Heat exchanger

Abstract

The invention relates to a heat exchanger which comprises heat exchange plates arranged in a stacked mode, the included angle between the stacking direction of the heat exchange plates and the gravity direction is larger than 0 degree, the heat exchanger is provided with outflow channels, the outflow channels penetrate through the heat exchange plates in the stacking direction of the heat exchange plates, first flow channels are arranged between the adjacent heat exchange plates, and the first flow channels communicate with the outflow channels. At least part of the first flow channel comprises a heat exchange area and a bypass area, the bypass area is located above the heat exchange area in the gravity direction, and under the same width, the circulation sectional area of at least part of the bypass area is larger than that of the heat exchange area; the phase refrigerant is more easily discharged from the outflow channel through the bypass area, the proportion of the gas-phase refrigerant is reduced, then the proportion of the two-phase area (liquid-phase area and gas-phase area) refrigerant is increased, and due to the fact that the heat exchange capacity of the two-phase area refrigerant is higher than that of the gas-phase area refrigerant, the heat exchange performance of the heat exchanger is improved.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of heat management, in particular to a heat exchanger. BACKGROUND

[0002] When the heat exchanger is working, the liquid phase of the refrigerant evaporates into gas phase, and the gas phase is lighter than the liquid phase. When the heat exchanger is installed in a way that the stacking direction of the heat exchange plates is not parallel to the direction of gravity, the gas phase refrigerant will gather at the top of the refrigerant flow channel, and thus a gas phase area will appear in the refrigerant flow channel. Because the heat exchange effect of the gas phase refrigerant is worse than that of the liquid phase refrigerant, the heat exchange performance of the gas phase area is worse than that of the area with both liquid phase and gas phase. The gathering of the gas phase refrigerant at the top of the refrigerant channel will affect the heat exchange performance of the heat exchanger. SUMMARY

[0003] Therefore, it is necessary to provide a heat exchanger with improved heat exchange performance to solve the above problems.

[0004] The technical scheme adopted by the present application is as follows:

[0005] A heat exchanger comprises heat exchange plates stacked in a stacking direction, the angle between the stacking direction of the heat exchange plates and the direction of gravity is greater than 0°, the heat exchanger has an outflow channel, the outflow channel passes through the heat exchange plates along the stacking direction of the heat exchange plates, the first flow channel is formed between adjacent heat exchange plates, the first flow channel is in communication with the outflow channel, at least part of the first flow channel comprises a heat exchange area and a bypass area, the bypass area is located above the heat exchange area in the direction of gravity, and the flow cross-sectional area of at least part of the bypass area is greater than the flow cross-sectional area of the heat exchange area under the same width.

[0006] In the above technical solution, when the refrigerant flows in the first flow channel, the temperature of the refrigerant near the outlet channel is higher, and there is more gaseous refrigerant present. Furthermore, because the angle between the stacking direction of the heat exchange plates and the direction of gravity is greater than 0°, the gaseous phase of the refrigerant is more likely to accumulate in the upper region of the first flow channel. A bypass zone is provided in at least a portion of the first flow channel. For the same width, the flow cross-sectional area of ​​at least a portion of the bypass zone is larger than the flow cross-sectional area of ​​the heat exchange zone. That is, compared to the heat exchange zone, the refrigerant flows more easily in the bypass zone. And because the bypass zone is located above the heat exchange zone along the direction of gravity, the gaseous phase is more likely to accumulate. The gaseous refrigerant flows more easily in the bypass zone, thus allowing it to exit more easily through the bypass zone and reduce its proportion. This, in turn, increases the proportion of the two-phase (liquid and gas) refrigerant. Since the heat exchange capacity of the two-phase refrigerant is higher than that of the gaseous refrigerant, the heat exchanger's performance is improved. Furthermore, because the flow cross-sectional area of ​​the bypass zone is larger than that of the heat exchange zone, the refrigerant exits more easily through the bypass zone and reduces its pressure drop. As the pressure of the refrigerant decreases, its temperature also decreases, further enhancing its heat exchange performance. Attached Figure Description

[0007] Figure 1 A three-dimensional structural schematic diagram of the heat exchanger provided by the present invention;

[0008] Figure 2 for Figure 1 A schematic diagram of the first embodiment of the heat exchange plate;

[0009] Figure 3 for Figure 2 Schematic diagram of the structure in the AA direction;

[0010] Figure 4 for Figure 2 Schematic diagram of the structure in the middle BB direction;

[0011] Figure 5 for Figure 2 Schematic diagram of the structure in the CC direction;

[0012] Figure 6 for Figure 2 Schematic diagram of the structure in the DD direction;

[0013] Figure 7 for Figure 2 Schematic diagram of the mating structure of the heat exchange plates;

[0014] Figure 8 This is a schematic diagram of the heat exchanger in Example 1;

[0015] Figure 9 for Figure 8Schematic diagram of the structure in the GG direction;

[0016] Figure 10 for Figure 8 Schematic diagram of the structure in the HH direction;

[0017] Figure 11 for Figure 8 Schematic diagram of the structure in the FF direction;

[0018] Figure 12 for Figure 8 Schematic diagram of the structure in the EE direction;

[0019] Figure 13 for Figure 8 A schematic diagram of the mating structure of the first and second plates;

[0020] Figure 14 This is a schematic diagram of the structure of the first plate in Embodiment 2;

[0021] Figure 15 This is a schematic diagram of the mating structure of the first and second plates in Embodiment 2;

[0022] Figure 16 This is a schematic diagram of the first mating structure of the first plate and the second plate in Embodiment 3;

[0023] Figure 17 This is a schematic diagram of the second mating structure of the first and second plates in Embodiment 3;

[0024] Figure 18 for Figure 17 A schematic diagram of the structure of the first plate in the middle;

[0025] Figure 19 This is a schematic diagram of the mating structure of the first plate and the second plate in Embodiment 4;

[0026] Figure 20 This is a schematic diagram of the structure of the first plate in Example 5;

[0027] Figure 21 for Figure 2 A schematic diagram of another embodiment of the heat exchange plate;

[0028] Figure 22 for Figure 21 A schematic diagram of another implementation of the inflow and outflow channels.

[0029] Explanation of reference numerals in the attached figures

[0030] 11. Heat exchange plate; 111. First plate; 112. Second plate; 12. Outflow channel; 121. First channel; 122. Second channel; 13. First flow channel; 131. First wall; 132. Second wall; 133. Rib; 134. Third wall; 14. Protrusion; 141. Fourth wall; 142. First protrusion; 15. Base; 16. Bypass area; 161. Fifth wall; 162. Second protrusion; 163. Third protrusion; 17. First heat exchange channel; 18. Second heat exchange channel; 19. First opening; 20. Second opening; 21. Inflow channel; 22. Bypass channel; 23. Shielding part; 30. Heat exchange area; 31. Edge; 32. Substrate. Detailed Implementation

[0031] To make the objectives, technical solutions, and advantages of this invention clearer, the invention will be further described in detail below with reference to the accompanying drawings and technical solutions. It should be understood that the specific technical solutions described herein are merely illustrative of the invention and are not intended to limit the invention.

[0032] like Figures 1-22 The illustrated heat exchanger includes stacked heat exchange plates 11. The angle between the stacking direction of the heat exchange plates 11 and the direction of gravity is greater than 0°. During the heat exchange process, the liquid refrigerant absorbs heat and evaporates into a gaseous refrigerant. Since the gaseous refrigerant is lighter than the liquid phase, when the stacking direction of the heat exchange plates 11 is greater than 0° with the direction of gravity, the gaseous refrigerant will accumulate above the direction of gravity in the heat exchanger. The heat exchanger has an outlet channel 12 that passes through the heat exchange plates 11 along the stacking direction. A first flow channel 13 is provided between adjacent heat exchange plates 11, and the first flow channel 13 communicates with the outlet channel 12. It should be noted that the first flow channel 13 refers to the portion between adjacent heat exchange plates 11 that is directly connected to the outlet channel 12, for example, as shown in the diagram. Figure 2 In the heat exchange plates 11 shown, the first flow channel 13 refers to the entire area between adjacent heat exchange plates 11, such as... Figure 21 , 22 In the heat exchange plate 11 shown, the first flow channel 13 refers to the portion of the area connected to the outflow channel 12. Figure 2 , 21The area of ​​the first flow channel 13 highlighted in section 22 is only for illustrative purposes and does not limit the scope of the first flow channel 13 to the area highlighted in the box. The refrigerant flows in the first flow channel 13 and exits the heat exchanger from the outlet channel 12. At least a portion of the first flow channel 13 includes a heat exchange zone 30 and a bypass zone 16. The refrigerant mainly undergoes heat exchange in the heat exchange zone 30. Along the direction of gravity, the bypass zone 16 is located above the heat exchange zone 30. For the same width, at least a portion of the bypass zone 16 has a larger flow cross-sectional area than the heat exchange zone 30. Therefore, the refrigerant flows more easily in the bypass zone 16 than in the heat exchange zone 30. Because the bypass zone 16 is located above the heat exchange zone 30, and the gaseous refrigerant is located above the liquid refrigerant, the gaseous refrigerant can more easily pass through the bypass zone 16 and be discharged from the outlet channel 12, reducing the proportion of gaseous refrigerant and thus increasing the proportion of refrigerant in the two-phase zone (liquid and gaseous phases), thereby improving the heat exchange performance of the heat exchanger. Furthermore, since the flow cross-sectional area of ​​the bypass zone 16 is larger than that of the heat exchange zone 30, the refrigerant can more easily pass through the bypass zone 16 and be discharged from the outlet channel 12, reducing the pressure drop of the refrigerant. Since the pressure of the refrigerant decreases, the temperature of the refrigerant will decrease accordingly, thus further increasing the heat exchange performance of the refrigerant.

[0033] This article focuses on the structure of bypass area 16, which will be explained in detail below with attached figures.

[0034] Example 1

[0035] like Figures 1-13The first embodiment shown discloses a heat exchanger. The heat exchange plates 11 include a first plate 111 and a second plate 112 (the first plate 111 and the second plate 112 are collectively referred to as heat exchange plates 11). The first plate 111 and the second plate 112 are alternately stacked. In this embodiment, the stacking direction of the first plate 111 and the second plate 112 is perpendicular to the direction of gravity. The heat exchanger includes a first heat exchange channel 17 and a second heat exchange channel 18. 8 are located between adjacent first plates 111 and second plates 112. In this embodiment, refrigerant flows through the first heat exchange channel 17, and coolant flows through the second heat exchange channel 18. Heat exchange occurs between the refrigerant and the coolant. Along the stacking direction of the heat exchange plates 11, the first heat exchange channel 17 is located on one side of the first plate 111, and the second heat exchange channel 18 is located on the other side of the first plate 111. The first heat exchange channel 17 and the second heat exchange channel 18 are not connected. In this embodiment, the first heat exchange channel 17 and the second heat exchange channel 18 are connected. The heat exchange channels 18 are arranged alternately. In other embodiments, multiple first heat exchange channels 17 can be arranged continuously followed by a second heat exchange channel 18, or multiple second heat exchange channels 18 can be arranged continuously followed by a first heat exchange channel 17. The heat exchanger has a first channel 121 and a second channel 122 (the first channel 121 and the second channel 122 are collectively referred to as the outflow channel 12). The outflow channel 12 passes through the heat exchange plates 11 along the stacking direction of the heat exchange plates 11. The first channel 121 is connected to the first heat exchange channel 17, but not connected to the second heat exchange channel 18. The second channel 122 is connected to the second heat exchange channel 18, but not connected to the first heat exchange channel 17. There is a first flow channel 13 between adjacent first plates 111 and second plates 112. The first heat exchange channel 17 includes the first flow channel 13. Therefore, the first flow channel 13 in the first heat exchange channel 17 is connected to the first channel 121. The refrigerant flows in the first flow channel 13 and flows out of the first heat exchange channel 17 through the first channel 121.

[0036] Further, the heat exchanger includes a side portion 31 and a substrate 32. The side portion 31 is arranged circumferentially along the substrate 32. Along the stacking direction of the heat exchange plates 11, the side portion 31 is sealed to the side portion 31 of adjacent heat exchange plates 11, thereby connecting and fixing multiple heat exchange plates 11. The side portion 31 also seals the first heat exchange channel 17 and the second heat exchange channel 18 between adjacent heat exchange plates 11. Along the direction of gravity, the walls of the side portion 31 located on the upper and lower sides of the substrate 32 are defined as the first wall portion 131 and the second wall portion 132. In the direction of gravity, the wall portion forming the first flow channel 13 includes the first wall portion 131 and the second wall portion 132. The refrigerant is restricted by the first wall portion 131 and the second wall portion 132 and flows along the extension direction of the first wall portion 131 towards the outflow channel 12. Along the direction of gravity, the first wall portion 131... Located above the second wall portion 132, the bypass region 16 is closer to the first wall portion 131 than the heat exchange region 30 along the direction of gravity. The first wall portion 131 is located above the second wall portion 132 along the direction of gravity, and the bypass portion is closer to the first wall portion 131 than the heat exchange region 30. Therefore, the gaseous refrigerant is more likely to be discharged from the outlet channel 12 through the bypass region 16 than the liquid refrigerant, reducing the proportion of gaseous refrigerant and increasing the proportion of two-phase (liquid and gaseous) refrigerant, thereby improving the heat exchange performance of the heat exchanger. Furthermore, since the flow cross-sectional area of ​​the bypass region 16 is larger than that of the heat exchange region 30, the refrigerant is more likely to be discharged from the outlet channel 12 through the bypass region 16, reducing the pressure drop of the refrigerant. Since the pressure of the refrigerant decreases, the temperature of the refrigerant will decrease accordingly, thus further increasing the heat exchange performance of the refrigerant. In this embodiment, the first wall portion 131 is closer to the outflow channel 12 than the second wall portion 132, and the refrigerant flows in a diagonal flow. Alternatively, the second wall portion 132 may be closer to the outflow channel 12 than the first wall portion 131, and the refrigerant flows in a unilateral flow.

[0037] Furthermore, the heat exchange zone 30 includes a protrusion 14 and a base 15. The protrusion 14 protrudes relative to the base 15. It should be noted that in this embodiment, the protrusion direction of the protrusion 14 is opposite to that of the edge 31. Therefore, the edge 31 sealing the first heat exchange channel 17 is the edge 31 of the adjacent heat exchange plate 11. The protrusion 14 turbulently turbulently turbulents the refrigerant, thereby enhancing the heat exchange performance of the refrigerant. The protrusion 14 includes a fourth wall 141, and the bypass zone 16 includes a fifth wall 161. Along the stacking direction of the heat exchange plates 11, the fourth wall 141 is adjacent to the heat exchange plate 11 on the other side of the first heat exchange channel 17. The distance between the fifth wall portion 161 and the heat exchange plate 11 on the other side of the first heat exchange channel 17 is less than the distance between the fourth wall portion 141 and the heat exchange plate 11. Since the distance between the fourth wall portion 141 and the heat exchange plate 11 is less than the distance between the fifth wall portion 161 and the heat exchange plate 11, the flow cross-sectional area of ​​the first flow channel 13 between the fourth wall portion 141 and the heat exchange plate 11 is less than the flow cross-sectional area of ​​the first flow channel 13 between the fifth wall portion 161 and the heat exchange plate 11. That is, the flow cross-sectional area of ​​the heat exchange zone 30 is less than the flow cross-sectional area of ​​the bypass zone 16. Therefore, compared with the heat exchange zone 30, the refrigerant flows more easily in the bypass zone 16. In this embodiment, the protrusion The first plate 14 includes multiple first protrusions 142, which protrude into the first heat exchange channel 17 relative to the base 15. These protrusions turbulently flow the refrigerant within the first heat exchange channel 17, thereby enhancing the heat exchange effect. The fourth wall portion 141 is located at the top of the first protrusions 142. The first plate 111 includes a bypass region 16, which includes multiple second protrusions 162. These second protrusions 162 protrude into the first heat exchange channel 17 relative to the base 15 of the first plate 111. The inner protrusion 17 turbulents the refrigerant flowing within the first heat exchange channel 17, thereby enhancing the heat exchange effect. The fifth wall portion 161 is located at the top of the second protrusion 162. The distance between the fourth wall portion 141 and the base 15 of the first plate 111 is greater than the distance between the fifth wall portion 161 and the base 15 of the first plate 111. Therefore, the pressure drop in the first flow channel 13 at the second protrusion 162 is lower, making it easier for the refrigerant to flow between the fifth wall portion 161 and the heat exchange plate 11. Furthermore, the reduced refrigerant pressure corresponds to a decrease in refrigerant temperature, further increasing the heat exchange performance of the refrigerant. Alternatively, as... Figure 20As shown, the protrusion 14 includes a plurality of first protrusions 142, and the bypass region 16 includes a plurality of second protrusions 162. The second protrusions 162 are sparser than the first protrusions 142. In this embodiment, because the second protrusions 162 are sparser than the first protrusions 142, the distance between adjacent second protrusions 162 is greater than the distance between adjacent first protrusions 142. The refrigerant flows more easily between the second protrusions 162. Therefore, the flow cross-sectional area at the bypass region 16 is larger than the flow cross-sectional area at the heat exchange region 30, and the refrigerant flows more freely in the bypass region 16. The gaseous refrigerant flows more easily through the bypass zone 16 and is discharged from the outlet channel 12 more easily, reducing the proportion of gaseous refrigerant and increasing the proportion of two-phase (liquid and gaseous) refrigerant, thereby improving the heat exchange performance of the heat exchanger. Furthermore, since the flow cross-sectional area of ​​the bypass zone 16 is larger than that of the heat exchange zone 30, the refrigerant is more easily discharged from the outlet channel 12 through the bypass zone 16, reducing the pressure drop of the refrigerant. Since the pressure of the refrigerant decreases, the temperature of the refrigerant will decrease accordingly, thus further increasing the heat exchange performance of the refrigerant.

[0038] like Figures 8-13 As shown, the heat exchange plate 11 includes a first opening 19. Along the stacking direction of the heat exchange plate 11, multiple first openings 19 form an outflow channel 12, which is connected to the first heat exchange channel 17. The heat exchange plate 11 also includes a second opening 20. Along the stacking direction of the heat exchange plate 11, the heat exchanger includes an inflow channel 21. Multiple second openings 20 form an inflow channel 21, which is connected to the first heat exchange channel 17. The refrigerant flows into the heat exchanger from the inflow channel 21 and then flows out of the heat exchanger through the outflow channel 12. That is, the refrigerant enters the first heat exchange channel 17 from the second opening 20 and flows along the first heat exchange channel 17, and then flows out of the first heat exchange channel 17 from the first opening 19. In this embodiment, along the direction of gravity, the first opening 19 is located above the second opening 20. Therefore, along the direction of gravity, the refrigerant generally flows upward in the first heat exchange channel 17.

[0039] Furthermore, such as Figures 8-13As shown, because the flow cross-sectional area of ​​at least part of the bypass region 16 is larger than that of the heat exchange region 30, the refrigerant flows more easily in the bypass region 16 compared to the heat exchange region 30. Since the bypass region 16 is closer to the first wall 131 than the heat exchange region 30, the gaseous refrigerant is located in the bypass region 16, making it easier for the gaseous refrigerant to flow into the outflow channel 12. The bypass region 16 includes a bypass channel 22, which is connected to the outflow channel 12. Because the bypass channel 22 is connected to the outflow channel 12, the gaseous refrigerant can directly flow into the outflow channel 12 through the bypass channel 22, further reducing the difficulty for the gaseous refrigerant to flow out of the first heat exchange channel 17. This makes it easier for the gaseous refrigerant to flow out of the first heat exchange channel 17, reducing the proportion of gaseous refrigerant and increasing the proportion of the two-phase region (liquid phase plus gaseous phase) refrigerant, thereby improving the heat exchange performance of the heat exchanger. The bypass region 16 includes a shielding portion 23 along the communication direction between the bypass channel 22 and the outflow channel 12. The bypass channel 22 is closer to the outlet channel 12 than the shielding part 23. Since the refrigerant generally flows upward in the first heat exchange channel 17 along the direction of gravity, during the movement of the gaseous refrigerant, some liquid refrigerant will be carried from the bypass area 16 into the outlet channel 12, resulting in a decrease in heat exchange performance. The shielding part 23 can shield the bypass channel 22, reducing the probability of the gas and liquid phases flowing directly into the bypass area 16 along the extension direction of the first wall 131, and reducing the probability of the liquid phase flowing into the outlet channel 12 from the bypass area 16, so that more liquid refrigerant participates in heat exchange, thereby improving the heat exchange performance of the heat exchanger. Moreover, the gaseous refrigerant is lighter than the liquid phase. When it flows along the extension direction of the first wall 131, the gaseous refrigerant will move towards the direction closer to the first wall 131, enter the bypass area 16 and flow into the outlet channel 12. Therefore, the shielding part 23 does not affect the gaseous refrigerant entering the bypass area 16 and flowing into the outlet channel 12.

[0040] Furthermore, along the direction of gravity, the first opening 19 is positioned close to the first wall portion 131. Since the gaseous refrigerant is lighter than the liquid phase, the gaseous refrigerant is closer to the first wall portion 131. Therefore, by positioning the first opening 19 close to the first wall portion 131, the gaseous refrigerant flowing in the bypass area 16 can more easily flow into the first opening 19 and out of the heat exchanger through the first channel 121. This further reduces the difficulty for the gaseous refrigerant to flow out of the first heat exchange channel 17, making it easier for the gaseous refrigerant to flow out of the first heat exchange channel 17, reducing the proportion of the gaseous refrigerant, and thus increasing the proportion of the two-phase region (liquid phase plus gaseous phase) refrigerant, thereby improving the heat exchange performance of the heat exchanger. Of course, in other embodiments, the first opening 19 can also be positioned close to the second wall portion 132.

[0041] Example 2

[0042] like Figures 17-18The second embodiment shown differs from the first embodiment in that the protrusion distance of the second protrusion 162 relative to the base 15 of the first plate 111 is 0. In this embodiment, the protrusion distance of the second protrusion 162 is 0, so the pressure drop of the first flow channel 13 at the second protrusion 162 is lower, and the refrigerant flows more easily between the fifth wall portion 161 and the heat exchange plate 11. Furthermore, the temperature of the refrigerant will decrease accordingly due to the reduced pressure of the refrigerant, further increasing the heat exchange performance of the refrigerant. Also, since the first plate 111 only has the first protrusion 142 as its structural shape, the molding difficulty of the first plate 111 is reduced.

[0043] Furthermore, since the protrusion distance of the second protrusion 162 relative to the base 15 is 0, the pressure drop of the first flow channel 13 at the second protrusion 162 is lower, and the refrigerant flows more easily between the fifth wall portion 161 and the heat exchange plate 11. Moreover, the reduced refrigerant pressure corresponds to a lower refrigerant temperature, further increasing the heat exchange performance of the refrigerant. The bypass region 16 includes a third protrusion 163, which protrudes into the first heat exchange channel 17 relative to the base 15 of the first plate 111. The third protrusion 163 is fixedly connected to the adjacent second plate 112, strengthening the connection between the first plate 111 and the second plate 112 and compensating for the pressure drop caused by the zero protrusion distance of the second protrusion 162 in this embodiment. To address the issue of weak connection strength between the first plate 111 and the second plate 112, at least a portion of the second protrusion 162 is located above the third protrusion 163 along the direction of gravity. Since the gaseous refrigerant is lighter than the liquid refrigerant, it is closer to the first wall portion 131, restricting a portion of the second protrusion 162 from being located above the third protrusion 163. This allows the gaseous refrigerant to flow through the first flow channel 13 between the second protrusion 162 and the adjacent heat exchange plate 11. The gaseous refrigerant can more easily flow out from the outflow channel 12, reducing the proportion of the gaseous refrigerant and thus increasing the proportion of the two-phase region (liquid phase plus gaseous phase) refrigerant. This improves the heat exchange performance of the heat exchanger and reduces the pressure drop of the refrigerant. Since the pressure drop of the refrigerant will correspondingly reduce the temperature of the refrigerant, it further increases the heat exchange performance of the refrigerant.

[0044] Example 3

[0045] like Figure 1 , Figure 19The third embodiment shown differs from the first embodiment in that the second plate 112 includes a bypass region 16. Along the stacking direction of the heat exchange plates 11, the bypass region 16 is recessed away from the first heat exchange channel 17. The fifth wall portion 161 is located at the bottom of the bypass region 16. It should be noted that the bottom here refers to the wall portion away from the first heat exchange channel 17 along the stacking direction of the first plate 111 and the second plate 112. Therefore, the pressure drop of the first flow channel 13 at the bypass region 16 is lower, and the refrigerant flows more easily between the fifth wall portion 161 and the heat exchange plates 11. The gaseous refrigerant flows more easily from the outflow channel 12, reducing the proportion of gaseous refrigerant and increasing the proportion of two-phase (liquid phase plus gas phase) refrigerant, thereby improving the heat exchange performance of the heat exchanger. Furthermore, the decrease in refrigerant pressure will correspondingly reduce the refrigerant temperature, further increasing the heat exchange performance of the refrigerant.

[0046] Example 4

[0047] like Figures 1-6 , Figure 20 Figures 8-13 Figures 8-13 Figures 17-18 Figure 1 Figure 19 Figures 1-6 Figure 20 , 21 The fourth embodiment shown differs from the previous embodiments in that the heat exchanger includes an edge 31 and a base plate 32. The edge 31 is arranged circumferentially along the base plate 32. Along the stacking direction of the heat exchange plates 11, the edge 31 is sealed to the edge 31 of adjacent heat exchange plates 11, thereby connecting and fixing multiple heat exchange plates 11. The edge 31 also seals the first heat exchange channel 17 and the second heat exchange channel 18 between adjacent heat exchange plates 11. The base plate 32 includes a rib 133 and a base 15. The rib 133 protrudes relative to the base 15 and extends along the stacking direction of the heat exchange plates 11. In the stacking direction, the rib 133 and the edge 31 are located on the same side of the base 15. When the refrigerant flows in the first heat exchange channel 17, it needs to flow around the rib 133. The edge 31 includes the third wall 134. The wall forming the first flow channel 13 includes the rib 133 and the third wall 134. In the direction of gravity, the rib 133 is located on one side of the first flow channel 13, and the third wall 134 is located on the opposite side of the first flow channel 13. The refrigerant is restricted by the third wall 134 and the rib 133 and flows along the extension direction of the third wall 134 or the rib 133 towards the outlet channel 12.

[0048] In this embodiment, along the direction of gravity, the rib 133 is located above the third wall 134. The bypass region 16 is closer to the rib 133 than the heat exchange region 30. Since the rib 133 is located above the third wall 134 along the direction of gravity, the gaseous refrigerant will move towards the rib 133. Therefore, the bypass region 16 is positioned closer to the rib 133 than the heat exchange region 30, which facilitates the flow of gaseous refrigerant into the outflow channel 12 through the bypass region 16. Alternatively, along the direction of gravity, the third wall 134 can be located above the rib 133, and the bypass region 16 can be closer to the third wall 134 than the heat exchange region 30. Since the third wall 134 is located above the rib 133 along the direction of gravity, the gaseous refrigerant will move towards the third wall 134. The bypass zone 16 is positioned closer to the third wall 134 than the heat exchange zone 30 due to the movement of the wall portion 134. This facilitates the flow of gaseous refrigerant into the outlet channel 12 through the bypass zone 16. Consequently, gaseous refrigerant is more likely to be discharged from the outlet channel 12 through the bypass zone 16 than liquid refrigerant, reducing the proportion of gaseous refrigerant and increasing the proportion of refrigerant in the two-phase zone (liquid and gaseous phases). This improves the heat exchange performance of the heat exchanger. Furthermore, since the flow cross-sectional area of ​​the bypass zone 16 is larger than that of the heat exchange zone 30, refrigerant is more likely to be discharged from the outlet channel 12 through the bypass zone 16, reducing the pressure drop of the refrigerant. As the pressure of the refrigerant decreases, the temperature of the refrigerant will decrease accordingly, further increasing the heat exchange performance of the refrigerant.

[0049] In this embodiment, the refrigerant needs to flow around the rib 133 in the first heat exchange channel 17. At this time, the refrigerant flows in a U-shaped flow. In other embodiments, multiple ribs 133 can also be provided to increase the flow path of the refrigerant. In this case, the rib 133 is the rib 133 closest to the outflow channel 12 along the direction of gravity.

[0050] The technical features of the above-described technical solutions can be combined in any way. For the sake of brevity, not all possible combinations of the technical features in the above-described technical solutions are described. However, as long as there is no contradiction in the combination of these technical features, they should be considered to be within the scope of this specification.

[0051] The above-described technical solutions merely illustrate several embodiments of the present invention, and while the descriptions are relatively specific and detailed, they should not be construed as limiting the scope of the invention patent. It should be noted that those skilled in the art can make various modifications and controls without departing from the concept of the present invention, and these all fall within the protection scope of the present invention. Therefore, the protection scope of this invention patent should be determined by the appended claims.

Claims

1. A heat exchanger, characterized in that, The heat exchanger includes stacked heat exchange plates (11), the stacking direction of which forms an angle greater than 0° with the direction of gravity. The heat exchanger has an outflow channel (12) that passes through the heat exchange plates (11) along the stacking direction. Adjacent heat exchange plates (11) have a first flow channel (13) that communicates with the outflow channel (12). At least a portion of the first flow channel (13) includes a heat exchange zone (30) and a bypass zone (16). Along the direction of gravity, the bypass zone (16) is located above the heat exchange zone (30). For the same width, at least a portion of the bypass zone (16) has a flow cross-sectional area larger than that of the heat exchange zone (30).

2. The heat exchanger according to claim 1, characterized in that, The heat exchange plates (11) include a first plate (111) and a second plate (112), which are alternately arranged. The heat exchanger includes a first heat exchange channel (17) and a second heat exchange channel (18). Along the stacking direction of the heat exchange plates (11), the first heat exchange channel (17) is located on one side of the first plate (111), and the second heat exchange channel (18) is located on the other side of the first plate (111). The first heat exchange channel (17) and the second heat exchange channel (18) are not connected. The first heat exchange channel (17) includes a first flow channel (13). The bypass area (16) is located in the first heat exchange channel (17), and refrigerant flows in the first heat exchange channel (17).

3. The heat exchanger according to claim 2, characterized in that, The heat exchanger includes a side portion (31) and a substrate (32). The side portion (31) is arranged circumferentially along the substrate (32). Along the stacking direction of the heat exchange plates (11), the side portion (31) is sealed to the side portion (31) of the adjacent heat exchange plates (11). Along the direction of gravity, the wall portions of the side portion (31) located on the upper and lower sides of the substrate (32) are defined as the first wall portion (131) and the second wall portion (132). The wall portion forming the first flow channel (13) includes the first wall portion (131) and the second wall portion (132). Along the direction of gravity, the first wall portion (131) is located above the second wall portion (132). Along the direction of gravity, the bypass area (16) is closer to the first wall portion (131) than the heat exchange area (30).

4. The heat exchanger according to claim 2, characterized in that, The heat exchanger includes a side portion (31) and a base plate (32). The side portion (31) is arranged circumferentially along the base plate (32) and along the stacking direction of the heat exchange plates (11). The side portion (31) is sealed to the side portion (31) of the adjacent heat exchange plates (11). The base plate (32) includes a rib portion (133) and a base portion (15). The rib portion (133) protrudes relative to the base portion (15) and is arranged along the stacking direction of the heat exchange plates (11). In the stacking direction, the rib (133) and the edge (31) are located on the same side of the base (15), the edge (31) includes a third wall (134), the wall forming the first flow channel (13) includes the rib (133) and the third wall (134), in the direction of gravity, the rib (133) is located on one side of the first flow channel (13), and the third wall (134) is located on the opposite side of the first flow channel (13); Along the direction of gravity, the rib (133) is located above the third wall portion (134), and the bypass area (16) is closer to the rib (133) than the heat exchange area (30). Alternatively, along the direction of gravity, the third wall portion (134) is located above the rib (133), and the bypass area (16) is closer to the third wall portion (134) than the heat exchange area (30).

5. The heat exchanger according to claim 3 or 4, characterized in that, The heat exchange zone (30) includes a protrusion (14) and a base (15). The protrusion (14) protrudes relative to the base (15). The protrusion (14) includes a fourth wall (141). The bypass zone (16) includes a fifth wall (161). Along the stacking direction of the heat exchange plates (11), the distance between the fourth wall (141) and the heat exchange plate (11) on the other side of the first heat exchange channel (17) is less than the distance between the fifth wall (161) and the heat exchange plate (11) on the other side of the first heat exchange channel (17). Alternatively, the protrusion (14) may include a plurality of first protrusions (142), and the bypass region (16) may include a plurality of second protrusions (162), the second protrusions (162) being sparser than the first protrusions (142).

6. The heat exchanger according to claim 5, characterized in that, The protrusion (14) includes a plurality of first protrusions (142), the first protrusions (142) protruding into the first heat exchange channel (17) relative to the base (15), the fourth wall portion (141) is located on top of the first protrusions (142), the first plate (111) includes the bypass area (16), the bypass area (16) includes a plurality of second protrusions (162), the second protrusions (162) protruding into the first heat exchange channel (17) relative to the base (15) of the first plate (111), the fifth wall portion (161) is located on top of the second protrusions (162), and the distance between the fourth wall portion (141) and the base (15) of the first plate (111) is greater than the distance between the fifth wall portion (161) and the base (15) of the first plate (111).

7. The heat exchanger according to claim 6, characterized in that, The second protrusion (162) protrudes 0 distance from the base (15) of the first plate (111); Alternatively, the second protrusion (162) protrudes 0 distance from the base (15), the bypass area (16) includes a third protrusion (163), the third protrusion (163) protrudes into the first heat exchange channel (17) relative to the base (15) of the first plate (111), the third protrusion (163) is fixedly connected to the adjacent second plate (112), and at least part of the second protrusion (162) is located above the third protrusion (163) along the direction of gravity.

8. The heat exchanger according to claim 5, characterized in that, The second plate (112) includes the bypass area (16), which is recessed in a direction away from the first heat exchange channel (17) along the stacking direction of the heat exchange plate (11), and the fifth wall portion (161) is located at the bottom of the bypass area (16).

9. The heat exchanger according to any one of claims 2-8, characterized in that, The heat exchange plate (11) includes a first opening (19). Along the stacking direction of the heat exchange plate (11), a plurality of first openings (19) form the outflow channel (12). The outflow channel (12) is connected to the first heat exchange channel (17). The heat exchange plate (11) includes a second opening (20). Along the stacking direction of the heat exchange plate (11), the heat exchanger includes an inflow channel (21). A plurality of second openings (20) form the inflow channel (21). The inflow channel (21) is connected to the first heat exchange channel (17). Along the direction of gravity, the first opening (19) is located above the second opening (20).

10. The heat exchanger according to claim 9, characterized in that, The bypass area (16) includes a bypass channel (22) that communicates with the outflow channel (12). The bypass area (16) includes a shielding portion (23). Along the communication direction between the bypass channel (22) and the outflow channel (12), the bypass channel (22) is closer to the outflow channel (12) than the shielding portion (23).

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