Heat exchanger and air conditioning device

Abstract

The application discloses a heat exchanger and an air conditioning device. The heat exchanger comprises a plurality of heat exchange plates, the plurality of heat exchange plates are arranged in a stacking mode along the thickness direction of the heat exchange plates, the length direction of the heat exchange plates is arranged to be intersected with a horizontal plane, a plurality of branch flow channels extending along the length direction are arranged at the middle part of the length direction of the heat exchange plates, the plurality of branch flow channels are arranged in a spaced mode along the width direction of the heat exchange plates, a first collecting flow channel connected with the lower ends of the plurality of branch flow channels is arranged at the part of the heat exchange plates located at the lower side of the plurality of branch flow channels, the first collecting flow channel extends along the width direction, wherein, the part of the plurality of heat exchange plates located below the first collecting flow channel is formed with a first collecting flow channel penetrating through the plurality of heat exchange plates along the thickness direction, the first collecting flow channel is communicated with the first collecting flow channel through a first connecting flow channel, the first collecting flow channel is also communicated with the first collecting flow channel through a second connecting flow channel, the connecting position of the first connecting flow channel and the first collecting flow channel is higher than the connecting position of the second connecting flow channel and the first collecting flow channel, and the heat exchanger can improve the heat exchange performance of the heat exchanger when operating as an evaporator without affecting the heat exchange effect of the heat exchanger when operating as a condenser.

Description

Technical Field

[0001] This invention relates to the field of air conditioner technology, and more specifically, to a heat exchanger and an air conditioning device. Background Technology

[0002] In the existing technology, heat exchangers used for both cooling and heating suffer from the problem of gaseous refrigerant affecting the heat exchanger's heat exchange performance when operating as evaporators, which leaves room for improvement. Summary of the Invention

[0003] The present invention aims to at least partially solve one of the aforementioned technical problems in the prior art. To this end, the present invention proposes a heat exchanger that can improve the heat exchange performance of the heat exchanger when operating as an evaporator without affecting its heat exchange efficiency as a condenser.

[0004] The present invention also proposes an air conditioning device having the above-mentioned heat exchanger.

[0005] According to a first aspect of the present invention, a heat exchanger includes a plurality of heat exchange plates stacked along their thickness direction. The length direction of each heat exchange plate is arranged to intersect a horizontal plane. A plurality of branch channels extending along the length direction are provided at the middle of the length direction of each heat exchange plate. The plurality of branch channels are spaced apart along the width direction of the heat exchange plate. A first collecting channel, connected to the lower end of the plurality of branch channels, is provided on a portion of the heat exchange plate located below the branch channels. The first collecting channel extends along the width direction.

[0006] Wherein, a first confluence channel is formed in the portion of the plurality of heat exchange plates located below the first collection channel, extending through the plurality of heat exchange plates along the thickness direction. The first confluence channel is connected to the first collection channel through a first connecting channel, and the first confluence channel is also connected to the first collection channel through a second connecting channel. The connection point between the first connecting channel and the first confluence channel is higher than the connection point between the second connecting channel and the first confluence channel.

[0007] According to an embodiment of the present invention, the heat exchanger can improve the heat exchange performance when operating as an evaporator without affecting the heat exchange effect when the heat exchanger is operating as a condenser.

[0008] In addition, the heat exchanger according to the embodiments of the invention may also have the following additional technical features:

[0009] According to some embodiments of the present invention, the heat exchanger is used in an air conditioning device, wherein the connection between the first connecting channel and the first collecting channel is located downstream of the airflow direction compared to the connection between the second connecting channel and the first collecting channel.

[0010] According to some embodiments of the present invention, the first connecting channel includes a first lateral extension section and a first vertical extension section, one end of the first lateral extension section is connected to the first converging channel and the other end is connected to the lower end of the first vertical extension section, and the upper end of the first vertical extension section is connected to the first collecting channel.

[0011] According to some embodiments of the present invention, the second connecting channel includes a second lateral extension section and a second vertical extension section, one end of the second lateral extension section is connected to the first converging channel and the other end is connected to the lower end of the second vertical extension section, and the upper end of the second vertical extension section is connected to the first converging channel.

[0012] According to some embodiments of the present invention, the first flow collecting channel includes a first flow collecting part and a second flow collecting part, the first flow collecting part and the second flow collecting part are arranged side by side along the width direction, the first connecting channel is connected to the first flow collecting part, and the second connecting channel is connected to the second flow collecting part.

[0013] According to some embodiments of the present invention, the length of the first current collector is less than the length of the second current collector.

[0014] According to some embodiments of the present invention, the top of the first collector is higher than the top of the second collector.

[0015] According to some embodiments of the present invention, a protrusion protruding downward along the length direction is formed between the top of the first collector and the top of the second collector.

[0016] According to some embodiments of the present invention, a curved portion that bends downward along the length direction is formed between the first current collector and the second current collector.

[0017] According to some embodiments of the present invention, the heat exchange plate includes two plate-shaped components that are fitted together to define a first collection channel, a plurality of branch channels, a first connecting channel, and a second connecting channel.

[0018] According to some embodiments of the present invention, a second collecting channel is provided on the portion of the heat exchange plate above the plurality of branch channels, and is connected to the upper end of the plurality of branch channels. A second confluence channel is formed on the portion of the plurality of heat exchange plates above the second collecting channel, extending through the plurality of heat exchange plates along the thickness direction. The second confluence channel and the second collecting channel are connected by a third connecting channel.

[0019] The two plate-shaped components further define the second flow collection channel and the third connecting channel.

[0020] According to some embodiments of the present invention, the heat exchanger includes a first connecting pipe and a second connecting pipe, the first connecting pipe being in communication with the first manifold and the second connecting pipe being in communication with the second manifold.

[0021] An air conditioning apparatus according to a second aspect of the present invention includes a heat exchanger as described in the above embodiments. Attached Figure Description

[0022] Figure 1 This is a schematic diagram of the structure of a heat exchanger according to an embodiment of the present invention;

[0023] Figure 2 This is a partial structural schematic diagram of a heat exchange plate according to an embodiment of the present invention;

[0024] Figure 3 This is a partial structural schematic diagram of a heat exchange plate according to an embodiment of the present invention;

[0025] Figure 4 This is a partial structural schematic diagram of a heat exchange plate according to an embodiment of the present invention;

[0026] Figure 5 This is a partial structural schematic diagram of a heat exchange plate according to an embodiment of the present invention;

[0027] Figure 6 This is a partial structural schematic diagram of the liquid refrigerant passing through the heat exchange plate according to an embodiment of the present invention.

[0028] Figure 7 This is a partial structural schematic diagram of the liquid and gaseous refrigerants passing through the heat exchange plate according to an embodiment of the present invention.

[0029] Figure 8 This is a heat flow analysis comparison diagram of the heat exchanger according to an embodiment of the present invention and other heat exchangers with different structures.

[0030] Figure label:

[0031] Heat exchanger 100, heat exchange plate 10, first flow collecting channel 1, first flow collecting part 11, second flow collecting part 12, protrusion 13, bend 14, branch flow channel 2, first flow converging channel 3, second flow converging channel 4, first connecting flow channel 5, first lateral extension section 51, first vertical extension section 52, second connecting flow channel 6, second lateral extension section 61, second vertical extension section 62, second flow collecting channel 7, third connecting flow channel 8, first connecting pipe 91, second connecting pipe 92. Detailed Implementation

[0032] Embodiments of the present invention are described in detail below, examples of which are illustrated in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and intended to explain the present invention, and should not be construed as limiting the present invention.

[0033] In the description of this invention, it should be understood that the terms "center," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," and "outer," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this invention.

[0034] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of indicated technical features. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this invention, "a plurality of" means at least two, such as two, three, etc., unless otherwise explicitly specified.

[0035] In this invention, unless otherwise explicitly specified and limited, the terms "installation," "connection," "linking," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection, an electrical connection, or a connection that allows communication between them; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components. Those skilled in the art can understand the specific meaning of the above terms in this invention according to the specific circumstances.

[0036] In this invention, unless otherwise explicitly specified and limited, "above" or "below" the second feature can include direct contact between the first and second features, or contact between the first and second features through another feature between them. Furthermore, "above," "over," and "on top" of the second feature includes the first feature directly above or diagonally above the second feature, or simply indicates that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature includes the first feature directly below or diagonally below the second feature, or simply indicates that the first feature is at a lower horizontal level than the second feature.

[0037] In the prior art, heat exchangers used for both cooling and heating suffer from the problem of gaseous refrigerant affecting their heat exchange performance when operating as evaporators. To address this, this invention presents a heat exchanger 100 with a novel flow channel design. This design avoids the heat exchange performance degradation caused by gaseous refrigerant retention in the first manifold 3 when the heat exchanger 100 operates as an evaporator, without affecting its heat exchange effect when operating as a condenser. Furthermore, it avoids the performance degradation caused by only gaseous refrigerant flowing through the refrigerant path in the heat exchange plate 10 at the inlet side of the first manifold 3, thus improving the heat exchange performance of the heat exchanger 100 when operating as an evaporator.

[0038] The following is for reference. Figures 1-8 A heat exchanger 100 according to an embodiment of the present invention is described.

[0039] According to embodiments of the present invention, the heat exchanger can be a finless heat exchanger, particularly a heat exchanger 100 composed of stacked heat exchange plates 10 having internal refrigerant flow paths, wherein there is a space between the heat exchange plates 10 to allow air to flow so that air can exchange heat with the refrigerant in the refrigerant flow paths.

[0040] Heat exchanger 100 includes a plurality of heat exchange plates 10, the plurality of heat exchange plates 10 being arranged along the thickness direction of the heat exchange plates 10 (e.g., Figure 1 The heat exchange plates 10 are stacked in the CD direction (as shown), and the length direction of the heat exchange plates 10 is (e.g., ...). Figure 1 The AB direction shown is set to intersect the horizontal plane, that is, the vertical direction of the heat exchanger 100 is in the same direction as the length direction of the heat exchange plate 10, the longitudinal direction of the heat exchanger 100 is in the same direction as the thickness direction of the heat exchange plate 10, and the transverse direction of the heat exchanger 100 is in the same direction as the width direction of the heat exchange plate 10 (e.g., the AB direction is shown in the figure). Figure 1 (The EF direction shown is the same).

[0041] The heat exchange plate 10 has multiple branch channels 2 extending along its length at its center. These branch channels 2 are independent of each other to avoid mutual interference of the refrigerant within the channels, which would affect the normal flow of the refrigerant. The multiple branch channels 2 are arranged at intervals along the width of the heat exchange plate 10 to ensure that the branch channels 2 are evenly distributed within the heat exchange plate 10, thereby improving heat exchange performance.

[0042] A first collecting channel 1 is provided on the lower side of the heat exchange plate 10, which is connected to the lower end of the multiple branch channels 2. The first collecting channel 1 can collect the refrigerant in each branch channel 2 when the heat exchanger 100 is cooling, and distribute the refrigerant to each branch channel 2 when the heat exchanger 100 is heating. The first collecting channel 1 extends in the width direction to communicate with the multiple branch channels 2 that are spaced apart in the width direction of the heat exchange plate 10.

[0043] A first confluence channel 3 is formed in the portion of the plurality of heat exchange plates 10 located below the first manifold channel 1, extending through the plurality of heat exchange plates 10 in the thickness direction. The first confluence channel 3 is connected to the refrigerant flow path in each heat exchange plate 10 below the heat exchange plate 10, and the refrigerant achieves heat exchange in the first manifold channel 1 and the plurality of branch channels 2 provided in the heat exchange plate 10.

[0044] When the refrigerant in the first confluence channel 3 is transported to the first collection channel 1, the longitudinal flow trend of the refrigerant will disappear, thereby effectively suppressing the refrigerant deviation that occurs during the process of the refrigerant entering each branch channel 2.

[0045] When the heat exchanger 100 is heating, the refrigerant that enters the heat exchanger 100 through the first manifold 3 is split and flows into the first manifold 1 of multiple heat exchange plates 10. After being split twice in the first manifold 1, it enters each branch 2 for heat exchange.

[0046] When using heat exchanger 100 for refrigeration, heat exchanger 100 will operate as a condenser. The high-temperature and high-pressure gaseous refrigerant, after being pressurized by the compressor, enters multiple branch channels 2 in the heat exchange plate 10 after being split from the top of heat exchanger 100. After heat exchange, the gaseous refrigerant is converted into liquid refrigerant and finally converges into the first confluence channel 3, and is further transported to the expander to realize the circulation of refrigerant.

[0047] When using heat exchanger 100 for refrigeration, the refrigeration effect is good because the refrigerant splitting and the refrigerant converging in the first confluence channel 3 are both unidirectional.

[0048] When the heat exchanger 100 is needed for heating, the flow direction of the refrigerant is reversed, and the heat exchanger 100 will operate as an evaporator. At this time, the refrigerant will be supplied to the first manifold 3 of the heat exchanger 100 in a gas-liquid two-phase flow state. After being split in the first manifold 3, the refrigerant enters the refrigerant flow path of the heat exchange plate 10. After heat exchange, the refrigerant in the gas-liquid two-phase flow state is converted into gaseous refrigerant. Finally, after being collected, it is further transported to the compressor to realize the circulation of refrigerant.

[0049] Since the refrigerant is supplied to the first confluence channel 3 of the heat exchanger 100 in the state of gas-liquid two-phase flow, and the refrigerant contains a certain amount of gas, it can be determined from the mass, velocity and dryness of the refrigerant that the gas-liquid two-phase flow is a flow pattern of clumps, with bubbles flowing in the liquid in the shape of cannonballs. Therefore, a large amount of gaseous refrigerant will accumulate above the first confluence channel 3.

[0050] In order to connect the first manifold 3 with the refrigerant flow path in the heat exchange plate 10, a connecting channel is provided between the first manifold 3 and the first collector 1. When the connecting channel is only connected to the upper part of the first manifold 3, the gaseous refrigerant with low density will flow above the first manifold 3, and the liquid refrigerant with high density will flow below the first manifold 3. The gaseous refrigerant can easily enter the refrigerant flow path of the heat exchange plate 10 from the connecting channel connected to the upper part of the first manifold 3. Therefore, the refrigerant flow path of the heat exchange plate 10 near the inlet side of the first manifold 3 is mostly gaseous refrigerant. As a result, this part of the heat exchange plate 10 cannot absorb heat, which leads to a reduction in the heat exchange performance of the heat exchanger 100.

[0051] Furthermore, when the connecting channel is only connected to the lower part of the first manifold 3, the less dense gaseous refrigerant will flow above the first manifold 3, while the more dense liquid refrigerant will flow below the first manifold 3. The liquid refrigerant can easily enter the refrigerant flow path of the heat exchange plate 10 from the connecting channel connected to the lower part of the first manifold 3. Therefore, a large amount of gaseous refrigerant will remain inside the first manifold 3. When the gaseous refrigerant remains at the end opposite to the inlet of the first manifold 3, the liquid refrigerant will be unable to move to the end of the first manifold 3, resulting in a decrease in the heat exchange performance of the heat exchange plate 10 connected near the end of the first manifold 3, and consequently a decrease in the overall heat exchange performance of the heat exchanger 100.

[0052] Therefore, the heat exchanger 100 of this embodiment of the invention is designed with two connecting channels between the first confluence channel 3 and the first collection channel 1. Specifically, the first confluence channel 3 and the first collection channel 1 are connected by the first connecting channel 5, and the first confluence channel 3 and the first collection channel 1 are also connected by the second connecting channel 6. The connection point between the first connecting channel 5 and the first confluence channel 3 is higher than the connection point between the second connecting channel 6 and the first confluence channel 3.

[0053] Therefore, when the heat exchanger 100 is heating, the gaseous refrigerant and liquid refrigerant in the gas-liquid two-phase flow state flowing in through the first manifold 3 can be reasonably distributed. They enter the first collector 1 from the first connecting channel 5 and the second connecting channel 6, and undergo secondary distribution in the first collector 1. After being converted into gaseous refrigerant through the branch channel 2, they are collected and further transported to the compressor to realize the circulation of refrigerant.

[0054] Specifically, the gaseous refrigerant flowing through the inlet side of the first manifold channel 3 of the heat exchanger 100 can enter the first collector channel 1 of the heat exchange plate 10 near the inlet side through the first connecting channel 5, and flow upward through the branch channel 2 of the heat exchange plate 10. At the same time, the liquid refrigerant flowing through the inlet side of the first manifold channel 3 can enter the first collector channel 1 of the heat exchange plate 10 near the inlet side through the second connecting channel 6, and after heat exchange through the branch channel 2 of the heat exchange plate 10, it is converted into gaseous refrigerant and flows upward. Thus, the heat exchange plate 10 near the inlet side of the first manifold channel 3 can both expel the gaseous refrigerant from the first manifold channel 3 and achieve heat exchange through the liquid refrigerant, ensuring the heat exchange performance of the heat exchanger 100.

[0055] Furthermore, since the gaseous refrigerant in the first manifold 3 of the heat exchanger 100 can enter the first manifold 1 of the heat exchange plate 10 through the first connecting 5, and flow upward through the branch 2 of the heat exchange plate 10 to the outside of the heat exchanger 100, the gaseous refrigerant in the first manifold 3 can be discharged in time, avoiding the stagnation of refrigerant gas in the heat exchanger 100, and further ensuring the heat exchange performance of the heat exchanger 100.

[0056] According to an embodiment of the present invention, the heat exchanger 100 can improve the heat exchange performance of the heat exchanger 100 when operating as an evaporator without affecting the heat exchange effect when the heat exchanger 100 operates as a condenser.

[0057] Furthermore, the heat exchanger 100 is used in an air conditioning unit. The connection between the first connecting channel 5 and the first collecting channel 1 is located downstream in the airflow direction compared to the connection between the second connecting channel 6 and the first collecting channel 1. Since the liquid refrigerant flows more from the branch channel 2 near the connection between the second connecting channel 6 and the first collecting channel 1, while the gaseous refrigerant that affects the heat exchange performance flows from the branch channel 2 near the connection between the first connecting channel 5 and the first collecting channel 1, by making the connection between the first connecting channel 5 and the first collecting channel 1 located downstream in the airflow direction compared to the connection between the second connecting channel 6 and the first collecting channel 1, the air can first flow to the branch channel 2 near the connection between the second connecting channel 6 and the first collecting channel 1, which has better heat exchange performance, thus improving the heat exchange performance at this part of the branch channel 2. Only then will the gas flow to the branch channel 2 near the connection between the first connecting channel 5 and the first collecting channel 1, further reducing the impact of the gaseous refrigerant on the heat exchange performance.

[0058] In other words, by placing the branch flow channel 2 with better performance of heat exchanger 100 upstream of the air flow direction and the branch flow channel 2 with poorer heat exchange performance downstream of the air flow direction, the heat exchange performance of heat exchanger 100 can be improved, thereby further improving the heat exchange performance of heat exchanger 100 in the heating state.

[0059] Furthermore, when no gaseous refrigerant passes through the first manifold 3, both the first connecting channel 5 and the second connecting channel 6 can be used to transport liquid refrigerant, such as... Figure 6 As shown, at this time, liquid refrigerant can be supplied to more branch channels 2, and heat exchanger 100 can obtain higher heat exchange performance.

[0060] Figure 7 When both gaseous and liquid refrigerant are supplied to the first manifold 3, the distribution of refrigerant within the heat exchange plates 10 of the heat exchanger 100 is as follows: the black portion represents liquid refrigerant, and the white portion represents gaseous refrigerant. The gaseous refrigerant is concentrated in the branch channel 2 near the end of the first manifold 1 in the heat exchanger 100, preventing it from stagnating in the first manifold 3 and affecting the flow rate of the liquid refrigerant within the heat exchanger 100. This improves the heat exchange performance of the heat exchanger 100. Furthermore, it ensures that the heat exchange plates 10 near the inlet side of the first manifold 3 also have a supply of liquid refrigerant, further enhancing the heat exchange performance of the heat exchanger 100.

[0061] Figure 8This is a heat flow analysis comparison diagram of the heat exchanger 100 according to an embodiment of the present invention and other heat exchangers 100 with different structures. From left to right, the diagrams are as follows: (1) a heat flow analysis comparison diagram of the heat exchanger 100 when the connecting channel is only connected above the first confluence channel 3; (2) a heat flow analysis comparison diagram of the heat exchanger 100 when the connecting channel is only connected below the first confluence channel 3; and (3) a heat flow analysis diagram of the heat exchanger 100 when the connecting channel of the embodiment of the present invention is simultaneously connected above and below the first confluence channel 3 and respectively connected to both ends of the first collector channel 1. The heat flow analysis demonstrates that in the heat exchanger 100 of the embodiment of the present invention, liquid refrigerant can reach the end of the heat exchanger 100, and liquid refrigerant is also supplied to the heat exchange plate 10 near the inlet side of the first confluence channel 3. Gas refrigerant can be concentrated at one end of the heat exchanger 100, and liquid refrigerant can be supplied to the upstream side of the air with higher heat exchange performance, thus improving the performance of the heat exchanger 100.

[0062] like Figure 2 As shown, according to some embodiments of the present invention, the first connecting channel 5 includes a first lateral extension section 51 and a first vertical extension section 52. One end of the first lateral extension section 51 is connected to the first confluence channel 3 and the other end is connected to the lower end of the first vertical extension section 52. The upper end of the first vertical extension section 52 is connected to the first collection channel 1. Thus, the refrigerant can be guided to a position that is vertically parallel to the first end of the first collection channel 1 through the first lateral extension section 51, and the refrigerant can be guided to the first collection channel 1 through the first vertical extension section 52, thereby realizing the connection between the upper end of the first confluence channel 3 and the first collection channel 1.

[0063] Reference Figure 2 According to some embodiments of the present invention, the second connecting channel 6 includes a second lateral extension section 61 and a second vertical extension section 62. One end of the second lateral extension section 61 is connected to the first confluence channel 3 and the other end is connected to the lower end of the second vertical extension section 62. The upper end of the second vertical extension section 62 is connected to the first collection channel 1. Thus, the refrigerant can be guided to a position parallel to the first collection channel 1 in the vertical direction through the second lateral extension section 61, and the refrigerant can be guided to the first collection channel 1 through the second vertical extension section 62, thereby realizing the connection between the first confluence channel 3 and the first collection channel 1.

[0064] like Figure 4As shown, the first collecting channel 1 includes a first collecting section 11 and a second collecting section 12, which are arranged side by side along the width direction. A first connecting channel 5 is connected to the first collecting section 11, and a second connecting channel 6 is connected to the second collecting section 12. The first collecting channel 1 allows gaseous refrigerant to pass through when gaseous refrigerant is present in the first confluence channel 3, or liquid refrigerant to pass through when there is less gaseous refrigerant in the first confluence channel 3. The structure of the first collecting channel 1 restricts the flow of liquid refrigerant to the second collecting section 12 as much as possible, while gaseous refrigerant is discharged only through the first collecting section 11. This results in a more rational distribution of liquid and gaseous refrigerant within the heat exchanger 100, improving heat exchange performance.

[0065] The length of the first collector 11 is shorter than the length of the second collector 12, so that the length of the first collector channel 1 through which the gaseous refrigerant can pass is shorter. This reduces the number of branch channels 2 required in the heat exchanger 100 to ensure the passage of the gaseous refrigerant in the first collector channel 1, and the fewer branch channels 2 affected by the passage of the gaseous refrigerant. As a result, the flow rate of the liquid refrigerant in the branch channels 2 of the heat exchange plate 10 can be increased. Consequently, the gaseous refrigerant has a smaller impact on the heat exchange performance of the heat exchanger 100, thereby further improving the heat exchange performance of the heat exchanger 100.

[0066] Furthermore, since the air flow direction in the heat exchanger 100 is from the branch channel 2 corresponding to the second collection section 12 of the first collection channel 1 to the branch channel 2 corresponding to the first collection section 11, the air heat exchange performance is better near the branch channel 2 corresponding to the second collection section 12. Therefore, increasing the flow rate of the liquid refrigerant in the branch channel 2 corresponding to the second collection section 12 can further improve the heat exchange performance of the heat exchanger 100.

[0067] like Figure 3 As shown, the top of the first collector 11 is higher than the top of the second collector 12. Since the gaseous refrigerant will concentrate at the top of the second collector 12, when the gaseous refrigerant flows from the first collector 11 to the second collector 12, it will be inhibited by the fact that the top of the second collector 12 is lower than the first collector 12. This makes it difficult for the gaseous refrigerant to flow further into the second collector 12. Therefore, the influence of the gaseous refrigerant on the flow rate of the liquid refrigerant in the branch channel 2 corresponding to the first collector channel 1 of the heat exchange plate 10 is further reduced. This reduces the influence of the gaseous refrigerant on the branch channel 2 with better heat exchange performance in the upstream part of the air, ensures the flow rate of the liquid refrigerant in the branch channel 2 in the upstream part of the air, and improves the heat exchange performance of the heat exchanger 100.

[0068] According to some embodiments of the present invention, a downwardly projecting protrusion 13 is formed between the top of the first collector 11 and the top of the second collector 12. Since the gaseous refrigerant concentrates at the top of the second collector 12, when the gaseous refrigerant flows from the first collector 11 to the second collector 12, it is inhibited by the downwardly projecting protrusion 13 between the tops of the first collector 11 and the second collector 12, making it difficult for the gaseous refrigerant to flow further into the second collector 12. Therefore, the influence of the gaseous refrigerant on the flow rate of the liquid refrigerant in the branch channel 2 corresponding to the first collector 11 of the heat exchange plate 10 is further reduced, and the influence of the gaseous refrigerant on the heat exchange performance of the branch channel 2 with better heat exchange performance in the upstream part of the air is also reduced, ensuring the flow rate of the liquid refrigerant in the branch channel 2 in the upstream part of the air and improving the heat exchange performance of the heat exchanger 100.

[0069] Reference Figure 5 A downward-curving section 14 is formed between the first collector section 11 and the second collector section 12. Since the gaseous refrigerant concentrates at the top of the second collector section 12, when the gaseous refrigerant flows from the first collector section 11 to the second collector section 12, it is inhibited by the downward-curving section 14, making it difficult for the gaseous refrigerant to flow further into the second collector section 12. Therefore, the influence of the gaseous refrigerant on the flow rate of the liquid refrigerant in the branch channel 2 corresponding to the first collector section 11 of the heat exchange plate 10 is further reduced, and the influence of the gaseous refrigerant on the heat exchange performance of the branch channel 2 with better heat exchange performance in the upstream part of the air is also reduced, ensuring the flow rate of the liquid refrigerant in the branch channel 2 in the upstream part of the air and improving the heat exchange performance of the heat exchanger 100.

[0070] like Figure 4 As shown, the first flow channel 1 includes a first end and a second end. The connection between the first connecting channel 5 and the first flow channel 1 is located at the first end, and the connection between the second connecting channel 6 and the first flow channel 1 is located at the second end. The first end is located downstream in the airflow direction, and the second end is located upstream in the airflow direction. The first flow collecting part 11 is close to the first end, and the second flow collecting part 12 is close to the second end.

[0071] In some embodiments, the flow area of ​​the first manifold 1 near the first end is larger than the flow area of ​​the first manifold 1 near the second end. As a result, the gaseous refrigerant can be concentrated more near the first end, which makes the length of the first manifold 1 corresponding to the gaseous refrigerant shorter. Consequently, fewer branch channels 2 are needed in the heat exchanger 100 to ensure that the gaseous refrigerant in the first manifold 1 passes through, thereby increasing the flow rate of the liquid refrigerant in the branch channel 2 with better heat exchange performance corresponding to the first manifold 1. In other words, the gaseous refrigerant in the first manifold 3 has a smaller impact on the heat exchange performance of the heat exchanger 100, thereby further improving the heat exchange performance of the heat exchanger 100.

[0072] In some embodiments, a first collecting channel 1 and multiple branch channels 2 are arranged within the heat exchange plate 10. The space between heat exchange plates 10 serves as an air channel, and the refrigerant achieves heat exchange in the first collecting channel 1 and multiple branch channels 2 within the heat exchange plate 10. A first collecting channel 3 penetrates multiple heat exchange plates 10 to communicate with the first collecting channel 1 and branch channels 2 arranged within the heat exchange plate 10.

[0073] In other embodiments, the heat exchange plate 10 includes two plate-shaped components with grooves machined on them. The two plate-shaped components are fitted together to define a first collection channel 1, multiple branch channels 2, a first connecting channel 5, and a second connecting channel 6. The space between the heat exchange plate 10 and its adjacent heat exchange plate 10 is an air channel. The refrigerant achieves heat exchange in the first collection channel 1 and multiple branch channels 2 defined by the heat exchange plate 10. The first collection channel 3 penetrates multiple heat exchange plates 10 to connect with the first collection channel 1 and branch channels 2 defined by the two plate-shaped components.

[0074] like Figure 1 As shown, a second collecting channel 7 is provided on the upper side of the heat exchange plate 10, which is connected to the upper end of the multiple branch channels 2. The second collecting channel 7 can collect the refrigerant in each branch channel 2 when the heat exchanger 100 is heating, and distribute the refrigerant to each branch channel 2 when the heat exchanger 100 is cooling. Furthermore, the second collecting channel 7 can also ensure that the refrigerant flows evenly into each branch channel 2.

[0075] A second confluence channel 4 is formed in the portion of the multiple heat exchange plates 10 above the second manifold 7, extending through the multiple heat exchange plates 10 in the thickness direction. The second confluence channel 4 is connected to the refrigerant flow path in each heat exchange plate 10 above the heat exchange plate 10. The second confluence channel 4 can deliver gaseous refrigerant to each heat exchange plate 10 of the heat exchanger 100 when the heat exchanger 100 is cooling, and can exhaust the gaseous refrigerant generated in each heat exchange plate 10 of the heat exchanger 100 when the heat exchanger 100 is heating.

[0076] Furthermore, the second manifold 4 and the second collector 7 are connected by the third connecting channel 8. That is, when the heat exchanger 100 is heating, the refrigerant in the first manifold 3 enters the first collector 1 through the first connecting channel 5 and the second connecting channel 6. After being split in the first collector 1, it enters the branch channel 2. In the branch channel 2, it absorbs heat and is converted into gaseous refrigerant before entering the second collector 7. Then, it enters the second manifold 4 through the third connecting channel 8 and is discharged outside the heat exchanger 100.

[0077] Among them, the two plate-shaped components also define the second flow channel 7 and the third connecting flow channel 8.

[0078] According to some embodiments of the present invention, the heat exchanger 100 includes a first connecting pipe 91 and a second connecting pipe 92, which are disposed on the same side of the longitudinal direction of the heat exchanger 100 to make the overall structure of the heat exchanger 100 more compact and to facilitate the arrangement of the heat exchanger 100. The first connecting pipe 91 is connected to the first manifold 3 and the second connecting pipe 92 is connected to the second manifold 4.

[0079] In other words, when the heat exchanger 100 is heating, the refrigerant in a gas-liquid two-phase flow state enters the first manifold 3 of the heat exchanger 100 through the first connecting pipe 91. The refrigerant in the first manifold 3 enters the first collector 1 through the first connecting channel 5 and the second connecting channel 6. After being split in the first collector 1, it enters the branch channel 2. In the branch channel 2, it absorbs heat and is converted into gaseous refrigerant before entering the second collector 7. Then, it enters the second manifold 4 through the third connecting channel 8 and is discharged from the heat exchanger 100 through the second connecting pipe 92.

[0080] Furthermore, the first confluence channel 3 and the second confluence channel 4 can be cylindrical channels with a serpentine pattern, and the central axis of the first confluence channel 3 and the second confluence channel 4 extends longitudinally.

[0081] A specific embodiment of the heat exchanger 100 is described below with reference to the accompanying drawings.

[0082] like Figure 1 As shown, the heat exchanger 100 includes a plurality of heat exchange plates 10 stacked longitudinally, the thickness direction of the heat exchange plates 10 extending longitudinally, the length direction of the heat exchange plates 10 extending vertically, and the width direction of the heat exchange plates 10 extending laterally.

[0083] The heat exchange plate 10 has grooves machined on it, and the heat exchange plate 10 and the heat exchange plate 10 adjacent to it on one side define a first flow channel 1, a second flow channel 7, a first connecting flow channel 5, a second connecting flow channel 6, a third connecting flow channel 8, and multiple branch flow channels 2. The multiple branch flow channels 2 extend vertically and are arranged sequentially in the transverse direction. The second flow channel 7 and the first flow channel 1 extend in the transverse direction and are respectively located on the upper and lower sides of the branch flow channels 2.

[0084] The first confluence channel 3 and the second confluence channel 4 extend longitudinally and respectively penetrate multiple heat exchange plates 10, so as to communicate with the first collection channel 1 and the second collection channel 7 defined by the heat exchange plates 10. Among them, the first confluence channel 3 is connected to the first collection channel 1 through the first connecting channel 5 and the second connecting channel 6, the second confluence channel 4 is connected to the second collection channel 7 through the third connecting channel 8, and the branch channel 2 is connected between the first collection channel 1 and the second collection channel 7.

[0085] The first connecting channel 5 connects the upper end of the first confluence channel 3 to the first side of the first collection channel 1, and the second connecting channel 6 connects the lower end of the first confluence channel 3 to the second side of the first collection channel 1, so that the gaseous refrigerant and the liquid refrigerant can flow through different connecting channels, thereby avoiding the gaseous refrigerant from affecting the heat exchanger 100.

[0086] The space between heat exchange plate 10 and its adjacent heat exchange plate 10 on the other side is an air flow channel. Air flows from the second side to the first side in the transverse direction of heat exchange plate 10 to further improve the heat exchange effect of heat exchanger 100.

[0087] An air conditioning device according to an embodiment of the present invention includes the heat exchanger 100 described in the above embodiment. Since the heat exchanger 100 according to the embodiment of the present invention has the above-described technical effects, the air conditioning device according to the embodiment of the present invention also has the above-described technical effects, that is, by employing the heat exchanger 100, it is beneficial to improve the heat exchange performance of the heat exchanger 100 when operating as an evaporator, thereby improving the working performance of the air conditioning device.

[0088] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "example," "specific example," or "some examples," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of the invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples. In addition, those skilled in the art can combine and integrate the different embodiments or examples described in this specification.

[0089] Although embodiments of the present invention have been shown and described above, it is understood that the above embodiments are exemplary and should not be construed as limiting the present invention. Those skilled in the art can make changes, modifications, substitutions and variations to the above embodiments within the scope of the present invention.

Claims

1. A heat exchanger, characterized in that, The heat exchanger includes multiple heat exchange plates stacked along their thickness direction. The length direction of each heat exchange plate intersects a horizontal plane. Multiple branch channels extending along the length direction are provided at the middle of each heat exchange plate. These branch channels are spaced apart along the width direction of the heat exchange plate. A first collecting channel, connected to the lower end of each branch channel, is provided on the portion of the heat exchange plate located below the branch channels. This first collecting channel extends along the width direction. Wherein, a first confluence channel is formed in the portion of the plurality of heat exchange plates located below the first collection channel, extending through the plurality of heat exchange plates along the thickness direction. The first confluence channel is connected to the first collection channel through a first connecting channel, and the first confluence channel is also connected to the first collection channel through a second connecting channel. The connection point between the first connecting channel and the first confluence channel is higher than the connection point between the second connecting channel and the first confluence channel. The heat exchanger is used in an air conditioning unit, and the connection between the first connecting channel and the first collecting channel is located downstream of the airflow direction compared to the connection between the second connecting channel and the first collecting channel.

2. The heat exchanger according to claim 1, characterized in that, The first connecting channel includes a first lateral extension section and a first vertical extension section. One end of the first lateral extension section is connected to the first converging channel and the other end is connected to the lower end of the first vertical extension section. The upper end of the first vertical extension section is connected to the first collecting channel.

3. The heat exchanger according to claim 1, characterized in that, The second connecting channel includes a second lateral extension section and a second vertical extension section. One end of the second lateral extension section is connected to the first converging channel and the other end is connected to the lower end of the second vertical extension section. The upper end of the second vertical extension section is connected to the first converging channel.

4. The heat exchanger according to claim 1, characterized in that, The first flow channel includes a first flow collection section and a second flow collection section, which are arranged side by side along the width direction. The first connecting channel is connected to the first flow collection section, and the second connecting channel is connected to the second flow collection section.

5. The heat exchanger according to claim 4, characterized in that, The length of the first current collector is less than the length of the second current collector.

6. The heat exchanger according to claim 4, characterized in that, The top of the first collector is higher than the top of the second collector.

7. The heat exchanger according to claim 4, characterized in that, A protrusion protruding downward along the length direction is formed between the top of the first collector and the top of the second collector.

8. The heat exchanger according to claim 7, characterized in that, A curved section that bends downward along the length direction is formed between the first collector section and the second collector section.

9. The heat exchanger according to any one of claims 1-8, characterized in that, The heat exchange plate includes two plate-shaped components that are fitted together to define the first collection channel, the plurality of branch channels, the first connecting channel, and the second connecting channel.

10. The heat exchanger according to claim 9, characterized in that, A second collecting channel is provided on the portion of the heat exchange plate above the plurality of branch channels, connecting to the upper ends of the plurality of branch channels. A second converging channel is formed on the portion of the plurality of heat exchange plates above the second collecting channel, penetrating the plurality of heat exchange plates along the thickness direction. The second converging channel and the second collecting channel are connected by a third connecting channel. The two plate-shaped components further define the second flow collection channel and the third connecting channel.

11. The heat exchanger according to claim 10, characterized in that, The heat exchanger includes a first connecting pipe and a second connecting pipe, wherein the first connecting pipe is connected to the first confluence channel and the second connecting pipe is connected to the second confluence channel.

12. An air conditioning device, characterized in that, Includes the heat exchanger according to any one of claims 1-11.

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