Patent Application
20240328723
This application is based on and claims priority to Chinese Patent Application No. 202320725217.3 filed on Mar. 31, 2023, the entire contents of which are incorporated herein by reference for all purposes.
The present disclosure relates to the field of heat exchange devices, and in particular to a heat exchanger.
A refrigerant vapor in a compression system will become into a gas-liquid two-phase state after passing through a throttling device and then arrives at an inlet of an evaporator. The gas-liquid separation of the gas-liquid two-phase refrigerant will lead to uneven distribution of the refrigerant entering the heat exchange tube. Some channels have less liquid flow rate and evaporate prematurely, thus resulting in a too large superheat at the channel outlet. However, some channels have too much liquid flow rate, thus resulting in a too little superheat at the channel outlet. Both of the above two make the heat exchange area of the evaporator not fully utilized. Thus, whether the two-phase refrigerant fluid, especially the liquid in it, can be evenly distributed into each channel for heat exchange is the key for the design and structure of the evaporator.
Embodiments of the present disclosure provide a heat exchange, and the heat exchanger includes a heat exchange tube, a first tube, a second tube and an inlet tube. The first tube and the second tube extend and are arranged along a length direction of the heat exchanger, and the inlet tube is connected with the first tube. The heat exchange tube is connected with the first tube and the second tube, and has a plurality of flow channels communicated with the first tube and the second tube. The heat exchange tube at least includes a first heat exchange tube and a second heat exchange tube, and a flow inlet of the first heat exchange tube and a flow inlet of the second heat exchange tube are both arranged in a tube cavity of the first tube. There is a height difference between the flow inlet of the first heat exchange tube and the flow inlet of the second heat exchange tube in a height direction of the heat exchanger.
Hereinafter, embodiments of the present disclosure will be described in detail, examples of which are illustrated in the accompanying drawings. The embodiments described below by referring to the accompanying drawings are illustrative and are intended to explain the present disclosure, and should not be construed as limiting the present disclosure.
A heat exchanger 100 according to an embodiment of the present disclosure will be described below with reference to
The heat exchanger 100 of the embodiment of the present disclosure includes a heat exchange tube 4, a first tube 1, a second tube 2 and an inlet tube 3.
The first tube 1 and the second tube 2 extend along a length direction of the heat exchanger (for example, a left-right direction shown in
The flow inlet is defined as a port through which the liquid or gaseous refrigerant correspondingly flows into the first heat exchange tube 41 or the second heat exchanger tube 42. The first heat exchange tube 41 has a first heat exchange cavity, a first flow inlet and a first flow outlet, and the first flow inlet is the flow inlet of the first heat exchange tube 41. The second heat exchange tube 42 has a second heat exchange cavity, a second flow inlet and a second outlet, and the flow second inlet is the flow inlet of the second heat exchange tube 42.
When the refrigerant enters the first tube 1 from the inlet tube 3, part of the gaseous refrigerant will be mixed into the liquid refrigerant. Therefore, when the liquid refrigerant mixed with the gaseous refrigerant enters the first tube 1 from the inlet tube 3, the cavitation will occur. As a result, the refrigerant in the first tube 1 is stirred and is unable to be evenly and timely distributed into each heat exchange tube 4. Furthermore, the refrigerant continuously enters part of the heat exchange tubes 4 due to the cavitation, resulting in an excessive flow rate in the part of the heat exchange tubes 4 and a corresponding increase in a flow speed of the refrigerant in the tube cavity. Thus, part of the liquid refrigerant may be carried and bypassed to an outlet of the evaporator, thereby resulting in a liquid hammer phenomenon of a compressor and causing damages on the compressor. The other part of the heat exchange tubes 4 enter an overheated state prematurely due to the entry of a small amount of the refrigerant.
In the heat exchanger 100 according to the embodiments of the present disclosure, based on the principle of different densities of the liquid refrigerant and the gaseous refrigerant, the flow inlet of the first heat exchange tube 41 has the height difference relative to the flow inlet of the second heat exchange tube 42 in the height direction of the heat exchanger 100, and the gaseous refrigerant is timely discharged through the higher flow inlet of the second heat exchange tube 42, thus avoiding the problem of cavitation caused by the gaseous refrigerant stirring the liquid refrigerant. As a result, the liquid refrigerant may be evenly distributed in the flow inlet of the first heat exchange tube 41. That is, the flow inlet of the first heat exchange tube 41 has the height difference relative to the flow inlet of the second heat exchange tube 42 in the height direction of the heat exchanger 100, which creates a condition for the timely discharge of the gaseous refrigerant in the first tube 1. Thus, the heat exchanger 100 in the embodiments of the present disclosure optimizes the distribution of the refrigerant and improves the heat exchange efficiency of the heat exchange tube 4.
Therefore, the heat exchanger 100 of the embodiment of the present disclosure has the advantages of optimizing the distribution of the refrigerant and improving the heat exchange efficiency of the heat exchange tube 4.
The heat exchange tube 4 has a plurality of spiral flow channels to improve the heat exchange area and the heat exchange effect of the flow channel.
As shown in
In the heat exchanger 100 of the embodiment of the present disclosure, the first end portion 411 is higher than the second end portion 412 in the height direction of the heat exchanger, and the length of the first heat exchange tube 41 inserted into the tube cavity of the first tube 1 is smaller than the length of the second heat exchange tube 42 inserted into the tube cavity of the first tube 1. Therefore, the first heat exchange tube 41 and the second heat exchange tube 42 have the advantages of a simple structure and convenient installation.
Specifically, as shown in
In some embodiments, the first heat exchange tube 41 may be a straight tube, and both ends of the straight tube are connected to the first tube 1 and the second tube 2 in a one-to-one correspondence.
The embodiments of the present disclosure are not limited to this. For example, in other embodiments, as shown in
The embodiments of the present disclosure are not limited to this. For example, in other embodiments, as shown in
Specifically, as shown in
The embodiments of the present disclosure are not limited to this. For example, in other embodiments, in the height direction of the heat exchanger, as shown in
As shown in
The heat exchanger 100 of the embodiment of the present disclosure has the advantage of improving the heat exchange efficiency of the heat exchanger 100 by arranging the plurality of the first heat exchange tubes 41 and the plurality of second heat exchange tubes 42. In addition, in the heat exchanger 100 of the embodiment of the present disclosure, the inlet tube 3 is arranged at the end of the first tube 1, and the first heat exchange tube group is arranged closer to the inlet tube 3, to avoid the influence of the increased height of the second heat exchange tube 42 on the flow of the refrigerant in the first tube 1. Because the higher second heat exchange tube 42 will block and stir the refrigerant in the first tube 1. Furthermore, by arranging the second heat exchange tube 42 on the side away from the inlet tube 3 relative to the first heat exchange tube 41, it is possible to avoid stirring the refrigerant and affecting the reasonable distribution of the refrigerant. Therefore, the heat exchanger 100 of the embodiment of the present disclosure has the advantage of further optimizing the distribution rationality of the refrigerant, thereby improving the heat exchange efficiency of the heat exchanger 100.
Further, the height of the flow inlet of the first heat exchange tube group increases in a direction from the end of the first tube 1 where the inlet tube 3 is to the other end of the first tube 1.
In some embodiments, along the length direction of the heat exchanger, the heights of the flow inlets of the first heat exchange tube group gradually increase from the end of the first tube 1 where the inlet tube 3 is to the other end of the first tube 1.
Similarly, along the length direction of the heat exchanger, the heights of the flow inlets of the second heat exchange tube group increase from the end of the first tube 1 where the inlet tube 3 is to the other end of the first tube 1.
The embodiments of the present disclosure are not limited to this. For example, in other embodiments, the second heat exchange tube 42 may be arranged between two adjacent first heat exchange tubes 41.
The embodiments of the present disclosure are not limited to this. For example, in other embodiments, the heat exchanger 100 further includes a third heat exchange tube 43, which is located between the first heat exchange tube group and the second heat exchange tube group in the length direction of the heat exchanger, and a flow inlet of the third heat exchange tube 43 is located between the flow inlet of the first heat exchange tube 41 and the flow inlet of the second heat exchange tube 42 in the height direction of the heat exchanger. Therefore, the distribution of the refrigerant can be better optimized and the heat exchange efficiency of the heat exchange tube 4 can be improved.
For example, as shown in
In the heat exchanger 100 of the embodiment of the present disclosure, the first side portion 413 is lower than the second side portion 414 in the height direction of the heat exchanger. Therefore, the gaseous refrigerant can be discharged in time through the higher second side portion 414, and the problem of the uneven distribution of the gas-liquid mixed refrigerant caused by the cavitation can be avoided. Thus, the heat exchanger 100 of the embodiment of the present disclosure has the advantages of further optimizing the distribution of the refrigerant and improving the heat exchange efficiency of the heat exchange tube 4.
Further, a width direction of the first heat exchange tube 41 is consistent with a windward direction, and the first heat exchange tube 41 has the first side portion 413 and the second side portion 414 arranged opposite to each other along the width direction of the first heat exchange tube 41. The first side portion 413 is arranged adjacent to a windward side, and the first side portion 413 is lower than the second side portion 414 in the height direction of the heat exchanger.
Specifically, as shown in
As shown in
Specifically, a width direction of the second heat exchange tube 42 is consistent with the windward direction, and the second heat exchange tube 42 has the third side portion 421 and the fourth side portion 422 arranged opposite to each other along the width direction of the second heat exchange tube 42, the third side portion 421 is arranged adjacent to the windward side, and a height of the third side portion 421 is smaller than a height of the fourth side portion 422 in the height direction of the heat exchanger. In the same way, the heat exchanger 100 of the embodiment of the present disclosure further improves the heat exchange efficiency of the whole first heat exchange tube 41.
As shown in
In the heat exchanger 100 of the embodiment of the present disclosure, the flow inlet of the first heat exchange tube 41 includes the first through hole 415, and/or the flow inlet of the second heat exchange tube 42 includes the second through hole 423. Therefore, the speed at which the refrigerant enters the first heat exchange tube 41 and/or the second heat exchange tube 42 can be increased. Thus, the heat exchanger 100 of the embodiment of the present disclosure has the advantage of further improving the heat exchange efficiency.
In some embodiments, the first through hole 415 may be formed in a side wall of the first heat exchange tube 41, for example, as shown in
Further, the flow inlet of the first heat exchange tube 41 may include a port of the first heat exchange tube 41 and/or the first through hole 415, and the flow inlet of the second heat exchange tube 42 may include a port of the second heat exchange tube 42 and/or the second through hole 423.
The height difference between the flow inlet of the first heat exchange tube 41 and the flow inlet of the second heat exchange tube 42 in the height direction of the heat exchanger is ΔH, the hydraulic diameter of the first tube 1 is D, and ΔH and D satisfy a condition: 1/12D<ΔH<D.
In the heat exchanger 100 of the embodiment of the present disclosure, the height difference ΔH between the flow inlet of the first heat exchange tube 41 and the flow inlet of the second heat exchange tube 42 in the height direction of the heat exchanger and the hydraulic diameter of the first tube 1 D satisfy the condition of 1/12D<ΔH<D, so that the problem that the end portion of the second heat exchange tube 42 abuts against the wall surface of the first tube 1 due to a too large height difference, which otherwise will result in the inability to circulate the refrigerant, can be avoided, and the problem that the gas-liquid separation cannot be realized due to a too small height difference can be avoided.
A ratio of a total cross-sectional area of the flow channels of the second heat exchange tube 42 to a total cross-sectional area of the flow channels of the first heat exchange tube 41 is more than or equal to 0.05 and less than or equal to 0.5.
In the heat exchanger 100 of the embodiment of the present disclosure, the ratio of the cross-sectional area of the flow channels of the second heat exchange tube 42 to the cross-sectional area of the flow channels of the first heat exchange tube 41 is greater than or equal to 0.05 and less than or equal to 0.5. Therefore, this may avoid a too large ratio, which otherwise will cause the inability of the liquid refrigerant to enter the part of the heat exchange tube 4 with the high height and hence cause the problem of the low overall heat exchange efficiency, even though the gaseous refrigerant may be timely exported. Moreover, this may also avoid the problem that the ratio is too small to timely discharge the gaseous refrigerant in the first tube 1, which otherwise will result in poor refrigerant distribution rationality.
As shown in
The embodiments of the present disclosure are not limited to this. For example, in other embodiments, as shown in
Specifically, the first heat exchange tube 41 may have one of a V shape, a U shape, a S shape and a serpentine shape. The second heat exchange tube 42 may have one of a V shape, a S shape and a serpentine shape. Thus, the gaseous refrigerant in the first heat exchange tube 41 and the second heat exchange tube 42 can fully exchange heat with the air.
In some embodiments, the shape of the first heat exchange tube 41 may be selected to be consistent with the shape of the second heat exchange tube 42.
In the description of the present disclosure, it should be understood that the orientation or positional relationship indicated by the terms “center”, “longitudinal”, “transverse”, “length”, “width”, “thickness”, “up”, “down”, “front”, “back”, “left”, “right”, “vertical”, “horizontal”, “top”, “bottom”, “inside”, “outside”, “clockwise”, “counterclockwise”, “axial”, “radial” and “circumferential” and the like, is based on the orientation or positional relationship shown in the attached drawings, which is only for the convenience of describing the present disclosure and simplifying the description, and does not indicate or imply that the referred device or element must have a specific orientation, and be constructed and operated in a specific orientation, so it cannot be understood as a limitation of the present disclosure.
In addition, the terms “first” and “second” are only used for purpose of description, and cannot be understood as indicating or implying relative importance or implicitly indicating the number of indicated technical features. Therefore, the feature defined as “first” or “second” may explicitly or implicitly include at least one such feature. In the description of the present disclosure, “a plurality of” means at least two, such as two, three, etc., unless otherwise specifically defined.
In the present disclosure, unless otherwise expressly defined, terms such as “install”, “interconnect”, “connect”, “fix” shall be understood broadly, and may be, for example, fixed connections, detachable connections, or integral connections; may also be mechanical or electrical connections or intercommunication; may also be direct connections or indirect connections via intervening media; may also be inner communications or interactions of two elements. For those skilled in the art, the specific meaning of the above terms in the present disclosure can be understood according to the specific situations.
In the present disclosure, unless otherwise expressly defined and specified, a structure in which a first feature is “on” or “under” a second feature may include an embodiment in which the first feature is in direct contact with the second feature, or may further include an embodiment in which the first feature and the second feature are in indirect contact through intermediate media. Furthermore, a first feature “on”, “above”, or “on top of” a second feature may include an embodiment in which the first feature is right or obliquely “on”, “above”, or “on top of” the second feature, or just means that the first feature is at a height higher than that of the second feature, while a first feature “below”, “under”, or “on bottom of” a second feature may include an embodiment in which the first feature is right or obliquely “below”, “under”, or “on bottom of” the second feature, or just means that the first feature is at a height lower than that of the second feature.
In the description of the present disclosure, terms such as “an embodiment”, “some embodiments”, “an example”, “a specific example” or “some examples” means that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the present disclosure. Thus, the appearances of these terms in various places throughout this specification are not necessarily referring to the same embodiment or example of the present disclosure. Furthermore, the particular features, structures, materials, or characteristics may be combined in any suitable manner in one or more embodiments or examples. In addition, without contradiction, those skilled in the art may combine and unite different embodiments or examples or features of the different embodiments or examples described in this specification.
Although the embodiments of the present disclosure have been shown and described above, it can be understood that the above embodiments are illustrative and shall not be understood as limitation to the present disclosure, and changes, modifications, alternatives and variations can be made in the above embodiments within the scope of the present disclosure by those skilled in the art.
| Number | Date | Country | Kind |
|---|---|---|---|
| 202320725217.3 | Mar 2023 | CN | national |
