CN212720249U - Heat exchanger and air conditioner - Google Patents
Heat exchanger and air conditioner Download PDFInfo
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- CN212720249U CN212720249U CN202020961983.6U CN202020961983U CN212720249U CN 212720249 U CN212720249 U CN 212720249U CN 202020961983 U CN202020961983 U CN 202020961983U CN 212720249 U CN212720249 U CN 212720249U
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Abstract
The application relates to the technical field of refrigeration equipment and discloses a heat exchanger. The heat exchanger includes: the system comprises an supercooling pipe set and a heat exchange pipe set, wherein the supercooling pipe set at least comprises a first supercooling pipe section and a second supercooling pipe section along the serial direction, and the heat exchange pipe set at least comprises a first heat exchange supercooling section and a second heat exchange pipe section along the serial direction; the supercooling bypass pipe is connected with the second supercooling pipe section and the first heat exchange pipe section in parallel; the supercooling bypass pipe is provided with a supercooling one-way valve; the shunt bypass pipe is connected with the first heat exchange pipe section and the second heat exchange pipe section in parallel; the shunt by-pass pipe is provided with a shunt one-way valve. The heat exchanger provided by the embodiment of the disclosure can realize the refrigeration flow direction of a single flow path and the heating flow direction of a plurality of branches, not only can make the refrigerant fully exchange heat downwards to realize supercooling in the refrigeration flow, but also can avoid the pressure loss problem caused by overlong flow path downwards in the heating flow. The application also discloses an air conditioner of using above-mentioned heat exchanger.
Description
Technical Field
The application relates to the technical field of refrigeration equipment, for example to a heat exchanger and an air conditioner.
Background
The machine types of the existing air-conditioning products are mostly of split structures, and comprise an indoor unit and an outdoor unit which are respectively arranged indoors and outdoors, wherein an indoor heat exchanger of the indoor unit and an outdoor heat exchanger of the outdoor unit are directly used for carrying out heat exchange with the corresponding side environment, so that the indoor heat exchanger and the outdoor heat exchanger are key equipment of the air-conditioning products, and the refrigerating/heating performance of the air conditioner can be directly influenced by the heat exchange efficiency of the heat exchangers. In order to improve the refrigeration efficiency of the air conditioner during refrigeration operation, a supercooling section is additionally arranged on part of the heat exchangers so as to prolong the flow path of a high-temperature refrigerant in the heat exchangers by utilizing the supercooling section, thereby achieving the purpose of fully exchanging heat.
In the process of implementing the embodiments of the present disclosure, it is found that at least the following problems exist in the related art:
the outdoor heat exchanger is taken as an example for illustration, the existing heat exchanger generally adopts a shunt pipe or a shunt to carry out shunt design, the shunt mode has no refrigerant flow direction distinction, although the refrigerant passes through the same pipeline during the cooling operation and the heating operation, the flow directions are opposite, the refrigerant can meet the cooling operation requirement through a supercooling section during the cooling operation, and the refrigerant still passes through the supercooling section during the heating operation, so that the pressure loss of the system is increased, and the overall heat exchange efficiency of the air conditioning system is reduced.
SUMMERY OF THE UTILITY MODEL
The following presents a simplified summary in order to provide a basic understanding of some aspects of the disclosed embodiments. This summary is not an extensive overview nor is intended to identify key/critical elements or to delineate the scope of such embodiments but rather as a prelude to the more detailed description that is presented later.
The embodiment of the disclosure provides a heat exchanger and an air conditioner, and aims to solve the technical problems that the pressure loss is increased, the heat exchange efficiency is reduced and the like caused by the fact that the refrigeration/heating flow direction cannot be distinguished in the shunting design of the heat exchanger in the related art.
In some embodiments, a heat exchanger comprises:
the system comprises an supercooling pipe group and a heat exchange pipe group, wherein the supercooling pipe group and the heat exchange pipe group are connected in series, the supercooling pipe group at least comprises a first supercooling pipe section and a second supercooling pipe section along the series direction, and the heat exchange pipe group at least comprises a first heat exchange passage section and a second heat exchange pipe section along the series direction;
the supercooling bypass pipe is connected with the second supercooling pipe section and the first heat exchange pipe section in parallel; the supercooling bypass pipe is provided with a supercooling one-way valve, the conduction direction of the supercooling one-way valve is limited to flow from a first supercooling node to a second supercooling node, the first supercooling node is positioned between the first supercooling pipe section and the second supercooling pipe section, and the second supercooling node is positioned between the first heat exchange pipe section and the second heat exchange pipe section;
the shunt bypass pipe is connected with the first heat exchange pipe section and the second heat exchange pipe section in parallel; the shunting by-pass pipe is provided with a shunting one-way valve, the conduction direction of which is defined as flowing from a first shunting node to a second shunting node, wherein the first shunting node is positioned between the second supercooling pipe section and the first heat exchange pipe section, and the second shunting node is positioned on at least part of the second heat exchange pipe section.
In still other embodiments, the air conditioner includes a refrigerant circulation circuit configured by at least an indoor heat exchanger, an outdoor heat exchanger, a compressor, and a four-way valve, and the indoor heat exchanger and/or the outdoor heat exchanger are/is a heat exchanger as in the above embodiments.
The air conditioner provided by the embodiment of the disclosure can realize the following technical effects:
the heat exchanger that this disclosed embodiment provided is through the design by subcooling bypass pipe and reposition of redundant personnel bypass pipe etc for subcooling pipeline and heat exchange tube group can carry out the refrigerant with different flow paths respectively under the air conditioner mode of difference and carry out the refrigerant transport, including the refrigeration flow direction of single flow path and the heating flow direction of many branches, adopt the heat exchanger of above-mentioned reposition of redundant personnel design, not only can make the refrigerant can fully heat transfer realize "subcooling" downwards at the refrigeration flow, also can avoid the pressure loss problem that the flow path overlength leads to downwards simultaneously at the heating flow, thereby can guarantee the performance demand of heat exchanger under different mode simultaneously.
The foregoing general description and the following description are exemplary and explanatory only and are not restrictive of the application.
Drawings
One or more embodiments are illustrated by way of example in the accompanying drawings, which correspond to the accompanying drawings and not in limitation thereof, in which elements having the same reference numeral designations are shown as like elements and not in limitation thereof, and wherein:
fig. 1 is a schematic structural diagram of a heat exchanger provided in an embodiment of the present disclosure.
11, a first supercooling pipe section; 12. a second subcooled tube section; 21. a first heat exchange tube section; 22. a second heat exchange tube section; 3. a sub-cooling bypass pipe; 31. a first subcooling node; 32. a second subcooling node; 4. a bypass pipe is shunted; 41. a first shunting node; 42. a second shunting node; 5. a super-cooling one-way valve; 6. a shunt one-way valve.
Detailed Description
So that the manner in which the features and elements of the disclosed embodiments can be understood in detail, a more particular description of the disclosed embodiments, briefly summarized above, may be had by reference to the embodiments, some of which are illustrated in the appended drawings. In the following description of the technology, for purposes of explanation, numerous details are set forth in order to provide a thorough understanding of the disclosed embodiments. However, one or more embodiments may be practiced without these details. In other instances, well-known structures and devices may be shown in simplified form in order to simplify the drawing.
Fig. 1 is a schematic structural diagram of a heat exchanger provided in an embodiment of the present disclosure, in which solid arrows indicate a cooling flow direction, and dashed arrows indicate a heating flow direction.
As shown in fig. 1, an embodiment of the present disclosure provides a heat exchanger including an supercooling pipe set and a heat exchange pipe set. The supercooling function of the supercooling pipe set is realized by heat exchange between the refrigerant and the environment where the refrigerant is located, and the principle of realizing the supercooling function is that the supercooling pipe set can play a role of prolonging the length of a refrigerant flow path downwards to increase the heat exchange time duration when the refrigerant flows downwards, so that the purpose of supercooling at lower temperature of the refrigerant is realized; that is to say, the supercooling pipe group and the heat exchange pipe group both have the capacity of enabling the refrigerant flowing through the supercooling pipe group to exchange heat with the surrounding environment, so that the supercooling pipe group can still exchange heat with the surrounding environment like the heat exchange pipe group when the heating flow is downward, the supercooling pipe group is arranged in such a way, the refrigerating flow can be used for supercooling the refrigerant downward to improve the refrigerating efficiency, and meanwhile, the heating flow can be used as a branch pipeline to exchange heat downward to improve the heating efficiency.
In the embodiment, the single pipe structures forming the supercooling pipe group and the heat exchange pipe group adopt the same structural design, for example, the pipe diameters of the single pipes of the supercooling pipe group and the heat exchange pipe group are consistent, the pipe wall thicknesses are uniform, the curvature and the length of the bent pipe are the same, and the like, so that the refrigerant can uniformly flow in the heat exchanger, the unstable changes of the pressure and the flow speed of the refrigerant caused by the change of the pipe diameters are avoided, and the refrigerant can stably realize heat exchange with the surrounding environment when flowing through the heat exchanger.
For the convenience of the following explanation of the structure of the heat exchanger of the present application, the tube body forming the supercooling tube group is defined as the supercooling tube, and the tube body forming the heat exchange tube group is defined as the heat exchange tube, and the above tube body definition mainly aims at dividing the refrigerant acting on each lower part tube group by the refrigerant flow, but does not limit the structural design of the tube body of the heat exchanger of the present application, the heat exchange effect of the heating flow direction, and the like.
The heat exchanger is provided with a supercooling bypass pipe 3 and a shunt bypass pipe 4, wherein the supercooling bypass pipe 3 and the shunt bypass pipe 4 are respectively matched with part of pipe sections of a corresponding supercooling pipe group and a corresponding heat exchange pipe group to form parallel pipelines so as to form a single flow path in the downward direction of a refrigerating flow and a multi-branch flow path in the downward direction of the refrigerating flow.
In some optional embodiments, both the supercooling tube set and the heat exchange tube set of the heat exchanger are connected in series, and it should be noted that in the flow dividing design of the heat exchanger of the present application, the refrigerant flows downward to be a single flow path, and the heating flows downward to be a multi-branch flow path, so the series connection is defined by the matching relationship between the tube sets of each part of the heat exchanger that the refrigerant flows downward. The single flow path design enables all refrigerants to flow through the heat exchange tube set and the supercooling tube set and exchange heat with the surrounding environment in real time when flowing through the two part tube sets, the refrigerant flow path is long in whole length and long in heat exchange time, and the refrigerants can fully exchange heat with the surrounding environment.
In some alternative embodiments, the subcooling tube bank is divided into at least a first subcooling tube section 11 and a second subcooling tube section 12 along a serial direction, the serial direction is the opposite direction of the downward direction of the refrigeration flow, that is, the refrigeration flow is downward, the refrigerant flows through the second subcooling tube section 12 first and then flows through the first subcooling tube section 11, and both the first subcooling tube section 11 and the second subcooling tube section 12 can perform a "subcooling" function.
Optionally, the first subcooling section 11 comprises one or more subcooling tubes and the second subcooling section 12 comprises one or more subcooling tubes. The specific arrangement number of the supercooling pipes of each supercooling pipe section can be adjusted adaptively according to heat exchange requirements.
Optionally, the number of the supercooled tubes of the first supercooled tube section 11 is equal to the number of the supercooled tubes of the second supercooled tube section 12, for example, the number of the supercooled tubes of the first supercooled tube section 11 is 15, and the number of the supercooled tubes of the second supercooled tube section 12 is also 15.
Optionally, the number of the supercooled tubes of the first supercooled tube segment 11 is less than the number of the supercooled tubes of the second supercooled tube segment 12, and for example, the number of the supercooled tubes of the first supercooled tube segment 11 is 5, and the number of the supercooled tubes of the second supercooled tube segment 12 is also 15, which has an advantage that, in the heating mode, the second supercooled tube segment 12 is a branch tube segment for heat exchange, and the first supercooled tube segment 11 is a confluence tube segment for each branch tube segment, so that the second supercooled tube segment 12 is provided with more supercooled tubes, which enables the refrigerant flowing through the second supercooled tube segment 12 to fully exchange heat, and the first supercooled tube segment 11 is provided with less supercooled tubes, which can reduce the overall pressure loss of the converged refrigerant in the tube segment.
In some alternative embodiments, the number of the supercooling pipes of the supercooling pipe group is at least one third of the total number of the pipe bodies of the heat exchanger, so that the refrigerant can fully release heat when flowing through the supercooling pipe group to be reduced to a lower refrigerant temperature. Here, the total number of tube bodies of the heat exchanger is the sum of the number of the supercooling tubes of the supercooling tube bank and the number of the heat exchange tubes of the heat exchange tube bank.
Illustratively, when the total number of tube bodies of the heat exchanger is 90, the number of the supercooling tubes of the supercooling tube group is 32, 35, 37, and the like.
Optionally, the number ratio between the number of the supercooling pipes of the supercooling pipe group and the number of the heat exchange pipes of the heat exchange pipe group is 1:2, for example, when the total number of pipe bodies of the heat exchanger is 90, the number of the supercooling pipes of the supercooling pipe group is 30, and the number of the heat exchange pipes of the heat exchange pipe group is 60.
In some alternative embodiments, the heat exchange tube bank is divided into at least a first heat exchange pass section and a second heat exchange tube section 22 along the aforementioned series direction; when the refrigerant flows downwards, the refrigerant flows into the heat exchanger from the second heat exchange tube section 22, flows through the second heat exchange tube section 22 first and then flows through the first heat exchange tube section 21, and both the first heat exchange tube section 21 and the second heat exchange tube section 22 can play a role in heat exchange. In this embodiment, the heat exchange tube bank and the subcooling tube bank are connected in series, so that the refrigerant flows to the second subcooling tube section 12 after flowing through the first heat exchange tube section 21.
Optionally, the first heat exchange tube section 21 comprises one or more heat exchange tubes and the second heat exchange tube section 22 comprises one or more heat exchange tubes. The specific arrangement number of the heat exchange tubes of each heat exchange tube section can be adaptively adjusted according to heat exchange requirements.
Optionally, the number of the heat exchange tubes of the first heat exchange tube section 21 is equal to the number of the heat exchange tubes of the second heat exchange tube section 22, for example, the number of the heat exchange tubes of the first heat exchange tube section 21 is 30, and the number of the heat exchange tubes of the second heat exchange tube section 22 is also 30.
As yet another alternative, the number of the heat exchange tubes of the first heat exchange tube section 21 is greater than the number of the heat exchange tubes of the second heat exchange tube section 22, for example, the number of the heat exchange tubes of the first heat exchange tube section 21 is 40, and the number of the heat exchange tubes of the second heat exchange tube section 22 is 20; the quantity setting mode has the advantages that in the heating mode, the inflow node of the second heat exchange tube section 22 is the second supercooling node 32, the outflow node is the second flow dividing node 42, the refrigerant pressure of the second flow dividing node 42 is influenced by the refrigerant pressure of the first flow dividing node 41, and the refrigerant of the first flow dividing node 41 is the sum of the refrigerants flowing through the second supercooling tube section 12 and the first heat exchange tube section 21, so that the problem that the refrigerant flowing in the second heat exchange tube section 22 is not smooth due to overhigh refrigerant pressure of the second flow dividing node 42 is solved, the number of heat exchange tubes of the first heat exchange tube section 21 is increased, the pressure loss of the refrigerant flowing through the first heat exchange tube section 21 is increased, and the refrigerant pressure of the second flow dividing node 42 is reduced.
In some alternative embodiments, the subcooling bypass pipe 3 is connected in parallel with the second subcooling pipe section 12 and the first heat exchange pipe section 21; the supercooling bypass pipe 3 is provided with a supercooling check valve 5 whose conducting direction is defined as flowing from a first supercooling node 31 to a second supercooling node 32, wherein the first supercooling node 31 is located between the first supercooling pipe section 11 and the second supercooling pipe section 12, and the second supercooling node 32 is located between the first heat exchange pipe section 21 and the second heat exchange pipe section 22.
When the refrigerant flows downwards, the refrigerant flows through the second heat exchange tube section 22 and then reaches the second supercooling node 32, a branch flow path of the second supercooling node 32 flows to the first heat exchange tube section 21, and the branch flow path is in a conducting state; the other branch flow path of the second supercooling node 32 flows through the supercooling bypass pipe 3, and the flow direction is opposite to the conduction flow direction defined by the supercooling check valve 5, so that the branch flow path is in a blocking state, and a refrigerant flowing downwards in the refrigeration flow can keep a single flow path at the second supercooling node 32; then, the refrigerant reaches the first supercooling node 31 after flowing through the second supercooling section 12, a branch flow path of the first supercooling node 31 flows to the first supercooling section 11, and the branch flow path is in a conducting state; the other branch flow path of the first supercooling node 31 is directed to the supercooling bypass pipe 3, and since the refrigerant pressure on the second supercooling node 32 side is higher than that on the first supercooling node 31 side, the branch flow path is blocked and the refrigerant does not flow through the supercooling bypass pipe 3 although the supercooling check valve 5 is in the on state.
When the heating flow is downward, the refrigerant reaches the first supercooling node 31 after flowing through the first supercooling pipe section 11, a branch flow path of the first supercooling node 31 flows to the second supercooling pipe section 12, and the branch flow path is in a conducting state; the other branch flow path of the first subcooling node 31 reaches the second subcooling node 32 after passing through the subcooling bypass pipe 3, and is branched again at the second subcooling node 32, and the two branch flow paths pass through the first heat exchange tube section 21 and the second heat exchange tube section 22 respectively.
In some embodiments, the bypass branch 4 is connected in parallel with the first heat exchange tube section 21 and the second heat exchange tube section 22; the bypass branch conduit 4 is provided with a branch check valve 6 having a direction of conduction defined from a first branch junction 41 to a second branch junction 42, wherein the first branch junction 41 is located between the second subcooling section 12 and the first heat exchange section 21 and the second branch junction 42 is located on at least a portion of the second heat exchange section 22.
The refrigerant flows downwards, the refrigerant is divided at a second division node 42, one branch flow path of the second division node 42 flows to the second heat exchange tube section 22, and the branch flow path is in a conducting state; the other branch flow path of the second branch node 42 is a branch bypass pipe 4, and the flow direction is opposite to the conduction flow direction defined by the branch check valve 6, so that the branch flow path is in a blocking state, and a refrigerant flowing downwards in the refrigeration flow can keep a single flow path at the second branch node 42; then, the refrigerant flows through the second heat exchange tube section 22 and the first heat exchange tube section 21 and reaches the first branch node 41, a branch flow path of the first branch node 41 flows to the second supercooling tube section 12, and the branch flow path is in a conducting state; the other branch flow path of the first branch node 41 is directed to the branch bypass pipe 4, and the refrigerant pressure on the second branch node 42 side is higher than that on the first branch node 41 side, so that the branch flow path is blocked and the refrigerant does not flow through the branch bypass pipe 4 even though the branch check valve 6 is in the on state.
In the heating flow direction, the refrigerant flows through the second subcooling section 12 and then reaches the first branch point 41, one branch flow path of the first branch point 41 flows to the first heat exchange tube section 21, and it can be known from the foregoing that at this time, the refrigerant in the first heat exchange tube section 21 flows to the first branch point 41, so that the two portions of the refrigerant flow together and then flow to the other branch flow path, and the other branch flow path flows through the branch bypass tube 4 and then reaches the second branch point 42, and finally flows out of the heat exchanger.
Here, to the first supercooling pipe section 11 that sets up, the heating flow is downward, the refrigerant flows into the heat exchanger from first supercooling pipe section 11, and shunt after flowing through first supercooling pipe section 11, and there is pressure loss when refrigerant reposition of redundant personnel node is shunted, velocity of flow when the refrigerant flows to reposition of redundant personnel node can influence pressure loss's height, consequently this application is for reducing pressure loss, make the refrigerant carry out certain heat exchange in first supercooling pipe section 11 department before shunting, reduce the refrigerant velocity of flow through the mode that reduces the refrigerant heat, thereby make the pressure of refrigerant loss when shunting can further reduce. In this way, the first subcooling pipe section 11 can not only perform the "subcooling" function in the cooling mode, but also reduce the pressure loss during the split flow in the heating mode, so that the first subcooling pipe section 11 can perform the gain function for the cooling/heating flow downward.
In connection with the embodiments illustrated in the figures, the subcooling tube bank and the heat exchange tube bank are constructed in a single-column arrangement; in yet another embodiment, not shown, the banks of subcooling tubes and the banks of heat exchange tubes are configured in a multi-column arrangement, such as a two-column, three-column arrangement, or the like. The concrete form of arranging of supercooling nest of tubes and heat exchange tube group can be selected according to the actual heat transfer demand of heat exchanger, and this application is not limited to this.
In the above embodiments, the free end of the first supercooling section 11 of the supercooling pipe set is the first refrigerant port of the heat exchanger, and the free end of the second heat exchange section 22 of the heat exchange pipe set is the second refrigerant port of the heat exchanger.
Optionally, in the cooling mode and when the heat exchanger is used as an outdoor heat exchanger, the first refrigerant port is a port through which a refrigerant flows out, and the second refrigerant port is a port through which a refrigerant flows in; when the heat exchanger is used as an outdoor heat exchanger in the heating mode, the first refrigerant port is used as a refrigerant inflow port, and the second refrigerant port is used as a refrigerant outflow port.
Optionally, when the heat exchanger is used as an indoor heat exchanger in the cooling mode, the first refrigerant port is a port through which a refrigerant flows in, and the second refrigerant port is a port through which a refrigerant flows out; when the heat exchanger is used as an indoor heat exchanger in the heating mode, the first refrigerant port is used as a refrigerant outflow port, and the second refrigerant port is used as a refrigerant inflow port.
Further, an embodiment of the present disclosure further provides an air conditioner, which includes a refrigerant circulation loop configured by at least an indoor heat exchanger, an outdoor heat exchanger, a compressor, and a four-way valve, wherein the indoor heat exchanger and/or the outdoor heat exchanger of the air conditioner is the heat exchanger as shown in any one of the foregoing embodiments.
The air conditioner adopting the heat exchanger shown in the embodiment can respectively convey the refrigerant in the refrigerating flow direction of the single flow path and the heating flow direction of the multiple branches when the air conditioner runs in the refrigerating mode or the heating mode, not only can enable the refrigerant to fully exchange heat to realize supercooling under the refrigerating flow direction, but also can avoid the problem of pressure loss caused by overlong flow paths under the heating flow direction, and therefore the performance requirements of the heat exchanger under different working modes can be simultaneously met.
Optionally, when the outdoor heat exchanger is a heat exchanger, the second heat exchange tube section 22 of the heat exchanger is communicated with the compressor, and the first supercooling tube section 11 is communicated with the indoor heat exchanger. Therefore, when the refrigerant flows downwards, the high-temperature refrigerant discharged from the compressor enters the heat exchanger from the second heat exchange tube section 22, sequentially flows through the first heat exchange tube section 21, the second supercooling tube section 12 and the first supercooling tube section 11 according to a single flow path, then flows out of the heat exchanger, and flows into the indoor heat exchanger after being throttled. The first supercooling pipe section 11 and the second supercooling pipe section 12 can extend the length and duration of a path for heat exchange between a high-temperature refrigerant and an outdoor environment, so that the high-temperature refrigerant can reach a lower temperature after flowing through an outdoor heat exchanger, and the refrigeration performance is improved.
As a further alternative, when the indoor heat exchanger is a heat exchanger, the second heat exchange tube section 22 of the heat exchanger is communicated with the compressor, and the first supercooling tube section 11 is communicated with the outdoor heat exchanger. Therefore, in the heating flow direction, the high-temperature refrigerant discharged from the compressor enters the heat exchanger from the second heat exchange tube section 22, sequentially flows through the first heat exchange tube section 21, the second supercooling tube section 12 and the first supercooling tube section 11 according to a single flow path, then flows out of the heat exchanger, and flows into the indoor heat exchanger after being throttled. The first supercooling pipe segment 11 and the second supercooling pipe segment 12 can extend the length and duration of a path for heat exchange between a high-temperature refrigerant and an indoor environment, so that heat of the high-temperature refrigerant can be greatly transferred to the indoor environment, and the heating performance is improved.
It is to be understood that the present invention is not limited to the procedures and structures that have been described above and shown in the drawings, and that various modifications and changes may be made without departing from the scope thereof. The scope of the present invention is limited only by the appended claims.
Claims (10)
1. A heat exchanger, comprising:
the system comprises an supercooling pipe set and a heat exchange pipe set, wherein the supercooling pipe set is connected in series and at least comprises a first supercooling pipe section and a second supercooling pipe section along the series direction, and the heat exchange pipe set at least comprises a first heat exchange pipe section and a second heat exchange pipe section along the series direction;
the supercooling bypass pipe is connected with the second supercooling pipe section and the first heat exchange pipe section in parallel; the supercooling bypass pipe is provided with a supercooling one-way valve, and the conduction direction of the supercooling one-way valve is limited to flow from a first supercooling node to a second supercooling node, wherein the first supercooling node is positioned between the first supercooling pipe section and the second supercooling pipe section, and the second supercooling node is positioned between the first heat exchange pipe section and the second heat exchange pipe section;
a bypass line connected in parallel with the first heat exchange tube section and the second heat exchange tube section; the bypass branch pipe is provided with a branch check valve, and the conduction direction of the bypass branch pipe is defined to flow from a first branch node to a second branch node, wherein the first branch node is positioned between the second supercooling pipe section and the first heat exchange pipe section, and the second branch node is positioned on at least part of the second heat exchange pipe section.
2. The heat exchanger of claim 1, wherein the subcooling tube bank and the heat exchange tube bank are configured in a single-column arrangement or a multiple-column arrangement.
3. The heat exchanger of claim 1, wherein the free end of the first subcooling tube section of the subcooling tube bank is a first refrigerant port of the heat exchanger;
and the free end of the second heat exchange pipe section of the heat exchange pipe set is a second refrigerant port of the heat exchanger.
4. The heat exchanger of claim 1, wherein the number of subcooling tubes of the bank of subcooling tubes is at least one-third of the total number of tubes of the heat exchanger.
5. The heat exchanger of claim 4, wherein the number of subcooling tubes of the first subcooling tube section is less than the number of subcooling tubes of the second subcooling tube section.
6. The heat exchanger according to claim 4, wherein the number ratio between the number of the supercooling tubes of the supercooling tube group and the number of the heat exchange tubes of the heat exchange tube group is 1: 2.
7. The heat exchanger as recited in claim 1 wherein the number of heat exchange tubes of the first heat exchange tube section is greater than or equal to the number of heat exchange tubes of the second heat exchange tube section.
8. An air conditioner comprising a refrigerant circulation circuit constructed of at least an indoor heat exchanger, an outdoor heat exchanger, a compressor, and a four-way valve, wherein the indoor heat exchanger and/or the outdoor heat exchanger is the heat exchanger according to any one of claims 1 to 7.
9. The air conditioner according to claim 8, wherein when the outdoor heat exchanger is the heat exchanger, the second heat exchange tube section of the heat exchanger is in communication with the compressor, and the first subcooling tube section is in communication with the indoor heat exchanger.
10. The air conditioner according to claim 8 or 9, wherein when the indoor heat exchanger is the heat exchanger, the second heat exchange pipe section of the heat exchanger is in communication with the compressor, and the first supercooling pipe section is in communication with the outdoor heat exchanger.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202020961983.6U CN212720249U (en) | 2020-05-27 | 2020-05-27 | Heat exchanger and air conditioner |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202020961983.6U CN212720249U (en) | 2020-05-27 | 2020-05-27 | Heat exchanger and air conditioner |
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| CN212720249U true CN212720249U (en) | 2021-03-16 |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111895501A (en) * | 2020-08-07 | 2020-11-06 | 南京天加环境科技有限公司 | Air conditioner indoor unit |
| CN114440321A (en) * | 2022-02-09 | 2022-05-06 | 珠海格力电器股份有限公司 | Heat exchanger and air conditioner |
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2020
- 2020-05-27 CN CN202020961983.6U patent/CN212720249U/en active Active
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111895501A (en) * | 2020-08-07 | 2020-11-06 | 南京天加环境科技有限公司 | Air conditioner indoor unit |
| CN114440321A (en) * | 2022-02-09 | 2022-05-06 | 珠海格力电器股份有限公司 | Heat exchanger and air conditioner |
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