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

Abstract

This invention belongs to the field of heat exchangers, specifically relating to a flow path structure for a heat exchanger, a heat exchanger, and an air conditioner. The invention aims to solve the problem of insufficient cooling or heating performance in current heat exchangers. To this end, the flow path structure for the heat exchanger includes a heat exchange flow path and a dryness regulating section. One end of the heat exchange flow path is connected to an external pipe via a third pipe, and the other end of the heat exchange flow path is connected to a third end of the dryness regulating section. A seventh end of the dryness regulating section is connected to the third pipe via a sixth pipe, and a fourth end of the dryness regulating section is connected to an external pipe via a second pipe. A first valve is also provided on the sixth pipe. The second pipe is configured such that its end connected to the dryness regulating section can communicate with locations at different depths within the dryness regulating section. The flow path structure for the heat exchanger of this invention can effectively improve the heat exchange effect during condensation and evaporation heat exchange in 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] Air conditioners are common devices used to regulate temperature. Heat exchangers are frequently used components in air conditioners and other devices involving heat exchange. The performance of a heat exchanger largely depends on its flow path design. However, for some dual-function products, such as heat pumps, the heat exchanger is not used solely as a condenser or evaporator. This results in a flow path design that is biased towards either cooling or heating, making it difficult to achieve the desired 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 issue of unsatisfactory cooling or heating performance in current heat exchangers, this invention provides a flow path structure for a heat exchanger, including a heat exchange flow path and a dryness adjustment section. One delivery end of the heat exchange flow path is connected to an external pipeline via a third pipeline, and the other delivery end of the heat exchange flow path is connected to the third delivery end of the dryness adjustment section. A seventh delivery end of the dryness adjustment section is connected to the third pipeline via a sixth pipeline, and a fourth delivery end of the dryness adjustment section is connected to an external pipeline via a second pipeline. A first valve is also provided on the sixth pipeline.

[0005] The second pipeline is configured such that one end connected to the dryness adjustment section can communicate with positions at different depths inside the dryness adjustment section.

[0006] In the preferred embodiment of the flow path structure for the heat exchanger described above, the second pipeline includes a deep connecting pipe, a shallow connecting pipe, and a connecting pipe. One end of the connecting pipe is connected to an external pipeline, and the other end of the connecting pipe is connected to both the deep connecting pipe and the shallow connecting pipe. The ends of the deep connecting pipe and the shallow connecting pipe furthest from the connecting pipe are both located within the dryness adjustment section. Furthermore, within the dryness adjustment section, the depth of the end of the deep connecting pipe is greater than the depth of the end of the shallow connecting pipe. Alternatively,

[0007] The flow path structure further includes a pipeline driving unit, the output end of which is connected to the second pipeline driving unit; under the drive of the pipeline driving unit, the end of the second pipeline connected to the dryness adjustment unit can move to different depths inside the dryness adjustment unit.

[0008] In the preferred embodiment of the flow path structure for the heat exchanger described above, the bottom of the dryness adjustment section is further provided with an eighth conveying end, which is connected to the compressor through a seventh pipeline, and the seventh pipeline is provided with a fourth valve.

[0009] In the preferred embodiment of the flow path structure for the heat exchanger described above, the heat exchange flow path includes 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 the 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 pipeline. 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 pipeline.

[0010] 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.

[0011] In the preferred embodiment of the flow path structure for the heat exchanger described above, a second valve and / or a heater are further provided on the sixth pipe; and / or,

[0012] 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.

[0013] 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,

[0014] No separator is installed between the sixth delivery end of the second heat exchange tube flow path and the fourth pipeline.

[0015] 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...

[0016] 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.

[0017] 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.

[0018] 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.

[0019] The present invention also provides an air conditioner, which includes the heat exchanger described in the above technical solution.

[0020] The present invention provides a flow path structure for a heat exchanger, including a heat exchange flow path and a dryness adjustment section. One conveying end of the heat exchange flow path is connected to an external pipeline through a third pipeline, and the other conveying end of the heat exchange flow path is connected to the third conveying end of the dryness adjustment section. The seventh conveying end of the dryness adjustment section is connected to the third pipeline through a sixth pipeline, and the fourth conveying end of the dryness adjustment section is connected to an external pipeline through a second pipeline. A first valve is also provided on the sixth pipeline.

[0021] The second pipeline is configured such that one end connected to the dryness regulating unit can communicate with different depths inside the dryness regulating unit.

[0022] In the flow path structure for the heat exchanger of the present invention, during evaporative heat exchange, the gaseous refrigerant directly enters the third pipe through the sixth pipe while passing through the dryness adjustment section. The remaining refrigerant, in a better dryness state, then enters the heat exchange flow path and then the third pipe, effectively improving the heat exchange effect. Furthermore, the end of the second pipe connected to the dryness adjustment section can communicate with different depths within the dryness adjustment section. This allows the refrigerant to enter or leave the dryness adjustment section from different depths depending on whether the heat exchanger is evaporating or condensing, further enhancing the heat exchange effect. Attached Figure Description

[0023] 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:

[0024] Figure 1 This is a schematic diagram of the flow path structure in the prior art;

[0025] Figure 2 This is a schematic diagram of the flow path structure of the present invention;

[0026] Figure 3 This is a schematic diagram of the structure of the second pipeline of the present invention.

[0027] List of reference numerals:

[0028] 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.

[0029] 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, 51-Deep connecting pipe, 52-Shallow connecting pipe, 53-Connecting pipe, 54-Deep connecting valve, 55-Shallow connecting valve, 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, 15-Eighth conveying end, 16-Seventh pipeline, 17-Fourth valve. Detailed Implementation

[0030] 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.

[0031] 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.

[0032] Furthermore, it should be noted that, in the description of this invention, unless otherwise explicitly specified and limited, the terms "connection," "provided with," 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 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.

[0033] Reference Figure 1First, 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 distributor 1006 and a second distributor 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.

[0034] 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 heat exchange flow path, comprising 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. The number of heat exchange tubes in a single first heat exchange tube flow path 1 (one flow path includes multiple heat exchange tubes) is less than the number of heat exchange tubes in a single second heat exchange tube flow path 2. A first delivery end 101 of the first heat exchange tube flow path 1 and a second delivery end 21 of the second heat exchange tube flow path 2 are connected by a dryness adjustment unit 3. The dryness adjustment unit 3 is a flash tank, and a third delivery end 31 is connected to the first delivery end 101 of the first heat exchange tube flow path 1 via a first pipe 4. The first pipe 4 and the first delivery end 101 are connected by a distributor 14. A 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 via a second pipe 5.

[0035] The fifth delivery end 102 of the first heat exchanger tube flow path 1 is connected to an external pipeline via 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 via the fourth pipeline 7. The seventh delivery end 33 of the dryness adjustment unit 3 is connected to the third pipeline 6 via the sixth pipeline 9.

[0036] 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.

[0037] The second pipe 5 is configured such that one end connected to the dryness adjustment section 3 can communicate with positions at different depths inside the dryness adjustment section 3 (in this embodiment, depth refers to the vertical length of the dryness adjustment section 3 from top to bottom; a larger depth value indicates a larger vertical length). Specifically, for example... Figure 3 As shown, the second pipeline 5 includes a deep connecting pipe 51, a shallow connecting pipe 52, and a connecting pipe 53. One end of the connecting pipe 53 is connected to an external pipeline, and the other end of the connecting pipe 53 is connected to both the deep connecting pipe 51 and the shallow connecting pipe 52. The deep connecting pipe 51 is equipped with a deep connecting valve 54, and the shallow connecting pipe 52 is equipped with a shallow connecting valve 55. The ends of both the deep connecting pipe 51 and the shallow connecting pipe 52 furthest from the connecting pipe 53 are located within the dryness adjustment section 3. Furthermore, within the dryness adjustment section 3, the depth of the end of the deep connecting pipe 51 is greater than the depth of the end of the shallow connecting pipe 52. Wherein, as... Figure 2 As shown, one end of the connecting pipe 53 that connects to the deep connecting pipe 51 and the shallow connecting pipe 52 can be located outside the dryness adjustment section 3 (or alternatively, inside the dryness adjustment section 3, not shown in the figure). Figure 2-3 As shown, both the shallow connecting pipe 52 and the deep connecting pipe 51 enter the interior of the dryness adjustment section 3 from the top (or the shallow connecting pipe 52 enters from the top of the dryness adjustment section 3, while the deep connecting pipe 51 enters from the lower part of the side of the dryness adjustment section 3, not shown in the figure, or other similar entry methods can be used). Correspondingly, the fourth conveying end 32 can be composed of two channels provided in the dryness adjustment section 3, with the shallow connecting pipe 52 and the deep connecting pipe 51 entering the dryness adjustment section 3 from their respective channels.

[0038] The bottom of the dryness adjustment section 3 is also provided with an eighth conveying end 15, which is connected to the compressor via a seventh pipeline 16, and the seventh pipeline 16 is provided with a fourth valve 17. The seventh pipeline 16 can be connected to the third pipeline 6 (not shown in the figure). By periodically opening the fourth valve 17, the compressor can be periodically returned to oil.

[0039] 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.

[0040] 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.

[0041] The flow path structure for the heat exchanger of the present invention further 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 frosting 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.

[0042] 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.

[0043] 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.

[0044] In this example, when the heat exchanger is performing condensation heat exchange, the gaseous refrigerant is input from the third pipe 6. 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 delivery end 33. Therefore, the gaseous refrigerant entering the third pipe 6 enters the first heat exchange tube flow path 1 through the fifth delivery end 102. After condensation heat exchange, the refrigerant enters the first pipe 4 through the first delivery end 101, and then enters the dryness regulating section 3 through the third delivery end 31. Then, the refrigerant enters the second heat exchanger tube flow path 2 through the second delivery end 21 via the deep connecting pipe 51 in the second pipe 5 (if the deep connecting pipe 51 is not installed, and the second pipe 5 does not enter the bottom of the dryness adjustment section 3, the refrigerant entering the dryness adjustment section 3 from the third delivery end 31 will accumulate in the dryness adjustment section 3 and will not flow out of the dryness adjustment section 3 for a long time, which will easily lead to compressor oil loss and reduced energy efficiency), and then enters the fourth pipe 7 through the sixth delivery end 22. During the condensation heat exchange process of the heat exchanger, since the refrigerant first passes through the first heat exchanger tube flow path 1 and then through the dryness adjustment section 3 to enter the second heat exchanger tube flow path 2, the second heat exchanger 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.

[0045] In this example, during evaporative heat exchange, 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 to gaseous refrigerant, which then flows from the second delivery end 21 through the shallow connecting pipe 52 in the second pipe 5 and from the fourth delivery end 32 into the dryness regulating section 3. (If the shallow connecting pipe 52 is not provided, and the second pipe 5 enters the bottom of the dryness regulating section 3, the adjustment of the second valve 11 can easily lead to a certain amount of gaseous refrigerant accumulating in the upper layer inside the dryness regulating section 3. This would cause a liquid seal to form at the ends of the first pipe 4 and the second pipe 5, which are immersed in the liquid refrigerant in the lower layer inside the dryness regulating section 3, making it difficult for the refrigerant to enter the first heat exchange tube flow path 1, significantly reducing heat exchange performance.) Simultaneously, the pressure drop in the second heat exchange tube flow path 2 can be controlled through the third valve 12 and the fifth pipe 8, thereby reducing resistance loss. In the dryness adjustment section 3, the gaseous refrigerant enters the sixth pipeline 9 via the seventh delivery end 33 and then directly enters the third pipeline 6; while the liquid refrigerant first enters the first pipeline 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 pipeline 6 from the fifth delivery end 102.

[0046] 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 can be omitted between the sixth delivery end 22 and the fourth pipe 7 of the second heat exchange pipe flow path 2 to reduce costs and the workload of adjusting the flow distribution effect of the second heat exchange pipe flow path 2. Furthermore, the end of the second pipe 5 connected to the dryness adjustment section 3 can communicate with positions at different depths inside the dryness adjustment section 3, allowing the refrigerant to enter or leave the dryness adjustment section 3 from different depths depending on the different states of evaporative or condensative heat exchange, further improving the heat exchange effect.

[0047] 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.

[0048] 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.

[0049] For example, in another alternative embodiment, the heat exchange flow path described in the current embodiment, which includes a first heat exchange tube flow path 1 and a second heat exchange tube flow path 2, can be replaced with a single-phase heat exchange tube flow path (not shown in the figure). One delivery end of the heat exchange flow path is connected to an external pipeline via a third pipeline 6, and the other delivery end of the heat exchange flow path is connected to the third delivery end 31 of the dryness adjustment unit 3. The seventh delivery end 33 of the dryness adjustment unit 3 is connected to the third pipeline 6 via a sixth pipeline 9, and the fourth delivery end 32 of the dryness adjustment unit 3 is connected to an external pipeline via a second pipeline 5. A first valve 10 is also provided on the sixth pipeline 9. These modifications do not deviate from the principles of the present invention and therefore all fall within the protection scope of the present invention.

[0050] For example, in another alternative embodiment, the second conduit 5 described in the current embodiment, which includes a deep connecting pipe 51, a shallow connecting pipe 52, and a connecting pipe 53, can be replaced by a flow path structure that also includes a conduit drive unit (not shown in the figure). The output end of the conduit drive unit is driven to connect to the second conduit 5. Under the drive of the conduit drive unit, the end of the second conduit 5 connected to the dryness adjustment unit 3 can move to different depths within the dryness adjustment unit 3. The conduit drive unit can be an electric push rod, and the second conduit 5 can be an elastic telescopic tube. These modifications do not deviate from the principles of the present invention and therefore fall within the scope of protection of the present invention.

[0051] For example, in another alternative embodiment, instead of the deep connecting pipe having a deep connecting valve 54 and the shallow connecting pipe having a shallow connecting valve 55 as described in the current embodiment, the deep connecting pipe may be without a deep connecting valve 54 (not shown in the figure), or without a shallow connecting valve 55 (not shown in the figure), or without both a deep connecting valve 54 and a shallow connecting valve 55 (not shown in the figure). This still achieves the goal of allowing the refrigerant to enter or leave the dryness adjustment section 3 at different depths depending on the different states of evaporative or condensative heat exchange in the heat exchanger, further improving the heat exchange effect. These modifications do not deviate from the principles of the present invention and therefore all fall within the scope of protection of the present invention.

[0052] 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.

[0053] 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 dryness of the refrigerant 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.

[0054] 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 provided on 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.

[0055] For example, in another alternative embodiment, instead of the second valve 11 and heater 13 described in the current embodiment, a heater 13 can be provided on the sixth pipe 9. This also achieves the 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.

[0056] 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.

[0057] The present invention also provides an air conditioner having the heat exchanger described in the above embodiments.

[0058] 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.

[0059] 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, characterized in that, It includes a heat exchange flow path and a dryness regulating section. One conveying end of the heat exchange flow path is connected to an external pipeline through a third pipeline, and the other conveying end of the heat exchange flow path is connected to the third conveying end of the dryness regulating section. The seventh conveying end of the dryness regulating section is connected to the third pipeline through a sixth pipeline, and the fourth conveying end of the dryness regulating section is connected to an external pipeline through a second pipeline. A first valve is also provided on the sixth pipeline. The second pipeline is configured such that one end connected to the dryness adjustment section can communicate with positions at different depths inside the dryness adjustment section. The heat exchange flow path includes 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 the 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 pipeline. 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 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, and the seventh delivery end of the dryness adjustment section is a gas delivery end, through which the gaseous components of the refrigerant entering the dryness adjustment section are input into the sixth pipeline; The flow path structure also includes a fifth pipeline, which is equipped with a third valve and connected at both ends to the fourth pipeline and the second pipeline, respectively. The pressure drop of the second heat exchanger tube flow path is controlled through the third valve and the fifth pipeline, thereby reducing resistance loss.

2. The flow path structure for a heat exchanger according to claim 1, characterized in that, The second conduit includes a deep connecting pipe, a shallow connecting pipe, and a connecting pipe. One end of the connecting pipe is connected to an external conduit, and the other end of the connecting pipe is connected to both the deep connecting pipe and the shallow connecting pipe. The ends of the deep connecting pipe and the shallow connecting pipe furthest from the connecting pipe are both located within the dryness adjustment section. Furthermore, within the dryness adjustment section, the depth of the end of the deep connecting pipe is greater than the depth of the end of the shallow connecting pipe; or... The flow path structure further includes a pipeline driving unit, the output end of which is connected to the second pipeline driving unit; under the drive of the pipeline driving unit, the end of the second pipeline connected to the dryness adjustment unit can move to different depths inside the dryness adjustment unit.

3. The flow path structure for a heat exchanger according to claim 1 or 2, characterized in that, The bottom of the dryness adjustment section is also provided with an eighth conveying end, which is connected to the compressor through a seventh pipeline, and the seventh pipeline is provided with a fourth valve.

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

5. 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.

6. 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.

7. 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 1-6.

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

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