Heat exchanger and heat exchange device

Abstract

The present application relates to a heat exchanger. The heat exchanger comprises a first header, a second header, a plurality of first heat exchange tubes, a first partition member, a first tube, a second tube, and a first communicating part. The first header comprises a first tube section and a second tube section. The second header and the first header are spaced apart from each other, and the second header comprises a third tube section and a fourth tube section. The plurality of first heat exchange tubes are communicated with the first tube section and the third tube section, and are communicated with the second tube section and the fourth tube section. The first partition member is at least partially located on the first tube section, the first tube section comprises a first sub-tube section and a second sub-tube section, and the first sub-tube section and the second sub-tube section are located on two sides of the first partition member in the thickness direction. The first tube is at least partially located in the first tube section, the first tube at least partially extends in the length direction of the first tube section, and the first tube is communicated with the first sub-tube section and the second sub-tube section. The second tube is communicated with the first sub-tube section and the second tube section. The first communicating part is communicated with the second sub-tube section and the fourth tube section.

Description

Heat exchanger and heat exchange device

[0001] CROSS-REFERENCE TO RELATED APPLICATIONS

[0002] This application claims priority and benefits of Chinese patent application with application number 202410176160.5 and application date February 7, 2024. The entire contents of the above Chinese patent application are hereby incorporated by reference into this application. Technical Field

[0003] The present application relates to the field of heat exchange technology, and in particular to a heat exchanger and a heat exchange device. Background Art

[0004] Some heat exchangers in air conditioners or heat pumps have a subcooling section design. Such heat exchangers can be equipped with partitions and distribution pipes in a collecting pipe to improve the uniformity of refrigerant distribution when the heat exchanger works as an evaporator. However, when the heat exchanger works as a condenser, the flow direction of the refrigerant is opposite to the flow direction of the refrigerant when working as an evaporator. Due to the obstruction of the partition, a part of the refrigerant flowing in the reverse direction needs to pass through the distribution pipe before it can flow out of the collecting pipe, resulting in a large flow resistance when the refrigerant circulates in the area between the partition and the subcooling section. The refrigerant flows slowly and the circulation volume per unit time is small, which reduces the heat exchange efficiency of the heat exchanger when working as a condenser. Summary of the Invention

[0005] A first aspect of the present application provides a heat exchanger that can reduce the flow resistance encountered by a refrigerant during circulation, thereby improving the heat exchange efficiency of the heat exchanger when operating as a condenser.

[0006] The heat exchanger provided in the first aspect of the present application includes:

[0007] a first header, the first header comprising a first pipe segment and a second pipe segment, the first header further comprising a first partition and a first tube, the first partition being at least partially located in the first pipe segment, the first pipe segment comprising a first sub-pipe segment and a second sub-pipe segment, the first sub-pipe segment and the second sub-pipe segment being located on both sides of the first partition in a thickness direction; the first tube being at least partially located in the first pipe segment, the first tube extending at least partially along a length direction of the first pipe segment, and the first tube communicating with the first sub-pipe segment and the second sub-pipe segment;

[0008] a second header, the second header being spaced apart from the first header, the second header comprising a third pipe section and a fourth pipe section;

[0009] a plurality of first heat exchange tubes, wherein a portion of the first heat exchange tubes is connected to the first tube segment and the third tube segment, and another portion of the first heat exchange tubes is connected to the second tube segment and the fourth tube segment;

[0010] a second pipe, the second pipe communicating with the first sub-pipe segment and the second pipe segment;

[0011] A first connecting portion connects the second sub-pipe segment and the fourth pipe segment.

[0012] The beneficial effects of this application are:

[0013] When the heat exchanger of the present application works as a condenser, a portion of the refrigerant entering the second sub-tube segment from the first heat exchange tube flows out of the second sub-tube segment through the first tube, and the other portion of the refrigerant can enter the fourth tube segment through the first connecting portion, thereby reducing the resistance encountered by the refrigerant when flowing in the second sub-tube segment area and improving the heat exchange efficiency of the heat exchanger when working as a condenser.

[0014] The second aspect of the present application provides a heat exchange device, which includes at least two heat exchange units, wherein the heat exchange units are the heat exchangers in the embodiment of the first aspect, and two adjacent heat exchangers are arranged along the length direction of the first header, and one heat exchanger is fixedly connected to the other adjacent heat exchanger.

[0015] The beneficial effects of this application are:

[0016] The heat exchange device of the present application includes at least two heat exchangers in the first aspect embodiment. Since the heat exchanger in the first aspect embodiment has a higher heat exchange efficiency when working as a condenser, the heat exchange device also has a higher heat exchange efficiency when working as a condenser.

[0017] It should be understood that the foregoing general description and the following detailed description are merely illustrative and are not restrictive of the present application. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] FIG1 is a schematic structural diagram of a heat exchanger provided in the present application in a specific embodiment;

[0019] FIG2 is a schematic diagram of a partial enlarged structure of the heat exchanger at point A in FIG1 ;

[0020] FIG3 is a simplified structural diagram of the heat exchanger in FIG1 ;

[0021] FIG4 is a schematic diagram of the refrigerant flow direction of the heat exchanger provided by the present application when working as a condenser;

[0022] FIG5 is a schematic structural diagram of a heat exchanger provided in the present application in a second specific embodiment;

[0023] FIG6 is a schematic diagram of a partial enlarged structure of the heat exchanger at position B in FIG5 ;

[0024] FIG7 is a schematic structural diagram of a heat exchanger provided in the present application in a third specific embodiment;

[0025] FIG8 is a schematic structural diagram of a heat exchanger provided in the present application in a fourth specific embodiment;

[0026] FIG9 is a schematic structural diagram of a heat exchange device provided in the present application in a specific embodiment.

[0027] Figure numerals: first header 1, first pipe section 11, first sub-pipe section 111, second sub-pipe section 112, first cavity 113, second cavity 114, second pipe section 12, second header 2, third pipe section 21, fourth pipe section 22, first heat exchange tube 3, first section 31, second section 32, first bent section 33, first partition 4, first tube 5, first hole 51, second tube 61, fourth tube 62, first interface 63, second interface 64, first connecting portion 7, second heat exchange tube 71, third section 711, fourth section 712, second bent section 713, third tube 72, second partition 73, third header 8, fifth pipe section 81, sixth pipe section 82, fourth header 9, seventh pipe section 91, eighth pipe section 92, third heat exchange tube 10.

[0028] The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate embodiments consistent with the present application and, together with the description, serve to explain the principles of the present application. DETAILED DESCRIPTION

[0029] In order to better understand the technical solution of the present application, the embodiments of the present application are described in detail below with reference to the accompanying drawings.

[0030] It should be clear that the embodiments described are only part of the embodiments of this application, not all of the embodiments. Based on the embodiments in this application, all other embodiments obtained by ordinary technicians in this field without making creative work are within the scope of protection of this application.

[0031] The terms used in the embodiments of the present application are for the purpose of describing specific embodiments only and are not intended to limit the present application. The singular forms "a", "an", "the" and "the" used in the embodiments of the present application and the appended claims are also intended to include plural forms unless the context clearly indicates otherwise.

[0032] It should be understood that the term "and / or" as used herein is merely a description of the relationship between associated objects, indicating that three possible relationships exist. For example, "A and / or B" can represent: A exists alone, A and B exist simultaneously, or B exists alone. Furthermore, the character " / " in this document generally indicates that the associated objects are in an "or" relationship.

[0033] It should be noted that the directional words such as "upper", "lower", "left", and "right" described in the embodiments of the present application are described based on the angles shown in the accompanying drawings and should not be understood as limiting the embodiments of the present application. In addition, in the context, it should be understood that when it is mentioned that an element is connected to another element "on" or "under", it can not only be directly connected to the other element "on" or "under", but also be indirectly connected to the other element "on" or "under" through an intermediate element.

[0034] As shown in Figures 1-8, an embodiment of the present application provides a heat exchanger, which specifically includes a first header 1, a second header 2, a plurality of first heat exchange tubes 3, a first partition 4, a first tube 5, a second tube 61, and a first connecting portion 7, wherein the first header 1 includes a first tube segment 11 and a second tube segment 12; the second header 2 is spaced apart from the first header 1, and the second header 2 includes a third tube segment 21 and a fourth tube segment 22; a portion of the plurality of first heat exchange tubes 3 connects the first tube segment 11 and the third tube segment 21, and another portion of the first heat exchange tubes 3 connects the second tube segment 12 and the fourth tube segment 22. Pipe segment 22; the first partition 4 is at least partially located in the first pipe segment 11, the first pipe segment 11 includes a first sub-pipe segment 111 and a second sub-pipe segment 112, the first sub-pipe segment 111 and the second sub-pipe segment 112 are located on both sides of the first partition 4 along the thickness direction; the first tube 5 is at least partially located in the first pipe segment 11, the first tube 5 extends at least partially along the length direction of the first pipe segment 11, and the first tube 5 connects the first sub-pipe segment 111 and the second sub-pipe segment 112; the second tube 61 connects the first sub-pipe segment 111 and the second pipe segment 12; the first connecting portion 7 connects the second sub-pipe segment 112 and the fourth pipe segment 22.

[0035] In this embodiment, the first partition 4 and the first tube 5 effectively distribute the refrigerant in the heat exchanger, resulting in more uniform refrigerant distribution when the heat exchanger operates as an evaporator. Specifically, when the heat exchanger functions as an evaporator, the refrigerant enters the heat exchanger through the fourth tube segment 22, then passes through the connected first heat exchange tube 3 into the second tube segment 12, and then passes through the second tube 61 into the first sub-segment 111 of the first tube segment 11.

[0036] After the two-phase refrigerant enters the first sub-pipe segment 111, a portion of the refrigerant will be directly distributed and enter the first heat exchange tube 3 connected to the first sub-pipe segment 111 for heat exchange, while the other portion of the refrigerant will enter the second sub-pipe segment 112 through the first tube 5 for distribution. During this process, the refrigerant will spontaneously enter the low-pressure area from the high-pressure area. In addition, due to the vapor-liquid separation under the evaporation condition and the difference in the dead weight of the vapor refrigerant and the liquid refrigerant, the refrigerant entering the first tube 5 contains a higher content of vapor refrigerant, thereby reducing the accumulation of refrigerant in the first sub-pipe segment 111 and promoting the flow of refrigerant. The continuous flow of refrigerant can better facilitate the sufficient mixing of the two-phase refrigerant during distribution, thereby improving the distribution effect of the two-phase refrigerant.

[0037] It should be noted that when the heat exchanger in this embodiment does not have the first connecting portion 7, the performance of the heat exchanger is less affected when operating as an evaporator. However, when the heat exchanger operates as a condenser, after the reverse-flowing refrigerant enters the heat exchanger from the third pipe section 21, the refrigerant below the first partition 4 needs to pass through the first tube 5 before entering the first sub-pipe section 111, and then enter the second pipe section 12 (subcooling section) through the second tube 61. In such a flow process, the circulation resistance to the refrigerant is relatively large, which will cause most of the refrigerant to flow from the upper section of the first partition 4, thereby resulting in less refrigerant flowing through the first heat exchange tube 3 in the lower section of the first partition 4, and the area of ​​the heat exchanger is not fully utilized.

[0038] Furthermore, when the heat exchanger has the first connecting portion 7 and operates as a condenser, a portion of the refrigerant entering the second sub-segment 112 from the first heat exchange tube 3 flows out of the second sub-segment 112 through the first tube 5, while the remaining portion of the refrigerant can directly enter the fourth tube segment 22 through the first connecting portion 7. This reduces the resistance encountered by the refrigerant during flow in the second sub-segment 112 region and improves the heat exchange efficiency of the heat exchanger when operating as a condenser. Intuitively, as the refrigerant in the second sub-segment 112 enters the fourth tube segment 22 through the first connecting portion 7, the refrigerant flowing within the first connecting portion 7 can still exchange heat with the air, thereby ensuring the heat exchange effect of the subcooling section.

[0039] Furthermore, when the heat exchanger has a first connecting portion 7 and operates as an evaporator, a portion of the refrigerant in the fourth tube segment 22 can also directly enter the second sub-tube segment 112 through the first connecting portion 7. Due to the different weights of vapor and liquid refrigerant under evaporation conditions, the refrigerant entering the first tube 5 from the first sub-tube segment 111 contains a higher proportion of vapor refrigerant, while the refrigerant entering the second sub-tube segment 112 from the first connecting portion 7 has a higher proportion of liquid refrigerant than the former. Therefore, this connection method can also supplement the refrigerant in the second sub-tube segment 112 with liquid refrigerant, making the vapor-liquid ratio of the refrigerant in the second sub-tube segment 112 more balanced, thereby further improving the uniformity of refrigerant distribution when the heat exchanger operates as an evaporator. Thus, the provision of the first connecting portion 7 not only improves the heat exchange efficiency of the heat exchanger under condenser conditions, but also simultaneously improves the distribution effect of the heat exchanger under evaporator conditions.

[0040] In this embodiment, the second pipe segment 12, the fourth pipe segment 22, and the plurality of first heat exchange tubes 3 connecting the second pipe segment 12 and the fourth pipe segment 22 form a subcooling section of the heat exchanger. It should be noted that the mutually isolated first pipe segment 11 and the second pipe segment 12 mean that the first pipe segment 11 and the second pipe segment 12 are not connected when there is no connection between other components. The two pipe segments can be separated by a partition or by two independent pipes. In addition, the phrase "at least partially" that the first pipe 5 is at least partially located within the first pipe segment 11 should be understood in a broad sense, that is, the first pipe 5 can be partially located within the first pipe segment 11 or completely located within the first pipe segment 11, and this is not specifically limited in this article.

[0041] As shown in Figures 1-4, in a specific embodiment, the first tube 5 can be completely located in the first tube segment 11. In this case, the first tube is a hollow straight tube with openings at both ends. A through hole can be opened at a preset position on the side wall to facilitate the refrigerant in the first sub-tube segment 111 to enter the first tube 5. It should be noted that the distribution principle of the first tube 5 is different from the distribution principle of the distribution tube in the related art. The distribution tube in the related art directly introduces the refrigerant. After entering the distribution tube, the refrigerant flows out of the distribution tube through the holes evenly distributed on the distribution tube, and then enters the heat exchange tube at the corresponding position to complete the distribution. The first tube 5 in this article introduces a part of the refrigerant in the first sub-tube segment 111 into the second sub-tube segment 112, reducing the accumulation of refrigerant in the first sub-tube segment 111 and promoting the flow of refrigerant, thereby improving the distribution effect. Such a distribution method can reduce the stratification of the refrigerant and improve the uniformity of the refrigerant distribution.

[0042] In addition, the heat exchanger also includes fins, which can be corrugated fins or horizontally inserted fins. The specific fins can be adjusted and preset according to the installation method, size and heat exchange requirements of the heat exchanger, and this article does not make specific restrictions on this.

[0043] In a specific embodiment, if the cross-sectional area of ​​the first connecting portion 7 is defined as S1, and the sum of the cross-sectional areas of the first heat exchange tube 3 connecting the second tube segment 12 and the fourth tube segment 22 is defined as S2, then S1 and S2 satisfy the following relationship: 1 / 5 ≤ S1 / S2 ≤ 1 / 2. As mentioned above, the first connecting portion 7 allows the refrigerant in the second sub-tube segment 112 to flow directly into the fourth tube segment 22 when the heat exchanger operates as a condenser, and also allows the refrigerant in the fourth tube segment 22 to flow directly into the second sub-tube segment 112 for distribution when the heat exchanger operates as an evaporator. However, if the cross-sectional area of ​​the first connecting portion 7 is too large, the refrigerant flow rate between the second sub-tube segment 112 and the fourth tube segment 22 will be too large. This will reduce the refrigerant flow rate in other sections when the heat exchanger operates as a condenser, hindering the full utilization of the heat exchange area of ​​the heat exchanger. When the heat exchanger operates as an evaporator, excessive refrigerant will directly enter the second sub-tube segment 112, affecting the overall distribution effect. Therefore, it is necessary to control the flow cross-sectional area of ​​the first connecting part 7 to balance the flow of the refrigerant so that the heat exchange area of ​​the heat exchanger can be fully utilized. That is, when the flow cross-sectional area S1 of the first connecting part 7 and the sum of the flow cross-sectional area S2 of the first heat exchange tube 3 connecting the second pipe segment 12 and the fourth pipe segment 22 satisfy: 1 / 5≤S1 / S2≤1 / 2, the first connecting part 7 can achieve the best effect.

[0044] As shown in Figure 3, in a specific embodiment, the first connecting portion 7 includes a second heat exchange tube 71, and the second heat exchange tube 71 connects the second sub-tube segment 112 and the fourth tube segment 22. If the number of second heat exchange tubes 71 is defined as A, then: 1≤A≤3. The reason for setting the number of second heat exchange tubes 71 in this embodiment is similar to the reason for setting the flow cross-sectional area in the previous embodiment. Both are to restrict the refrigerant flow rate of the first connecting portion 7 to achieve the best technical effect. Therefore, this article will not elaborate on them one by one. It should be supplemented that the flow cross-sectional area of ​​the second heat exchange tube 71 is roughly the same as the flow cross-sectional area of ​​the first heat exchange tube 3. The first heat exchange tube 3 and the second heat exchange tube 71 of the same size and structure can facilitate the assembly of the heat exchanger without increasing additional manufacturing costs. Generally speaking, the number of second heat exchange tubes 71 is 1-2.

[0045] In this embodiment, the refrigerant in the second sub-segment 112 is introduced into the fourth pipe segment 22 by connecting the second sub-segment 112 and the fourth pipe segment 22 through the second heat exchange tube 71. When the heat exchanger works as a condenser, the pressure in the second sub-segment 112 is higher than that in the fourth pipe segment 22 (because the fourth pipe segment 22 is the outlet segment of the refrigerant, the pressure is the lowest), and the refrigerant can spontaneously enter the fourth pipe segment 22 from the second sub-segment 112 without the refrigerant not flowing or flowing slowly.

[0046] As shown in Figures 5-6, in a specific embodiment, the heat exchanger also includes a third tube 72 and a second partition 73, the second partition 73 is at least partially located in the second sub-tube segment 112, the second sub-tube segment 112 has a first cavity 113 and a second cavity 114, the first cavity 113 and the second cavity 114 are located on both sides of the second partition 73 along the thickness direction; the first tube 5 connects the first sub-tube segment 111 and the first cavity 113, the second heat exchange tube 71 connects the fourth tube segment 22 and the second cavity 114, and the third tube 72 connects the first cavity 113 and the second cavity 114.

[0047] In this embodiment, the third tube 72 connects the first chamber 113 and the second chamber 114. When the heat exchanger operates as a condenser, a portion of the refrigerant in the first chamber 113 can be introduced into the second chamber 114. The refrigerant then flows through the second heat exchange tube 71, which is connected to the second chamber 114, into the fourth tube segment 22. This reduces the resistance encountered by the refrigerant during flow in the second sub-tube segment 112, thereby improving the heat exchange efficiency of the heat exchanger when operating as a condenser. Generally speaking, because the refrigerant flow rate in the third tube 72 is much smaller than that in the second tube 61, its cross-sectional area is also smaller than that of the second tube 61.

[0048] It should be noted that the function of the second partition 73 in this embodiment is the same as that of the first partition 4, both of which are to separate the tube cavity of the first collecting pipe 1 to form two relatively independent and non-connected areas. Generally speaking, the first partition 4 and the second partition 73 can be partitions, and the specific structure and installation method of the partition are not specifically limited in this article.

[0049] As shown in Figure 3, in a specific embodiment, if the length of the first sub-tube segment 111 is defined as L1 and the length of the second sub-tube segment 112 is defined as L2, then L1 and L2 satisfy: 0.5≤L1 / (L1+L2)≤0.9; the first tube 5 includes at least one first hole 51, and the first hole 51 is located on the tube wall of the first tube 5.

[0050] In this embodiment, the primary purpose of the first sub-segment 111 and the first tube 5 is to distribute the refrigerant. When the heat exchanger functions as an evaporator, the refrigerant dryness at the evaporator inlet is generally below 0.5. When this ratio is less than 0.5, if the first sub-segment 111 is small, the refrigerant quickly fills the first sub-segment 111, causing a large amount of two-phase refrigerant to be carried into the second sub-segment 112. This results in significant gas-liquid stratification of the refrigerant in the second sub-segment 112 along the gravity direction (the vertical direction in the figure). If the ratio is greater than 0.9, the second sub-segment 112 is too small and easily fills with refrigerant introduced by the first tube 5, but a large amount of gas cannot be introduced, resulting in uneven liquid distribution throughout the first tube 11. Therefore, when 0.5 ≤ L1 / (L1 + L2) ≤ 0.9, the refrigerant can flow more evenly.

[0051] In addition, the arrangement of the first hole 51 can also be beneficial to the distribution of the refrigerant, facilitating the refrigerant in the first sub-tube segment 111 to enter the first tube 5, and then be introduced from the first tube 5 into the second sub-tube segment 112 for distribution. Therefore, the position of the first hole 51 can be set according to the actual distribution requirements or the gas-liquid ratio of the refrigerant. For example, if more vapor refrigerant needs to be introduced into the second sub-tube segment 112, the first hole 51 can be arranged on the side of the first tube 5 close to the top, otherwise it can be arranged close to the first partition 4 to introduce more liquid refrigerant. This will not be explained one by one in this article.

[0052] As shown in Figure 7, in a specific embodiment, the heat exchanger also includes: a third header 8 and a fourth header 9, the third header 8 and the fourth header 9 are arranged at intervals; a plurality of third heat exchange tubes 10, the plurality of third heat exchange tubes 10 connecting the third header 8 and the fourth header 9; a fourth tube 62, the fourth tube 62 connecting the fourth header 9 and the fourth pipe section 22.

[0053] In this embodiment, the heat exchanger further includes a third header 8 and a fourth header 9, as well as a third heat exchange tube 10 connecting the third header 8 and the fourth header 9. The third header 8 and the fourth header 9 are respectively located on the radial sides of the first header 1 and the second header 2. The entire heat exchanger has a double-row arrangement structure, thereby improving the overall heat exchange capacity. It should be noted that when the heat exchanger is a double-row heat exchanger and operates as a condenser, the dryness of the refrigerant often decreases by the second row of the condenser. The outflow resistance of the refrigerant in the second row is large due to the obstruction of the first partition 4. Therefore, the portion consisting of the first header 1 and the second header 2 can be placed in the second row, forming a semi-forward and semi-reverse refrigerant flow path, thereby improving the distribution of the entire heat exchanger in the condensing and evaporating modes and enhancing the heat exchange capacity.

[0054] It should be noted that the structure, length and diameter of the third header 8 and the fourth header 9 can be the same as or different from the structure of the first header 1 and the second header 2. The specific structure can be determined according to the usage scenario and heat exchange requirements of the heat exchanger. Generally speaking, the first header 1, the second header 2, the third header 8 and the fourth header 9 are headers of uniform specifications; in addition, the structure and size of the third heat exchange tube 10 can also be the same as the structure and size of the first heat exchange tube 3 and the second heat exchange tube 71. This article will not elaborate on this.

[0055] As shown in Figure 7, in a specific embodiment, the third header 8 includes a fifth pipe segment 81 and a sixth pipe segment 82, the fourth header 9 includes a seventh pipe segment 91 and an eighth pipe segment 92, the third heat exchange tube 10 connects the fifth pipe segment 81 and the seventh pipe segment 91, and the sixth pipe segment 82 and the eighth pipe segment 92; the fourth tube 62 connects the seventh pipe segment 91 and the fourth pipe segment 22.

[0056] As shown in FIG8 , in a specific embodiment, the first heat exchange tube 3 includes a first section 31, a second section 32, and a first curved section 33, wherein the first curved section 33 connects the first section 31 and the second section 32. The second heat exchange tube 71 includes a third section 711, a fourth section 712, and a second curved section 713, wherein the second curved section 713 connects the third section 711 and the fourth section 712. The bending angle of the first curved section 33 is the same as the bending angle of the second curved section 713. It should be noted that the structures of the first heat exchange tube 3 and the second heat exchange tube 71 can be exactly the same, and the difference between the two can only be reflected in the difference in position and function. However, the structure of the second heat exchange tube 71 can also be different from that of the first heat exchange tube 3. For example, the first heat exchange tube 3 is a microchannel heat exchange tube, but in order to increase the refrigerant flow rate of the second heat exchange tube 71, the second heat exchange tube 71 is a single-channel heat exchange tube.

[0057] In a specific embodiment, the first heat exchange tube 3 includes one or more first channels that extend through the first heat exchange tube 3 along its length; and / or the second heat exchange tube 71 includes one or more second channels that extend through the second heat exchange tube 71 along its length. The cross-sectional area of ​​one first heat exchange tube 3 is equal to the cross-sectional area of ​​one second heat exchange tube 71. The first heat exchange tube 3 and the second heat exchange tube 71 can be small round heat exchange tubes, microchannel heat exchange tubes, etc.

[0058] As shown in Figures 1-5, in a specific embodiment, the heat exchanger also includes a first interface 63 and a second interface 64, the first interface 63 is connected to the fourth pipe segment 22, and the second interface 64 is connected to the third pipe segment 21; when the heat exchanger is working, the length direction of the first header 1 is roughly perpendicular to the horizontal plane direction, and the heat exchanger includes evaporation mode and condensation mode when working. In the evaporation mode, the first interface 63 is the refrigerant inlet, and in the condensation mode, the second interface 64 is the refrigerant inlet.

[0059] It should be noted that when the heat exchanger does not have the first connecting part 7, two interfaces are often required to be set at the third pipe segment 21, and then a connecting pipe is connected through the adapter block. The two interfaces are intended to reduce the flow length from the interface to the lower section of the first partition 4 under the condenser working condition, that is, to reduce the flow resistance. After the first connecting part 7 is set, the flow resistance in the lower section of the first partition 4 becomes smaller, so there is no need to set two interfaces. That is, generally speaking, only one second interface 64 is required to be set at the third pipe segment 21. This not only reduces the processing cost of opening a hole in the third pipe segment 21, but also saves the material cost and processing cost of the adapter block for connection, thereby achieving a cost reduction effect.

[0060] As shown in Figure 9, a second aspect of the present application provides a heat exchange device comprising at least two heat exchange units, each of which is the heat exchanger described in the first aspect. Two adjacent heat exchangers are arranged along the length of the first header 1, with one heat exchanger fixedly connected to the other adjacent heat exchanger. The heat exchange device of the present application comprises at least two heat exchangers described in the first aspect. Because the heat exchangers described in the first aspect have higher heat exchange efficiency when operating as condensers, the present heat exchange device also has higher heat exchange efficiency when operating as a condenser.

[0061] The above are only preferred embodiments of the present application and are not intended to limit the present application. For those skilled in the art, various modifications and variations of the present application are possible. Any modifications, equivalent substitutions, improvements, etc. made within the spirit and principles of the present application shall be included in the scope of protection of the present application.

Claims

1. A heat exchanger comprising: A first header (1), the first header (1) comprising a first tube section (11) and a second tube section (12), the first header (1) further comprising a first partition (4) and a first tube (5); the first partition (4) is at least partially located in the first tube section (11), the first tube section (11) comprises a first sub-tube section (111) and a second sub-tube section (112), the first sub-tube section (111) and the second sub-tube section (112) being located on both sides of the first partition (4) in a thickness direction; the first tube (5) is at least partially located in the first tube section (11), the first tube (5) at least partially extends along the length direction of the first tube section (11), and the first tube (5) is connected to the first sub-tube section (111) and the second sub-tube section (112); a second header (2), the second header (2) being spaced apart from the first header (1), the second header (2) comprising a third pipe section (21) and a fourth pipe section (22); a plurality of first heat exchange tubes (3), wherein a portion of the first heat exchange tubes (3) are connected to the first tube segment (11) and the third tube segment (21), and another portion of the first heat exchange tubes (3) are connected to the second tube segment (12) and the fourth tube segment (22); a second pipe (61), the second pipe (61) communicating with the first sub-pipe section (111) and the second pipe section (12); A first connecting portion (7), wherein the first connecting portion (7) connects the second sub-pipe section (112) and the fourth pipe section (22).

2. The heat exchanger according to claim 1, wherein The flow cross-sectional area of the first connecting portion (7) is defined as S1, and the sum of the flow cross-sectional areas of the first heat exchange tube (3) connecting the second tube section (12) and the fourth tube section (22) is defined as S2. Then, S1 and S2 satisfy: 1 / 5≤S1 / S2≤1 / 2.

3. The heat exchanger according to claim 1 or 2, wherein: The first connecting portion (7) comprises a second heat exchange tube (71), and the second heat exchange tube (71) connects the second sub-tube segment (112) and the fourth tube segment (22). The number of the second heat exchange tubes (71) is defined as A, then: 1≤A≤3.

4. The heat exchanger according to claim 3, wherein: The invention also includes a third tube (72) and a second partition (73), wherein the second partition (73) is at least partially located in the second sub-tube segment (112), and the second sub-tube segment (112) has a first cavity (113) and a second cavity (114), and the first cavity (113) and the second cavity (114) are located on both sides of the second partition (73) in the thickness direction; The first tube (5) is connected to the first sub-tube segment (111) and the first cavity (113), the second heat exchange tube (71) is connected to the fourth tube segment (22) and the second cavity (114), and the third tube (72) is connected to the first cavity (113) and the second cavity (114).

5. The heat exchanger according to claim 3, wherein: The length of the first sub-segment (111) is defined as L1, and the length of the second sub-segment (112) is defined as L2, then L1 and L2 satisfy: 0.5≤L1 / (L1+L2)≤0.9; The first tube (5) comprises at least one first hole (51), and the first hole (51) is located on the tube wall of the first tube (5).

6. The heat exchanger according to claim 5, wherein: Also includes: a third header (8) and a fourth header (9), wherein the third header (8) and the fourth header (9) are arranged at intervals; a plurality of third heat exchange tubes (10), wherein the plurality of third heat exchange tubes (10) are connected to the third header (8) and the fourth header (9); A fourth pipe (62), the fourth pipe (62) is connected to the fourth header (9) and the fourth pipe section (22).

7. The heat exchanger according to claim 6, wherein: The third header (8) includes a fifth pipe segment (81) and a sixth pipe segment (82), the fourth header (9) includes a seventh pipe segment (91) and an eighth pipe segment (92), and the third heat exchange tube (10) is in communication with the fifth pipe segment (81) and the seventh pipe segment (91), and with the sixth pipe segment (82) and the eighth pipe segment (92); The fourth pipe (62) communicates with the seventh pipe section (91) and the fourth pipe section (22).

8. The heat exchanger according to claim 3, wherein: The first heat exchange tube (3) comprises a first section (31), a second section (32) and a first curved section (33), wherein the first curved section (33) communicates with the first section (31) and the second section (32); The second heat exchange tube (71) comprises a third section (711), a fourth section (712) and a second curved section (713); the second curved section (713) connects the third section (711) and the fourth section (712); the bending angle of the first curved section (33) is the same as the bending angle of the second curved section (713).

9. The heat exchanger according to claim 3, wherein: The first heat exchange tube (3) comprises one or more first channels, and the one or more first channels penetrate the first heat exchange tube (3) along the length direction of the first heat exchange tube (3); And / or, the second heat exchange tube (71) includes one or more second channels, and the one or more second channels penetrate the second heat exchange tube (71) along the length direction of the second heat exchange tube (71), and the flow cross-sectional area of the first heat exchange tube (3) is equal to the flow cross-sectional area of the second heat exchange tube (71).

10. The heat exchanger according to any one of claims 1-2 or 4-9, wherein: The heat exchanger further comprises a first interface (63) and a second interface (64), wherein the first interface (63) is in communication with the fourth pipe section (22), and the second interface (64) is in communication with the third pipe section (21); When the heat exchanger is in operation, the length direction of the first header (1) is approximately perpendicular to the horizontal plane direction. The heat exchanger includes an evaporation mode and a condensation mode when in operation. In the evaporation mode, the first interface (63) is a refrigerant inlet, and in the condensation mode, the second interface (64) is a refrigerant inlet.

11. A heat exchange device comprising at least two heat exchange units, wherein the heat exchange units are the heat exchangers according to any one of claims 1 to 10, two adjacent heat exchangers are arranged along the length direction of the first header (1), and one heat exchanger is fixedly connected to the other adjacent heat exchanger.

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