling capillary tube and the outdoor heat exchanger, and the second supercooling pipe is used for connecting the throttling capillary tube and the indoor heat exchanger.
According to some embodiments of the present invention, the air conditioning system further comprises a first electronic expansion valve disposed between the second port of the outdoor heat exchanger and the first port of the subcooling assembly. Here, the first electronic expansion valve is used to adjust the flow rate of the refrigerant flowing therethrough.
According to some embodiments of the present invention, the air conditioning system further comprises a second electronic expansion valve disposed between the second port of the indoor heat exchanger and the second port of the subcooling assembly. Here, the second electronic expansion valve is used to adjust the flow rate of the refrigerant flowing therethrough.
According to some embodiments of the present invention, the air conditioning system further comprises a bypass flow path, the bypass flow path being disposed between the second port of the outdoor heat exchanger and the second port of the indoor heat exchanger, the bypass flow path being provided with an electrically controlled valve. When the temperature of the gaseous refrigerant in the muffler is higher than the upper limit value of the temperature of the muffler, the bypass flow path can be opened through the electric control valve to reduce the flow of the refrigerant entering the supercooling assembly, so that the temperature of the gaseous refrigerant in the muffler is reduced to a normal value.
According to some embodiments of the air conditioning system of the present invention, the electrically controlled valve is an electronic expansion valve.
According to some embodiments of the air conditioning system of the present invention, the air conditioning system further includes a gas-liquid separator, the gas-liquid separator is disposed between the four-way valve and the air return pipe, and a liquid portion of the refrigerant is filtered by the gas-liquid separator, so as to improve a purity of the gaseous refrigerant entering the air return pipe.
According to some embodiments of the present invention, the air conditioning system further includes a temperature sensor disposed on the air return pipe, and the temperature sensor can detect a temperature of a gaseous refrigerant in the air return pipe.
Additional features and advantages of the utility model will be set forth in the description which follows, and in part will be obvious from the description, or may be learned by practice of the utility model. The objectives and other advantages of the utility model may be realized and attained by the structure particularly pointed out in the written description and drawings.
Drawings
The supercooling return air device and the air conditioning system of the present invention are described below with reference to the accompanying drawings. In the drawings:
fig. 1 and 2 are schematic structural views of an air conditioning system according to an embodiment of the present invention;
fig. 3 is a schematic structural diagram of a supercooling air return device according to an embodiment of the present invention.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention more apparent, the present invention is described in further detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative of the utility model and are not intended to limit the utility model.
It should be understood that in the description of the embodiments of the present invention, if there is any description of "first", "second", etc., it is only for the purpose of distinguishing technical features, and it is not to be understood as indicating or implying relative importance or implicitly indicating the number of indicated technical features or implicitly indicating the precedence of the indicated technical features. "at least one" means one or more, "a plurality" means two or more. "and/or" describes the association relationship of the associated objects, and means that there may be three relationships, for example, a and/or B, and may mean that a exists alone, a and B exist simultaneously, and B exists alone. Wherein A and B can be singular or plural. The character "/" generally indicates that the former and latter associated objects are in an "or" relationship. "at least one of the following" and similar expressions refer to any combination of these items, including any combination of singular or plural items. For example, at least one of a, b, and c may represent: a, b, c, a and b, a and c, b and c or a and b and c, wherein a, b and c can be single or multiple.
Those of ordinary skill in the art will appreciate that the connections described in the embodiments of the present invention include direct connections and indirect connections through intermediate components.
It should be noted that the technical features related to the embodiments of the present invention described below may be combined with each other as long as they do not conflict with each other.
The sub-cooling air returning device 150 and the air conditioning system according to the embodiment of the present invention will be described in detail with reference to the accompanying drawings.
Referring to fig. 1 and 2, fig. 1 and 2 both show a schematic structural diagram of an air conditioning system according to an embodiment of the present invention, where arrows in fig. 1 indicate a refrigerant flow direction when the air conditioning system according to the embodiment of the present invention operates in a cooling mode, and arrows in fig. 2 indicate a refrigerant flow direction when the air conditioning system according to the embodiment of the present invention operates in a heating mode.
As shown in fig. 1 and 2, the air conditioning system according to the embodiment of the present invention includes a compressor 110, a four-way valve 120, an outdoor heat exchanger 130, an indoor heat exchanger 140, and a supercooling return air device 150. It should be understood that the compressor 110, the four-way valve 120, the outdoor heat exchanger 130, the indoor heat exchanger 140 and the supercooling return air device 150 form a refrigerant circulation circuit of the air conditioning system.
Referring to fig. 3, fig. 3 shows a supercooling return air device 150 according to an embodiment of the present invention. As shown in fig. 3, the supercooling return air means 150 includes a return air pipe 151 and a supercooling assembly provided inside the return air pipe 151. The muffler 151 has two ports, one of which is connected to the four-way valve 120 and the other of which is connected to the compressor 110. The subcooling assembly also has two ports, one for connection to the outdoor heat exchanger 130 and the other for connection to the indoor heat exchanger 140.
It can be understood that the compressor 110 is a core device of the air conditioning system, and functions to compress the driving refrigerant. In particular implementations, the compressor 110 may be, but is not limited to, a piston compressor, a scroll compressor, a dual rotor compressor, a screw compressor, or the like. The compressor 110 has a discharge port and a return port.
It is understood that the four-way valve 120 is responsible for switching the flow direction of the refrigerant in the refrigerant circulation loop. The four-way valve 120 has four ports, a first port of the four-way valve 120 is connected to a discharge port of the compressor 110, a second port of the four-way valve 120 is connected to a first port of the outdoor heat exchanger 130, a third port of the four-way valve 120 is connected to a first port of the indoor heat exchanger 140, and a fourth port of the four-way valve 120 is connected to a first port of the muffler 151.
It is understood that the second port of the air return pipe 151 is connected to the air return port of the compressor 110.
It will be appreciated that the first port of the supercooling assembly is connected to the second port of the outdoor heat exchanger 130, and the second port of the supercooling assembly is connected to the second port of the indoor heat exchanger 140.
In a specific implementation, the outdoor heat exchanger 130 and the indoor heat exchanger 140 may be, but are not limited to, plate heat exchangers.
The operation principle of the air conditioning system provided by the embodiment of the utility model in the cooling mode is described below with reference to fig. 1.
When the air conditioning system operates in a refrigeration mode, the first port and the second port of the four-way valve 120 are communicated, the third port and the fourth port of the four-way valve 120 are communicated, and the compressor 110 compresses a gaseous refrigerant and then discharges the high-temperature and high-pressure gaseous refrigerant through the exhaust port; the gaseous refrigerant from the compressor 110 sequentially passes through the first port and the second port of the four-way valve 120 to reach the first port of the outdoor heat exchanger 130, and exchanges heat with outdoor air in the outdoor heat exchanger 130 to be condensed into a liquid state; however, the liquid refrigerant exiting the outdoor heat exchanger 130 may be mixed with a small amount of gaseous refrigerant due to insufficient heat exchange.
After exiting the outdoor heat exchanger 130, the refrigerant containing a small amount of gas enters the supercooling assembly, so that the refrigerant exchanges heat with the refrigerant in the muffler 151 in the supercooling assembly. It should be understood that, since the refrigerant in the muffler 151 is evaporated by the indoor heat exchanger 140, the temperature of the refrigerant in the muffler 151 is lower than that of the refrigerant in the supercooling assembly; therefore, the refrigerant which is not completely liquefied is transmitted to the supercooling assembly, the temperature of the refrigerant can be reduced, the refrigerant is further subjected to heat exchange and supercooling, the refrigerant which is not liquefied is liquefied, the purpose of supercooling the refrigerant is achieved, and the liquefaction degree of the refrigerant entering the indoor heat exchanger 140 is effectively improved.
The refrigerant coming out of the supercooling assembly enters the indoor heat exchanger 140, the liquid refrigerant exchanges heat with the indoor air in the indoor heat exchanger 140, and the liquid refrigerant is evaporated and then converted into a gas state. The gaseous refrigerant exiting the indoor heat exchanger 140 may be doped with a small amount of liquid refrigerant due to insufficient heat exchange.
The refrigerant containing a small amount of liquid from the indoor heat exchanger 140 sequentially passes through the third port and the fourth port of the four-way valve 120 and enters the muffler 151; the refrigerant in the muffler 151 exchanges heat with the refrigerant in the supercooling assembly, and the temperature of the refrigerant in the muffler 151 is lower than that of the refrigerant in the supercooling assembly because the refrigerant in the muffler 151 is evaporated by the indoor heat exchanger 140; therefore, the refrigerant in the return air pipe 151 can obtain a higher return air temperature by exchanging heat with the refrigerant in the supercooling assembly, and simultaneously gasify the non-gasified refrigerant, thereby effectively increasing the gasification degree of the refrigerant flowing back to the compressor 110.
Based on the above analysis, in the embodiment of the present invention, the supercooling assembly is disposed inside the air return pipe 151, when the air conditioning system operates in the refrigeration mode, the high-temperature and high-pressure gaseous refrigerant discharged from the compressor 110 exchanges heat with the outdoor air through the outdoor heat exchanger 130, and then enters the supercooling assembly, because part of the non-liquefied gaseous refrigerant may exist in the refrigerant flowing out of the outdoor heat exchanger 130, and the part of the gaseous refrigerant may exchange heat with the refrigerant with a lower temperature in the air return pipe 151 in the supercooling assembly, so that the gaseous refrigerant flowing out of the outdoor heat exchanger 130 is liquefied, the temperature of the refrigerant is reduced, and the purpose of supercooling the refrigerant is achieved. According to the scheme of the embodiment of the utility model, on one hand, the liquefaction degree of the refrigerant entering the indoor heat exchanger 140 can be effectively improved; on the other hand, the refrigerant in the muffler 151 exchanges heat with the refrigerant in the supercooling assembly, so that the heat exchange efficiency of the supercooling assembly can be improved, and the temperature of the gaseous refrigerant flowing back to the compressor 110 can be increased, thereby reducing the energy consumption of the compressor 110.
The operation principle of the air conditioning system provided by the embodiment of the utility model in the heating mode will be described with reference to fig. 2.
When the air conditioning system operates in a heating mode, the first port of the four-way valve 120 is communicated with the third port, the second port of the four-way valve 120 is communicated with the fourth port, and the compressor 110 compresses the gaseous refrigerant and then discharges the high-temperature and high-pressure gaseous refrigerant through the exhaust port; the gaseous refrigerant from the compressor 110 sequentially passes through the first port and the third port of the four-way valve 120 to reach the first port of the indoor heat exchanger 140, and exchanges heat with the indoor air in the indoor heat exchanger 140 to be condensed into a liquid state. The liquid refrigerant from the indoor heat exchanger 140 may be doped with a small amount of gaseous refrigerant due to insufficient heat exchange.
After exiting the indoor heat exchanger 140, the refrigerant containing a small amount of gas enters the supercooling assembly, so that the refrigerant exchanges heat with the refrigerant in the muffler 151 in the supercooling assembly. It should be understood that, since the refrigerant in the muffler 151 is evaporated by the outdoor heat exchanger 130, the temperature of the refrigerant in the muffler 151 is lower than that of the refrigerant in the supercooling assembly; therefore, the refrigerant which is not completely liquefied is transmitted to the supercooling assembly, the temperature of the refrigerant can be reduced, the refrigerant is further subjected to heat exchange and supercooling, the refrigerant which is not liquefied is liquefied, the purpose of supercooling the refrigerant is achieved, and the liquefaction degree of the refrigerant entering the outdoor heat exchanger 130 is effectively improved.
The refrigerant from the supercooling assembly enters the outdoor heat exchanger 130, the liquid refrigerant exchanges heat with outdoor air in the outdoor heat exchanger 130, and the liquid refrigerant is evaporated and converted into a gas state. It should be appreciated that the gaseous refrigerant exiting the outdoor heat exchanger 130 may be contaminated with a small amount of liquid refrigerant due to insufficient heat exchange.
The refrigerant containing a small amount of liquid from the outdoor heat exchanger 130 sequentially passes through the second port and the fourth port of the four-way valve 120 and enters the muffler 151; the refrigerant in the muffler 151 exchanges heat with the refrigerant in the supercooling assembly, and the temperature of the refrigerant in the muffler 151 is lower than that of the refrigerant in the supercooling assembly because the refrigerant in the muffler 151 is evaporated by the outdoor heat exchanger 130; therefore, the refrigerant in the return air pipe 151 can obtain a higher return air temperature by exchanging heat with the refrigerant in the supercooling assembly, and simultaneously gasify the non-gasified refrigerant, thereby effectively increasing the gasification degree of the refrigerant flowing back to the compressor 110.
Based on the above analysis, in the embodiment of the present invention, the supercooling assembly is disposed inside the air return pipe 151, when the air conditioning system operates in the heating mode, the high-temperature and high-pressure gaseous refrigerant discharged from the compressor 110 enters the supercooling assembly after exchanging heat with the indoor air through the indoor heat exchanger 140, and since a part of the non-liquefied gaseous refrigerant may exist in the refrigerant flowing out of the indoor heat exchanger 140, the part of the gaseous refrigerant may exchange heat with the refrigerant with a lower temperature in the air return pipe 151 in the supercooling assembly, so that the gaseous refrigerant flowing out of the indoor heat exchanger 140 is liquefied, the temperature of the refrigerant is reduced, and the purpose of supercooling the refrigerant is achieved. According to the scheme of the embodiment of the utility model, on one hand, the liquefaction degree of the refrigerant entering the outdoor heat exchanger 130 can be effectively improved; on the other hand, the refrigerant in the muffler 151 exchanges heat with the refrigerant in the supercooling assembly, so that the heat exchange efficiency of the supercooling assembly can be improved, and the temperature of the gaseous refrigerant flowing back to the compressor 110 can be increased, thereby reducing the energy consumption of the compressor 110.
As shown in fig. 3, the supercooling assembly may include a first supercooling pipe 152, a throttle capillary 153, and a second supercooling pipe 154 connected in series in this order. The first supercooling pipe 152 is used to connect with the outdoor heat exchanger 130, and the second supercooling pipe 154 is used to connect with the indoor heat exchanger 140. It should be understood that in order to realize the supercooling assembly in the gas return pipe 151, the first supercooling pipe 152, the throttling capillary 153 and the second supercooling pipe 154 should have pipe diameters smaller than that of the gas return pipe 151. The first subcooling pipe 152 and the second subcooling pipe 154 may be L-shaped pipes, and each of the first subcooling pipe 152 and the second subcooling pipe 154 has a port penetrating through a side wall of the air return pipe 151 to facilitate connection with the corresponding outdoor heat exchanger 130 or the corresponding indoor heat exchanger 140.
In the specific implementation process, when the air conditioning system operates in the refrigeration mode, part of the gaseous refrigerant may exist in the refrigerant coming out of the outdoor heat exchanger 130 and not be liquefied, the refrigerant enters the supercooling gas return device 150 through the first supercooling pipe 152 after coming out of the outdoor heat exchanger 130, heat exchange is performed between the low-temperature refrigerant in the first supercooling pipe 152 and the low-temperature refrigerant in the gas return pipe 151, and the non-liquefied gaseous refrigerant is liquefied, so that the temperature of the refrigerant is reduced, the refrigerant obtains higher supercooling degree, and the liquefaction degree of the refrigerant is improved. When the liquid refrigerant with a certain supercooling degree flows through the throttling capillary tube 153, the temperature is further reduced, so that a higher supercooling degree is obtained, meanwhile, the high-pressure liquid refrigerant is converted into the low-pressure liquid refrigerant through throttling of the throttling capillary tube 153, and at the moment, a small amount of gaseous refrigerant is generated due to the fact that the pressure of the refrigerant is lowered. The low-pressure liquid refrigerant containing a small amount of gaseous refrigerant enters the second subcooling pipe 154 again, the liquid refrigerant is further subjected to heat exchange and subcooling through the second subcooling pipe 154, and the small amount of gaseous refrigerant is converted into a liquid refrigerant again due to temperature reduction. Thus, the refrigerant coming out of the supercooling assembly is a low-pressure liquid refrigerant with extremely high supercooling degree and few bubbles.
When the air conditioning system operates in the heating mode, part of the gaseous refrigerant may exist in the refrigerant coming out of the indoor heat exchanger 140 and not be liquefied, the refrigerant enters the supercooling gas return device 150 through the second supercooling pipe 154 after coming out of the indoor heat exchanger 140, and the low-temperature refrigerant in the second supercooling pipe 154 and the gas return pipe 151 exchanges heat to liquefy the non-liquefied gaseous refrigerant, so that the temperature of the refrigerant is reduced, the refrigerant obtains higher supercooling degree, and the liquefaction degree of the refrigerant is improved. When the liquid refrigerant with a certain supercooling degree flows through the throttling capillary tube 153, the temperature is further reduced, so that a higher supercooling degree is obtained, meanwhile, the high-pressure liquid refrigerant is converted into the low-pressure liquid refrigerant through throttling of the throttling capillary tube 153, and at the moment, a small amount of gaseous refrigerant is generated due to the fact that the pressure of the refrigerant is lowered. The low-pressure liquid refrigerant containing a small amount of gaseous refrigerant enters the first supercooling pipe 152 again, the liquid refrigerant is further subjected to heat exchange and supercooling through the first supercooling pipe 152, and the small amount of gaseous refrigerant is converted into a liquid state again due to temperature reduction. Thus, the refrigerant coming out of the supercooling assembly is a low-pressure liquid refrigerant with extremely high supercooling degree and few bubbles.
It is understood that, in the embodiment, the first subcooling pipe 152 or the second subcooling pipe 154 in the subcooling assembly shown in fig. 3 may be eliminated. That is, the supercooling assembly includes only the first supercooling pipe 152 and the throttle capillary 153; alternatively, the subcooling component comprises only the second subcooling tube 154 and the throttle capillary tube 153. Of course, it is also possible to eliminate both the first subcooling pipe 152 and the second subcooling pipe 154 in the subcooling assembly shown in fig. 3, that is, the subcooling assembly contains only the throttling capillary tube 153.
The embodiment of the present invention does not limit the specific structure of the supercooling assembly too much.
It is understood that the air conditioning system may further include a first electronic expansion valve 160. Specifically, the first electronic expansion valve 160 is disposed between the second port of the outdoor heat exchanger 130 and the first port of the supercooling assembly. Here, the first electronic expansion valve 160 is used to throttle and depressurize the refrigerant flowing therethrough. In addition, the flow rate of the refrigerant flowing through the first electronic expansion valve 160 may be adjusted by adjusting the opening degree thereof.
It is understood that the air conditioning system may further include a second electronic expansion valve 170. Specifically, the second electronic expansion valve 170 is disposed between the second port of the indoor heat exchanger 140 and the second port of the supercooling assembly. Here, the second electronic expansion valve 170 is used to throttle and depressurize the refrigerant flowing therethrough. In addition, the flow rate of the refrigerant flowing through the second electronic expansion valve 170 may be adjusted by adjusting the opening degree thereof.
For example, the air conditioning system according to the embodiment of the present invention may have the first electronic expansion valve 160 fully opened and the second electronic expansion valve 170 partially opened (i.e., not fully opened) when the air conditioning system operates in the cooling mode. In this way, the refrigerant coming out of the outdoor heat exchanger 130 enters the supercooling assembly after being throttled by the first electronic expansion valve 160 with the fully opened opening degree, so as to obtain higher supercooling degree and liquefaction degree; the refrigerant from the supercooling assembly flows into the second electronic expansion valve 170, and since the second electronic expansion valve 170 is opened only by a portion of the opening, the flow rate of the refrigerant flowing therethrough can be reduced, so that the refrigerant can sufficiently exchange heat in the supercooling assembly, and a high supercooling degree and a high liquefaction ratio can be obtained. The refrigerant enters the indoor heat exchanger 140 after being throttled by the second electronic expansion valve 170.
For example, in the air conditioning system according to the embodiment of the present invention, when the heating mode is operated, the second electronic expansion valve 170 may be fully opened, and the first electronic expansion valve 160 may be opened to a partial opening degree (i.e., not fully opened). In this way, the refrigerant coming out of the indoor heat exchanger 140 enters the supercooling assembly after being throttled by the second electronic expansion valve 170 with a fully opened opening degree, so as to obtain a higher supercooling degree and a higher liquefaction degree; the refrigerant coming out of the supercooling assembly flows into the first electronic expansion valve 160, and since the first electronic expansion valve 160 is opened only by a portion of the opening degree, the flow rate of the refrigerant flowing therethrough can be reduced, so that the refrigerant can sufficiently exchange heat in the supercooling assembly, and a high supercooling degree and a high liquefaction ratio can be obtained. The refrigerant is throttled by the first electronic expansion valve 160 and enters the outdoor heat exchanger 130.
It is understood that the air conditioning system may also include a bypass flow path. Specifically, the bypass flow path is provided between the second port of the outdoor heat exchanger 130 and the second port of the indoor heat exchanger 140, and an electrically controlled valve is provided on the bypass flow path.
For example, the electronic control valve of the bypass flow path may be an electronic expansion valve, a solenoid valve or other similar valve devices, and the specific type of the electronic control valve on the bypass flow path is not limited in this embodiment of the utility model.
Taking the electric control valve on the bypass flow path as the third electronic expansion valve 180 as an example, the third electronic expansion valve 180 is in a fully closed state no matter in a cooling mode or a heating mode during the normal operation of the air conditioning system. When the temperature of the refrigerant in the return pipe 151 is higher than the upper limit value of the return temperature, the third electronic expansion valve 180 is opened, so that the bypass flow path is opened to reduce the flow rate of the refrigerant entering the supercooling assembly, and further reduce the temperature of the gaseous refrigerant in the return pipe 151 to a normal value.
Illustratively, when the air conditioning system operates in the cooling mode, the initial state of the third electronic expansion valve 180 is a fully closed state, and when it is detected that the temperature of the refrigerant in the return air pipe 151 is greater than the upper limit value of the return air temperature, the third electronic expansion valve 180 is opened, so that the bypass flow path is opened, the refrigerant coming out of the outdoor heat exchanger 130 is divided into two paths, one path enters the supercooling assembly, and enters the indoor heat exchanger 140 after the supercooling assembly exchanges heat; the other path enters a bypass flow path and directly enters the indoor heat exchanger 140 through the bypass flow path. Therefore, the flow of the refrigerant entering the supercooling assembly is reduced, the heat exchange amount in the supercooling return air device 150 is reduced, the temperature of the refrigerant in the return air pipe 151 is prevented from being further increased, the return air temperature returns to a normal range, and the safe operation of the compressor 110 is ensured. After the temperature of the refrigerant in the muffler 151 returns to the normal range, the third electronic expansion valve 180 may return to the fully closed state.
Illustratively, when the air conditioning system operates in the heating mode, the initial state of the third electronic expansion valve 180 is a fully closed state, and when the temperature of the refrigerant in the return air pipe 151 is detected to be greater than the upper limit value of the return air temperature, the third electronic expansion valve 180 is opened, so that the bypass flow path is opened, the refrigerant coming out of the indoor heat exchanger 140 is divided into two paths, one path enters the supercooling assembly, and enters the outdoor heat exchanger 130 after the supercooling assembly exchanges heat; the other path enters the bypass flow path and directly enters the outdoor heat exchanger 130 through the bypass flow path. Therefore, the flow of the refrigerant entering the supercooling assembly is reduced, the heat exchange amount in the supercooling return air device 150 is reduced, the temperature of the refrigerant in the return air pipe 151 is prevented from being further increased, the return air temperature returns to a normal range, and the safe operation of the compressor 110 is ensured. After the temperature of the refrigerant in the muffler 151 returns to the normal range, the third electronic expansion valve 180 may return to the fully closed state.
In a specific implementation, the temperature sensor 155 may be disposed on the air return pipe 151, and the temperature of the gaseous refrigerant in the air return pipe 151 may be detected by the temperature sensor 155, so as to determine whether the temperature of the gaseous refrigerant in the air return pipe 151 exceeds the upper limit value of the air return temperature, and adjust the state of the third electronic expansion valve 180 according to the temperature value detected by the temperature sensor 155 of the air return pipe 151.
It is understood that the air conditioning system may further include a gas-liquid separator 190, and the gas-liquid separator 190 is disposed between the four-way valve 120 and the gas return pipe 151. Specifically, a first port of the gas-liquid separator 190 is connected to the fourth port of the four-way valve 120, and a second port of the gas-liquid separator 190 is connected to a first port of the gas return pipe 151. The refrigerant flowing out of the fourth port of the four-way valve 120 passes through the gas-liquid separator 190 to filter a liquid portion of the refrigerant, and then enters the gas return pipe 151, so that the purity of the gaseous refrigerant entering the gas return pipe 151 can be improved.
While the preferred embodiments of the present invention have been described in detail, it will be understood by those skilled in the art that the foregoing and various other changes, omissions and deviations in the form and detail thereof may be made without departing from the scope of this invention.
Claims (12)
1. A supercooling air return device is characterized by comprising an air return pipe and a supercooling assembly, wherein,
the supercooling assembly is arranged inside the air return pipe;
the first port of the air return pipe is used for being connected with a four-way valve in an air conditioning system, and the second port of the air return pipe is used for being connected with an air return port of a compressor in the air conditioning system;
the first port of the supercooling assembly is used for being connected with an outdoor heat exchanger in the air conditioning system, and the second port of the supercooling assembly is used for being connected with an indoor heat exchanger in the air conditioning system.
2. A subcooling device as described in claim 1, wherein said subcooling component comprises a throttling capillary tube.
3. The subcooling device according to claim 2, wherein the subcooling component further comprises at least one of a first subcooling tube and a second subcooling tube, wherein the first subcooling tube is configured to connect the throttling capillary tube and the outdoor heat exchanger, and the second subcooling tube is configured to connect the throttling capillary tube and the indoor heat exchanger.
4. An air conditioning system, comprising: a compressor, a four-way valve, an outdoor heat exchanger, an indoor heat exchanger and a supercooling air return device, wherein,
the supercooling air return device comprises an air return pipe and a supercooling assembly, and the supercooling assembly is arranged inside the air return pipe;
the compressor has a discharge port and a return port;
a first port of the four-way valve is connected with the exhaust port, a second port of the four-way valve is connected with a first port of the outdoor heat exchanger, a third port of the four-way valve is connected with a first port of the indoor heat exchanger, and a fourth port of the four-way valve is connected with a first port of the muffler;
the second port of the air return pipe is connected with the air return port;
the second port of the outdoor heat exchanger is connected with the first port of the supercooling assembly;
the second port of the indoor heat exchanger is connected with the second port of the supercooling assembly.
5. The air conditioning system of claim 4, wherein the subcooling component comprises a throttling capillary tube.
6. The air conditioning system of claim 5, wherein the subcooling component further comprises at least one of a first subcooling tube and a second subcooling tube, wherein the first subcooling tube is configured to connect the throttling capillary tube and the outdoor heat exchanger, and the second subcooling tube is configured to connect the throttling capillary tube and the indoor heat exchanger.
7. The air conditioning system of claim 4, further comprising a first electronic expansion valve disposed between the second port of the outdoor heat exchanger and the first port of the subcooling assembly.
8. The air conditioning system of claim 4, further comprising a second electronic expansion valve disposed between the second port of the indoor heat exchanger and the second port of the subcooling assembly.
9. The air conditioning system of claim 4, further comprising a bypass flow path disposed between the second port of the outdoor heat exchanger and the second port of the indoor heat exchanger, the bypass flow path having an electrically controlled valve disposed thereon.
10. The air conditioning system of claim 9, wherein the electrically controlled valve is an electronic expansion valve.
11. The air conditioning system of claim 4, further comprising a gas-liquid separator disposed between the four-way valve and the return air pipe.
12. The air conditioning system of claim 4, further comprising a temperature sensor disposed on the air return duct.
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| Application Number | Priority Date | Filing Date | Title |
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| CN202122355441.1U CN215930202U (en) | 2021-09-27 | 2021-09-27 | Supercooling air return device and air conditioning system |
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| CN202122355441.1U CN215930202U (en) | 2021-09-27 | 2021-09-27 | Supercooling air return device and air conditioning system |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN115507530A (en) * | 2022-05-12 | 2022-12-23 | 青岛海尔空调器有限总公司 | Evacuation structure applied to saddle type air conditioner and saddle type air conditioner |
| CN115682457A (en) * | 2022-09-22 | 2023-02-03 | 珠海格力电器股份有限公司 | Air conditioning system with heat exchange structure |
-
2021
- 2021-09-27 CN CN202122355441.1U patent/CN215930202U/en active Active
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN115507530A (en) * | 2022-05-12 | 2022-12-23 | 青岛海尔空调器有限总公司 | Evacuation structure applied to saddle type air conditioner and saddle type air conditioner |
| WO2023216661A1 (en) * | 2022-05-12 | 2023-11-16 | 青岛海尔空调器有限总公司 | Evacuation structure applied to saddle-type air conditioner and saddle-type air conditioner |
| CN115682457A (en) * | 2022-09-22 | 2023-02-03 | 珠海格力电器股份有限公司 | Air conditioning system with heat exchange structure |
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