A condensing device and an air conditioning system having the same.

Abstract

The present invention provides a condensing device and an air conditioning system having the same, wherein the condensing device comprises a first heat exchanger and a second heat exchanger, wherein the first heat exchanger has a first inlet for allowing refrigerant to enter and a first outlet for allowing refrigerant to flow out after cooling and heat exchange, and the second heat exchanger has a second inlet for allowing refrigerant to enter and a second outlet for allowing refrigerant to flow out after cooling and heat exchange; the supercooling section of the second heat exchanger has a third inlet that can be connected to the first outlet, and the third inlet and the first outlet are connected through an intermediate pipe, so that the fluid flows from the first outlet, the intermediate pipe and the third inlet to the second heat exchanger in sequence, and the diameter of the first heat exchange tube of the first heat exchanger is greater than the diameter of the second heat exchange tube of the second heat exchanger. The present invention increases the flow rate of the refrigerant in the supercooling section heat exchange tube, quickly takes away the liquid film refrigerant on the wall, effectively strengthens the effect of condensation heat exchange, increases the heat exchange amount, and reduces the amount of refrigerant charged in the condenser.

Description

Technical Field

[0001] The present invention belongs to the technical field of air conditioning, and in particular relates to a condensing device and an air conditioning system having the same. Background Art

[0002] As one of the important components of the refrigeration system, the heat exchange performance of the condenser has a crucial impact on the performance of the system. Generally, the condenser can be divided into the gas phase zone, the two-phase zone and the supercooling zone according to the state of the refrigerant. In the gas phase zone, the gas phase refrigerant under high temperature and high pressure is gradually cooled by the low-temperature air of forced convection in the condenser heat exchange tube; in the two-phase zone, the refrigerant state is a gas-liquid two-phase state. As the two-phase refrigerant gradually condenses into a liquid refrigerant, the thickness of the condensate on the inner wall of the heat exchange tube gradually increases, which hinders the contact between the steam and the wall. It is the main thermal resistance of condensation heat exchange, and the heat exchange effect of the condensate thickness phase change is gradually reduced; when the gas phase refrigerant is completely converted into a liquid phase refrigerant and flows into the supercooling zone, the heat exchange situation at this time changes from condensation phase change heat exchange to single-phase convection heat exchange. Under the same heat exchange conditions, the single-phase convection heat exchange capacity is worse than the condensation phase change heat exchange capacity. Due to the decrease in the heat exchange effect of the refrigerant in the supercooling section of the condenser and the greater density of the liquid phase refrigerant than the gas phase, the refrigerant filling amount at the end of the condenser is large and the heat exchange effect is poor. Therefore, using a condenser without enhanced heat exchange in a dual condensing temperature system or a single condensing temperature system results in low system energy efficiency and a large amount of refrigerant charged in the system.

[0003] Since the heat exchange effect of the refrigerant in the prior art decreases in the subcooling section of the condenser and the density of the liquid phase refrigerant is greater than that of the gas phase, the refrigerant filling amount in the last section of the condenser is large and the heat exchange effect is poor, resulting in technical problems such as low system energy efficiency in a double condensing temperature system or a single condensing temperature system and a large refrigerant filling amount in the system. Therefore, the present invention studies and designs a condensing device and an air-conditioning system having the same. Summary of the invention

[0004] Therefore, the technical problem to be solved by the present invention is to overcome the defect of poor heat exchange effect in the subcooling section of the condenser in the prior art due to increased thermal resistance of the inner wall of the heat exchange tube, thereby providing a condensing device and an air-conditioning system having the same.

[0005] The present invention provides a condensing device, comprising:

[0006] A first heat exchanger and a second heat exchanger, wherein the first heat exchanger has a first inlet for allowing the refrigerant to enter and a first outlet for allowing the refrigerant to flow out after cooling and heat exchange, and the second heat exchanger has a second inlet for allowing the refrigerant to enter and a second outlet for allowing the refrigerant to flow out after cooling and heat exchange;

[0007] The subcooling section of the second heat exchanger is provided with a third inlet that can be communicated with the first outlet, and the third inlet and the first outlet are connected through an intermediate pipe, so that the fluid flows from the first outlet, the intermediate pipe and the third inlet to the second heat exchanger in sequence, and the diameter of the first heat exchange tube of the first heat exchanger is larger than the diameter of the second heat exchange tube of the second heat exchanger.

[0008] Preferably,

[0009] The subcooling section of the second heat exchanger is a partial section of the second heat exchange tube relatively close to the second outlet; and / or a pressure regulating device is also provided on the intermediate tube.

[0010] Preferably,

[0011] The first heat exchanger is a finned heat exchanger, the first heat exchange tube is a serpentine bent tube, and a plurality of heat exchange fins are arranged on the first heat exchange tube; and / or the second heat exchanger is a microchannel heat exchanger, the second heat exchange tube includes a heat exchange flat tube and a header, the supercooling section includes at least one of the heat exchange flat tubes close to the second outlet, the intermediate tube is connected to the header and communicates with the heat exchange flat tubes in the supercooling section, and the cross-sectional area of ​​the first heat exchange tube is greater than the cross-sectional area of ​​the heat exchange flat tubes.

[0012] Preferably,

[0013] The first heat exchanger is a fin heat exchanger, the second heat exchanger is also a fin heat exchanger, and the cross-sectional area of ​​the first heat exchange tube is larger than the cross-sectional area of ​​the second heat exchange tube; or, the first heat exchanger is a microchannel heat exchanger, the second heat exchanger is also a microchannel heat exchanger, and the cross-sectional area of ​​the heat exchange flat tubes of the first heat exchanger is larger than the cross-sectional area of ​​the heat exchange flat tubes of the second heat exchanger.

[0014] Preferably,

[0015] It also includes an evaporative cooling device, which can spray water or spray mist to cool the first heat exchanger and / or the second heat exchanger.

[0016] Preferably,

[0017] The evaporative cooling device comprises a spray device, and the spray device is located above the first heat exchanger so as to spray water onto the first heat exchanger.

[0018] Preferably,

[0019] The evaporative cooling device also includes a water pump and a water receiving pan. The water pump is connected to the spray device through a first water pipe, and the water receiving pan is connected to the water pump through a second water pipe. The water receiving pan is located at the lower end of the first heat exchanger to receive water falling from the first heat exchanger.

[0020] Preferably,

[0021] The evaporative cooling device further comprises a spray device, which is connected to the water pump via a third water pipe, and the spray device can spray the second heat exchanger.

[0022] Preferably,

[0023] The first heat exchanger and the second heat exchanger are arranged up and down, the first heat exchanger is located above the second heat exchanger, the water receiving tray is arranged below the first heat exchanger and above the second heat exchanger, and the spray device is arranged above the second heat exchanger and below the water receiving tray.

[0024] The present invention also provides an air conditioning system, which comprises a compression device, a throttling device, an evaporator and the condensing device described in any of the preceding items.

[0025] Preferably,

[0026] The compression device includes a low-pressure compressor and a high-pressure compressor, the exhaust port of the low-pressure compressor is connected to the second inlet of the second heat exchanger, the exhaust port of the high-pressure compressor is connected to the first inlet of the first heat exchanger, the second outlet of the second heat exchanger is connected to one end of the evaporator after passing through the throttling device, and the other end of the evaporator is divided into two paths, which are respectively connected to the intake port of the low-pressure compressor and the intake port of the high-pressure compressor.

[0027] Preferably,

[0028] The compression device includes a single compressor, the exhaust port of the single compressor is divided into two paths, and is respectively connected to the first inlet of the first heat exchanger and the second inlet of the second heat exchanger, the second outlet of the second heat exchanger is connected to one end of the evaporator after passing through the throttling device, and the other end of the evaporator is connected to the suction port of the single compressor.

[0029] A condensing device and an air conditioning system having the same provided by the present invention have the following beneficial effects:

[0030] The present invention arranges two heat exchangers with heat exchange tubes of different diameters, and the outlet of the heat exchanger with a larger diameter is connected to the subcooling section of the heat exchanger with a smaller diameter. The refrigerant is mixed in the subcooling section and then discharged together. Such a structure makes the diameter of the heat exchange tube suddenly smaller, thereby effectively increasing the flow rate of the refrigerant in the heat exchange tube of the subcooling section, reducing the residence time in the tube, quickly taking away the liquid film refrigerant on the wall, and reducing the thickness of the thick condensate on the inner wall of the heat exchange tube. Therefore, the effect of condensation heat exchange is effectively enhanced, the heat exchange amount is increased, and more refrigerant can be discharged from the heat exchange tube of the subcooling section faster, thereby effectively reducing the refrigerant charge in the condenser and further improving the heat exchange capacity of the subcooling section. BRIEF DESCRIPTION OF THE DRAWINGS

[0031] Figure 1 is a schematic structural diagram of a condensing device of the present invention;

[0032] Figure 2 1 is a schematic diagram of the structure of the air conditioning system embodiment 1 (dual condensing temperature system) of the present invention;

[0033] Figure 3 It is a structural schematic diagram of the second embodiment of the air conditioning system of the present invention (single condensation temperature system).

[0034] The reference numerals in the figure are as follows:

[0035] 1. First heat exchanger; 11. First inlet; 12. First outlet; 13. First heat exchange tube; 14. Heat exchange fin; 2. Second heat exchanger; 21. Second inlet; 22. Second outlet; 23. Third inlet; 24. Second heat exchange tube; 241. Heat exchange flat tube; 242. Collecting pipe; 3. Intermediate pipe; 4. Pressure regulating device; 5. Spraying device; 6. Water pump; 7. Water receiving tray; 8. Spraying device; 91. Compression device; 911. Low-pressure compressor; 912. High-pressure compressor; 913. Single compressor; 92. Throttling device; 93. Evaporator; 101. First water pipe; 102. Second water pipe; 103. Third water pipe. DETAILED DESCRIPTION

[0036] like Figure 1 As shown, the present invention provides a condensing device, which includes:

[0037] A first heat exchanger 1 and a second heat exchanger 2, wherein the first heat exchanger 1 has a first inlet 11 for allowing the refrigerant to enter and a first outlet 12 for allowing the refrigerant to flow out after cooling and heat exchange, and the second heat exchanger 2 has a second inlet 21 for allowing the refrigerant to enter and a second outlet 22 for allowing the refrigerant to flow out after cooling and heat exchange;

[0038] The subcooling section of the second heat exchanger 2 is provided with a third inlet 23 which can be communicated with the first outlet 12, and the third inlet 23 and the first outlet 12 are connected through an intermediate pipe 3, so that the fluid flows from the first outlet 12, the intermediate pipe 3 and the third inlet 23 to the second heat exchanger 2 in sequence, and the diameter of the first heat exchange tube 13 of the first heat exchanger 1 is larger than the diameter of the second heat exchange tube 24 of the second heat exchanger 2.

[0039] The present invention arranges two heat exchangers with heat exchange tubes of different diameters, and the outlet of the heat exchanger with a larger diameter is connected to the subcooling section of the heat exchanger with a smaller diameter. The refrigerant is mixed in the subcooling section and then discharged together. Such a structure makes the diameter of the heat exchange tube suddenly smaller, thereby effectively increasing the flow rate of the refrigerant in the heat exchange tube of the subcooling section, reducing the residence time in the tube, quickly taking away the liquid film refrigerant on the wall, and reducing the thickness of the thick condensate on the inner wall of the heat exchange tube. Therefore, the effect of condensation heat exchange is effectively enhanced, the heat exchange amount is increased, and more refrigerant can be discharged from the heat exchange tube of the subcooling section faster, thereby effectively reducing the refrigerant charge in the condenser and further improving the heat exchange capacity of the subcooling section.

[0040] The present invention 1. By changing the pipe diameters of each zone of the heat exchanger, the refrigerant flow rate in the liquid phase zone and / or the gas phase zone is changed, thereby enhancing the heat exchange effect of the condenser.

[0041] 2. Reduce the pipe diameter in the subcooling zone to reduce the amount of refrigerant charged in the condenser.

[0042] 3. Add evaporative cooling device, absorb heat by evaporating water droplets on the heat exchanger surface, or reduce the inlet air temperature by spraying, which strengthens the heat exchange effect of the condenser and improves the energy efficiency of the dual condensation temperature system or the single condensation temperature system.

[0043] Preferably,

[0044] The subcooling section of the second heat exchanger 2 is a portion of the second heat exchange tube 24 relatively close to the second outlet 22 (relative to the second inlet 21); and / or the intermediate tube 3 is also provided with a pressure regulating device 4. This is the preferred position of the subcooling section of the second heat exchanger of the present invention. Figure 1It is located at the bottom of the second heat exchanger (because its second outlet is at the bottom to discharge refrigerant). Since the refrigerant of the second heat exchanger flows in from the second inlet at the top and exchanges heat in the second heat exchanger, it becomes mostly liquid refrigerant when it reaches the bottom of the second heat exchanger. At this time, since the output pipeline of the first heat exchanger is connected, the refrigerant flow rate can be increased, and the flow rate can be increased, so that the refrigerant can be quickly discharged from the second heat exchanger, so that the liquid film on the inner wall of the tube is effectively reduced, and the heat exchange efficiency of the refrigerant in the supercooling section is effectively improved; the pressure of the refrigerant coming out of the first heat exchanger can be adjusted by the pressure regulating device, so that it can normally enter the supercooling of the second heat exchanger.

[0045] Preferably,

[0046] The first heat exchanger 1 is a finned heat exchanger, the first heat exchange tube 13 is a serpentine bent tube, and a plurality of heat exchange fins 14 are arranged on the first heat exchange tube 13; and / or, the second heat exchanger 2 is a microchannel heat exchanger, the second heat exchange tube 24 includes a heat exchange flat tube 241 and a header 242, the supercooling section includes at least one heat exchange flat tube 241 close to the second outlet 22, the intermediate tube 3 is connected to the header 242 and communicates with the heat exchange flat tube 241 in the supercooling section, and the cross-sectional area of ​​the first heat exchange tube 13 is greater than the cross-sectional area of ​​the heat exchange flat tube 241. This is the structural form of the first preferred embodiment of the present invention, that is, the first heat exchanger is a fin heat exchanger and the second heat exchanger is a microchannel heat exchanger. After heat exchange in the fin heat exchanger with a large tube diameter, the refrigerant flows into the microchannel of the microchannel heat exchanger with a smaller tube diameter (enters the flat tube), and the flow cross-sectional area is reduced, so that the flow rate is increased, the effect of refrigerant discharge is enhanced, and the thickness of the liquid film on the inner wall of the tube is reduced, thereby effectively improving the heat exchange effect.

[0047] Preferably,

[0048] The first heat exchanger 1 is a fin heat exchanger, the second heat exchanger 2 is also a fin heat exchanger, and the cross-sectional area of ​​the first heat exchange tube 13 is greater than the cross-sectional area of ​​the second heat exchange tube 24; or, the first heat exchanger 1 is a microchannel heat exchanger, the second heat exchanger 2 is also a microchannel heat exchanger, and the cross-sectional area of ​​the heat exchange flat tubes of the first heat exchanger 1 is greater than the cross-sectional area of ​​the heat exchange flat tubes of the second heat exchanger 2. This is the preferred structural form of the second embodiment of the present invention and the preferred structural form of the third embodiment, that is, the first heat exchanger and the second heat exchanger are both fin heat exchanger structures, and the first heat exchanger and the second heat exchanger are both microchannel heat exchanger structures, that is, by setting the tube diameters of the two fin heat exchangers to be different, the effect of reducing the flow channel, increasing the flow rate, and improving the heat exchange capacity can be achieved; and by setting the cross-sectional areas of the flat tubes of the two microchannel heat exchangers to be different, the effect of reducing the flow channel, increasing the flow rate, and improving the heat exchange capacity can be achieved.

[0049] Preferably,

[0050] It also includes an evaporative cooling device, which can spray water or spray to cool the first heat exchanger 1 and / or the second heat exchanger 2. The present invention enhances the heat exchange effect of the condenser by adding an evaporative cooling device, absorbing heat by evaporation of water droplets on the surface of the heat exchanger, or reducing the inlet air temperature by spraying. The water pump circulation system is set to collect and fully utilize unevaporated or unused water, thereby producing a better energy-saving effect. Especially in high temperature and low humidity environments.

[0051] Preferably,

[0052] The evaporative cooling device includes a spray device 5, which is located above the first heat exchanger 1 and can spray water onto the first heat exchanger 1. The spray device can enhance the cooling effect of the first heat exchanger and strengthen the heat exchange effect of the condenser.

[0053] Preferably,

[0054] The evaporative cooling device further includes a water pump 6 and a water receiving pan 7. The water pump 6 is connected to the spray device 5 through a first water pipe 101. The water receiving pan 7 is connected to the water pump 6 through a second water pipe 102. The water receiving pan 7 is located at the lower end of the first heat exchanger 1 to receive water falling from the first heat exchanger 1. The present invention can collect water dripping from the condenser through the water receiving pan, and circulate it to the top of the first heat exchanger through the water pump to further cool the first heat exchanger. The water that has not evaporated or been used is collected and fully utilized through the water pump circulation system, thereby producing a better energy-saving effect.

[0055] Preferably,

[0056] The evaporative cooling device further comprises a spray device 8, which is connected to the water pump 6 via a third water pipe 103, and can spray the second heat exchanger 2. The spray device can enhance the cooling effect of the second heat exchanger and strengthen the heat exchange effect of the condenser.

[0057] Preferably,

[0058] The first heat exchanger 1 and the second heat exchanger 2 are arranged up and down, the first heat exchanger 1 is located above the second heat exchanger 2, the water receiving tray 7 is arranged below the first heat exchanger 1 and above the second heat exchanger 2, and the spray device 8 is arranged above the second heat exchanger 2 and below the water receiving tray 7. This is the preferred arrangement of the two heat exchangers of the present invention, so that the first heat exchanger, the water receiving tray, the spray device, and the second heat exchanger are arranged from top to bottom in sequence, and the water received by the water receiving tray can be pumped to the spray device or the spray device through a water pump, thereby realizing function sharing and multi-use, so that the two heat exchangers can be enhanced in heat exchange and cooling functions at the same time.

[0059] like Figure 2-3 The present invention also provides an air conditioning system, which includes a compression device 91, a throttling device 92, an evaporator 93 and a condensing device as described in any of the preceding items.

[0060] 1. The present invention uses two or more heat exchangers with different tube diameters, which are connected in parallel flow paths, so that the gas-liquid two-phase refrigerant is brought together and enters the heat exchanger with a smaller tube diameter, thereby changing the flow rate of the refrigerant in the condenser tube, enhancing the condensation heat exchange effect, and reducing the refrigerant charge in the condenser. (Since the gas-liquid two-phase refrigerant is brought together and enters the heat exchanger with a smaller tube diameter, the reduction in the flow cross-sectional area leads to an increase in the refrigerant flow rate, thereby enhancing the condensation heat exchange effect and reducing the refrigerant charge in the condenser.)

[0061] 2. The present invention is to use two or more heat exchangers with different pipe diameters in a double condensing temperature system or a single condensing temperature system in a parallel flow path to improve system performance and reduce the amount of refrigerant charged in the system. (The flow rate of the refrigerant is increased and the heat exchange effect is enhanced)

[0062] like Figure 2 , preferably,

[0063] The compression device 91 includes a low-pressure compressor 911 and a high-pressure compressor 912. The exhaust port of the low-pressure compressor 911 is connected to the second inlet 21 of the second heat exchanger 2, and the exhaust port of the high-pressure compressor 912 is connected to the first inlet 11 of the first heat exchanger 1. The second outlet 22 of the second heat exchanger 2 is connected to one end of the evaporator 93 after passing through the throttling device 92. The other end of the evaporator 93 is divided into two paths, which are respectively connected to the intake port of the low-pressure compressor 911 and the intake port of the high-pressure compressor 912.

[0064] This is the preferred structural form of embodiment 1 (double condensing temperature system) of the air-conditioning system of the present invention, that is, the high-pressure compressor delivers the compressed high-pressure refrigerant to the first heat exchanger, and the low-pressure compressor delivers the compressed low-pressure refrigerant to the second heat exchanger. Since the pressure of the first heat exchanger is higher than that of the second heat exchanger, the pressure of the refrigerant is adjusted by the pressure regulating device on the intermediate pipe and introduced into the supercooling section of the second heat exchanger to complete the mixing of two refrigerants with different pipe diameters, increase the flow rate, discharge the refrigerant as soon as possible, reduce the liquid film thickness, and improve the heat exchange capacity.

[0065] like Figure 3 , preferably,

[0066] The compression device 91 includes a single compressor 913, the exhaust port of the single compressor 913 is divided into two paths, and is respectively connected to the first inlet 11 of the first heat exchanger 1 and the second inlet 21 of the second heat exchanger 2, the second outlet 22 of the second heat exchanger 2 is connected to one end of the evaporator 93 after passing through the throttling device 92, and the other end of the evaporator 93 is connected to the intake port of the single compressor 913.

[0067] This is the preferred structural form of the second embodiment (single condensing temperature system) of the air-conditioning system of the present invention, that is, the single compressor transports the compressed refrigerant into two paths to the first heat exchanger and the second heat exchanger respectively, the pressure of the first heat exchanger is equal to the pressure of the second heat exchanger, and the refrigerant at the outlet of the first heat exchanger is introduced into the supercooling section of the second heat exchanger to complete the mixing of two refrigerants with different pipe diameters, increase the flow rate, discharge the refrigerant as soon as possible, reduce the liquid film thickness, and improve the heat exchange capacity.

[0068] Figure 1 The condenser is a condenser of two heat exchangers with different tube diameters connected in a parallel flow path. The condenser consists of a microchannel heat exchanger, a fin tube heat exchanger, a spray device, a mist device, a water pump and a water receiving tray. Figure 2 The dual condensation temperature system using the condenser includes a condenser with two heat exchangers of different tube diameters connected in parallel flow, a high-pressure compressor, a low-pressure compressor, an evaporator, a pressure regulating device and a throttling device. The placement position between the microchannel heat exchanger and the fin tube heat exchanger can be based on Figure 1 The spray device corresponds to the fin-tube heat exchanger and is located directly above the fin-tube heat exchanger. The water tray corresponds to the fin-tube heat exchanger and is located directly below the fin-tube heat exchanger. The spray device corresponds to the microchannel heat exchanger and can be located directly above the microchannel heat exchanger or in front of the windward surface of the microchannel heat exchanger.

[0069] The gas-phase refrigerant discharged from the low-pressure compressor flows into the microchannel heat exchanger. The gas-phase refrigerant is cooled into a gas-liquid two-phase state by forced convection air whose temperature is lower than the refrigerant temperature in the microchannel heat exchange flat tubes after n processes, and the proportion of liquid refrigerant gradually increases. The gas-phase refrigerant discharged from the high-pressure compressor flows into the fin-tube heat exchanger. The forced convection air absorbs heat when flowing over the fin surface, causing the gas-phase refrigerant in the copper tube to gradually condense into a gas-liquid two-phase refrigerant. The refrigerant at the outlet of the fin-tube heat exchanger is reduced in pressure by the pressure regulating device, and then merges with the refrigerant at the outlet of the nth process of the microchannel heat exchanger, and enters the supercooling section of the microchannel heat exchanger together. The supercooled refrigerant in the microchannel heat exchanger flows through the throttling device and enters the evaporator to absorb heat. Then part of the gas-phase refrigerant enters the low-pressure compressor, and the other part of the gas-phase refrigerant enters the high-pressure compressor, and the refrigerant completes a cycle. Since the diameter of the microchannel heat exchange flat tube is small, the increase in refrigerant flow leads to an increase in the refrigerant flow velocity in the tube, which enhances the heat exchange effect. In addition, the small diameter of the microchannel heat exchange flat tube reduces the refrigerant charge amount.

[0070] Evaporative cooling devices are installed on both heat exchangers to improve refrigeration efficiency. The microchannel heat exchanger is preferably a spray device, which is located in front of the windward surface of the heat exchanger. The water pump sends part of the water in the water receiving tray into the spray device for atomization and spraying. The fine water droplets evaporate directly into water vapor in the air, cooling the air, increasing the temperature difference between the microchannel heat exchanger and the air, and enhancing the heat exchange effect.

[0071] The fin-tube heat exchanger preferably has a spray device, which is located at the top of the fin-tube heat exchanger. The sprayed water will slide down along the fins and the surface of the heat exchanger tube under the action of gravity and form a water film. The water film absorbs the heat of the fin-tube heat exchanger during evaporation, thereby enhancing its heat exchange effect. By controlling the amount of water spraying, the spray water can be completely evaporated on the surface of the heat exchanger. If it fails to evaporate completely, the spray water flows into the water receiving tray under the heat exchanger. The water collected in the water receiving tray is sent to the spray device and the spray device through a water pump. The water used by the evaporative cooling device preferably comes from the condensed water of the indoor evaporator, and can also be tap water or other water sources.

[0072] 1. Furthermore, the microchannel heat exchanger can be replaced with a fin-tube heat exchanger with a small diameter. The liquid refrigerant in the supercooling section of the fin-tube heat exchanger with a larger diameter merges with the liquid refrigerant in the fin-tube heat exchanger with a small diameter and then enters the supercooling section of the fin-tube heat exchanger with a small diameter, thereby increasing the flow rate in the supercooling section of the fin-tube heat exchanger with a small diameter and enhancing the heat exchange effect.

[0073] 2. Further. Figure 3The single condensation temperature system using the condenser includes a condenser, a compressor, an evaporator, a pressure regulating device and a throttling device which are connected in parallel flow paths with the first heat exchanger 1 and the second heat exchanger 2. The exhaust gas of the compressor is divided into two paths, one of which is a gas-phase refrigerant flowing into the second heat exchanger 2. The refrigerant is supercooled in the supercooling section at the bottom of the second heat exchanger 2 and then flows out of the second heat exchanger 2. The refrigerant with a certain degree of supercooling flows through the throttling device to throttle and reduce the pressure, and then enters the evaporator to evaporate and phase change to absorb heat.

[0074] Another path of gas-phase refrigerant flows into the first heat exchanger 1. After the refrigerant at the outlet of the first heat exchanger 1 is reduced in pressure by the pressure regulating device, it merges with the refrigerant at the nth process outlet of the second heat exchanger 2 and enters the supercooling section of the second heat exchanger 2 together. The supercooled refrigerant in the second heat exchanger 2 flows through the throttling device and enters the evaporator to absorb heat. The gas-phase refrigerant is absorbed by the compressor again, completing a refrigerant cycle. Evaporative cooling devices are installed on both heat exchangers to improve the refrigeration efficiency. Furthermore, the first heat exchanger 1 and the second heat exchanger 2 can be a combination of different types of heat exchangers.

[0075] 3. Furthermore, the condenser of the present invention can be composed of two or more heat exchangers with different diameters or types. Different heat exchangers through which the refrigerant flows are selected according to the state of the refrigerant. The refrigerant with lower dryness or full liquid phase is heat exchanged in the heat exchange tube with smaller diameter to improve the heat exchange efficiency and reduce the refrigerant charge.

[0076] The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. Any modifications, equivalent substitutions and improvements made within the spirit and principle of the present invention shall be included in the protection scope of the present invention. The above description is only a preferred embodiment of the present invention. It should be pointed out that for ordinary technicians in this technical field, several improvements and variations can be made without departing from the technical principles of the present invention. These improvements and variations should also be regarded as the protection scope of the present invention.

Claims

1. A condensing device, characterized in that: include: A first heat exchanger (1) and a second heat exchanger (2), wherein the first heat exchanger (1) has a first inlet (11) for allowing a refrigerant to enter and a first outlet (12) for allowing the refrigerant to flow out after cooling and exchanging heat, and the second heat exchanger (2) has a second inlet (21) for allowing the refrigerant to enter and a second outlet (22) for allowing the refrigerant to flow out after cooling and exchanging heat; The second heat exchanger (2) has a third inlet (23) in the subcooling section that can communicate with the first outlet (12); the third inlet (23) and the first outlet (12) are in communication via an intermediate pipe (3), so that the fluid flows from the first outlet (12), the intermediate pipe (3) and the third inlet (23) to the second heat exchanger (2) in sequence; and the diameter of the first heat exchange tube (13) of the first heat exchanger (1) is greater than the diameter of the second heat exchange tube (24) of the second heat exchanger (2).

2. The condensing device according to claim 1, characterized in that: The subcooling section of the second heat exchanger (2) is a partial section of the second heat exchange tube (24) relatively close to the second outlet (22); and / or a pressure regulating device (4) is also provided on the intermediate tube (3).

3. The condensing device according to claim 1, characterized in that: The first heat exchanger (1) is a finned heat exchanger, the first heat exchange tube (13) is a serpentine bent tube, and a plurality of heat exchange fins (14) are provided on the first heat exchange tube (13); and / or the second heat exchanger (2) is a microchannel heat exchanger, the second heat exchange tube (24) comprises a heat exchange flat tube (241) and a header (242), the subcooling section comprises at least one of the heat exchange flat tubes (241) close to the second outlet (22), the intermediate tube (3) is connected to the header (242) and communicates with the heat exchange flat tubes (241) in the subcooling section, and the cross-sectional area of ​​the first heat exchange tube (13) is greater than the cross-sectional area of ​​the heat exchange flat tubes (241).

4. The condensing device according to claim 1, characterized in that: The first heat exchanger (1) is a fin heat exchanger, the second heat exchanger (2) is also a fin heat exchanger, and the cross-sectional area of ​​the first heat exchange tube (13) is greater than the cross-sectional area of ​​the second heat exchange tube (24); or, the first heat exchanger (1) is a microchannel heat exchanger, the second heat exchanger (2) is also a microchannel heat exchanger, and the cross-sectional area of ​​the heat exchange flat tubes of the first heat exchanger (1) is greater than the cross-sectional area of ​​the heat exchange flat tubes of the second heat exchanger (2).

5. The condensing device according to any one of claims 1 to 4, characterized in that: It also comprises an evaporative cooling device, which is capable of spraying water or mist to cool the first heat exchanger (1) and / or the second heat exchanger (2).

6. The condensing device according to claim 5, characterized in that: The evaporative cooling device comprises a spray device (5), and the spray device (5) is located above the first heat exchanger (1) so as to spray water onto the first heat exchanger (1).

7. The condensing device according to claim 6, characterized in that: The evaporative cooling device further comprises a water pump (6) and a water receiving pan (7); the water pump (6) is connected to the spray device (5) via a first water pipe (101); the water receiving pan (7) is connected to the water pump (6) via a second water pipe (102); the water receiving pan (7) is located at the lower end of the first heat exchanger (1) to receive water falling from the first heat exchanger (1).

8. The condensing device according to claim 7, characterized in that: The evaporative cooling device further comprises a spray device (8), wherein the spray device (8) is connected to the water pump (6) via a third water pipe (103), and the spray device (8) is capable of spraying the second heat exchanger (2).

9. The condensing device according to claim 8, characterized in that: The first heat exchanger (1) and the second heat exchanger (2) are arranged vertically, the first heat exchanger (1) is located above the second heat exchanger (2), the water receiving tray (7) is arranged below the first heat exchanger (1) and above the second heat exchanger (2), and the spray device (8) is arranged above the second heat exchanger (2) and below the water receiving tray (7).

10. An air conditioning system, characterized in that: It comprises a compression device (91), a throttling device (92), an evaporator (93) and a condensing device as claimed in any one of claims 1 to 9.

11. The air conditioning system according to claim 10, characterized in that: The compression device (91) comprises a low-pressure compressor (911) and a high-pressure compressor (912); the exhaust port of the low-pressure compressor (911) is connected to the second inlet (21) of the second heat exchanger (2); the exhaust port of the high-pressure compressor (912) is connected to the first inlet (11) of the first heat exchanger (1); the second outlet (22) of the second heat exchanger (2) is connected to one end of the evaporator (93) after passing through the throttling device (92); the other end of the evaporator (93) is divided into two paths, which are respectively connected to the intake port of the low-pressure compressor (911) and the intake port of the high-pressure compressor (912).

12. The air conditioning system according to claim 10, characterized in that: The compression device (91) includes a single compressor (913), the exhaust port of the single compressor (913) is divided into two paths, and is respectively connected to the first inlet (11) of the first heat exchanger (1) and the second inlet (21) of the second heat exchanger (2); the second outlet (22) of the second heat exchanger (2) is connected to one end of the evaporator (93) after passing through the throttling device (92), and the other end of the evaporator (93) is connected to the suction port of the single compressor (913).

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