Flow path structure for heat exchanger, heat exchanger and air conditioner

Abstract

The present application belongs to the field of heat exchanger, and particularly relates to a flow path structure for heat exchanger, a heat exchanger and an air conditioner. The present application aims to solve the problem that the refrigeration or heating effect of the current heat exchanger is not ideal. For this purpose, the flow path structure for heat exchanger of the present application comprises a first heat exchange pipe flow path and a second heat exchange pipe flow path, and is communicated through a dryness adjustment part. The first heat exchange pipe flow path is communicated with an external pipe through a third pipe, and the second heat exchange pipe flow path is communicated with the external pipe through a fourth pipe; the dryness adjustment part is communicated with the third pipe through a sixth pipe; and a first valve is further arranged on the sixth pipe. The flow path structure for heat exchanger of the present application can effectively improve the heat exchange effect when condensing heat exchange and evaporating heat exchange of the heat exchanger.

Description

Technical Field

[0001] This invention belongs to the field of heat exchanger technology, specifically relating to a flow path structure for a heat exchanger, a heat exchanger, and an air conditioner. Background Technology

[0002] Heat exchangers are frequently used components in devices involving heat exchange, such as air conditioners. The performance of a heat exchanger largely depends on its flow path design. However, for some dual-purpose (cooling and heating) products (such as heat pumps), the heat exchanger is not used solely as a condenser or evaporator. This results in the flow path being biased towards either cooling or heating in the initial design. Furthermore, in currently common heat exchangers, the liquid distribution method typically divides the heat exchanger into upper and lower sections, each equipped with a distributor for liquid separation. This causes the refrigerant, after heat exchange, to merge before entering the main pipeline, failing to achieve a truly ideal cooling or heating effect.

[0003] Accordingly, there is a need in the art for a new flow path structure for heat exchangers, heat exchangers, and air conditioners to address the aforementioned problem of unsatisfactory cooling or heating effects of current heat exchangers in the prior art. Summary of the Invention

[0004] To address the problem that the cooling or heating effect of current heat exchangers is not ideal, this invention provides a flow path structure for a heat exchanger, including a first heat exchange tube flow path and a second heat exchange tube flow path. The first delivery end of the first heat exchange tube flow path and the second delivery end of the second heat exchange tube flow path are connected through a dryness adjustment section. The third delivery end of the dryness adjustment section is connected to the first delivery end of the first heat exchange tube flow path through a first pipe. The fourth delivery end of the dryness adjustment section is connected to the second delivery end of the second heat exchange tube flow path through a second pipe.

[0005] The fifth delivery end of the first heat exchanger tube flow path is connected to an external pipeline through a third pipeline, and the sixth delivery end of the second heat exchanger tube flow path is connected to an external pipeline through a fourth pipeline; the seventh delivery end of the dryness adjustment section is connected to the third pipeline through a sixth pipeline; a first valve is also provided on the sixth pipeline.

[0006] In the preferred embodiment of the flow path structure for the heat exchanger described above, a second valve and / or heater are also provided on the sixth pipeline.

[0007] In the preferred embodiment of the flow path structure for the heat exchanger described above, the first valve is a one-way valve, and the first valve is configured such that the seventh conveying end of the dryness adjustment section is unidirectionally connected to the third pipeline through the sixth pipeline.

[0008] In the preferred embodiment of the flow path structure for the heat exchanger described above, the flow path structure further includes a fifth pipeline, which is provided with a third valve and its two ends are respectively connected to the fourth pipeline and the second pipeline.

[0009] In the preferred embodiment of the flow path structure for the heat exchanger described above, the seventh conveying end of the dryness adjustment section is a gas conveying end.

[0010] In the preferred embodiment of the flow path structure for the heat exchanger described above, the dryness adjustment unit is a gas-liquid separator or a flash tank.

[0011] In the preferred embodiment of the flow path structure for the heat exchanger described above, the flow path structure further includes a distributor, and the first delivery end of the first heat exchange tube flow path is connected to the first pipeline through the distributor; and / or,

[0012] No separator is installed between the sixth delivery end of the second heat exchange tube flow path and the fourth pipeline.

[0013] In the preferred embodiment of the flow path structure for the heat exchanger described above, the number of first heat exchange tube flow paths is greater than the number of second heat exchange tube flow paths; and / or...

[0014] The number of heat exchange tubes in a single first heat exchange tube flow path is less than the number of heat exchange tubes in a single second heat exchange tube flow path.

[0015] The present invention also provides a heat exchanger, the heat exchanger comprising the flow path structure for a heat exchanger as described in any of the above technical solutions.

[0016] The present invention also provides an air conditioner, which includes the heat exchanger described in any one of the above technical solutions.

[0017] The present invention provides a flow path structure for a heat exchanger, including a first heat exchange tube flow path and a second heat exchange tube flow path. A first conveying end of the first heat exchange tube flow path and a second conveying end of the second heat exchange tube flow path are connected through a dryness adjustment section. A third conveying end of the dryness adjustment section is connected to the first conveying end of the first heat exchange tube flow path through a first pipe. A fourth conveying end of the dryness adjustment section is connected to the second conveying end of the second heat exchange tube flow path through a second pipe. A fifth conveying end of the first heat exchange tube flow path is connected to an external pipe through a third pipe. A sixth conveying end of the second heat exchange tube flow path is connected to an external pipe through a fourth pipe. A seventh conveying end of the dryness adjustment section is connected to the third pipe through a sixth pipe. A first valve is also provided on the sixth pipe.

[0018] In the flow path structure for the heat exchanger of the present invention, during condensation heat exchange, the refrigerant first passes through the first heat exchange tube flow path, then through the dryness adjustment section, and enters the second heat exchange tube flow path. At this time, the second heat exchange tube flow path can be considered a subcooling section, effectively increasing the subcooling effect. During evaporation heat exchange, the refrigerant first passes through the second heat exchange tube flow path. During the process of passing through the dryness adjustment section, gaseous refrigerant directly enters the third tube through the sixth tube, while the remaining refrigerant is in a better dryness state before entering the first heat exchange tube flow path and then the third tube, effectively improving the heat exchange effect. Attached Figure Description

[0019] The flow path structure for a heat exchanger according to the present invention will now be described with reference to the accompanying drawings. In the drawings:

[0020] Figure 1 This is a schematic diagram of the flow path structure in the prior art;

[0021] Figure 2 This is a schematic diagram of the flow path structure of the present invention.

[0022] List of reference numerals:

[0023] 1001 - Upper flow path, 1002 - Lower flow path, 1003 - First channel, 1004 - Second channel, 1005 - Third channel, 1006 - First distributor, 1007 - Second distributor, 1008 - Fourth channel, 1009 - Fifth channel, 1010 - Sixth channel.

[0024] 1-First heat exchanger tube flow path, 101-First conveying end, 102-Fifth conveying end, 2-Second heat exchanger tube flow path, 21-Second conveying end, 22-Sixth conveying end, 3-Dryness adjustment section, 31-Third conveying end, 32-Fourth conveying end, 33-Seventh conveying end, 4-First pipeline, 5-Second pipeline, 6-Third pipeline, 7-Fourth pipeline, 8-Fifth pipeline, 9-Sixth pipeline, 10-First valve, 11-Second valve, 12-Third valve, 13-Heater, 14-Distributor. Detailed Implementation

[0025] Preferred embodiments of the present invention will now be described with reference to the accompanying drawings. Those skilled in the art should understand that these embodiments are merely illustrative of the technical principles of the invention and are not intended to limit the scope of protection of the invention. Those skilled in the art can make adjustments as needed to adapt to specific applications. For example, although the specification describes the first valve as a one-way valve, the present invention can obviously employ other similar means, such as using a ball valve as the first valve, as long as the first valve allows the gaseous refrigerant to directly enter the third pipe through the sixth pipe during heat exchange in the heat exchanger.

[0026] It should be noted that in the description of this invention, the terms "first," "second," etc., are used for descriptive purposes only and should not be construed as indicating or implying relative importance.

[0027] Furthermore, it should be noted that, in the description of this invention, unless otherwise explicitly specified and limited, the terms "connected," "provided," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium, etc. Those skilled in the art can understand the specific meaning of the above terms in this invention according to the specific circumstances.

[0028] Reference Figure 1 First, the flow path structure of the heat exchanger in the prior art will be described. The existing flow path structure includes an upper flow path 1001 and a lower flow path 1002. The upper flow path 1001 is connected to the second channel 1004 and the fourth channel 1008, respectively. The lower flow path 1002 is connected to the third channel 1005 and the fifth channel 1009, respectively. The second channel 1004 and the third channel 1005 are both connected to the first channel 1003. The fourth channel 1008 and the fifth channel 1009 are both connected to the sixth channel 1010. The fourth channel 1008 is connected to the upper flow path 1001 through the first distributor 1006, and the fifth channel 1009 is connected to the lower flow path 1002 through the second distributor 1007. In the existing flow path structure, the upper flow path 1001 and the lower flow path 1002 are respectively equipped with a first liquid separator 1006 and a second liquid separator 1007 connected to each other for liquid separation. This causes the refrigerant after heat exchange through the upper flow path 1001 and the lower flow path 1002 to merge before entering the main flow path, which cannot achieve a more ideal cooling or heating effect.

[0029] To address the issue of unsatisfactory cooling or heating performance in current heat exchangers, such as... Figure 2 As shown, the present invention provides a flow path structure for a heat exchanger, including a first heat exchange tube flow path 1 and a second heat exchange tube flow path 2. The number of first heat exchange tube flow paths 1 is greater than the number of second heat exchange tube flow paths 2, wherein the number of heat exchange tubes in a single first heat exchange tube flow path 1 is less than the number of heat exchange tubes in a single second heat exchange tube flow path 2. The first delivery end 101 of the first heat exchange tube flow path 1 and the second delivery end 21 of the second heat exchange tube flow path 2 are connected through a dryness adjustment unit 3. The dryness adjustment unit 3 is a flash tank, and the third delivery end 31 is connected to the first delivery end 101 of the first heat exchange tube flow path 1 through a first pipe 4. The first pipe 4 and the first delivery end 101 are connected through a distributor 14. The fourth delivery end 32 of the dryness adjustment unit 3 is connected to the second delivery end 21 of the second heat exchange tube flow path 2 through a second pipe 5.

[0030] The fifth delivery end 102 of the first heat exchanger tube flow path 1 is connected to an external pipeline through the third pipeline 6, and the sixth delivery end 22 of the second heat exchanger tube flow path 2 is connected to an external pipeline through the fourth pipeline 7. The seventh delivery end 33 of the dryness adjustment unit 3 is connected to the third pipeline 6 through the sixth pipeline 9.

[0031] The seventh delivery end 33 of the dryness regulating section 3 is a gas delivery end. Gaseous components of the refrigerant entering the dryness regulating section 3 are input into the sixth pipeline 9 through the seventh delivery end 33. A first valve 10 is also provided on the sixth pipeline 9. The first valve 10 is a one-way valve, configured to allow the seventh delivery end 33 of the dryness regulating section 3 to connect unidirectionally to the third pipeline 6 through the sixth pipeline 9. A second valve 11 (which can be a ball valve) and a heater 13 are also provided on the sixth pipeline 9. The second valve 11 controls the gas-liquid separation efficiency of the dryness regulating section 3, preventing excessively low pressure due to excessive flashing. If the first valve 10, i.e., the one-way valve, is too large, due to the low compressor suction pressure, some liquid refrigerant may flash due to compressor suction during actual operation and enter the third pipeline 6 through the sixth pipeline 9, potentially entering the compressor. Therefore, the heater 13 prevents liquid refrigerant from mixing in.

[0032] The liquid state at which the liquid refrigerant begins to vaporize is called a saturated liquid. When it has completely vaporized into a gaseous refrigerant state, the resulting gas is called dry saturated vapor. The state between these two is called the saturated state, where liquid and gas coexist, and is called wet vapor. If a saturated liquid is further cooled and releases heat, it becomes a subcooled liquid (subcooling a saturated refrigerant liquid below its saturation temperature while maintaining its saturation pressure is called subcooling). The temperature of the subcooled liquid is called the subcooling temperature, and the difference between the subcooling temperature and the condensation temperature is called the degree of subcooling. If some saturated vapor is further heated, it becomes superheated vapor. The temperature of the superheated vapor is called the superheating temperature, and the difference between the superheating temperature and the evaporation temperature is called the degree of superheating. In the saturated state range, because gaseous and liquid refrigerant coexist, it is called wet vapor. The proportion of gaseous refrigerant is expressed by dryness fraction, which is the percentage of the weight of gaseous refrigerant to the total weight of both gaseous and liquid refrigerants.

[0033] In existing technologies, heat exchangers are prone to frosting in certain operating environments due to various reasons. Typically, frosting occurs because the refrigerant temperature drops below 0 degrees Celsius in at least a localized area during its flow through the heat exchanger, causing frost to form on the flow path. The temperature of the refrigerant within the heat exchanger is usually correlated with its pressure; the higher the evaporation temperature, the higher the evaporation pressure. Evaporation temperature refers to the critical temperature at which the refrigerant changes from liquid to gas. In refrigeration systems, evaporation temperature refers to the saturation temperature at which the liquid refrigerant changes from liquid to gas during evaporation and heat exchange in the heat exchanger. The evaporation temperature of the refrigerant is closely related to the cooling temperature of refrigeration equipment such as air conditioners. If the evaporation temperature is too low, the operating economy of the refrigeration equipment will decrease. When heat exchangers are used in air conditioning, the evaporation temperature is generally above 5 degrees Celsius, so frosting does not occur under normal circumstances. Therefore, localized frosting on the heat exchanger is due to a decrease in the evaporation pressure of the refrigerant in that area, causing the evaporation temperature to drop below 0 degrees Celsius. Since the lower the evaporation temperature of the refrigerant, the worse the refrigeration effect of the refrigeration equipment, the lower the operating efficiency and the higher the energy consumption, and the more it will affect the working status of the compressor, the higher the evaporation temperature should be used as much as possible while meeting the requirements of normal refrigeration.

[0034] The flow path structure for the heat exchanger of the present invention also includes a fifth pipe 8, which is equipped with a third valve 12 and connected at both ends to a fourth pipe 7 and a second pipe 5, respectively. The pressure drop in the second heat exchanger flow path 2 can be controlled through the third valve 12 and the fifth pipe 8, thereby reducing resistance loss. During evaporative heat exchange in the heat exchanger, after adjustment by the dryness adjustment unit 3, a significant difference will occur between the evaporation temperature of the refrigerant in the first heat exchanger flow path 1 and the evaporation temperature of the refrigerant in the second heat exchanger flow path 2, with the evaporation temperature of the refrigerant in the second heat exchanger flow path 2 being higher than that in the first heat exchanger flow path 1. Therefore, the second heat exchanger flow path 2 is less prone to frost formation during evaporative heat exchange. Furthermore, since the air velocity in the first heat exchanger flow path 1 is usually higher, condensate is less likely to frost on the fins. Therefore, the structure of the present invention effectively extends the defrosting cycle of the heat exchanger during evaporative heat exchange, significantly improving the heat exchange effect during evaporative heat exchange.

[0035] Since the second heat exchanger tube flow path 2 is less prone to frost formation, whether or not the refrigerant is evenly distributed has little impact on the refrigerant's evaporation temperature, and consequently, less impact on the heat exchanger's performance. Therefore, a distributor is not required between the sixth delivery end 22 and the fourth pipe 7 of the second heat exchanger tube flow path 2. This not only reduces costs but also decreases the workload of adjusting the distribution effect of the second heat exchanger tube flow path 2.

[0036] Next, taking a specific application in an air conditioner as an example, the refrigerant condition of the flow path structure for the heat exchanger of the present invention will be explained.

[0037] In this invention, when the air conditioner is cooling, the gaseous refrigerant is input from the third pipe 6 when the heat exchanger is performing condensation heat exchange. However, due to the restriction of the first valve 10 on the sixth pipe 9, the gaseous refrigerant cannot directly enter the dryness regulating section 3 from the sixth pipe 9 via the seventh conveying end 33. Therefore, the gaseous refrigerant entering the third pipe 6 enters the first heat exchange tube flow path 1 via the fifth conveying end 102. After condensation heat exchange, the gaseous refrigerant is converted into liquid refrigerant and enters the first pipe 4 via the first conveying end 101. Then, it enters the dryness regulating section 3 via the third conveying end 31. After that, it enters the second heat exchange tube flow path 2 via the second pipe 5 via the second conveying end 21, and then enters the fourth pipe 7 via the sixth conveying end 22. During the condensation heat exchange process in the heat exchanger, the refrigerant first passes through the first heat exchange tube flow path 1 and then through the dryness adjustment section 3 before entering the second heat exchange tube flow path 2. Therefore, the second heat exchange tube flow path 2 can be used as the subcooling section of the entire heat exchanger flow path structure, which can increase the subcooling effect and thus improve the cooling effect of the air conditioner.

[0038] In this invention, when the air conditioner is heating, correspondingly, during evaporative heat exchange in the heat exchanger, liquid refrigerant enters the second heat exchange tube flow path 2 from the fourth pipe 7 via the sixth delivery end 22. Within the second heat exchange tube flow path 2, some of the liquid refrigerant is converted into gaseous refrigerant, which then enters the dryness regulating section 3 from the second delivery end 21 via the second pipe 5 and from the fourth delivery end 32. Simultaneously, the pressure drop in the second heat exchange tube flow path 2 can be controlled via the third valve 12 and the fifth pipe 8, thereby reducing resistance loss. Within the dryness regulating section 3, gaseous refrigerant enters the sixth pipe 9 via the seventh delivery end 33 and then directly enters the third pipe 6; while liquid refrigerant first enters the first pipe 4 from the third delivery end 31, then enters the first heat exchange tube flow path 1 from the first delivery end 101, and finally enters the third pipe 6 from the fifth delivery end 102.

[0039] In summary, in the flow path structure for the heat exchanger of the present invention, during condensation heat exchange, the refrigerant first passes through the first heat exchange tube flow path 1, then through the dryness adjustment section 3, and enters the second heat exchange tube flow path 2. At this time, the second heat exchange tube flow path 2 can be considered a subcooling section, effectively increasing the subcooling effect. During evaporation heat exchange, the refrigerant first passes through the second heat exchange tube flow path 2. During the process of passing through the dryness adjustment section 3, the gaseous refrigerant directly enters the third pipe 6 through the sixth pipe 9, while the remaining refrigerant is in a better dryness state before entering the first heat exchange tube flow path 1 and then the third pipe 6, effectively improving the heat exchange effect. Furthermore, during evaporation heat exchange, by controlling the second valve 11 and the third valve 12, excessive flashing of the refrigerant within the dryness adjustment section 3 can be effectively avoided, preventing rapid frosting of the second heat exchange tube flow path 2. Based on this, a distributor may not be installed between the sixth delivery end 22 of the second heat exchanger tube flow path 2 and the fourth pipe 7 to reduce costs and the workload of debugging the flow distribution effect of the second heat exchanger tube flow path 2.

[0040] It should be noted that the above embodiments are merely used to illustrate the principles of the present invention and are not intended to limit the scope of protection of the present invention. Without departing from the principles of the present invention, those skilled in the art can adjust the above structure so that the present invention can be applied to more specific application scenarios. These adjustments do not depart from the principles of the present invention and therefore fall within the scope of protection of the present invention.

[0041] For example, in an alternative embodiment, the first valve 10 described in the current embodiment, which is a one-way valve, can be replaced by a ball valve, etc. Specifically, the first valve 10 can be an electric ball valve or an electric valve, or a solenoid valve, etc. This first valve 10 can also allow the gaseous refrigerant in the dryness adjustment section 3 to directly enter the third pipe 6 through the sixth pipe 9 during heat exchange in the heat exchanger, thereby adjusting the dryness of the refrigerant. Similarly, depending on actual needs, the second valve 11 and the third valve 12 can also be electric ball valves or solenoid valves, etc. These do not deviate from the principle of the present invention and therefore all fall within the protection scope of the present invention.

[0042] For example, in another alternative embodiment, the dryness adjustment unit 3 described in the current embodiment can be replaced by a flash evaporator, or by a gas-liquid separator, as long as it can be used to adjust the dryness of the refrigerant. These modifications do not deviate from the principles of the present invention and therefore fall within the scope of protection of the present invention.

[0043] For example, in another alternative embodiment, instead of the current embodiment which includes a second valve 11 and a heater 13 on the sixth pipe 9, and a fifth pipe 8 with a third valve 12 on the fifth pipe 8, the second valve 11 and heater 13 on the sixth pipe 9, as well as the fifth pipe 8 and the third valve 12, can be omitted. The refrigerant dryness can still be adjusted by allowing the gaseous refrigerant in the dryness adjustment section 3 to directly enter the third pipe 6 through the sixth pipe 9. Compared to the previous structure, this embodiment has a larger resistance loss during evaporative heat exchange in the heat exchanger, and because the sixth pipe 9 is directly connected to the third pipe 6, the pressure in the sixth pipe 9 is prone to being too low. This can lead to excessive flashing of the refrigerant passing through the dryness adjustment section 3, resulting in liquid carryover during suction, and rapid frosting of the dryness adjustment section 3 and the second heat exchange pipe flow path 2. However, compared to the prior art, this embodiment can still effectively improve the heat exchange effect during both condensation and evaporative heat exchange in the heat exchanger. These do not deviate from the principles of the present invention, and therefore all fall within the protection scope of the present invention.

[0044] For example, in another alternative embodiment, instead of the second valve 11 and heater 13 described in the current embodiment, the second valve 11 can be added to the sixth pipe 9. When the size of the first valve 10, i.e., the one-way valve, is appropriate, the heater 13 (not shown in the figure) is not required. This achieves the same effect of allowing the gaseous refrigerant in the dryness adjustment section 3 to directly enter the third pipe 6 through the sixth pipe 9 to adjust the dryness of the refrigerant. These modifications do not deviate from the principles of the present invention and therefore fall within the scope of protection of the present invention.

[0045] For example, in another alternative embodiment, instead of the second valve 11 and heater 13 described in the current embodiment, a heater 13 can also be provided on the sixth pipe 9. This achieves the same effect of allowing the gaseous refrigerant in the dryness adjustment section 3 to directly enter the third pipe 6 through the sixth pipe 9 to adjust the dryness of the refrigerant. These modifications do not deviate from the principles of the present invention and therefore fall within the scope of protection of the present invention.

[0046] In addition, the present invention provides a heat exchanger having the flow path structure for a heat exchanger described in any of the above embodiments.

[0047] The present invention also provides an air conditioner having the heat exchanger described in any of the above embodiments.

[0048] Of course, the alternative implementation methods described above, as well as the alternative implementation methods and preferred implementation methods, can be used in combination to create new implementation methods that are suitable for more specific application scenarios.

[0049] The technical solution of the present invention has been described above with reference to the preferred embodiments shown in the accompanying drawings. However, it will be readily understood by those skilled in the art that the scope of protection of the present invention is obviously not limited to these specific embodiments. Without departing from the principles of the present invention, those skilled in the art can make equivalent changes or substitutions to the relevant technical features, and the technical solutions after such changes or substitutions will all fall within the scope of protection of the present invention.

Claims

1. A flow path structure for a heat exchanger, comprising a first heat exchange tube flow path and a second heat exchange tube flow path, characterized in that, The first conveying end of the first heat exchanger tube flow path and the second conveying end of the second heat exchanger tube flow path are connected through a dryness adjustment section. The third conveying end of the dryness adjustment section is connected to the first conveying end of the first heat exchanger tube flow path through a first pipeline. The fourth conveying end of the dryness adjustment section is connected to the second conveying end of the second heat exchanger tube flow path through a second pipeline. The fifth delivery end of the first heat exchanger tube flow path is connected to an external pipeline through a third pipeline, and the sixth delivery end of the second heat exchanger tube flow path is connected to an external pipeline through a fourth pipeline; the seventh delivery end of the dryness adjustment section is connected to the third pipeline through a sixth pipeline; a first valve is also provided on the sixth pipeline; The flow path structure also includes a fifth pipeline, which is equipped with a third valve and is connected at both ends to the fourth pipeline and the second pipeline, respectively. The pressure drop of the second heat exchange tube flow path is controlled through the third valve and the fifth pipeline to reduce resistance loss. The first valve is a one-way valve, and the first valve is configured to allow the seventh delivery end of the dryness adjustment unit to be connected unidirectionally to the third pipeline through the sixth pipeline. The seventh delivery end of the dryness adjustment unit is a gas delivery end. During the evaporative heat exchange in the heat exchanger, after adjustment by the dryness adjustment unit, the evaporation temperature of the refrigerant in the second heat exchange tube flow path is greater than that of the refrigerant in the first heat exchange tube flow path. Therefore, during the evaporative heat exchange in the heat exchanger, the second heat exchange tube flow path is less prone to frost formation.

2. The flow path structure for a heat exchanger according to claim 1, characterized in that, A second valve and / or heater are also provided on the sixth pipeline.

3. The flow path structure for a heat exchanger according to claim 1, characterized in that, The dryness adjustment unit is a gas-liquid separator or a flash tank.

4. The flow path structure for a heat exchanger according to claim 1, characterized in that, The flow path structure further includes a distributor, through which the first delivery end of the first heat exchange tube flow path is connected to the first pipeline; and / or No separator is installed between the sixth delivery end of the second heat exchange tube flow path and the fourth pipeline.

5. The flow path structure for a heat exchanger according to claim 1, characterized in that, The number of flow paths in the first heat exchanger tube is greater than the number of flow paths in the second heat exchanger tube; and / or, The number of heat exchange tubes in a single first heat exchange tube flow path is less than the number of heat exchange tubes in a single second heat exchange tube flow path.

6. A heat exchanger, characterized in that, The heat exchanger includes the flow path structure for a heat exchanger as described in any one of claims 1-5.

7. An air conditioner, characterized in that, The air conditioner includes the heat exchanger as described in claim 6.

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