TWI414735B - Air condition system and its subcool device - Google Patents

Abstract

A subcool device includes a body, a first flow tube, and a second flow tube. The body has a chamber. The chamber has a chamber entrance and a chamber exit. The first flow tube and the second flow tube are disposed in the chamber. The first flow tube has a first entrance and a first exit. The second flow tube has a second entrance and a second exit. A first modus coolant, a second modus coolant, and a third modus coolant respectively enter the chamber to from the first entrance, the chamber entrance, and the second entrance. A first modus coolant, a second modus coolant, and a third modus coolant are heart exchange in the chamber to improve the subcool of an air condition.

Description

Air conditioning system and its working fluid subcooling regulating device

The present proposal relates to an air conditioning system, and more particularly to an air conditioning system having an improved degree of subcooling of a working fluid and an undercooling adjusting device thereof.

Because the metropolitan area is narrow and dense, the buildings are close to each other, so it is easy to make the heat gather and spread. However, the modern people's material level is improved, and the comfort requirements for the living environment are relatively increased. Therefore, most of the buildings in the metropolitan area will be equipped with an air conditioning system.

The air-conditioning system controls the temperature, humidity, pressure, wind speed and cleanness in the building within a specified range, so that people in the building can live comfortably. In the general air conditioning system, a refrigerant is compressed by a compressor into a high temperature and high pressure refrigerant gas, and then sent to a condenser. Then, a cooling water tower is coupled with a pump to send cold water into the condenser to exchange heat between the cooling water and the high temperature and high pressure refrigerant gas. After the high temperature and high pressure refrigerant gas is condensed into a high pressure refrigerant liquid, it enters an expansion valve to expand to form a low pressure refrigerant liquid. Then, the low-pressure refrigerant liquid is re-entered into an evaporator to exchange heat of the low-pressure refrigerant liquid with the external environment to absorb a large amount of heat energy. Next, a cold air that is absorbed by the refrigerant is blown by a fan system to generate a cold room effect as an indoor cool air. Finally, the low-pressure refrigerant gas formed by the heat absorption enters a compressor from a low-pressure pipe to be compressed again into a high-temperature high-pressure refrigerant gas. Through the circulation operation of the above air conditioning system, the indoor space can be obtained as a cold room.

However, in general air-conditioning products on the market today, the temperature of the refrigerant after passing through the condenser is generally close to about 40 to 42 °C. According to the ambient temperature of 35 ° C, if the temperature of the refrigerant passing through the condenser can be further reduced by 5 to 7 ° C, the efficiency of the air conditioning system can be improved by about 10 to 15%. At present, the air conditioning system on the market improves the system efficiency, and most of them use methods such as increasing the condenser, increasing the speed of the condenser fan, or adding a change in the condenser circuit. However, all of these methods require an overall update of the air-conditioning system, which inevitably leads to an increase in the cost of repair and replacement. For older air-conditioning systems, if it is necessary to increase the degree of cooling to improve system efficiency, it will be a considerable expense.

In view of the above problems, the present invention proposes to provide an air conditioning system and a supercooling degree adjusting device for the working fluid thereof, thereby solving the problem that the system efficiency of the prior art air conditioning system is high.

The subcooling degree adjusting device for the working fluid disclosed in the proposal is for adjusting one of the refrigerants in a cycle state. The refrigerant changes between a first state, a second state, and a third state. Wherein, the refrigerant in the first state is in a liquid state, the refrigerant in the second state is in a liquid state, and the pressure and temperature are lower than the refrigerant in the first state, and the refrigerant in the third state is in a gaseous state and the pressure and temperature are lower than the temperature. The same state of refrigerant. The subcooling regulating device of the working fluid comprises a body, a first flow pipe and a second flow pipe. The body has a chamber having a chamber inlet and a chamber outlet. The first flow tube is disposed in the chamber, and the first flow tube has a first inlet and a first outlet outside the machine body. The second flow tube is disposed in the chamber, and the second flow tube has a second inlet and a second outlet outside the machine body. Wherein, the refrigerant of the first state, the refrigerant of the second state, and the refrigerant of the third state enter the chamber through the first inlet, the second inlet and the inlet of the chamber, respectively, and after heat exchange in the chamber, respectively The chamber exits the chamber from the first outlet, the second outlet, and the chamber outlet.

The air conditioning system disclosed in this proposal is for a refrigerant to circulate therein. The air conditioning system includes a subcooling regulator for the working fluid, an expansion valve, an evaporator, a compressor, and a condenser. The subcooling regulating device of the working fluid comprises a body, a first flow tube, a second flow tube and a first valve. The body has a chamber having a chamber inlet and a chamber outlet. The first flow tube is disposed in the chamber, and the first flow tube has a first inlet and a first outlet outside the machine body. The second flow tube is disposed in the chamber, and the second flow tube has a second inlet and a second outlet outside the machine body. The first valve is disposed outside the machine body, and the first valve communicates with the chamber inlet. In addition, the expansion valve has an expansion valve inlet and an expansion valve outlet, and the expansion valve inlet communicates with the first valve and the first outlet, respectively. The evaporator has an evaporator inlet and an evaporator outlet, the evaporator inlet is connected to the expansion valve outlet, and the evaporator outlet is connected to the second inlet. The compressor has a compressor inlet and a compressor outlet, and the compressor inlet communicates with the second outlet and the chamber outlet, respectively. The condenser has a condenser inlet and a condenser outlet, the condenser inlet is connected to the compressor outlet, and the condenser outlet is connected to the first inlet. Wherein, the refrigerant entering the chamber from the first inlet, the refrigerant entering the chamber from the second inlet, and the refrigerant entering the chamber from the inlet of the chamber exchange heat in the chamber.

According to the above air conditioning system, the refrigerant flow in the first state from the condenser to the expansion valve passes through the coldness adjusting device. Therefore, the refrigerant of the first state is exchanged with the refrigerant of the second state and the third state in the supercooling degree adjusting device to reduce the temperature of the refrigerant in the first state. Since the temperature of the refrigerant in the first state is lowered, the degree of subcooling of the air conditioning system is also improved. It is such a subcooling regulating device that can improve the system efficiency of the air conditioning system.

The features, implementation and efficacy of this proposal are described in detail below with reference to the preferred embodiment of the drawings.

Please refer to "Figure 1" and "Figure 2". Figure 1 is a schematic view showing the structure of an air-conditioning system according to an embodiment of the present proposal. "Figure 2" is a working fluid according to "Figure 1". An enlarged schematic view of the subcooling regulating device.

The air conditioning system 20 of an embodiment of the present invention causes a refrigerant to undergo a phase change cycle therein to lower the temperature of an area. The air conditioning system 20 includes a working fluid subcooling regulator 10, an expansion valve 200, an evaporator 300, a compressor 400, and a condenser 500. Moreover, the air conditioning system 20 can further include an oil separator 600.

The subcooling degree adjusting device 10 of the working fluid includes a body 100, a first flow tube 110 and a second flow tube 130. Moreover, the supercooling degree adjusting device 10 of the working fluid may further include a third flow tube 140, a first valve 150 and a second valve 160. The body 100 has a chamber 120 having a chamber inlet 122 and a chamber outlet 124. In addition, the first flow tube 110 is disposed in the chamber 120, and the first flow tube 110 has a first inlet 112 and a first outlet 114. The first inlet 112 and the first outlet 114 are respectively disposed outside the body 100, and the first flow tube 110 is not directly in communication with the chamber 120. That is, although the first flow tube 110 is disposed in the chamber 120, the first flow tube 110 does not have any through holes communicating with the chamber 120, as shown in "Fig. 2".

The second flow tube 130 is disposed in the chamber 120, and the second flow tube 130 has a second inlet 132 and a second outlet 134. The second inlet 132 and the second outlet 134 are respectively disposed outside the body 100, and the second flow tube 130 is not directly in communication with the chamber 120. Moreover, the second flow tube 130 can be covered by the first flow tube 110, and the first flow tube 110 and the second flow tube 130 can be connected as a concentric tube. The second flow tube 130 is not directly in communication with the first flow tube 110. That is, the second flow tube 130 is disposed in the first flow tube 110, but the second flow tube 130 does not have any through holes communicating with the first flow tube 110, as shown in FIG.

In addition, the third flow tube 140 is disposed in the chamber 120, and the third flow tube 140 has a third inlet 142 and a third outlet 144. The third inlet 142 and the third outlet 144 are respectively disposed outside the body 100, and the third flow tube 140 is not directly in communication with the chamber 120. In addition, the third flow tube 140 can surround the first flow tube 110 and the second flow tube 130 covered by the first flow tube 110 in a spiral manner. As shown in FIG. 2, the first flow tube 110 The coating of the second flow tube 130 can also adopt the design of the tube in the tube. The first flow tube 110, the second flow tube 130, and the third flow tube 140 are made of a material having a high conductivity, and for example, a material such as copper (model C1220T-H) is used.

In other words, from the chamber inlet 122 to the chamber outlet 124, from the first inlet 112 to the first outlet 114, from the second inlet 132 to the second outlet 134, and from the third inlet 142 to the third outlet 144, It is divided into four separate independent channels.

In addition, the first valve 150 is disposed outside the body 100 and has a first valve inlet 152 and a first valve outlet 154. The first valve outlet 154 communicates with the chamber inlet 122, and the first valve 150 regulates the flow of refrigerant from the chamber inlet 122 into the chamber 120. The second valve 160 is disposed outside the body 100 and has a second valve inlet 162 and a second valve outlet 164. The second valve outlet 164 communicates with the third inlet 142, and the second valve 160 regulates the flow of a refrigerant from the third inlet 142 into the chamber 120.

The expansion valve 200 of the present embodiment has an expansion valve inlet 210 and an expansion valve outlet 220. The expansion valve inlet 210 communicates with the first valve inlet 152 and the first outlet 114, respectively. The expansion valve 200 is used for expanding a high-pressure high-temperature liquid refrigerant into a low-pressure low-temperature two-phase refrigerant, and more recently, a gas-liquid coexisting refrigerant.

The evaporator 300 has an evaporator inlet 310 and an evaporator outlet 320. The evaporator inlet 310 communicates with the expansion valve outlet 220, and the evaporator outlet 320 communicates with the second inlet 132. The evaporator 300 is configured to evaporate the low-pressure low-temperature two-phase refrigerant flowing out of the expansion valve outlet 220 into a low-pressure low-temperature gaseous refrigerant, and simultaneously absorb a large amount of heat energy to lower the indoor air temperature.

The compressor 400 of the present embodiment has a compressor inlet 410 and a compressor outlet 420. The compressor inlet 410 communicates with the second outlet 134, the chamber outlet 124, and the third outlet 144, respectively. The compressor 400 is configured to compress the low-pressure low-temperature gaseous refrigerant flowing out of the supercooling degree adjusting device 10 of the working fluid into a high-pressure high-temperature gaseous refrigerant.

Further, the condenser 500 has a condenser inlet 510 and a condenser outlet 520. The condenser inlet 510 communicates with the compressor outlet 420 and the condenser outlet 520 communicates with the first inlet 112. The condenser 500 is used to condense the high-pressure high-temperature gaseous refrigerant flowing out of the compressor 400 into a high-pressure medium-temperature liquid refrigerant.

The oil separator 600 of the present embodiment is disposed between the condenser inlet 510 and the compressor outlet 420, and the oil separator 600 is connected to the condenser inlet 510 and the compressor outlet 420. Also, the oil separator 600 is also in communication with the second valve inlet 162. Since the lubricating oil is contained in the compressor 400 to maintain the normal operation of the compressor 400, the lubricating oil is usually discharged from the compressor 400 along with the refrigerant. Therefore, the oil separator 600 is used to separate the refrigerant mixed with the lubricating oil, so that the refrigerant continues to flow in the direction of the condenser 500, and the lubricating oil is separated by filtration and flows to the second valve inlet 162.

Next, the principle of circulating operation of the refrigerant in the air conditioning system of the present embodiment will be described. Please refer to "3" and "1" and "2". "3" is a schematic diagram showing the change in the pressure of the refrigerant circulating in the air-conditioning system according to "1".

In "Fig. 3", the area marked with a indicates that the refrigerant is in a liquid state. The label b area represents a type in which the refrigerant coexists in a gaseous state and a liquid state, and the closer to the label a region, the higher the proportion of the liquid state. The area labeled c indicates that the refrigerant is in a gaseous state.

The refrigerant 901 of the first state flows out of the condenser 500 and flows into the supercooling degree adjusting device 10 of the working fluid through the first inlet 112, and the refrigerant 901 in the first state is generally a high-pressure liquid refrigerant (such as " Figure 3). A refrigerant 902 of a second state flows into the subcooling regulator 10 of the working fluid from the chamber inlet 122, and the refrigerant 902 of the second state is a liquid refrigerant, and the refrigerant 901 having a temperature lower than that of the first state ( As shown in "Figure 3"). A third type of refrigerant 903 is a second inlet 132 flowing into the subcooling degree adjusting device 10 of the working fluid, and a third type of refrigerant 903 is a low pressure gaseous refrigerant (as shown in "Fig. 3"), and The refrigerant 901 whose temperature is lower than the first state.

After the refrigerant 902 of the second state flows into the chamber 120 of the supercooling degree adjusting device 10 of the working fluid, the refrigerant 902 of the second state is expanded from the liquid refrigerant into a gaseous state and a liquid state due to the instantaneous increase of the flow channel volume. The coexisting refrigerant and the refrigerant 901 having a lower temperature than the first state. The refrigerant 901 of the first state flows through the first flow tube 110 and exchanges heat with the refrigerant 903 of the third state in the second flow tube 130 covered by the first flow tube 110. The temperature of the refrigerant 903 in the third state in the second flow tube 130 is lower than the temperature 901 of the first state in the first flow tube 110 by about 20 degrees Celsius to 30 degrees Celsius, so that the first flow tube 110 can be reduced. The temperature of the refrigerant 901 in the same state. At the same time, the refrigerant 901 in the first state in the first flow tube 110 is also in heat exchange with the refrigerant 902 in the second state in the filling chamber 120. Therefore, when the refrigerant 901 of the first state flows through the first flow tube 110, its temperature drops. When the refrigerant 901 of the first state flows out of the first outlet 114, it is a refrigerant 904 of a fourth state. The refrigerant 904 of the fourth state is the same as the refrigerant 901 of the first state, and the difference is that the refrigerant 904 of the fourth state is in the form of the cooling state 901 of the first state, so that the refrigerant of the fourth state is the refrigerant of the fourth state. The temperature of 904 is lower than that of the refrigerant 901 of the first state (as shown in "Fig. 3").

Next, a portion of the refrigerant 904 of the fourth state flows to the expansion valve 200, and a portion flows to the first valve 150. In order to enable the supercooling degree of the air conditioning system 20 to be more accurately controlled, the first valve 150 of the embodiment can further have the function of an expansion valve and can accurately control the flow rate of the refrigerant. Therefore, when a portion of the refrigerant 904 of the fourth state flows through the first valve 150, the temperature is again decreased due to the volume expansion, and the refrigerant 902 becomes the second state (as shown in FIG. 3). ). It is worth mentioning that the amount of the refrigerant 904 of the fourth state flowing through the first valve 150 can be changed by adjusting the size of the valve port of the first valve 150, that is, the first valve 150 can control the fourth state of the refrigerant 904 respectively. The ratio of the flow to the expansion valve 200 to the first valve 150. For example, when the first valve inlet 152 of the first valve 150 is increased, the flow rate of the refrigerant 904 flowing through the fourth state of the first valve 150 is increased, and the fourth state of the expansion valve 200 is relatively increased. The refrigerant 904 flow is reduced.

When a portion of the refrigerant 904 of the fourth state flows through the expansion valve 200, it is expanded by the expansion valve 200 into a refrigerant 905 of a fifth state. The fifth refrigerant 905 is a refrigerant in which a gas and a liquid coexist. Next, the refrigerant 905 of the fifth state continues to flow through the evaporator 300, and is absorbed by the evaporator 300 to absorb a large amount of heat, thereby evaporating into a gaseous refrigerant. This gaseous refrigerant is the third refrigerant 903.

It is worth mentioning that when the refrigerant 905 of the fifth state in which the gas and the liquid coexist has a higher liquid ratio, the heat of the refrigerant 905 of the fifth state flowing through the evaporator 300 is larger, which also represents The air conditioning system 20 has better performance. Further, as shown in "Fig. 3", it is known that the refrigerant 905 of the fifth state of the higher liquid ratio is obtained (i.e., the label 905 of "Fig. 3" is closer to the a region), and the temperature of the refrigerant 904 of the fourth state is obtained. It has to be lowered. That is, the lower the temperature of the refrigerant 904 of the fourth state, the higher the liquid proportion of the refrigerant 905 of the fifth state. The higher the liquid proportion of the fifth refrigerant 905, the better the performance of the air conditioning system 20. Therefore, the degree of subcooling of the so-called air conditioning system 20 refers to the temperature of the refrigerant 904 flowing into the fourth state of the expansion valve 200. The lower the temperature of the refrigerant 904 of the fourth state, the higher the degree of subcooling of the air conditioning system 20.

Therefore, compared with the conventional air conditioning apparatus, since the supercooling degree adjusting device 10 of the working fluid is not provided, the refrigerant 901 of the first state directly flows into the expansion valve 200. Therefore, the degree of subcooling of the air conditioning system 20 of the present embodiment is higher than that of the conventional air conditioning system, and the system efficiency is also better.

In addition, the second state of the refrigerant 902 and the third state of the refrigerant 903 in the chamber 120 exchange heat in the chamber 120, and then flow out from the chamber outlet 124 and the second outlet 134, respectively. Further, the second refrigerant in the liquid state in the chamber 120 and the refrigerant 903 in the third state in which the liquid state is not evaporated during the evaporation process are left at the bottom of the chamber 120 by the specific gravity characteristics of the gas and the liquid. This purpose is to ensure that the refrigerant flowing into the compressor 400 is in a gaseous state to avoid damage to the compressor 400. Therefore, the subcooling degree adjusting device 10 of the working fluid of the present proposal also has the function of a conventional gas-liquid separator. Moreover, the subcooling degree adjusting device 10 of the working fluid of the present invention can store the refrigerant flowing out of the condenser 500, and thus can have the function of a conventional liquid storage cartridge. The subcooling degree adjusting device 10 of the working fluid can replace the gas-liquid separator and the liquid storage tank of the conventional air conditioning device, that is, the supercooling degree adjusting device 10 of the working fluid combines the gas-liquid separator with the liquid storage tube. And for one. Therefore, the subcooling degree adjusting device 10 of the working fluid can reduce the overall volume of the air conditioning system 20 of the present proposal.

Then, when the refrigerant 902 of the second state and the refrigerant 903 of the third state flow out from the chamber outlet 124 and the second outlet 134, respectively, they are gathered together to form a sixth state of refrigerant 906. The refrigerant 906 of the sixth state is a low-pressure gaseous refrigerant, and its temperature is higher than that of the refrigerant 903 of the third state which is also a low-pressure gas state (caused by the heat of the refrigerant 901 of the first state due to heat exchange). The refrigerant 906 of the sixth state flows into the compressor 400 from the compressor inlet 410, and is compressed into a seventh state of refrigerant 907 by the influence of the compressor 400. The refrigerant 907 of the seventh state is a high-pressure high-temperature gaseous refrigerant.

Further, when the compressor 400 is in operation, the refrigerant 907 of the seventh state is generally discharged from the compressor outlet 420 with a small amount of lubricating oil 908. When the refrigerant 907 of the seventh state in which the lubricating oil 908 is mixed flows through the oil separator 600 between the compressor 400 and the condenser 500, the oil separator 600 separates the lubricating oil 908 to make the seventh state. The refrigerant 907 continues to flow to the condenser 500. The refrigerant 907 of the seventh state flows into the condenser 500 through the condenser inlet 510, and is then condensed into a high-pressure liquid refrigerant by the influence of the condenser 500. This high-pressure liquid refrigerant is the refrigerant 901 of the first state mentioned above.

In addition, the lubricating oil 908 separated by the oil separator 600 can flow into the second valve 160 via the second valve inlet 162 and out of the second valve outlet 164 to flow to the third inlet 142. The second valve 160 can adjust the size of its second valve inlet 162 to control the amount of lubricating oil 908 flowing into the third flow tube 140. The lubricating oil 908 has a high temperature gaseous state. When the lubricating oil 908 flows into the third flow tube 140, it can be heated with the refrigerant 901 of the first state, the refrigerant 902 of the second state, and the refrigerant 903 of the third state. exchange. The lubricating oil 908 flowing into the third flow tube 140 flows out through the third outlet 144 into a lubricating oil 909 after performing heat exchange. The temperature of the lubricating oil 909 is lower than that of the lubricating oil 908 (the heat is absorbed by the heat exchange). After the lubricating oil 909 flows out of the supercooling degree adjusting device 10 of the working fluid, the sixth state refrigerant 906 is mixed and flows back into the compressor 400 for recycling. The lubricating oil 908 is used to exchange heat between the refrigerant 901 in the first state, the refrigerant 902 in the second state, and the refrigerant 903 in the third state. When the temperature of the refrigerant 904 of the fourth state is too low, the lubricating oil 908 can raise the temperature of the refrigerant 904 of the fourth state. In addition, the lubricating oil 908 can be used to increase the temperature of the refrigerant 906 in the sixth state, and to prevent the temperature of the refrigerant 906 in the sixth state from being too low to damage the compressor 400.

Please refer to FIG. 4, which is a schematic structural view of an air conditioning system according to another embodiment of the present proposal. The air conditioning system 20 of the present embodiment further includes a controller 700 electrically connected to the first valve 150 and the second valve 160. The controller 700 is configured to control the flow rate of the first valve inlet 152 of the first valve 150 and the second valve inlet 162 of the second valve 160. In addition, the air conditioning system 20 further includes a first temperature sensor 710 and a second temperature sensor 720. The first temperature sensor 710 is disposed at the evaporator 300 of the air conditioning system 20, and the first temperature sensor 710 is configured to measure the temperature of the cold air discharged by the air conditioning system 20 via the evaporator 300. The second temperature sensor 720 is disposed on the flow tube between the supercooling degree adjusting device 10 of the working fluid and the compressor 400 for detecting the temperature of the sixth state refrigerant 906. The controller 700 is electrically connected to the first temperature sensor 710 and the second temperature sensor 720 respectively. The first temperature sensor 710 and the second temperature sensor 720 can feedback the measured temperature signal to the controller 700. The controller 700 can appropriately control the flow rate of the first valve inlet 152 of the first valve 150 and the second valve inlet 162 of the second valve 160 for the current temperature environmental conditions to maintain the air conditioning system 20 in optimal operating efficiency. State.

For example, when the first temperature sensor 710 measures that the temperature of the cold air discharged by the air conditioning system 20 is higher than the desired temperature, it represents that the refrigerant flowing through the evaporator 300 is insufficient. At this time, the first valve inlet 152 of the first valve 150 can be controlled to be reduced, so that the flow rate of the refrigerant flowing through the first valve 150 is lowered to increase the flow rate of the refrigerant flowing through the evaporator 300. When the second temperature sensor 720 measures the temperature of the sixth state of the refrigerant 906 is too low, the compressor 400 may be damaged by the low refrigerant at this time. Therefore, the amount by which the controller 700 controls the second valve inlet 162 of the second valve 160 to increase, so that the high-temperature lubricating oil 908 flows into the working fluid supercooling degree adjusting device 10 increases. The high-temperature lubricating oil 908 can increase the temperature of the refrigerant 906 of the sixth state by heat exchange, thereby achieving the effect of protecting the compressor 400. Therefore, the air conditioning system 20 of the present embodiment utilizes the first temperature sensor 710 and the second temperature sensor 720 to monitor the system temperature to return the temperature data to the controller 700. The controller 700 receives the temperature data and adjusts the flow rates of the first valve 150 and the second valve 160 to enable the air conditioning system 20 to maintain stable system benefits over temperature changes in various states.

According to the air conditioning system disclosed in the above embodiment, the refrigerant flow in the first state from the condenser to the expansion valve passes through the coldness adjusting device. Therefore, the refrigerant of the first state is exchanged with the refrigerant of the second state and the third state in the supercooling degree adjusting device to reduce the temperature of the refrigerant in the first state. Since the temperature of the refrigerant in the first state is lowered, the degree of subcooling of the air conditioning system is also improved. It is such a subcooling regulating device that can improve the system efficiency of the air conditioning system.

In addition, the supercooling degree adjusting device of the working fluid of the embodiment may have the functions of a conventional gas-liquid separator and a conventional liquid accumulator. The subcooling degree adjusting device of the working fluid can replace the gas-liquid separator and the accumulator of the conventional air conditioning apparatus, and therefore the overall volume of the air conditioning system of the present embodiment is also reduced.

Moreover, since the controller of the embodiment can control the size of the valve ports of the first valve and the second valve, the flow rate of the refrigerant flowing through the first valve and the lubricating oil flowing through the second valve is controlled. Therefore, under the setting of the temperature sensor, the controller appropriately controls the size of the valve ports of the first valve and the second valve according to the system temperature condition, so that the air conditioning system is maintained in an optimal working efficiency state.

While the present invention has been disclosed in the foregoing preferred embodiments, it is not intended to limit the present invention. Any skilled person skilled in the art can make some changes and refinements without departing from the spirit and scope of the present proposal. The scope of patent protection of the proposal shall be subject to the definition of the scope of the patent application attached to this specification.

10. . . Working fluid subcooling regulator

20. . . Air Conditioning System

100. . . Body

110. . . First flow tube

112. . . First entrance

114. . . First exit

120. . . Chamber

122. . . Chamber entrance

124. . . Chamber outlet

130. . . Second flow tube

132. . . Second entrance

134. . . Second exit

140. . . Third flow tube

142. . . Third entrance

144. . . Third exit

150. . . First valve

152. . . First valve inlet

154. . . First valve outlet

160. . . Second valve

162. . . Second valve inlet

164. . . Second valve outlet

200. . . Expansion valve

210. . . Expansion valve inlet

220. . . Expansion valve outlet

300. . . Evaporator

310. . . Evaporator inlet

320. . . Evaporator outlet

400. . . compressor

410. . . Compressor inlet

420. . . Compressor outlet

500. . . Condenser

510. . . Condenser inlet

520. . . Condenser outlet

600. . . Oil separator

700. . . Controller

710. . . First temperature sensor

720. . . Second temperature sensor

901. . . The same state of refrigerant

902. . . The second form of refrigerant

903. . . The third form of refrigerant

904. . . The fourth form of refrigerant

905. . . The fifth form of refrigerant

906. . . The sixth form of refrigerant

907. . . The seventh form of refrigerant

908. . . Lubricating oil

909. . . Lubricating oil

Fig. 1 is a schematic structural view of an air conditioning system according to an embodiment of the present proposal.

Fig. 2 is an enlarged schematic view showing the subcooling degree adjusting device of the working fluid according to Fig. 1.

Fig. 3 is a schematic diagram showing the state change of the refrigerant in the air conditioning system according to Fig. 1.

Figure 4 is a schematic view showing the structure of an air conditioning system according to another embodiment of the present proposal.

10. . . Working fluid subcooling regulator

20. . . Air Conditioning System

100. . . Body

110. . . First flow tube

112. . . First entrance

114. . . First exit

120. . . Chamber

122. . . Chamber entrance

124. . . Chamber outlet

130. . . Second flow tube

132. . . Second entrance

134. . . Second exit

140. . . Third flow tube

142. . . Third entrance

144. . . Third exit

150. . . First valve

152. . . First valve inlet

154. . . First valve outlet

160. . . Second valve

162. . . Second valve inlet

164. . . Second valve outlet

200. . . Expansion valve

210. . . Expansion valve inlet

220. . . Expansion valve outlet

300. . . Evaporator

310. . . Evaporator inlet

320. . . Evaporator outlet

400. . . compressor

410. . . Compressor inlet

420. . . Compressor outlet

500. . . Condenser

510. . . Condenser inlet

520. . . Condenser outlet

600. . . Oil separator

901. . . The same state of refrigerant

902. . . The second form of refrigerant

903. . . The third form of refrigerant

904. . . The fourth form of refrigerant

905. . . The fifth form of refrigerant

906. . . The sixth form of refrigerant

907. . . The seventh form of refrigerant

908. . . Lubricating oil

909. . . Lubricating oil

Claims (21)

A subcooling regulating device for adjusting a refrigerant in a cycle state, the refrigerant changing between a first state, a second state and a third state, the first The refrigerant in the second state is in a liquid state, and the refrigerant in the second state is liquid and the pressure and temperature are lower than the refrigerant in the first state. The refrigerant in the third state is in a gaseous state and the pressure and temperature are both The refrigerant having a subcooling degree lower than the first state, the supercooling degree adjusting device of the working fluid comprises: a body having a chamber having a chamber inlet and a chamber outlet; a first flow tube, setting In the chamber, the first flow tube has a first inlet and a first outlet outside the machine body; and a second flow tube is disposed in the chamber, the second flow tube has a body outside the machine body. a second inlet and a second outlet; wherein the refrigerant in the first state, the refrigerant in the second state, and the refrigerant in the third state are respectively via the first inlet, the chamber inlet, and the The second inlet enters the chamber and is heat exchanged in the chamber Respectively from the first outlet, the chamber outlet and the second outlet from the chamber. The subcooling degree adjusting device of the working fluid according to Item 1, further comprising a first valve disposed outside the machine, the first valve communicating with the chamber inlet. The subcooling degree adjusting device of the working fluid according to Item 1, wherein the first flow tube covers the second flow tube. The subcooling degree adjusting device of the working fluid according to Item 2 of the present invention, further comprising a third flow tube disposed in the chamber, the third flow tube having a body outside the machine body a third inlet and a third outlet, the first quality enters the chamber through the third inlet, the temperature of the fluid is greater than the refrigerant in the first state, and the liquid is in the same state, the second state And after the refrigerant of the third state is subjected to heat exchange in the chamber, the third outlet exits the chamber. The subcooling degree adjusting device for the working fluid according to Item 4 of the claim further includes a second valve disposed outside the machine body, the second valve communicating with the third inlet. The subcooling degree adjusting device of the working fluid according to Item 4, wherein the third flow tube surrounds the first flow tube and the second flow tube in the chamber. An air conditioning system in which a refrigerant circulates, the air conditioning system comprising: a subcooling degree adjusting device for a working fluid, comprising: a body having a chamber having a chamber inlet and a chamber An outlet tube is disposed in the chamber, the first flow tube has a first inlet and a first outlet outside the machine body; a second flow tube is disposed in the chamber, the second flow tube Having a second inlet and a second outlet outside the machine body; and a first valve disposed outside the machine body, the first valve communicating with the chamber inlet; an expansion valve having an expansion valve inlet and an expansion a valve outlet, the expansion valve inlet respectively communicating with the first valve and the first outlet; an evaporator having an evaporator inlet and an evaporator outlet, the evaporator inlet communicating with the expansion valve outlet, the evaporator outlet communicating with the a second inlet; a compressor having a compressor inlet and a compressor outlet, the compressor The inlet is respectively connected to the second outlet and the chamber outlet; and a condenser having a condenser inlet and a condenser outlet, the condenser inlet communicating with the compressor outlet, the condenser outlet communicating with the first inlet; The refrigerant entering the chamber from the first inlet, the refrigerant entering the chamber from the second inlet, and the refrigerant entering the chamber from the inlet of the chamber exchange heat in the chamber. The air conditioning system of claim 7, wherein the first flow tube of the supercooling degree adjusting device of the working fluid wraps the second flow tube. The air conditioning system of claim 7, further comprising a controller electrically connected to the first valve to adjust the flow rate of the first valve. The air conditioning system of claim 9, further comprising a first temperature sensor electrically coupled to the controller, the first temperature sensor being adjacent to the evaporator, the controller receiving the first temperature sense The detector feeds back a temperature signal to adjust the flow rate of the first valve. The air conditioning system of claim 10, further comprising a second temperature sensor electrically coupled to the controller, the second temperature sensor being disposed in the supercooling degree adjusting device of the working fluid and the compressing Between the machines, the controller receives a temperature signal fed back by the second temperature sensor to adjust the flow rate of the first valve. The air conditioning system of claim 7, wherein the supercooling degree adjusting device of the working fluid further comprises a third flow tube disposed in the chamber, the third flow tube having a third body outside the machine body An inlet and a third outlet, the third outlet is connected to the compressor inlet, and the first quality enters the chamber through the third inlet, and the liquid exchanges heat with the refrigerant in the chamber. The air conditioning system of claim 12, wherein the third flow tube surrounds the first flow tube and the second flow tube in the chamber. The air conditioning system of claim 12, wherein the supercooling degree adjusting device of the working fluid further comprises a second valve disposed outside the machine body, the second valve communicating with the third inlet. The air conditioning system of claim 14, further comprising an oil separator, the oil separator being respectively connected to the second valve, the condenser inlet and the compressor outlet. The air conditioning system of claim 14, further comprising a controller electrically connected to the second valve to adjust the flow rate of the second valve. The air conditioning system of claim 16, further comprising a first temperature sensor electrically coupled to the controller, the first temperature sensor being adjacent to the evaporator, the controller receiving the first temperature sense The detector feeds back a temperature signal to adjust the flow rate of the second valve. The air conditioning system of claim 17, further comprising a second temperature sensor electrically coupled to the controller, the second temperature sensor being disposed in the supercooling degree adjusting device of the working fluid and the compressing Between the machines, the controller receives a temperature signal fed back by the second temperature sensor to adjust the flow rate of the second valve. The air conditioning system of claim 14, further comprising a controller electrically connected to the first valve and the second valve to adjust a flow rate of the first valve and the second valve. The air conditioning system of claim 19, further comprising a first temperature sensor electrically coupled to the controller, the first temperature sensor being adjacent to the evaporator, the controller receiving the first temperature sense The detector feeds back a temperature signal to adjust the first The flow rate of the valve and the second valve. The air conditioning system of claim 20, further comprising a second temperature sensor electrically coupled to the controller, the second temperature sensor being disposed in the supercooling degree adjusting device of the working fluid and the compressing The controller receives a temperature signal fed back by the second temperature sensor to adjust the flow rate of the first valve and the second valve.