Heat exchanger and air conditioner with same

Abstract

The utility model provides a heat exchanger and an air conditioner with the heat exchanger. The heat exchanger comprises a heat exchange flat pipe, a first collecting pipe and a flow guide plate. The guide plate is arranged between the heat exchange flat pipe and the first collecting pipe, one side of the guide plate is connected with the heat exchange flat pipe, and the other side of the guide plate is connected with the first collecting pipe; the first collecting pipe is provided with an air inlet, the flow guide plate is provided with a plurality of flow guide channels in the flowing direction of refrigerants, the heat exchange flat pipe is provided with a plurality of heat exchange channels, one end of each flow guide channel communicates with the first collecting pipe, and the other end of each flow guide channel communicates with at least one heat exchange channel. According to the utility model, the flow guide channel is convenient for uniformly guiding the refrigerant to each heat exchange channel, so that the problem of non-uniform distribution caused by the influence of gravity, pipeline resistance and the characteristics of the two-phase refrigerant is reduced.

Description

Technical Field

[0001] The utility model belongs to the technical field of air conditioners, and in particular relates to a heat exchanger and an air conditioner with the heat exchanger. Background Art

[0002] Microchannel heat exchangers are gradually replacing traditional heat exchangers with their high heat exchange efficiency, small size, light weight, compact structure, and small refrigerant charge. Microchannel heat exchangers are composed of multiple microchannel flat tubes connected in parallel with two collecting pipes, and the two-phase refrigerant is distributed to each microchannel flat tube through the collecting pipe. However, when the microchannel heat exchanger is used as an evaporator, due to the influence of gravity, pipeline resistance and the characteristics of the two-phase refrigerant, the two-phase flow refrigerant entering the microchannel heat exchanger is unevenly distributed, and generally there is more gas in the upper part and more liquid in the lower part. According to the heat transfer principle, the heat transfer coefficient of the gas-liquid two-phase phase change is relatively high, and the uneven flow distribution will cause "dry evaporation" in the upper part of the heat exchanger and "excessive liquid supply" in the lower part of the heat exchanger, which reduces the heat exchange capacity of the heat exchanger. Therefore, how to solve the uneven flow distribution of the heat exchanger is a problem that must be solved in the development of microchannel heat exchangers.

[0003] At present, most of the existing solutions to solve the uneven flow distribution of microchannel heat exchangers are zoned flow distribution solutions or designing a flow distribution structure in the manifold. However, these methods still have the problem that the microchannel flat tubes are small in size, and because the gaseous refrigerant is affected by buoyancy, it is difficult for the larger volume of gaseous refrigerant to enter the flat tube channel at the bottom of the heat exchanger, reducing the overall heat exchange effect of the heat exchanger. The related art discloses a refrigerant distributor, which makes the refrigerant flow entering the heat exchanger uniform by setting several branch pipes in the distributor, but does not mention the effect of uniform flow distribution of gaseous refrigerant; the related art discloses the design of a microchannel heat exchanger, which makes the refrigerant flow entering the heat exchanger more uniform by setting partition components and flow distribution holes in the manifold, but also does not mention the effect of flow distribution of gaseous refrigerant. Moreover, the patents surveyed are basically designed to design a flow distribution structure entering the heat exchanger, and rarely consider the uniformity of refrigerant flow distribution and the improvement of heat exchange performance from the perspective of the heat exchanger. Utility Model Content

[0004] The utility model provides a heat exchanger and an air conditioner having the heat exchanger, which can solve the technical problem that due to the influence of buoyancy of gaseous refrigerant, it is difficult for large-volume gaseous refrigerant to enter the flat tube channel at the bottom of the heat exchanger, thereby reducing the overall heat exchange effect of the heat exchanger.

[0005] The utility model provides a heat exchanger, which includes a heat exchange flat tube, a first collecting pipe and a guide plate;

[0006] The guide plate is disposed between the heat exchange flat tubes and the first header, one side of the guide plate is connected to the heat exchange flat tubes, and the other side of the guide plate is connected to the first header;

[0007] The first collecting pipe has an air inlet. Along the flow direction of the refrigerant, the guide plate has multiple guide channels. The heat exchange flat tube has multiple heat exchange channels. One end of the guide channel is connected to the first collecting pipe, and the other end of the guide channel is connected to at least one of the heat exchange channels.

[0008] In some embodiments, the flow guiding channel is in communication with one of the heat exchange channels, and a cross-sectional area of ​​the flow guiding channel is larger than a cross-sectional area of ​​the heat exchange channel.

[0009] In some embodiments, the heat exchange flat tubes include a first flat tube group and a second flat tube group, and the first flat tube group and the second flat tube group are arranged in sequence along the flow direction of the refrigerant; the first flat tube group and the second flat tube group each have a plurality of the heat exchange channels, and the number of heat exchange channels in the first flat tube group is greater than the number of heat exchange channels in the second flat tube group.

[0010] In some embodiments, the heat exchange flat tubes further include at least one third flat tube group. Along the flow direction of the refrigerant, the first flat tube group, the third flat tube group, and the second flat tube group are arranged in sequence; the third flat tube group has multiple heat exchange channels, and the number of heat exchange channels of the first flat tube group, the third flat tube group, and the second flat tube decreases in sequence.

[0011] In some embodiments, with the cross-section of the heat exchange flat tubes as a projection plane, the first flat tube group includes a plurality of first flat tubes, each of the first flat tubes having the heat exchange channel, and the heat exchange channel of the first flat tubes having a plurality of first sub-heat exchange channels; the third flat tube group includes a plurality of third flat tubes, each of the third flat tubes having the heat exchange channel, and the heat exchange channel of the third flat tubes having a plurality of third sub-heat exchange channels; the second flat tube group includes a plurality of second flat tubes, each of the second flat tubes having the heat exchange channel, and the heat exchange channel of the second flat tubes having a plurality of second sub-heat exchange channels, and the cross-sectional areas of the first sub-heat exchange channels, the third sub-heat exchange channels, and the second sub-heat exchange channels increase in sequence.

[0012] In some embodiments, a spoiler is provided in the first manifold, which separates the inner cavity of the first manifold into a first chamber and a second chamber. The spoiler is provided with a flow hole, which is used to connect the first chamber and the second chamber.

[0013] In some embodiments, the spoiler includes a connecting plate and a spoiler column, the connecting plate is connected to the first collecting pipe, and the flow hole is provided on the connecting plate; the spoiler column is provided on the end face of the connecting plate away from the flow direction of the refrigerant, the first end of the spoiler column is connected to the connecting plate, and the second end of the spoiler column is located on the flow path of the refrigerant.

[0014] In some embodiments, the spoiler column is obliquely arranged on the connecting plate, and an angle is formed between a line between the first end of the spoiler column and the second end of the spoiler column and an end face of the connecting plate, and the angle is greater than 45° and less than 60°.

[0015] In some embodiments, four spoiler columns are provided on the end face of the connecting plate facing away from the flow direction of the refrigerant, and the spoiler columns are triangular in shape. The top angle of the spoiler column is the second end of the spoiler column, and the bottom edge of the spoiler column is the first end of the spoiler column. With the end face of the connecting plate as the projection surface, the top angles of the four spoiler columns are directed toward the adjacent spoiler columns in a clockwise direction or counterclockwise direction.

[0016] An air conditioner includes a heat exchanger, wherein the heat exchanger is the above-mentioned heat exchanger.

[0017] The utility model provides a heat exchanger and an air conditioner having the heat exchanger, which has the following beneficial effects:

[0018] In this utility model, refrigerant flows from the air inlet into the first manifold. One end of the flow guide channel is connected to the first manifold, and the other end of the flow guide channel is connected to at least one heat exchange channel. Refrigerant flowing into the first manifold first flows into the flow guide channel, which then distributes the refrigerant from the first manifold to the various heat exchange channels. Compared to the refrigerant flowing directly into the heat exchange channels after entering the first manifold, the addition of a flow guide channel before the refrigerant enters the heat exchange channels makes it easier for gaseous refrigerant to enter the heat exchange channels, eliminating the difficulty of gaseous refrigerant entering the heat exchange channels of the flat heat exchange tubes at the bottom of the heat exchanger due to the small size of the heat exchange channels. In this embodiment, the flow guide plate and flow guide channel in the heat exchanger function to ensure that the refrigerant is evenly distributed to each heat exchange channel. The flow guide plate is located between the flat heat exchange tubes and the manifold, helping to optimize the flow characteristics of the fluid, reduce flow resistance, and improve heat exchange efficiency. When the refrigerant flows through the guide plate, the guide channel facilitates to evenly guide the refrigerant to each heat exchange channel, thereby reducing the uneven distribution problem caused by gravity, pipeline resistance and two-phase refrigerant characteristics, thereby reducing the phenomenon of "dry evaporation" in the upper part and "excessive liquid supply" in the lower part, and improving the overall heat exchange performance of the heat exchanger. BRIEF DESCRIPTION OF THE DRAWINGS

[0019] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the following briefly introduces the drawings required for the embodiments or the description of the prior art. Obviously, the drawings described below are merely exemplary, and those skilled in the art can, without inventive effort, derive other implementation drawings based on the provided drawings.

[0020] Figure 1 A schematic diagram of a heat exchanger according to an embodiment of the present invention;

[0021] Figure 2 Schematic diagrams of the first to third flat tube groups according to an embodiment of the present invention;

[0022] Figure 3 A schematic diagram of a guide plate according to an embodiment of the present invention;

[0023] Figure 4 This is a schematic diagram of a first manifold according to an embodiment of the present invention;

[0024] Figure 5 This is a schematic diagram of a first flat tube group according to an embodiment of the present invention;

[0025] Figure 6 This is a schematic diagram of a second flat tube group according to an embodiment of the present invention;

[0026] Figure 7 This is a schematic diagram of a third flat tube group according to an embodiment of the present invention;

[0027] Figure 8 for Figure 1 Detail enlargement in the figure;

[0028] Figure 9 Schematic diagram of the spoiler.

[0029] Figures: 1-heat exchange flat tube; 11-first flat tube group; 111-first flat tube; 112-first sub-heat exchange channel 12-second flat tube group; 121-second flat tube; 122-second sub-heat exchange channel; 13-third flat tube group; 131-third flat tube; 132-third sub-heat exchange channel; 101-heat exchange channel 2-first collecting pipe 21-first chamber 22-second chamber; 23-third chamber; 201-air inlet 3-guide plate 301-guide channel; 4-spoiler; 41-connecting plate; 42-spoiler column; 401-circulation hole; 5-second collecting pipe. DETAILED DESCRIPTION

[0030] The following will be combined with the drawings in the embodiments of the present invention to clearly and completely describe the technical solutions in the embodiments of the present invention. Obviously, the embodiments described are only some embodiments of the present invention, not all embodiments. The following description of at least one exemplary embodiment is actually only illustrative and is in no way intended to limit the present invention and its application or use. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without making creative efforts are within the scope of protection of the present invention.

[0031] In the description of the present invention, it needs to be understood that the directions or positional relationships indicated by directional words such as "front, back, up, down, left, right", "horizontal, vertical, vertical, horizontal" and "top, bottom" are usually based on the directions or positional relationships shown in the drawings. They are only for the convenience of describing the present invention and simplifying the description. Unless otherwise specified, these directional words do not indicate or imply that the device or element referred to must have a specific direction or be constructed and operated in a specific direction. Therefore, they cannot be understood as limiting the scope of protection of the present invention; the directional words "inside and outside" refer to the inside and outside relative to the outline of each component itself.

[0032] For ease of description, spatially relative terms such as "above", "above", "on the upper surface of", "above", etc. may be used herein to describe the spatial positional relationship of a device or feature to other devices or features as shown in the figures. It should be understood that spatially relative terms are intended to include different orientations of the device in use or operation in addition to the orientation described in the figures. For example, if the device in the drawings is inverted, the device described as "above other devices or structures" or "above other devices or structures" will be positioned as "below other devices or structures" or "below other devices or structures". Thus, the exemplary term "above" can include both "above" and "below". The device can also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatially relative descriptions used here are interpreted accordingly.

[0033] In addition, it should be noted that the use of words such as "first" and "second" to limit components is only for the convenience of distinguishing the corresponding components. Unless otherwise stated, the above words have no special meaning and therefore cannot be understood as limiting the scope of protection of this utility model.

[0034] See also Figure 1 and Figure 2 As shown, according to an embodiment of the present invention, a heat exchanger is provided, which includes heat exchange flat tubes 1, a first header 2 and a guide plate 3; the guide plate 3 is arranged between the heat exchange flat tubes 1 and the first header 2, one side of the guide plate 3 is connected to the heat exchange flat tubes 1, and the other side of the guide plate 3 is connected to the first header 2; the first header 2 has an air inlet 201, and the guide plate 3 has a plurality of guide channels 301 along the flow direction of the refrigerant. The heat exchange flat tubes 1 have a plurality of heat exchange channels 101, one end of the guide channel 301 is connected to the first header 2, and the other end of the guide channel 301 is connected to at least one heat exchange channel 101.

[0035] It is worth noting that a microchannel heat exchanger is a highly efficient heat exchange device that utilizes micro-sized channels to enhance heat transfer. The basic structure of a microchannel heat exchanger includes microchannels (i.e., heat exchange channels 101), manifolds, fins, etc. Microchannels typically have very small cross-sectional dimensions. These channels can be straight or have specific shapes, such as wavy, zigzag, or other shapes, to increase the turbulence of the refrigerant, thereby improving heat exchange efficiency. The manifolds are used to evenly distribute the refrigerant to each microchannel, while the fins are used to increase the heat exchange area.

[0036] Specifically, the refrigerant flows from the air inlet 201 into the first manifold 2. One end of the guide channel 301 is connected to the first manifold 2, and the other end of the guide channel 301 is connected to at least one heat exchange channel 101. The refrigerant flowing into the first manifold 2 first flows into the guide channel 301, which then distributes the refrigerant from the first manifold 2 to each heat exchange channel 101. Compared to the refrigerant flowing directly into the heat exchange channel 101 after flowing into the first manifold 2, the addition of the guide channel 301 before the refrigerant enters the heat exchange channel 101 makes it easier for the gaseous refrigerant to enter the heat exchange channel 101, and does not have difficulty entering the heat exchange channel 101 of the flat heat exchange tubes 1 at the lower portion of the heat exchanger due to the small size of the heat exchange channel 101.

[0037] In this embodiment, the function of the guide plate 3 and the guide channel 301 in the heat exchanger is to ensure that the refrigerant is evenly distributed to each heat exchange channel 101. The guide plate 3, located between the heat exchange flat tubes 1 and the manifold, helps optimize the flow characteristics of the refrigerant, reduce flow resistance, and improve heat exchange efficiency. When the refrigerant flows through the guide plate 3, the guide channel 301 facilitates the uniform guidance of the refrigerant to each heat exchange channel 101, thereby reducing the uneven distribution caused by gravity, pipe resistance, and the characteristics of the two-phase refrigerant. This, in turn, reduces the phenomenon of "dry evaporation" in the upper portion and "excessive liquid supply" in the lower portion, thereby improving the overall heat exchange performance of the heat exchanger.

[0038] See also Figure 1 and Figure 2 As shown, the flow guiding channel 301 is connected to one heat exchange channel 101 , and the cross-sectional area of ​​the flow guiding channel 301 is larger than the cross-sectional area of ​​the heat exchange channel 101 .

[0039] Specifically, the refrigerant flows into the first manifold 2 from the air inlet 201. During the upward flow of the refrigerant, the gas-phase refrigerant is more likely to gather at the upper part of the first manifold 2 due to the buoyancy, and larger bubbles are easily formed during the flow process. Since the cross-sectional area of ​​the guide channel 301 is larger than the cross-sectional area of ​​the heat exchange channel 101, the refrigerant is more likely to flow into the guide channel 301 with a larger cross-sectional area than the heat exchange channel 101 with a smaller cross-sectional area, which facilitates the gas-phase refrigerant to enter the heat exchange channel 101 of the heat exchange flat tube 1 at the lower part of the heat exchanger, thereby reducing the difficulty of the gas-phase refrigerant flowing into the flat tube.

[0040] In this embodiment, in the case of two-phase flow, that is, gaseous and liquid refrigerants exist at the same time, the larger guide channel 301 helps to balance the refrigerant flow in the two states, ensuring that the heat exchange channel 101 can perform heat exchange more effectively. The setting of the guide channel 301 also fully takes into account the fact that the volume of the gaseous refrigerant is large, and the larger cross-sectional area of ​​the guide channel 301 can reduce the resistance to the flow of the gaseous refrigerant, making it easier for it to enter the heat exchange channel 101. The larger guide channel 301 acts as a buffer zone, which helps to distribute the refrigerant more evenly to each heat exchange channel 101, reducing the problem of decreased heat exchange efficiency caused by uneven flow.

[0041] See also Figures 1 to 7 As shown, the heat exchange flat tubes 1 include a first flat tube group 11 and a second flat tube group 12. The first flat tube group 11 and the second flat tube group 12 are arranged in sequence along the flow direction of the refrigerant. The first flat tube group 11 and the second flat tube group 12 have the same length. The first flat tube group 11 and the second flat tube group 12 each have a plurality of heat exchange channels 101, and the number of heat exchange channels 101 in the first flat tube group 11 is greater than the number of heat exchange channels 101 in the second flat tube group 12.

[0042] Specifically, when the first manifold 2 and guide plate 3 are arranged vertically and the heat exchange channel 101 is arranged horizontally, the second flat tube group 12 is located above the first flat tube group 11. That is, the first flat tube group 11 is the lower portion of the heat exchange flat tubes 1, and the second flat tube group 12 is the upper portion of the heat exchange flat tubes 1. The refrigerant flows into the bottom of the first manifold 2 and flows from bottom to top, sequentially passing through the first flat tube group 11 and the second flat tube group 12. One reason for uneven refrigerant flow distribution in a heat exchanger is uneven pressure distribution within the heat exchanger. Due to the effect of gravity, the pressure drop in the first flat tube group 11 is small, making it easier for the refrigerant to flow into the heat exchange channel 101 or the guide channel 301. However, the pressure drop in the second flat tube group 12 is large, increasing the resistance to the refrigerant flowing into the heat exchange channel 101 or the guide channel 301.

[0043] In this embodiment, the rows of flat tubes in the traditional solution are all of the same specification and size. Due to gravity, the resistance in the upper and lower parts of the heat exchanger is different, which will cause uneven distribution of refrigerant flow. While keeping the same length, this embodiment introduces flat tube types of different specifications. The number of heat exchange channels 101 in the first flat tube group 11 is greater than the number of heat exchange channels 101 in the second flat tube group 12. That is, fewer flat tubes are arranged in the upper part of the heat exchanger. Fewer flat tubes means lower flow rate and pressure drop, while more flat tubes are arranged in the lower part of the heat exchanger. More flat tubes mean faster flow rate and greater pressure drop. Since the pressure drop of the first flat tube group 11 is small, the refrigerant is more likely to flow into the heat exchange channel 101 or the guide channel 301, while the pressure drop of the second flat tube group 12 is large. This arrangement helps to optimize the pressure drop distribution of the entire heat exchanger, making the refrigerant flow smoother. By arranging different numbers of flat tubes in different zones, the pressure inside the heat exchanger is balanced, thereby improving the uniformity of refrigerant flow distribution in the heat exchanger. If the wind speed distribution through the heat exchanger is relatively uniform, different numbers of flat tubes can be evenly distributed. If the wind speed distribution through the heat exchanger is uneven, the proportion of the number of flat tubes at the position where the wind speed mainly flows through the heat exchanger should be increased.

[0044] See also Figures 1 to 7 As shown, the heat exchange flat tubes 1 further include at least one third flat tube group 13. Along the flow direction of the refrigerant, the first flat tube group 11, the third flat tube group 13, and the second flat tube group 12 are arranged in sequence. The first flat tube group 11, the third flat tube group 13, and the second flat tube group 12 have the same length. The number of heat exchange channels 101 in the third flat tube group 13 can be greater than the number of heat exchange channels 101 in the second flat tube group 12, or greater than the number of heat exchange channels 101 in the first flat tube group 11.

[0045] Specifically, compared to setting up only two flat tube groups, since the flow path of the refrigerant has a certain length, the heat exchange flat tube 1 can be provided with several more partitions. The addition of the third flat tube group 13 can further increase the heat exchange area, so that the refrigerant has more opportunities to contact the tube wall when passing through the heat exchanger, thereby improving the overall heat exchange efficiency. The setting of the third flat tube group 13 can further optimize the flow path of the refrigerant, reduce the flow resistance, and allow the refrigerant to pass through the heat exchanger more smoothly, thereby improving energy efficiency. Moreover, the number of heat exchange channels 101 of the third flat tube group 13 can flexibly adjust the design of the heat exchanger according to market demand and customer specifications without the need for large-scale redesign or manufacturing.

[0046] See also Figure 1 and Figure 2 As shown, the third flat tube group 13 has a plurality of heat exchange channels 101 . The number of heat exchange channels 101 of the first flat tube group 11 , the third flat tube group 13 and the second flat tube decreases in sequence, while the cross-sectional areas of the heat exchange channels 101 of the first flat tube group 11 , the third flat tube group 13 and the second flat tube increase in sequence.

[0047] In this embodiment, by gradually reducing the number of heat exchange channels 101 and increasing their cross-sectional area from the first flat tube group 11 to the third flat tube group 13, the refrigerant flow rate and flow distribution can be more effectively controlled, flow resistance can be reduced, and the refrigerant dynamic characteristics of the entire heat exchanger can be optimized. During the refrigerant flow, the gradually increasing cross-sectional area helps reduce the pressure drop along the flow direction. By rationally designing the number of channels and cross-sectional area of ​​the flat tube groups, uneven refrigerant flow in the heat exchanger can be reduced.

[0048] It is worth noting that in this embodiment, since the number of heat exchange channels 101 in each tube zone is adjusted overall by varying the specifications of the first, second, and third flat tube groups 11, 12, and 13, there are at least two ways to adjust the number of heat exchange channels 101. The first adjustment method is to change the flat tube distribution density in each tube zone. Specifically, the first flat tube group 11 is provided with a larger number of flat tubes, the second flat tube group 12 is provided with a smaller number of flat tubes, and the third flat tube group 13 is provided with a moderate number of flat tubes. This adjusts the number of heat exchange channels 101 by adjusting the number of flat tubes. The second adjustment method is to have the same number of flat tubes in each flat tube group, but to have different numbers of holes in the flat tubes of each flat tube group. The greater the number of holes, the smaller the cross-sectional area of ​​each hole.

[0049] See also Figures 5 to 8 As shown, with the cross section of the heat exchange flat tubes 1 as the projection plane, the first flat tube group 11 includes a plurality of first flat tubes 111, each of which has a heat exchange channel 101, and the heat exchange channel 101 of the first flat tube 111 has a plurality of first sub-heat exchange channels 112; the third flat tube group 13 includes a plurality of third flat tubes 131, each of which has a heat exchange channel 101, and the heat exchange channel 101 of the third flat tube 131 has a plurality of third sub-heat exchange channels 132; the second flat tube group 12 includes a plurality of second flat tubes 121, each of which has a heat exchange channel 101, and the heat exchange channel 101 of the second flat tube 121 has a plurality of second sub-heat exchange channels 122, and the cross-sectional areas of the first sub-heat exchange channels 112, the third sub-heat exchange channels 132, and the second sub-heat exchange channels 122 increase in sequence.

[0050] Specifically, this embodiment changes the number of holes in the flat tubes of different tube zones. That is, the number of flat tubes in each flat tube group remains unchanged, and only the number of holes in each flat tube, that is, the number of sub-heat exchange channels of the heat exchange channel 101, is changed. The number of heat exchange channels 101 of the first flat tube group 11 is greater than the number of heat exchange channels 101 of the second flat tube group 12, that is, each flat tube in the upper part of the heat exchanger has fewer holes, and the number of sub-heat exchange channels is even smaller, while the cross-sectional area of ​​a single sub-heat exchange channel is larger. The fewer the number of flat tubes, the lower the heat exchanger is arranged with flat tubes with more holes. The flat tubes have more holes, the faster the flow rate, and the greater the pressure drop. Since the pressure drop of the first flat tube group 11 is small, the refrigerant is more likely to flow into the heat exchange channel 101 or the guide channel 301, while the pressure drop of the second flat tube group 12 is large. This setting helps to optimize the pressure drop distribution of the entire heat exchanger, making the refrigerant flow smoother. By arranging flat tubes with different numbers of holes in different areas, the pressure inside the heat exchanger is balanced, thereby improving the uniformity of the refrigerant flow distribution in the heat exchanger. If the air velocity distribution through the heat exchanger is relatively uniform, flat tubes with different numbers of holes can be evenly distributed. If the air velocity distribution through the heat exchanger is uneven, the proportion of flat tubes in the location where the wind primarily flows through the heat exchanger should be increased. In other embodiments, the number of flat tubes and the number of holes in each tube zone can be changed simultaneously, allowing for flexible adjustments based on heat exchange requirements.

[0051] As a specific embodiment, since the guide channel 301 is to be communicated with at least one heat exchange channel 101, Figure 8 As described above, the preferred embodiment is that a guide channel 301 is connected to a flat tube heat exchange channel 101, and the cross-sectional area of ​​the guide channel 301 is larger than the cross-sectional area of ​​the heat exchange channel 101, that is, the cross-sectional area of ​​the guide channel 301 is also larger than the cross-sectional area of ​​the sub-heat exchange channel.

[0052] See also Figure 1 、 Figure 2 、 Figure 8 and Figure 9 As shown, a spoiler 4 is provided in the first manifold 2, which divides the inner cavity of the first manifold 2 into a first chamber 21 and a second chamber 22. A flow hole 401 is provided on the spoiler 4, which is used to connect the first chamber 21 and the second chamber 22.

[0053] Specifically, when the microchannel heat exchanger is used as an evaporator, the gas-liquid two-phase refrigerant enters the first manifold 2 through the air inlet 201. During the upward flow of the refrigerant, the gas-phase refrigerant is more likely to accumulate in the upper part of the first manifold 2 due to buoyancy, and large bubbles are easily formed during the flow process. It is difficult for the gas-phase refrigerant to enter the microchannel flat tubes at the bottom of the heat exchanger, resulting in "dry evaporation" in the upper part of the heat exchanger and "excessive liquid supply" in the lower part of the heat exchanger. The refrigerant first flows into the bottom of the first manifold 2, then flows upward along the interior of the manifold, first flowing into the first chamber 21, and then flowing into the second chamber 22 through the flow hole 401. After the spoiler 4 is installed, the large bubbles formed during the refrigerant flow process can be broken into smaller bubbles, and the resulting vortex makes the gas-phase refrigerant flow more evenly into the heat exchanger.

[0054] In this embodiment, the spoiler 4 can increase the disturbance of the refrigerant, thereby improving the mixing degree of the refrigerant, making the heat exchange more sufficient and improving the heat exchange efficiency. In addition, the provision of the spoiler 4 can change the flow direction and flow velocity distribution of the refrigerant, reduce the flow dead zone, and make the refrigerant flow more evenly through the heat exchange channel 101, thereby improving the overall heat exchange performance. In particular, when the refrigerant flow velocity is low, the spoiler 4 can promote the turbulence of the refrigerant, increase the heat exchange area, and thus improve the heat exchange efficiency. Secondly, the spoiler 4 helps to optimize the pressure distribution within the heat exchanger, reduce the uneven refrigerant flow caused by uneven pressure, and thus improve the stability of the refrigerant flow and the heat exchange efficiency.

[0055] See also Figure 4 and Figure 9 As shown, the spoiler 4 includes a connecting plate 41 and a spoiler column 42. The connecting plate 41 is connected to the first collecting pipe 2, and a flow hole 401 is provided on the connecting plate 41; the spoiler column 42 is provided on the end face of the connecting plate 41 away from the flow direction of the refrigerant, the first end of the spoiler column 42 is connected to the connecting plate 41, and the second end of the spoiler column 42 is located on the flow path of the refrigerant.

[0056] Specifically, the refrigerant first flows in from the bottom of the first manifold 2 and then flows upward along the interior of the manifold. A connecting plate 41 is disposed within the first manifold 2. The flow holes 401 on the plate allow the refrigerant to flow from the first chamber 21 to the second chamber 22. The spoiler columns 42 are disposed on the end surface of the connecting plate 41, facing away from the refrigerant flow direction. When the refrigerant flows through the spoiler columns 42, their shape and position cause disturbances in the refrigerant flow, thereby generating eddies and turbulence. A portion of the refrigerant flowing into each chamber continues to flow upward, while the remaining portion flows into the guide channel 301 and then into the heat exchange channel 101 for heat exchange.

[0057] In this embodiment, when the refrigerant flows through the spoiler column 42, the first end of the spoiler column 42 is connected to the connecting plate 41, and the second end extends into the flow path, directly disturbing the flow of the refrigerant. This disturbance helps to break up the laminar structure of the refrigerant, break up larger bubbles, and increase the mixing and heat exchange area of ​​the refrigerant. Due to the action of the spoiler column 42, the refrigerant generates more eddies and turbulence when flowing through the spoiler 4, which increases the contact opportunity between the refrigerant and the wall of the heat exchange channel 101, thereby improving the heat exchange efficiency.

[0058] As a specific embodiment, the spoiler column 42 and the connecting plate 41 are an integral whole. The spoiler column 42 is stamped out and does not need to be installed separately. The setting of the spoiler 4 is mainly the effect produced by setting the spoiler column 42, and there is no fixed requirement for the structure of the spoiler column 42 that produces this effect.

[0059] See also Figure 9 As shown, the spoiler column 42 is obliquely arranged on the connecting plate 41, and an angle is formed between a line connecting the first end of the spoiler column 42 to the second end of the spoiler column 42 and the end surface of the connecting plate 41, which is greater than 45° and less than 60°.

[0060] Specifically, there is an angle between the spoiler column 42 and the end surface of the connecting plate 41, which is greater than 45° and less than 60°. If it is too small, the system resistance will increase, and if it is too large, it will not have the effect of breaking large bubbles.

[0061] In this embodiment, the inclined spoiler 42 can more effectively disturb the refrigerant and increase its turbulence. This helps disrupt the refrigerant's laminar flow structure, increasing the contact between the refrigerant and the heat exchange surface, thereby improving heat exchange efficiency. Furthermore, the provision of spoiler 42 helps accommodate different refrigerant flow states, including laminar and turbulent flow, as well as different flow directions, ensuring good heat exchange performance under various operating conditions.

[0062] See also Figure 9 As shown, four spoiler columns 42 are provided on the end face of the connecting plate 41 facing away from the flow direction of the refrigerant. The spoiler columns 42 are triangular in shape. The top angle of the spoiler column 42 is the second end of the spoiler column 42, and the bottom side of the spoiler column 42 is the first end of the spoiler column 42. With the end face of the connecting plate 41 as the projection surface, the top angles of the four spoiler columns 42 are directed toward the adjacent spoiler columns 42 in a clockwise direction or counterclockwise direction.

[0063] In this embodiment, the shape of the spoiler posts 42 is preferably triangular. In other embodiments, the spoiler posts 42 may also be rectangular or trapezoidal. The triangular arrangement and tilted arrangement of the spoiler posts 42 can more effectively disturb the refrigerant and increase the turbulence of the refrigerant. The clockwise or counterclockwise arrangement of the spoiler posts 42 helps to reduce dead zones in the refrigerant flow, ensuring that every part of the refrigerant in the heat exchanger can participate in the heat exchange process. This can promote the circulation of the refrigerant when it flows through the spoiler posts 42, increase the mixing and disturbance of the refrigerant, and thus improve the heat exchange efficiency.

[0064] It is worth noting that although the spoiler columns 42 will increase the flow resistance to a certain extent, reasonable arrangement and design can minimize the pressure loss, ensuring that the heat exchanger maintains low energy consumption while achieving efficient heat exchange.

[0065] As a specific embodiment, two spoilers 4 are provided in the heat exchange channel 101, and the two spoilers 4 divide the inner cavity of the first collecting pipe 2 into a first chamber 21, a third chamber 23 and a second chamber 22, and each spoiler 4 includes a connecting plate 41 and a spoiler column 42, and each connecting plate 41 is provided with four spoiler columns 42. At the same time, the heat exchange flat tubes 1 include a first flat tube group 11, a third flat tube group 13, and a second flat tube group 12. The guide plate 3 includes a first guide section, a third guide section, and a second guide section. The first chamber 21, the first guide section, and the first flat tube group 11 are correspondingly arranged. The third chamber 23, the third guide section, and the third flat tube group 13 are correspondingly arranged. The second chamber 22, the second guide section, and the second flat tube group 12 are correspondingly arranged. In this way, the refrigerant flows through the first chamber 21, the third chamber 23, and the second chamber 22 in sequence. The refrigerant flowing into each chamber then flows through the corresponding guide channel 301 and the heat exchange channel 101 in sequence.

[0066] Specifically, the refrigerant first enters from the bottom of the first manifold 2 and is then guided to the first chamber 21. In the first chamber 21, a portion of the refrigerant continues to flow upward and is affected by the spoiler columns 42. The refrigerant is disturbed and mixed to increase the surface area and efficiency of heat exchange. This portion of the refrigerant then flows into the third chamber 23, and the other portion of the refrigerant enters the corresponding guide channel 301. In the first flat tube group 11, the refrigerant exchanges heat with the inner wall of the flat tube; of the refrigerant entering the third chamber 23, a portion of the refrigerant continues to flow upward and is affected by the spoiler columns 42 and then flows into the second chamber 22. Here, the refrigerant is affected by the spoiler columns 42 for the last time to ensure sufficient heat exchange, and the other portion of the refrigerant enters the corresponding guide channel 301. In the third flat tube group 13, the refrigerant exchanges heat with the inner wall of the flat tube; the refrigerant flowing into the second chamber 22 exchanges heat in the second flat tube group 12.

[0067] In this embodiment, a guide plate 3 is provided, and a spoiler 4 is provided in the first manifold 2. The provision of the spoiler column 42 and the guide section increases the disturbance of the refrigerant, thereby improving the contact between the refrigerant and the wall of the heat exchange channel 101 and enhancing the heat exchange efficiency. Secondly, by providing multiple chambers and guide sections, the refrigerant can be more evenly distributed to each flat tube group, reducing the uneven distribution of the refrigerant in the heat exchanger. Moreover, since the refrigerant is disturbed when passing through each chamber and flat tube group, the heat exchange of the entire heat exchanger is more uniform, reducing the risk of local overheating or overcooling. This embodiment optimizes the flow of refrigerant and heat exchange by introducing a spoiler 4 and a guide structure into the microchannel heat exchanger, thereby improving the heat exchange efficiency and the overall performance of the system. The role of the guide plate 3 and the guide channel 301 in the heat exchanger is to ensure that the refrigerant can be evenly distributed to each heat exchange channel 101. The guide plate 3, located between the heat exchange flat tubes 1 and the manifold, helps optimize the refrigerant's flow characteristics, reduce flow resistance, and improve heat exchange efficiency. When the refrigerant flows through the guide plate 3, the guide channel 301 facilitates evenly directing the refrigerant to each heat exchange channel 101, thereby reducing the uneven distribution caused by gravity, pipeline resistance, and the characteristics of the two-phase refrigerant. This, in turn, reduces the phenomenon of "dry evaporation" in the upper part and "excessive liquid supply" in the lower part, thereby improving the overall heat exchange performance of the heat exchanger. The structure of this embodiment primarily addresses the problem of uneven gas-liquid two-phase refrigerant diversion in the microchannel heat exchanger, and after resolving this problem, the heat exchange performance of the heat exchanger is improved.

[0068] As a specific embodiment, a second header 5 is further provided at one end of the heat exchange flat tube 1 away from the first header 2. After the refrigerant exchanges heat in the heat exchange channel 101, the refrigerant in each heat exchange channel 101 converges in the second header 5.

[0069] An air conditioner is characterized by comprising a heat exchanger, wherein the heat exchanger is the heat exchanger described above.

[0070] It is easy for those skilled in the art to understand that, under the premise of no conflict, the above-mentioned advantageous methods can be freely combined and superimposed.

[0071] The above are only preferred embodiments of the present invention and are not intended to limit the present invention. Any modifications, equivalent replacements, and improvements made within the spirit and principles of the present invention shall be included within the scope of protection of the present invention. The above are only preferred embodiments of the present invention. It should be noted that for those skilled in the art, several improvements and variations can be made without departing from the technical principles of the present invention, and such improvements and variations shall also be considered within the scope of protection of the present invention.

Claims

1. A heat exchanger, characterized in that: include: Heat exchange flat tubes (1), a first header (2) and a guide plate (3); The guide plate (3) is arranged between the heat exchange flat tube (1) and the first header (2), one side of the guide plate (3) is connected to the heat exchange flat tube (1), and the other side of the guide plate (3) is connected to the first header (2); The first collecting pipe (2) has an air inlet (201), and along the flow direction of the refrigerant, the guide plate (3) has a plurality of guide channels (301), and the heat exchange flat tube (1) has a plurality of heat exchange channels (101), one end of the guide channel (301) is connected to the first collecting pipe (2), and the other end of the guide channel (301) is connected to at least one of the heat exchange channels (101).

2. The heat exchanger according to claim 1, characterized in that The guide channel (301) is in communication with one of the heat exchange channels (101), and the cross-sectional area of ​​the guide channel (301) is greater than the cross-sectional area of ​​the heat exchange channel (101).

3. The heat exchanger according to claim 1, characterized in that The heat exchange flat tube (1) comprises a first flat tube group (11) and a second flat tube group (12), and the first flat tube group (11) and the second flat tube group (12) are arranged in sequence along the flow direction of the refrigerant; the first flat tube group (11) and the second flat tube group (12) both have a plurality of the heat exchange channels (101), and the number of the heat exchange channels (101) of the first flat tube group (11) is greater than the number of the heat exchange channels (101) of the second flat tube group (12).

4. The heat exchanger according to claim 3, characterized in that The heat exchange flat tube (1) further comprises at least one third flat tube group (13), wherein along the flow direction of the refrigerant, the first flat tube group (11), the third flat tube group (13) and the second flat tube group (12) are arranged in sequence; The third flat tube group (13) has a plurality of heat exchange channels (101), and the number of heat exchange channels (101) of the first flat tube group (11), the third flat tube group (13) and the second flat tube decreases in sequence.

5. The heat exchanger according to claim 4, characterized in that Taking the cross section of the heat exchange flat tube (1) as a projection surface, the first flat tube group (11) includes a plurality of first flat tubes (111), each of the first flat tubes (111) has the heat exchange channel (101), and the heat exchange channel (101) of the first flat tube (111) has a plurality of first sub-heat exchange channels (112); the third flat tube group (13) includes a plurality of third flat tubes (131), each of the third flat tubes (131) has the heat exchange channel (101), and the third flat tubes (131) have a plurality of first sub-heat exchange channels (112). 1) has a plurality of third sub-heat exchange channels (132); the second flat tube group (12) includes a plurality of second flat tubes (121), each of the second flat tubes (121) has the heat exchange channel (101), the heat exchange channel (101) of the second flat tubes (121) has a plurality of second sub-heat exchange channels (122), and the cross-sectional areas of the first sub-heat exchange channel (112), the third sub-heat exchange channel (132), and the second sub-heat exchange channel (122) increase in sequence.

6. The heat exchanger according to any one of claims 1 to 5, characterized in that A spoiler (4) is provided in the first manifold (2), the spoiler (4) dividing the inner cavity of the first manifold (2) into a first chamber (21) and a second chamber (22), and a flow hole (401) is provided on the spoiler (4), the flow hole (401) being used to connect the first chamber (21) and the second chamber (22).

7. The heat exchanger according to claim 6, characterized in that The spoiler (4) includes a connecting plate (41) and a spoiler column (42), wherein the connecting plate (41) is connected to the first collecting pipe (2), and the connecting plate (41) is provided with the flow hole (401); the spoiler column (42) is provided on the end face of the connecting plate (41) away from the flow direction of the refrigerant, the first end of the spoiler column (42) is connected to the connecting plate (41), and the second end of the spoiler column (42) is located on the flow path of the refrigerant.

8. The heat exchanger according to claim 7, characterized in that The spoiler column (42) is obliquely arranged on the connecting plate (41), and an angle is formed between a line connecting the first end of the spoiler column (42) to the second end of the spoiler column (42) and an end surface of the connecting plate (41), and the angle is greater than 45° and less than 60°.

9. The heat exchanger according to claim 7, characterized in that Four spoiler columns (42) are provided on the end face of the connecting plate (41) facing away from the flow direction of the refrigerant, and the spoiler columns (42) are triangular in shape. The top angle of the spoiler column (42) is the second end of the spoiler column (42), and the bottom edge of the spoiler column (42) is the first end of the spoiler column (42). With the end face of the connecting plate (41) as the projection surface, the top angles of the four spoiler columns (42) are directed toward the adjacent spoiler columns (42) in a clockwise direction or a counterclockwise direction.

10. An air conditioner, characterized in that: The heat exchanger comprises a heat exchanger, wherein the heat exchanger is the heat exchanger according to any one of claims 1 to 9.

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