CN221077325U - Microchannel heat exchanger, heat pump water heater and air conditioner - Google Patents
Microchannel heat exchanger, heat pump water heater and air conditioner Download PDFInfo
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- CN221077325U CN221077325U CN202322737715.2U CN202322737715U CN221077325U CN 221077325 U CN221077325 U CN 221077325U CN 202322737715 U CN202322737715 U CN 202322737715U CN 221077325 U CN221077325 U CN 221077325U
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- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 title claims abstract description 10
- 239000003507 refrigerant Substances 0.000 claims abstract description 94
- 239000007788 liquid Substances 0.000 claims abstract description 69
- 238000000034 method Methods 0.000 claims description 132
- 230000008569 process Effects 0.000 claims description 130
- 238000011144 upstream manufacturing Methods 0.000 claims description 7
- 238000004891 communication Methods 0.000 claims description 5
- 238000005192 partition Methods 0.000 claims description 3
- 238000005265 energy consumption Methods 0.000 description 17
- 230000008859 change Effects 0.000 description 10
- 230000000694 effects Effects 0.000 description 5
- 239000011148 porous material Substances 0.000 description 5
- 238000012360 testing method Methods 0.000 description 4
- 230000006872 improvement Effects 0.000 description 3
- 230000035772 mutation Effects 0.000 description 3
- 230000009286 beneficial effect Effects 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
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- 238000013461 design Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000004907 flux Effects 0.000 description 1
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- 230000017525 heat dissipation Effects 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 239000000178 monomer Substances 0.000 description 1
- 238000005057 refrigeration Methods 0.000 description 1
- 238000004781 supercooling Methods 0.000 description 1
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Abstract
The present disclosure relates to a microchannel heat exchanger, a heat pump water heater and an air conditioner. The microchannel heat exchanger includes: the device comprises a first liquid collecting pipe (10), a second liquid collecting pipe (20) and a plurality of flat pipes (30), wherein one end of each flat pipe (30) is connected with the first liquid collecting pipe (10), the other end of each flat pipe is connected with the second liquid collecting pipe (20), and the flat pipe is provided with a plurality of micropores (31) which are communicated with the first liquid collecting pipe (10) and the second liquid collecting pipe (20); the first liquid collecting pipe (10), the second liquid collecting pipe (20) and the plurality of flat pipes (30) form a refrigerant flow path, the refrigerant flow path comprises a first group of micro-channel flow paths (F10) for circulating a gaseous refrigerant in a superheated state and/or a refrigerant in a gas-liquid two-phase state and a second group of micro-channel flow paths (F20) for circulating a liquid refrigerant in a supercooled state, and the number of flat pipes contained in each micro-channel flow path in the second group of micro-channel flow paths (F20) is smaller than the number of flat pipes contained in each micro-channel flow path in the first group of micro-channel flow paths (F10).
Description
Technical Field
The disclosure relates to the technical field of heat exchange, in particular to a micro-channel heat exchanger, a heat pump water heater and an air conditioner.
Background
A microchannel heat exchanger is a heat exchange device that transfers heat through a microchannel of the micron order, having a smaller size and higher surface area to volume ratio, suitable for heat exchange requirements for high heat flux and compact space. The micro-channel heat exchanger is widely applied to a plurality of fields such as automobile air conditioner, electronic device heat dissipation, aerospace, energy fields and the like due to the advantages of high heat exchange efficiency, small volume, light weight, high reliability and the like.
For a general parallel flow micro-channel heat exchanger, the number of flat tubes contained in each flow path of the micro-channel heat exchanger monomer is consistent under given design conditions.
Disclosure of utility model
The inventor finds that the microchannel heat exchangers with consistent numbers of flat tubes in each flow in the related technology are not easy to consider the heat exchange performance and pressure drop of the microchannel heat exchanger, so that the improvement of the overall operation performance is affected.
In view of the above, embodiments of the present disclosure provide a micro-channel heat exchanger, a heat pump water heater, and an air conditioner, which can improve overall operation performance.
In one aspect of the present disclosure, there is provided a microchannel heat exchanger comprising: the device comprises a first liquid collecting pipe, a second liquid collecting pipe and a plurality of flat pipes, wherein one end of each flat pipe is connected with the first liquid collecting pipe, the other end of each flat pipe is connected with the second liquid collecting pipe, and the flat pipes are provided with a plurality of micropores communicated with the first liquid collecting pipe and the second liquid collecting pipe;
The first liquid collecting pipe, the second liquid collecting pipe and the plurality of flat pipes form a refrigerant flow path, the refrigerant flow path comprises a first group of micro-channel flow paths for circulating a gaseous refrigerant in an overheated state and/or a refrigerant in a gas-liquid two-phase state and a second group of micro-channel flow paths for circulating a liquid refrigerant in a supercooled state, and the number of flat pipes contained in each micro-channel flow path in the second group of micro-channel flow paths is smaller than that of flat pipes contained in each micro-channel flow path in the first group of micro-channel flow paths.
In some embodiments, the ratio of the number of flat tubes contained in each of the second set of microchannel flows to the number of flat tubes contained in each of the first set of microchannel flows is greater than or equal to 0.3 and less than or equal to 0.75.
In some embodiments, the ratio of the number of flat tubes contained in each of the second set of microchannel flows to the number of flat tubes contained in each of the first set of microchannel flows is greater than or equal to 0.4 and less than or equal to 0.6.
In some embodiments, the second set of microchannel processes comprises at least two microchannel processes, the at least two microchannel processes being in serial communication with the first set of microchannel processes in sequence;
In the flow direction of the refrigerant in the refrigerant flow path, the number of flat tubes included in the upstream microchannel flow path in the at least two microchannel flow paths is greater than the number of flat tubes included in the downstream microchannel flow path in the at least two microchannel flow paths.
In some embodiments, the at least two micro-channel flows include a first micro-channel flow and a second micro-channel flow sequentially connected in series in a flow direction of the refrigerant in the refrigerant flow path, and a ratio of a number of flat tubes included in the first micro-channel flow to a number of flat tubes included in the second micro-channel flow is greater than or equal to 1 and less than 2.5.
In some embodiments, the ratio of the number of flat tubes included in the first microchannel process to the number of flat tubes included in the second microchannel process is greater than or equal to 1.5 and less than 2.
In some embodiments, the sum of the micropore cross-sectional areas of all of the flat tubes contained in each of the first set of microchannel flows is greater than the sum of the micropore cross-sectional areas of all of the flat tubes contained in each of the second set of microchannel flows.
In some embodiments, the ratio of the sum of the micro-pore cross-sectional areas of all the flat tubes contained in each of the first set of micro-channel processes to the sum of the cross-sectional areas of all the flat tubes contained in each of the second set of micro-channel processes is greater than or equal to 1.3 and less than or equal to 11.9.
In some embodiments, the ratio of the sum of the micropore cross-sectional areas of all the flat tubes contained in each microchannel process of the first set of microchannel processes to the sum of the micropore cross-sectional areas of all the flat tubes contained in each microchannel process of the second set of microchannel processes is greater than or equal to 2.17 and less than or equal to 8.5.
In some embodiments, at least one of the first liquid collecting pipe and the second liquid collecting pipe is separated by a partition plate to form a plurality of liquid collecting cavities, the plurality of liquid collecting cavities are communicated with the plurality of flat pipes to form the first group of micro-channel processes and the second group of micro-channel processes, the first group of micro-channel processes comprises a single micro-channel process for circulating a gaseous refrigerant in a superheated state and a refrigerant in a gas-liquid two-phase state, the number of flat pipes contained in the single micro-channel process is 5, the number of flat pipes contained in the first micro-channel process is 3, and the number of flat pipes contained in the second micro-channel process is 2.
In one aspect of the present disclosure, a heat pump water heater is provided comprising the foregoing microchannel heat exchanger.
In one aspect of the present disclosure, an air conditioner is provided that includes the foregoing microchannel heat exchanger.
According to the embodiment of the disclosure, in the microchannel heat exchanger, the heat exchange process of the flat tubes of the microchannel flow of the liquid refrigerant in the supercooling state is mainly convection sensible heat exchange, and the heat exchange coefficient is smaller, so that in order to increase the heat exchange performance, the flow rate and the turbulence degree of the refrigerant flowing in each flat tube are increased under the condition that the flow rate of the refrigerant entering the second group of microchannel flow is certain by reducing the number of the flat tubes included in the flow, and the heat exchange coefficient of the second group of microchannel flow is improved to realize enhanced heat exchange; the heat exchange process of the flat tubes of the microchannel process through which the gaseous refrigerant in the overheat state and/or the refrigerant in the gas-liquid two-phase state flows mainly comprises phase change latent heat exchange, the heat exchange coefficient is larger, and the pressure drop is also larger, so that the flow speed and the turbulence degree of the refrigerant flowing through each flat tube are reduced under the condition that the flow rate of the refrigerant entering the first group of microchannel process is certain by increasing the number of the flat tubes contained in the process, the pressure drop of the refrigerant in the first group of microchannel process is reduced, the energy utilization efficiency is improved, the operation stability of the heat exchanger is improved, and the overall operation performance of the microchannel heat exchanger is improved.
Drawings
The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate embodiments of the disclosure and together with the description, serve to explain the principles of the disclosure.
The disclosure may be more clearly understood from the following detailed description taken in conjunction with the accompanying drawings in which:
FIG. 1 is a schematic diagram of a micro-channel heat exchanger according to some embodiments of the present disclosure;
fig. 2 is a schematic cross-sectional view of a flat tube in a microchannel heat exchanger according to some embodiments of the present disclosure.
It should be understood that the dimensions of the various elements shown in the figures are not drawn to actual scale. Further, the same or similar reference numerals denote the same or similar members.
Detailed Description
Various exemplary embodiments of the present disclosure will now be described in detail with reference to the accompanying drawings. The description of the exemplary embodiments is merely illustrative, and is in no way intended to limit the disclosure, its application, or uses. The present disclosure may be embodied in many different forms and is not limited to the embodiments described herein. These embodiments are provided so that this disclosure will be thorough and complete, and will fully convey the scope of the disclosure to those skilled in the art. It should be noted that: the relative arrangement of parts and steps, the composition of materials, numerical expressions and numerical values set forth in these embodiments should be construed as exemplary only and not limiting unless otherwise specifically stated.
The terms "first," "second," and the like, as used in this disclosure, do not denote any order, quantity, or importance, but rather are used to distinguish one element from another. The word "comprising" or "comprises" and the like means that elements preceding the word encompass the elements recited after the word, and not exclude the possibility of also encompassing other elements. "upper", "lower", "left", "right", etc. are used merely to indicate relative positional relationships, which may also be changed when the absolute position of the object to be described is changed.
In this disclosure, when a particular device is described as being located between a first device and a second device, there may or may not be an intervening device between the particular device and either the first device or the second device. When it is described that a particular device is connected to other devices, the particular device may be directly connected to the other devices without intervening devices, or may be directly connected to the other devices without intervening devices.
All terms (including technical or scientific terms) used in this disclosure have the same meaning as commonly understood by one of ordinary skill in the art to which this disclosure belongs, unless specifically defined otherwise. It will be further understood that terms, such as those defined in commonly used dictionaries, should be interpreted as having a meaning that is consistent with their meaning in the context of the relevant art and will not be interpreted in an idealized or overly formal sense unless expressly so defined herein.
Techniques, methods, and apparatus known to one of ordinary skill in the relevant art may not be discussed in detail, but are intended to be part of the specification where appropriate.
In some related art, the flat tubes in different heat exchange areas of the parallel flow microchannel heat exchanger have uniformity in specification and size and internal structure. The inventor finds that the flat tube with consistent specification and size and internal structure in the related technology is not easy to consider the heat exchange performance and pressure drop of the micro-channel heat exchanger, thereby influencing the improvement of the whole operation performance.
In view of the above, embodiments of the present disclosure provide a micro-channel heat exchanger, a heat pump water heater, and an air conditioner, which can improve overall operation performance.
Fig. 1 is a schematic structural view of a microchannel heat exchanger according to some embodiments of the present disclosure. Fig. 2 is a schematic cross-sectional view of a flat tube in a microchannel heat exchanger according to some embodiments of the present disclosure.
Referring to fig. 1 and 2, embodiments of the present disclosure provide a microchannel heat exchanger comprising: a first header 10, a second header 20 and a plurality of flat tubes 30. Each flat tube 30 has one end connected to the first liquid collecting tube 10 and the other end connected to the second liquid collecting tube 20, and has a plurality of micropores 31 communicating the first liquid collecting tube 10 and the second liquid collecting tube 20. The first header pipe 10, the second header pipe 20 and the plurality of flat pipes 30 form a refrigerant flow path, the refrigerant flow path includes a first group of micro-channel flow paths F10 for flowing a gaseous refrigerant in a superheated state and/or a refrigerant in a gas-liquid two-phase state, and a second group of micro-channel flow paths F20 for flowing a liquid refrigerant in a supercooled state, and the number of flat pipes included in each micro-channel flow path in the second group of micro-channel flow paths F20 is smaller than the number of flat pipes included in each micro-channel flow path in the first group of micro-channel flow paths F10.
In the microchannel heat exchanger, the heat exchange process of the flat tubes 30 of the microchannel flow path through which the liquid refrigerant in the supercooled state flows is mainly convective heat exchange, and the heat exchange coefficient is smaller, so that in order to increase the heat exchange performance, the flow velocity and the turbulence degree of the refrigerant flowing through each flat tube 30 are increased by reducing the number of the flat tubes included in the flow path under the condition that the flow rate of the refrigerant entering the second group of microchannel flow paths F20 is fixed, and the heat exchange coefficient of the second group of microchannel flow paths F20 is improved to realize enhanced heat exchange. The heat exchange process of the flat tubes 30 of the micro-channel flow, through which the gaseous refrigerant in the overheat state and/or the refrigerant in the gas-liquid two-phase state flows, is mainly phase-change latent heat exchange, the heat exchange coefficient is larger, and the pressure drop is also larger, so that in order to improve the pressure drop, the flow speed and the turbulence degree of the refrigerant flowing through each flat tube 30 are reduced under the condition that the flow rate of the refrigerant entering the first group of micro-channel flow F10 flow is certain by increasing the number of the flat tubes included in the flow, thereby reducing the pressure drop of the refrigerant in the first group of micro-channel flow F10, improving the energy utilization efficiency and improving the operation stability of the heat exchanger. Thus, the overall operation performance of the micro-channel heat exchanger is improved.
The first set of microchannel processes F10 and the second set of microchannel processes F20 may each comprise one or more microchannel processes, each of which may comprise at least one flat tube 30. The flat tube 30 has a plurality of micro holes 31, and both ends of each micro hole 31 are respectively communicated with the first liquid collecting tube 10 and the second liquid collecting tube 20, so as to realize the flow path of the refrigerant from one end to the other end. In other words, the flow path refers to a flow structure in which the refrigerant flows from the header pipe (e.g., the first header pipe or the second header pipe) on one side to the header pipe (e.g., the second header pipe or the first header pipe) on the other side through the plurality of micropores in the flat pipe.
In this embodiment, the first group of micro-channel flows F10 may be used to flow the gaseous refrigerant in the superheated state, or to flow the refrigerant in the gas-liquid two-phase state, or to flow the gaseous refrigerant in the superheated state, or to flow the refrigerant in the gas-liquid two-phase state.
For example, the first group of micro-channel flows F10 includes a single micro-channel flow F11, where the refrigerant flows from the first end to the second end of the flat tube in the single micro-channel flow F11, the refrigerant nearer to the first end is in an upstream state according to the flow direction of the refrigerant, and is in a superheated state, while the refrigerant nearer to the second end is in a downstream state, and is converted into a gas-liquid two-phase state after undergoing heat exchange.
For another example, the first group of micro-channel processes F10 includes a plurality of micro-channel processes, which are sequentially connected in series according to the flow direction of the refrigerant, wherein the part of the micro-channel processes at the upstream may be used to flow the gaseous refrigerant in the superheated state, and the part of the micro-channel processes at the downstream may be used to flow the gaseous refrigerant in the gas-liquid two-phase state.
In this embodiment, the second group of micro-channel flow F20 is used to circulate the liquid refrigerant in the supercooled state. The second set of microchannel processes F20 may comprise one or more microchannel processes that are serially connected in series with the microchannel processes in the first set of microchannel processes F10 in the flow direction of the refrigerant. Each of the micro-channel processes included in the second set of micro-channel processes F10 is used for circulating the liquid refrigerant in the supercooled state after heat exchange through the second set of micro-channel processes F10.
The foregoing embodiment has mentioned that the number of flat tubes included in each of the second set of micro-channel processes F20 is smaller than the number of flat tubes included in each of the first set of micro-channel processes F10, and accordingly the ratio of the number of flat tubes included in each of the second set of micro-channel processes F20 to the number of flat tubes included in each of the first set of micro-channel processes F10 is smaller than 1.
Considering that if this ratio is too small, meaning that each of the second set of microchannel flows F20 contains a significantly smaller number of flat tubes than each of the first set of microchannel flows F10, a drastic change in pressure of the refrigerant when flowing from the first set of microchannel flows F10 to the second set of microchannel flows F20 may occur, resulting in energy loss, leading to an increase in energy consumption. If the ratio is too large, it means that the number of flat tubes contained in each of the second set of micro-channel flows F20 is relatively close to the number of flat tubes contained in each of the first set of micro-channel flows F10, which would impair the effect of improving the heat exchange performance of the second set of micro-channel flows F20 and improving the pressure drop of the first set of micro-channel flows F10.
Thus, in some embodiments, the ratio of the number of flat tubes included in each of the second set of micro-channel flows F20 to the number of flat tubes included in each of the first set of micro-channel flows F10 may be greater than or equal to 0.3 and less than or equal to 0.75. Therefore, the heat exchange performance of the second group of micro-channel flows F20 and the pressure drop of the first group of micro-channel flows F10 are improved, and meanwhile, the energy consumption loss caused by pressure mutation when the refrigerant flows from the first group of micro-channel flows F10 to the second group of micro-channel flows F20 is reduced, so that the overall operation performance is improved.
Further, the ratio of the number of flat tubes contained in each of the second set of micro-channel flows F20 to the number of flat tubes contained in each of the first set of micro-channel flows F10 may be greater than or equal to 0.4 and less than or equal to 0.6, for example, the ratio is 0.4, 0.5, 0.6, etc. By making the ratio satisfy the preferred range of 0.4 to 0.6, the heat exchange performance of the second group of micro-channel flows F20 and the pressure drop of the first group of micro-channel flows F10 can be improved, and meanwhile, the energy consumption loss caused by the abrupt change of the pressure of the refrigerant flowing from the first group of micro-channel flows F10 to the second group of micro-channel flows F20 can be further reduced, so that the overall operation performance can be more effectively improved.
Referring to fig. 1, in some embodiments, the second set of microchannel processes F20 comprises at least two microchannel processes that are in serial communication with the first set of microchannel processes F10 in sequence. In the flow direction of the refrigerant in the refrigerant flow path, the number of flat tubes included in the upstream microchannel flow path in the at least two microchannel flow paths is greater than the number of flat tubes included in the downstream microchannel flow path in the at least two microchannel flow paths.
In order to improve the energy consumption loss caused by the abrupt pressure change when the first group of micro-channel flows F10 flows to the second group of micro-channel flows F20, for the second group of micro-channel flows F20 comprising a plurality of micro-channel flows which are sequentially connected in series, the number of flat tubes in the micro-channel flow positioned at the upstream is larger than that of flat tubes in the micro-channel flow positioned at the downstream, so that the number of flat tubes in each flow path on the refrigerant flow path is sequentially changed from large to small, the pressure change degree is reduced in the refrigerant flow process, and the problem of energy consumption increase caused by the abrupt pressure change is restrained.
Referring to fig. 1, in some embodiments, the at least two micro-channel processes include a first micro-channel process F21 and a second micro-channel process F22 sequentially connected in series in a flow direction of the refrigerant in the refrigerant flow path, and a ratio of a number of flat tubes included in the first micro-channel process F21 to a number of flat tubes included in the second micro-channel process F22 is greater than or equal to 1 and less than 2.5.
Referring to the second set of micro-channel flows F20 shown in fig. 1, the second set of micro-channel flows F20 includes a first micro-channel flow F21 and a second micro-channel flow F22, and the number of flat tubes included in the first micro-channel flow F21 and the second micro-channel flow F22 may be the same or different. For the embodiment in which the first micro-channel flow F21 and the second micro-channel flow F22 include the same number of flat tubes, each flow in the second set of micro-channel flow F20 has better consistency, and pressure drops between each other are more uniform, which is beneficial to reducing energy consumption.
If the ratio of the number of flat tubes contained in the first micro-channel flow F21 to the number of flat tubes contained in the second micro-channel flow F22 is too small, a gradual pressure drop effect beneficial to reducing energy consumption is not easy to be formed. If the ratio of the number of flat tubes contained in the first microchannel process F21 to the number of flat tubes contained in the second microchannel process F22 is too large, that is, the number of flat tubes contained in the first microchannel process F21 is greater than the number of flat tubes contained in the second microchannel process F22, a pressure mutation is easily formed in the second group of microchannel processes F20, thereby bringing about energy consumption loss. Therefore, by making the ratio of the number of flat tubes contained in the first microchannel process F21 to the number of flat tubes contained in the second microchannel process F22 be greater than or equal to 1 and less than 2.5, the energy consumption loss during the flow of the refrigerant in the second set of microchannel process F20 can be reduced.
Further, the ratio of the number of flat tubes included in the first microchannel process F21 to the number of flat tubes included in the second microchannel process F22 may be greater than or equal to 1.5 and less than 2, for example, the ratio may be about 1.5, 1.67, 1.6, 1.75, etc. By making the ratio satisfy the preferable range of 1.5 or more and less than 2, the energy consumption loss in the flow process of the refrigerant in the second group of micro-channel flows F20 can be more effectively reduced, and the overall performance of the micro-channel heat exchanger can be further improved.
In some embodiments, the sum of the micropore cross-sectional areas of all of the flat tubes 30 contained in each of the first set of microchannel flows F10 is greater than the sum of the micropore cross-sectional areas of all of the flat tubes 30 contained in each of the second set of microchannel flows F20. Here, the micropore cross-sectional area of the flat tube refers to the sum of cross-sectional areas of all micropores contained in the flat tube on the same cross-section.
Considering that the gaseous refrigerant and the gas-liquid two-phase refrigerant flowing in the first group of micro-channel flow F10 all have latent heat of phase change, and the gaseous refrigerant part can form more sufficient heat exchange area with the inner walls of the micropores and has higher flow velocity, the heat exchange coefficient is higher, the pressure drop is higher, the energy consumption is higher, the energy utilization efficiency is reduced, and the higher pressure drop has adverse effect on the operation stability. By combining the fact that each micro-channel flow in the first group of micro-channel flows F10 contains a large number of flat tubes, the sum of the micro-pore cross-sectional areas of all the flat tubes 30 contained in each micro-channel flow in the first group of micro-channel flows F10 is relatively large by adopting the proper micro-pore cross-sectional areas of the flat tubes, so that the flow velocity of the refrigerant in the first group of micro-channel flows F10 is effectively reduced, the pressure drop of the refrigerant in the first group of micro-channel flows F10 is reduced, the energy consumption is reduced, the energy utilization efficiency is improved, and the operation stability of the heat exchanger is improved.
Considering that the heat exchange coefficient of the liquid refrigerant flowing in the second group of micro-channel flow F20 is smaller than that of the gaseous refrigerant, the heat exchange efficiency is lower, and the heat exchange needs to be enhanced. By combining the fact that each micro-channel flow in the second group of micro-channel flows F20 contains fewer flat tubes, and adopting proper micro-pore cross sections through the flat tubes, the sum of micro-pore cross sections of all the flat tubes 30 contained in each micro-channel flow in the second group of micro-channel flows F20 can be relatively smaller, so that the flow velocity of the refrigerant is effectively improved, and the heat exchange effect is enhanced.
Since the sum of the micropore sectional areas of all the flat tubes 30 included in each of the first group of microchannel processes F10 is larger than the sum of the micropore sectional areas of all the flat tubes 30 included in each of the second group of microchannel processes F20 in the present embodiment, the ratio of the sum of the micropore sectional areas of all the flat tubes 30 included in each of the first group of microchannel processes F10 to the sum of the micropore sectional areas of all the flat tubes 30 included in each of the second group of microchannel processes F20 is larger than 1, respectively.
Considering that if this ratio is too large, it means that the sum of the micropore sectional areas of all the flat tubes 30 included in each of the first group of microchannel processes F10 exceeds the sum of the micropore sectional areas of all the flat tubes 30 included in each of the second group of microchannel processes F20 to a large extent, this may cause a drastic change in pressure of the refrigerant when flowing from the first group of microchannel processes F10 to the second group of microchannel processes F20, resulting in energy loss, leading to an increase in energy consumption. If this ratio is too small, it means that the sum of the micropore cross-sectional areas of all the flat tubes 30 included in each of the first set of micro-channel processes F10 is close to the sum of the cross-sectional areas of all the flat tubes 30 included in each of the second set of micro-channel processes F20, which would impair the effect of improving the heat exchange performance of the second set of micro-channel processes F20 and the pressure drop improvement of the first set of micro-channel processes F10.
Thus, in some embodiments, the ratio of the sum of the micropore cross-sectional areas of all the flat tubes 30 included in each of the first set of micro-channel flows F10 to the sum of the cross-sectional areas of all the flat tubes 30 included in each of the second set of micro-channel flows F20 may be 1.3 or more and 11.9 or less. Therefore, the heat exchange performance of the second group of micro-channel flows F20 and the pressure drop of the first group of micro-channel flows F10 are improved, and meanwhile, the energy consumption loss caused by pressure mutation when the refrigerant flows from the first group of micro-channel flows F10 to the second group of micro-channel flows F20 is reduced, so that the overall operation performance is improved.
Further, the ratio of the sum of the micropore sectional areas of all the flat tubes 30 included in each of the first group of microchannel processes F10 to the sum of the micropore sectional areas of all the flat tubes 30 included in each of the second group of microchannel processes F20 may be 2.17 or more and 8.5 or less. By making the ratio satisfy the preferred range of 2.17 to 8.5, the heat exchange performance of the second group of micro-channel flows F20 and the pressure drop of the first group of micro-channel flows F10 can be improved, and meanwhile, the energy consumption loss caused by the abrupt change of the pressure of the refrigerant flowing from the first group of micro-channel flows F10 to the second group of micro-channel flows F20 can be further reduced, so that the overall operation performance can be more effectively improved.
Referring to fig. 1, in some embodiments, at least one of the first header 10 and the second header 20 is divided into a plurality of header chambers by a partition plate 40, the plurality of header chambers are communicated with the plurality of flat tubes 30 to form the first group of micro-channel processes F10 and the second group of micro-channel processes F20, the first group of micro-channel processes F10 includes a single micro-channel process F11 for circulating a gaseous refrigerant in a superheated state and a refrigerant in a gas-liquid two-phase state, the single micro-channel process F11 includes 5 flat tubes, the first micro-channel process F21 includes 3 flat tubes, and the second micro-channel process F22 includes 2 flat tubes.
The liquid collecting chambers in fig. 1 are a liquid collecting chamber 41 which is positioned in the first liquid collecting pipe 10 and is communicated with the liquid inlet pipe, a liquid collecting chamber 42 which is positioned in the second liquid collecting pipe 20, a liquid collecting chamber 43 which is positioned in the first liquid collecting pipe 10 and a liquid collecting chamber 44 which is positioned in the second liquid collecting pipe 20 and is communicated with the liquid outlet pipe. The pockets 41 to 44 are in series communication in turn through the flat tube 30 in the flow direction of the refrigerant.
The first group of micro-channel flows F10 has a single micro-channel flow F11 including 5 flat tubes, and the second group of micro-channel flows F20 has two micro-channel flows, namely a first micro-channel flow F21 including 3 flat tubes and a second micro-channel flow F22 including 2 flat tubes. In the flow direction of the refrigerant (refer to black arrows in fig. 1), the numbers of flat tubes included in the three flows are sequentially 5, 3, and 2, the numbers of flat tubes included in the first microchannel flow F21 and the second microchannel flow F22 through which the liquid refrigerant in the supercooled state flows are smaller than the numbers of flat tubes included in the single microchannel flow F11 in the first group of microchannel flow F10, and the numbers of flat tubes included in the first microchannel flow F21 located upstream are larger than the numbers of flat tubes included in the second microchannel flow F22 located downstream. Therefore, the heat exchange performance of the second group of micro-channel processes F20 and the pressure drop of the first group of micro-channel processes F10 are improved, and the energy consumption loss caused by the abrupt change of the pressure of the refrigerant flowing from the first group of micro-channel processes F10 to the second group of micro-channel processes F20 and the energy consumption loss caused by the flow of the refrigerant inside the second group of micro-channel processes F20 are reduced, so that the overall operation performance is improved more effectively.
Referring to the previous embodiment, a cross matching scheme of a first group of micro-channel flows and a second group of micro-channel flows with different numbers of flat tubes is selected and a complete machine test is performed. The following table shows the test results corresponding to the 6 cross-collocation schemes.
The heat exchange amount, the system power consumption and the system refrigeration coefficient (Coefficient Of Performance, abbreviated as COP) of the flat tubes in the processes contained in the first group of micro-channel processes and the second group of micro-channel processes in the table are realized under different values. Ignoring the test error due to the test accuracy, it can be seen from the above table that in the cross collocation scheme of 1-3, the system COP may reach a better result of 3.1 or more, especially, scheme 1 may simultaneously satisfy that the ratio of the number of flat tubes contained in each micro-channel flow in the second set of micro-channel flow F20 to the number of flat tubes contained in each micro-channel flow in the first set of micro-channel flow F10 is greater than or equal to 0.4 and less than or equal to 0.6, and the ratio of the number of flat tubes contained in the first micro-channel flow F21 to the number of flat tubes contained in the second micro-channel flow F22 is greater than or equal to 1.5 and less than 2, where the COP may reach a higher 3.42.
The microchannel heat exchanger of the above embodiments may be applicable to various devices or service scenarios where heat exchange is required, such as a heat pump water heater or an air conditioner.
Accordingly, in one aspect of the present disclosure, there is provided a heat pump water heater comprising a microchannel heat exchanger of any of the preceding embodiments.
In another aspect of the disclosure, there is also provided an air conditioner comprising a microchannel heat exchanger of any of the preceding embodiments.
Thus, various embodiments of the present disclosure have been described in detail. In order to avoid obscuring the concepts of the present disclosure, some details known in the art are not described. How to implement the solutions disclosed herein will be fully apparent to those skilled in the art from the above description.
Although some specific embodiments of the present disclosure have been described in detail by way of example, it should be understood by those skilled in the art that the above examples are for illustration only and are not intended to limit the scope of the present disclosure. It will be understood by those skilled in the art that the foregoing embodiments may be modified and equivalents substituted for elements thereof without departing from the scope and spirit of the disclosure. The scope of the present disclosure is defined by the appended claims.
Claims (12)
1. A microchannel heat exchanger comprising: a first liquid collecting pipe (10), a second liquid collecting pipe (20) and a plurality of flat pipes (30), wherein one end of each flat pipe (30) is connected with the first liquid collecting pipe (10), the other end is connected with the second liquid collecting pipe (20), and a plurality of micropores (31) for communicating the first liquid collecting pipe (10) and the second liquid collecting pipe (20) are formed;
The first liquid collecting pipe (10), the second liquid collecting pipe (20) and the flat pipes (30) form a refrigerant flow path, the refrigerant flow path comprises a first group of micro-channel flows (F10) for circulating gaseous refrigerant in an overheated state and/or refrigerant in a gas-liquid two-phase state and a second group of micro-channel flows (F20) for circulating liquid refrigerant in a supercooled state, and the number of flat pipes contained in each micro-channel flow in the second group of micro-channel flows (F20) is smaller than the number of flat pipes contained in each micro-channel flow in the first group of micro-channel flows (F10).
2. The microchannel heat exchanger according to claim 1, wherein a ratio of a number of flat tubes contained in each of the second set of microchannel processes (F20) to a number of flat tubes contained in each of the first set of microchannel processes (F10) is 0.3 or more and 0.75 or less.
3. The microchannel heat exchanger according to claim 2, wherein a ratio of a number of flat tubes contained in each of the second set of microchannel processes (F20) to a number of flat tubes contained in each of the first set of microchannel processes (F10) is 0.4 or more and 0.6 or less.
4. The microchannel heat exchanger according to claim 1, wherein the second set of microchannel processes (F20) comprises at least two microchannel processes, the at least two microchannel processes being in serial communication with the first set of microchannel processes (F10) in sequence;
In the flow direction of the refrigerant in the refrigerant flow path, the number of flat tubes included in the upstream microchannel flow path in the at least two microchannel flow paths is greater than the number of flat tubes included in the downstream microchannel flow path in the at least two microchannel flow paths.
5. The microchannel heat exchanger according to claim 4, wherein the at least two microchannel processes include a first microchannel process (F21) and a second microchannel process (F22) connected in series in order in a flow direction of a refrigerant in the refrigerant flow path, and a ratio of a number of flat tubes included in the first microchannel process (F21) to a number of flat tubes included in the second microchannel process (F22) is 1 or more and less than 2.5.
6. The microchannel heat exchanger according to claim 5, wherein the ratio of the number of flat tubes contained in the first microchannel process (F21) to the number of flat tubes contained in the second microchannel process (F22) is 1.5 or more and less than 2.
7. The microchannel heat exchanger according to claim 1, wherein the sum of the micropore cross-sectional areas of all flat tubes (30) comprised by each microchannel process in the first set of microchannel processes (F10) is greater than the sum of the micropore cross-sectional areas of all flat tubes (30) comprised by each microchannel process in the second set of microchannel processes (F20).
8. The microchannel heat exchanger according to claim 7, wherein a ratio of a sum of micropore sectional areas of all flat tubes (30) included in each of the first set of microchannel processes (F10) to a sum of sectional areas of all flat tubes (30) included in each of the second set of microchannel processes (F20) is 1.3 or more and 11.9 or less.
9. The microchannel heat exchanger according to claim 7, wherein a ratio of a sum of micropore sectional areas of all flat tubes (30) included in each microchannel process in the first set of microchannel processes (F10) to a sum of micropore sectional areas of all flat tubes (30) included in each microchannel process in the second set of microchannel processes (F20) is 2.17 or more and 8.5 or less.
10. The microchannel heat exchanger according to any one of claims 1 to 9, wherein at least one of the first header (10) and the second header (20) is partitioned into a plurality of header chambers (41, 42, 43, 44) by a partition plate (40), the plurality of header chambers (41, 42, 43, 44) are in communication with the plurality of flat tubes (30) to form the first set of microchannel processes (F10) and the second set of microchannel processes (F20), the first set of microchannel processes (F10) includes a single microchannel process (F11) for circulating a gaseous refrigerant in a superheated state and a refrigerant in a gas-liquid two-phase state, the single microchannel process (F11) includes 5 flat tubes, the second set of microchannel processes (F20) includes at least two microchannel processes including a first microchannel process (F21) and a second microchannel process (F20) connected in series in the flow direction of the refrigerant in order, the first microchannel process (F21) includes a flat tube (F2), and the second microchannel process (F22) includes a flat tube (F2).
11. A heat pump water heater, comprising:
the microchannel heat exchanger of any one of claims 1 to 10.
12. An air conditioner, comprising:
the microchannel heat exchanger of any one of claims 1 to 10.
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