Heat exchanger

Abstract

A heat exchanger, comprising a plurality of plates arranged in a stacked manner, wherein each plate has an inlet and an outlet, and the extension direction of the line connecting the center of the inlet and the center of the outlet is defined as a first direction; the plate comprises a base plate portion and a plurality of protrusions; the base plate portion comprises a plurality of intersection base plate portions and a plurality of flow channel base plate portions; the plurality of flow channel base plate portions comprise a first flow channel base plate portion, a second flow channel base plate portion, and a third flow channel base plate portion, and the first flow channel base plate portion, the second flow channel base plate portion, and the third flow channel base plate portion are respectively connected to the intersection base plate portions; the extension direction of the first flow channel base plate portion is parallel to the first direction; and in the extension direction of the first flow channel base plate portion, the second flow channel base plate portion and the third flow channel base plate portion are located on two sides of the first flow channel base plate portion. The heat exchanger has a high heat exchange performance.

Description

heat exchanger

[0001] This application claims priority to Chinese Patent Application No. 202410804504.2, filed on June 20, 2024, entitled "Heat Exchanger", the entire contents of which are incorporated herein by reference. Technical Field

[0002] This application relates to the field of heat exchange technology, specifically to a heat exchanger for a refrigeration system. Background Technology

[0003] Plate heat exchangers typically consist of multiple plates stacked together, with interplate channels formed between adjacent plates for fluid flow. Refrigerant and coolant can flow on opposite sides of the plates to achieve heat exchange between the plates.

[0004] In evaluating the performance of heat exchangers, both the heat transfer coefficient and the flow resistance (i.e., pressure drop) must be considered. A higher heat transfer coefficient and a lower pressure drop are generally better. However, structures with high heat transfer coefficients often also have high pressure drops, and vice versa.

[0005] Balancing pressure drop and heat transfer coefficient to improve the overall performance of heat exchangers is a technical problem that researchers urgently need to solve. Summary of the Invention

[0006] In view of the shortcomings of the existing technology, the present invention provides a heat exchanger with high heat exchange performance.

[0007] To achieve the above objectives, this application adopts the following technical solution:

[0008] A heat exchanger includes a plurality of stacked plates, each plate having an inlet and an outlet, wherein the direction of the line connecting the center of the inlet and the center of the outlet is defined as a first direction;

[0009] The plate includes a substrate portion and a plurality of protrusions; the substrate portion includes a plurality of intersecting substrate portions and a plurality of flow channel substrate portions;

[0010] The plurality of flow channel substrate portions include a first flow channel substrate portion, a second flow channel substrate portion and a third flow channel substrate portion, and the first flow channel substrate portion, the second flow channel substrate portion and the third flow channel substrate portion are respectively connected to the confluence substrate portion;

[0011] The extension direction of the first flow channel substrate portion is parallel to the first direction; along the extension direction of the first flow channel substrate portion, the second flow channel substrate portion and the third flow channel substrate portion are located on both sides of the first flow channel substrate portion.

[0012] Two adjacent plates are stacked together, and a first flow channel is formed at the portion of the first flow channel substrate between the two plates, a second flow channel is formed at the portion of the second flow channel substrate, a third flow channel is formed at the portion of the third flow channel substrate, and a junction is formed at the portion of the junction substrate. When the fluid passes through the channels between the plates, it enters the junction section after passing through the first channel section. From the junction section, it splits into the second and third channel sections. The fluid flowing out of the second and third channel sections re-enters the first channel section, and so on in an alternating cycle. Therefore, there are two flow modes within the channels: one is along the first channel section, where the flow resistance and pressure drop are small because the extension direction of the first channel section is parallel to the first direction; the other is along the second and third channel sections, where the extension directions of the second and third channel sections are located on both sides of the first channel section, and both are at an angle to the first direction. The fluid is forced to change direction, and the local flow direction is at an angle to the main flow direction of the entire plate (i.e., the first direction). In this case, the disturbance is greater, the heat transfer coefficient is higher, and the heat transfer is better. In this way, the two flow modes alternate, which enhances heat transfer while maintaining a relatively reasonable pressure drop level. Attached Figure Description

[0013] Figure 1 is a schematic diagram of the heat exchanger in Example 1;

[0014] Figure 2 is a schematic diagram of the structure of the first plate in the heat exchanger in Figure 1;

[0015] Figure 3 is a partial structural diagram of the first and second plates stacked in the heat exchanger of Figure 1.

[0016] Figure 4 is a partial structural diagram of the first and second plates in Figure 3 after being stacked.

[0017] Figure 5 is a partial structural diagram of the first plate in Figure 2;

[0018] Figure 6 is an enlarged view of point A in Figure 3;

[0019] Figure 7 is an enlarged view of point B in Figure 4;

[0020] Figure 8 is a partial cross-sectional view of the first and second plates in Figure 3 after they are stacked.

[0021] Figure 9 is a partial structural diagram of the first and second plates after being stacked in Example 2;

[0022] Figure 10 is a partial structural diagram of the first and second plates in Figure 9 after being stacked.

[0023] Figure 11 is a partial structural diagram of the first plate in Figure 9.

[0024] An enlarged view of point C in Figure 12;

[0025] Figure 13 is an enlarged view of point D in Figure 10.

[0026] Figure 14 shows the temperature field diagram of the computational fluid dynamics experiment;

[0027] Figure 15 shows the velocity field diagram of the computational fluid dynamics experiment.

[0028] Figure Descriptions: 1. Inlet; 2. Outlet; 3. Substrate section; 4. Protrusion; 5. Intersecting substrate section; 6. First flow channel substrate section; 7. Second flow channel substrate section; 8. Third flow channel substrate section; 9. Heat exchange core; 10. Top; 11. First sidewall; 12. Second sidewall; 13. Third sidewall; 14. Fourth sidewall; 15. First plate; 16. Second plate; 17. First plate surface; 18. Second plate surface; 19. First inter-plate channel; 20. Second inter-plate channel; 21. First 22. Second arc-shaped sidewall; 23. Third arc-shaped sidewall; 24. Fourth arc-shaped sidewall; 25. Heat exchanger; 26. First distribution zone; 27. Heat exchange zone; 28. Second distribution zone; 29. ​​First inlet pipe; 30. First outlet pipe; 31. First inlet channel; 32. First outlet channel; 33. Second inlet pipe; 34. Second outlet pipe; 35. Second inlet channel; 36. Second outlet channel; 37. First corner hole; 38. Second corner hole. Detailed Implementation

[0029] To make the above-mentioned objects, features, and advantages of the present invention more apparent and understandable, specific embodiments of the present invention will be described in detail below with reference to the accompanying drawings. Many specific details are set forth in the following description to provide a thorough understanding of the present invention. However, the present invention can be practiced in many other ways different from those described herein, and those skilled in the art can make similar modifications without departing from the spirit of the present invention. Therefore, the present invention is not limited to the specific embodiments disclosed below.

[0030] The present application will be further described below with reference to the accompanying drawings and specific embodiments.

[0031] Example 1:

[0032] As shown in Figures 1 and 2, the heat exchanger 25 includes a heat exchange core 9 and multiple connecting pipes. Fluid enters and exits the heat exchanger through the multiple connecting pipes. The heat exchange core 9 includes multiple plates stacked together. Each plate has an inlet 1 and an outlet 2. Flow channels are provided between adjacent plates. Fluid flows in the flow channels and exchanges heat through the plate walls.

[0033] Definition: The side of the plate with the protrusion 4 is the first plate surface 17, and the other side of the plate is the second plate surface 18; in the plate, the line connecting the center of the inlet 1 and the center of the outlet 2 extends in the first direction X.

[0034] As shown in Figures 2, 3, 5 and 6, the plate includes a base plate portion 3 and a plurality of protrusions 4 protruding from the first plate surface 17 of the plate; the base plate portion 3 includes a plurality of intersecting base plate portions 5 and a plurality of flow channel base plate portions, wherein the flow channel base plate portions are strip-shaped and the flow channel base plate portions are disposed between two adjacent protrusions 4; along the extension direction of the flow channel portions, two intersecting base plate portions 5 are located on both sides of the flow channel base plate portions and are connected to the flow channel base plate portions. The plurality of flow channel substrate portions include a first flow channel substrate portion 6, a second flow channel substrate portion 7, and a third flow channel substrate portion 8, and the first flow channel substrate portion 6, the second flow channel substrate portion 7, and the third flow channel substrate portion 8 are respectively connected to the junction substrate portion 5. The extending direction of the first flow channel substrate portion 6 is parallel to the first direction X. It should be noted that the parallelism between the extending direction of the first flow channel substrate portion 6 and the first direction X includes, but is not limited to, an angle of 0° between the extending direction of the first flow channel substrate portion 6 and the first direction X. This angle can vary within a small angle range, for example, the value range of the angle between the extending direction of the first flow channel substrate portion 6 and the first direction X is 0° to 10°. Along the first direction X, the second flow channel substrate portion 7 and the third flow channel substrate portion 8 are located on both sides of the first flow channel substrate portion 6.

[0035] Two adjacent plates are stacked together, and a first flow channel is formed at the location of the first flow channel substrate 6 between the two plates, a second flow channel is formed at the location of the second flow channel substrate 7, a third flow channel is formed at the location of the third flow channel substrate 8, and a junction is formed at the location of the junction substrate 5. When the fluid passes through the channels between the plates, it enters the junction section after passing through the first channel section. From the junction section, it splits into the second and third channel sections. The fluid flowing out of the second and third channel sections re-enters the first channel section, and so on in an alternating cycle. Therefore, there are two flow modes within the channels: one is along the first channel section, where the flow resistance and pressure drop are small because the extension direction of the first channel section is parallel to the first direction X; the other is along the second and third channel sections, where the extension directions of the second and third channel sections are located on both sides of the first channel section, and both are at an angle to the first direction X. The fluid is forced to change direction, and there is an angle between the local flow direction and the first direction X. In this case, the disturbance is greater, the heat transfer coefficient is higher, and the heat transfer is better. In this way, the two flow modes alternate, which enhances heat transfer while maintaining a relatively reasonable pressure drop level.

[0036] In this embodiment, as shown in Figures 3, 5, and 6, the junction substrate portion 5 includes a first junction substrate portion and a second junction substrate portion. The first and second junction substrate portions are located at both ends of the first flow channel substrate portion 6 and are connected to the first flow channel substrate portion 6. Preferably, the angle α between the extending direction of the second flow channel substrate portion 7 and the extending direction of the first flow channel substrate portion 6 is greater than 90°. More preferably, the value of the angle α is greater than or equal to 100°. More preferably, the value of the angle α is between 100° and 140°, for example, 105°, 110°, 115°, 120°, 125°, 130°, and 135°. The angle β between the extending direction of the third flow channel substrate 8 and the extending direction of the first flow channel substrate 6 is greater than 90°. Preferably, the value of the angle β is greater than or equal to 100°. More preferably, the value of the angle β is between 100° and 140°, for example, 105°, 110°, 115°, 120°, 125°, 130°, and 135°. The angles α and β may be the same or different. When fluid flows through the channels between the plates, there are two flow patterns. One is along the first channel, where the flow resistance and pressure drop are small. The other is along the second and third channels. Since the second and third channels are located on both sides of the first channel, and the angle α between the extension direction of the second channel base plate 7 and the extension direction of the first channel base plate 6 is greater than 90°, and the angle β between the extension direction of the third channel base plate 8 and the extension direction of the first channel base plate 6 is greater than 90°, that is, the extension directions of the second channel with the second channel base plate 7 and the third channel with the third channel base plate 8 both have an angle with the first direction X, the fluid is forced to change direction. At this time, the disturbance is larger, the heat transfer coefficient is higher, and the heat transfer is better. In this way, the two flow patterns alternate, which can enhance heat transfer while maintaining a relatively reasonable pressure drop level. If the included angles α and β are too large, the heat exchange effect will be weakened; if the included angles α and β are too small, the fluid will experience greater resistance and the pressure drop will be too large. The included angles α and β are in the range of 100° to 140°. The fluid is more disturbed in the second flow channel substrate 7 and the third flow channel substrate 8, resulting in better heat exchange and the pressure drop can be maintained within a reasonable range.

[0037] Furthermore, as shown in Figure 5, along the extension direction perpendicular to the substrate portion, the width of the first flow channel substrate portion 6 is W1, the width of the second flow channel substrate portion 7 is W2, and the width of the third flow channel substrate portion 8 is W3. W1, W2, and W3 satisfy the following relationship: W1 > W2, and W1 > W3. The pressure drop of the fluid flowing in the first flow channel substrate portion 6 is smaller, while the pressure drop of the fluid flowing in the second and third flow channel substrate portions 7 and 8 is larger. The two types of flow channel substrate portions circulate alternately, thus balancing the overall pressure drop level within the flow channel. The heat exchange efficiency of the fluid in the first flow channel substrate portion 6 is less than that in the second and third flow channel substrate portions 7 and 8. Similarly, the alternation of the two flow channels circulates alternately, thus simultaneously balancing the heat exchange efficiency within the flow channel. In summary, this flow channel design can effectively balance the pressure drop level and heat exchange efficiency within the flow channel, thereby improving the overall performance of the heat exchanger. Furthermore, W1, W2, and W3 satisfy the following relationship: W1 > (W2 + W3), thus further improving the overall performance of the heat exchanger.

[0038] As shown in Figures 4 and 5, along the first direction X, the line connecting the centers of two adjacent protrusions 4 extends in the second direction. The angle between the first direction X and the second direction is θ, and the value of θ is in the range of θ≤80°. Thus, θ affects the layout of the protrusions 4 on the plate. When θ>80°, the fluid experiences greater resistance, resulting in excessive pressure drop. When θ≤80°, the pressure drop level and heat exchange efficiency of the fluid can be better balanced, thereby improving the overall performance of the heat exchanger 25.

[0039] Preferably, as shown in Figures 4, 5 and 6, the protrusion 4 includes a sidewall and a top 10, the top 10 having a flat or slightly curved surface for welding, and the top 10 being connected to the substrate portion 3 via the sidewall.

[0040] As shown in Figures 4, 6, and 7, the plate includes a first plate 15 and a second plate 16, which are stacked together. The protrusion 4 of the first plate 15 protrudes relative to the first plate surface 17 of the first plate 15. The first flow channel substrate portion 6 of the first plate 15 is welded to the top 10 of the protrusion 4 of the second plate 16. This arrangement ensures the welding strength between the first plate 15 and the second plate 16. Furthermore, it offsets the protrusions 4 of the first plate 15 from those of the second plate 16. When fluid flows between the first plate 15 and the second plate 16, some fluid first flows towards the top 10 of the protrusion 4, and then flows along the protrusion 4 towards the substrate portion 3, similar to a ramp flow, which further enhances heat exchange.

[0041] In this embodiment, the top 10 of the protrusion 4 is a planar structure, and the planar shape is polygonal, elliptical, or circular. The first plate 15 and the second plate 16 are stacked, with the first plate 15 positioned above the second plate 16. The first flow channel substrate portion 6 of the first plate 15 is in contact with and welded to the top 10 of the protrusion 4 of the second plate 16. The top 10 of the protrusion 4 is polygonal, elliptical, or circular, which increases the contact area of ​​the weld joint, thereby enhancing the welding strength of the first plate 15 and the second plate 16.

[0042] Preferably, as shown in Figures 4, 7, and 8, the distance between the substrate portions 3 of two adjacent plates is defined as the interplate distance along a direction perpendicular to the substrate portion 3. The heat exchanger 25 is provided with a plurality of mutually isolated first interplate channels 19 and a plurality of second interplate channels 20. The interplate distance H1 of the first interplate channels 19 and the interplate distance H2 of the second interplate channels 20 satisfy the following relationship: H1 < H2. The fluid entering the first interplate channel 19 is defined as the first fluid, and the fluid entering the second interplate channel 20 is defined as the second fluid. In the first interplate channel 19, the first fluid has a large pressure drop, a fast flow rate, and a high heat exchange efficiency; in the second interplate channel 20, the second fluid has a small pressure drop and a slow flow rate. For example, the first fluid is a refrigerant and the second fluid is water. The refrigerant flows rapidly in the first inter-plate channel 19, while the water flows slowly in the second inter-plate channel 20. Due to the rapid flow of the refrigerant, the fluid in the first inter-plate channel 19 always maintains a low temperature. At the same time, the slow flow rate of the water allows it to absorb more cooling energy. In this way, the heat exchange requirements of a fast flow rate and high heat exchange efficiency for the first fluid and a slow flow rate for the second fluid can be met.

[0043] Specifically, as shown in Figures 4, 7, and 8, the protrusion 4 of the first plate 15 protrudes at a height H3 relative to the substrate portion 3 of the first plate 15, and the protrusion 4 of the second plate 16 protrudes at a height H4 relative to the substrate portion 3 of the second plate 16. H3 and H4 satisfy the following relationship: H3 > H4, that is, the stamping depths of the protrusion 4 of the first plate 15 and the protrusion 4 of the second plate 16 are different. The second plate surface 18 of the first plate 15 is opposite to the first plate surface 17 of the second plate 16. The protrusion 4 of plate 16 is welded to the base plate 3 of the first plate 15. At this time, the inter-plate distance between the base plate 3 of the first plate 15 and the base plate 3 of the second plate 16 is H1, where H1 = H4. The second plate surface 18 of the second plate 16 is opposite to the first plate surface 17 of the first plate 15. The protrusion 4 of the first plate 15 is welded to the base plate 3 of the second plate 16. The inter-plate distance between the base plate 3 of the second plate 16 and the base plate 3 of the first plate 15 is H2, where H2 = H3. In this way, different heat exchange requirements can be met.

[0044] Define the length direction and the width direction of the plate. The length direction of the plate is perpendicular to the width direction of the plate.

[0045] As shown in Figure 2, the first plate 15 includes a first distribution zone 26, a heat exchange zone 27, and a second distribution zone 28. The heat exchange zone 27 is located between the first distribution zone 26 and the second distribution zone 28. Along the length of the first plate 15, the length of the heat exchange zone 27 is greater than the length of the first distribution zone 26 and the second distribution zone 28. The first distribution zone 26 is provided with an inlet 1, and the second distribution zone 28 is provided with an outlet 2. In the first distribution zone 26 and the second distribution zone 28, the main flow direction of the fluid is the width direction of the plate, which is mainly used for fluid distribution. In the heat exchange zone 27, the main flow direction of the fluid is the length direction of the plate. The extension directions of the second flow channel base plate portion 7 and the third flow channel base plate portion 8 both have a large angle with the main flow direction of the fluid, which is used to increase turbulence and thus enhance heat transfer.

[0046] As shown in Figures 1 and 2, exemplarily, the connector includes a first inlet connector 29 and a first outlet connector 30. The first inlet connector 29 includes a first inlet channel 31, and the first outlet connector 30 includes a first outlet channel 32. Inlet 1 connects the first inlet channel 31 and the first inter-plate channel 19, and outlet 2 connects the first outlet channel 32 and the first inter-plate channel 19. Fluid sequentially enters the first inter-plate channel 19 through the first inlet channel 31 and inlet 1, and flows out from the first outlet channel 32.

[0047] As shown in Figures 1 and 2, exemplarily, the plate also includes a first corner hole 37 and a second corner hole 38, and the connector also includes a second inlet connector 33 and a second outlet connector 34. The second inlet connector 33 includes a second inlet channel 35, and the second outlet connector 34 includes a second outlet channel 36. The first corner hole 37 connects the second inlet channel 35 and the second inter-plate channel 20, and the second corner hole 38 connects the second outlet channel 36 and the second inter-plate channel 20. Fluid sequentially enters the second inter-plate channel 20 through the second inlet channel 35 and the first corner hole 37, and flows out from the second outlet channel 36.

[0048] Example 2:

[0049] The main difference between this embodiment and Embodiment 1 lies in the flow channel structure between the plates, as shown in Figures 9, 10, and 11. The extension direction of the first flow channel substrate 6 is parallel to the first direction X. It should be noted that the parallelism between the extension direction of the first flow channel substrate 6 and the first direction X includes, but is not limited to, an angle of 0° between the extension direction of the first flow channel substrate 6 and the first direction X. This angle can vary within a small range; for example, the angle between the extension direction of the first flow channel substrate 6 and the first direction X can range from 0° to 10°. The pressure drop of the fluid flowing in the first flow channel substrate 6 is small. The extension direction of the second flow channel substrate 7 is parallel to that of the first flow channel substrate 6. The angle α between the extension directions of the third flow channel substrate 8 and the first flow channel substrate 6 is 90°, and the angle β between them is also 90°. This means that the angle between the local flow direction of the fluid and the first direction X is 90°, resulting in the greatest disturbance to the fluid and better heat transfer. Simultaneously, the larger angle also improves fluid distribution. Flow distribution occurs when the fluid flows perpendicular to the first direction X, resulting in lower flow resistance. If local flow distribution is uneven, the second flow channel with the second flow channel substrate 7 and the second flow channel with the third flow channel substrate 8 are more conducive to fluid flow along this direction (i.e., perpendicular to the first direction X), thereby improving distribution. In short, this flow channel design is primarily used to improve fluid distribution and enhance heat transfer.

[0050] In the distribution area, the extension direction of the second flow channel substrate 7 and the extension direction of the third flow channel substrate 8 are both consistent with the fluid flow direction. There is no angle between the local flow direction and the main flow direction of the fluid. At this time, the fluid is less disturbed and the flow resistance is smaller, which is more conducive to the fluid flowing along this direction, thereby improving the distribution.

[0051] In the heat exchange zone, the extension directions of the second flow channel substrate 7 and the third flow channel substrate 8 are both perpendicular to the fluid flow direction. The fluid is forced to change direction by the second flow channel substrate 7 and the third flow channel substrate 8. The angle between the local flow direction and the main flow direction of the fluid is 90°. At this time, the fluid is subjected to greater disturbance, resulting in better heat exchange. In addition, the larger angle also plays a role in improving the distribution. The flow distribution is that the fluid flows in the direction of the plate width, and the flow resistance is small. When the local fluid flow distribution is uneven, the second flow channel substrate 7 and the third flow channel substrate 8 can further improve the distribution.

[0052] Preferably, as shown in Figure 11, the length of the first flow channel substrate 6 is L1, the length of the second flow channel substrate 7 is L2, and the length of the third flow channel substrate 8 is L3. L1, L2, and L3 satisfy the following relationship: L1 ≤ (L2 + L3). To verify the heat transfer effect of this flow channel design, computational fluid dynamics experiments were conducted, where L1 = 0.9 mm, L2 = 0.5 mm, and L3 = 0.5 mm. As shown in Figure 14, the flow direction is from left to right. The temperature field distribution diagram shows that the temperature distribution is relatively uniform. The velocity field distribution diagram, as shown in Figure 15, shows that the fluid velocity varies within a small local range, indicating that the fluid is disturbed and the heat transfer is good.

[0053] Furthermore, as shown in Figure 11, the width of the first flow channel substrate 6 is W1, the width of the second flow channel substrate 7 is W2, and the width of the third flow channel substrate 8 is W3. W1, W2, and W3 satisfy the following relationship: W1 > W2, and W1 > W3. W1, W2, and W3 also satisfy the following relationship: W1 > (W2 + W3). The technical effect of this flow channel design is the same as that of Embodiment 1, and will not be repeated here.

[0054] As shown in Figures 10, 11, and 12, the protrusion 4 includes a sidewall and a top 10, with the top 10 connected to the substrate portion 3 via the sidewall 9. Exemplarily, the sidewall includes a first sidewall 11, a second sidewall 12, a third sidewall 13, and a fourth sidewall 14; the line connecting the two ends of the first sidewall 11 extends parallel to the first direction X; one end of the first sidewall 11 is connected to the fourth sidewall 14 via a first arcuate sidewall 21, and the other end of the first sidewall 11 is connected to the second sidewall 12 via a second arcuate sidewall 22, with the first arcuate sidewall 21 closer to the inlet 1 than the second arcuate sidewall 22; the line connecting the two ends of the third sidewall 13 extends parallel to the first direction X. The direction X is parallel. One end of the third sidewall 13 is connected to the fourth sidewall 14 via the third arc-shaped sidewall 23, and the other end of the third sidewall 13 is connected to the second sidewall 12 via the fourth arc-shaped sidewall 24. The third arc-shaped sidewall 23 is closer to the inlet 1 than the fourth arc-shaped sidewall 24. The radius (R) of the first arc-shaped sidewall 21 is smaller than that of the second arc-shaped sidewall 22, where R represents the radius of the transition arc at the intersection of the two sidewalls. The radius (R) of the third arc-shaped sidewall 23 is smaller than that of the fourth arc-shaped sidewall 24. Thus, the smaller radius (R) of the third arc-shaped sidewall 23 can increase disturbance and enhance heat transfer; the larger radius (R) of the second arc-shaped sidewall 22 can reduce pressure drop, thereby further balancing the pressure drop level and heat transfer efficiency within the flow channel.

[0055] As shown in Figures 10, 11, and 13, multiple protrusions 4 are arranged parallel to the first direction X, with a length S between the centers of two adjacent protrusions 4. The protrusions 4 of the first plate 15 are offset from the protrusions 4 of the second plate 16 by 1 / 4S or 1 / 2S. The protrusions 4 are elongated, and their length and width directions are defined. Along the length direction of the protrusions 4, both ends of the protrusions 4 are welded portions. The first plate 15 and the second plate 16 are stacked, with the second surface 18 of the first plate 15 facing the first surface 17 of the second plate 16. As shown in Figure 13, when the first plate 15 is misaligned with the second plate 16 by 1 / 4S, the top 10 of the protrusion 4 of the second plate 16 is welded to the base plate 3 of the second plate 16 to form a weld point. This arrangement causes the protrusion 4 of the first plate 15 and the protrusion 4 of the second plate 16 to be misaligned. When the fluid flows between the first plate 15 and the second plate 16, some of the fluid first flows to the top 10 of the protrusion 4, and then flows along the protrusion 4 to the base plate 3, which is similar to a climbing flow, thus further enhancing heat exchange. In addition, since the weld point of the first plate 15 and the second plate 16 is the weld between the base plate 3 and the top 10 of the protrusion 4, the welding area is increased, thereby enhancing the welding strength. When the first plate 15 is misaligned with the second plate 16 by 1 / 2S, the welded part of the first plate 15 is welded to the top 10 of the second plate 16 and forms a weld point. Its heat exchange effect is the same as that of the misalignment by 1 / 4S, which will not be described in detail here.

[0056] Furthermore, the inter-plate distance of the inter-plate channel or the stamping depth of the protrusion 4 in this embodiment is the same as in Embodiment 1, and will not be repeated here.

[0057] The embodiments described above are merely examples of several implementations 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. 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 modifications and controls all fall within the scope of protection of the present invention.

Claims

1. A heat exchanger comprising a plurality of plates stacked together, the plates having an inlet (1) and an outlet (2), wherein the direction of the line connecting the center of the inlet (1) and the center of the outlet (2) is defined as a first direction; The plate includes a substrate portion (3) and a plurality of protrusions (4); the substrate portion (3) includes a plurality of intersecting substrate portions (5) and a plurality of flow channel substrate portions; the plurality of flow channel substrate portions include a first flow channel substrate portion (6), a second flow channel substrate portion (7) and a third flow channel substrate portion (8), and the first flow channel substrate portion (6), the second flow channel substrate portion (7) and the third flow channel substrate portion (8) are respectively connected to the intersecting substrate portion (5); The extension direction of the first flow channel substrate portion (6) is parallel to the first direction; along the extension direction of the first flow channel substrate portion (6), the second flow channel substrate portion (7) and the third flow channel substrate portion (8) are located on both sides of the first flow channel substrate portion (6).

2. The heat exchanger according to claim 1, characterized in that, The angle α between the extension direction of the second flow channel substrate (7) and the extension direction of the first flow channel substrate (6) is greater than 90°; the angle β between the extension direction of the third flow channel substrate (8) and the extension direction of the first flow channel substrate (6) is greater than 90°.

3. The heat exchanger according to claim 2, characterized in that, Along the first direction, the line connecting the centers of two adjacent protrusions (4) extends in the second direction, and the angle between the first direction and the second direction is θ, wherein the value of θ is ≤ 80°.

4. The heat exchanger according to any one of claims 1-3, characterized in that, The plate includes a first plate (15) and a second plate (16), which are stacked together. The first flow channel substrate portion (6) of the first plate (15) is welded to the top of the protrusion (4) of the second plate (16).

5. The heat exchanger according to claim 1, characterized in that, The angle α between the extension direction of the second flow channel substrate (7) and the extension direction of the first flow channel substrate (6) is 90°; the angle β between the extension direction of the third flow channel substrate (8) and the extension direction of the first flow channel substrate (6) is 90°.

6. The heat exchanger according to claim 5, characterized in that, The length of the first flow channel substrate (6) along its extension direction is L1, the length of the second flow channel substrate (7) along its extension direction is L2, and the length of the third flow channel substrate (8) along its extension direction is L3. L1, L2 and L3 satisfy the following relationship: L1≤(L2+L3).

7. The heat exchanger according to claim 4, characterized in that, The protrusion (4) includes a first sidewall (11), a second sidewall (12), a third sidewall (13), and a fourth sidewall (14); the line connecting the two ends of the first sidewall (11) extends parallel to the first direction, one end of the first sidewall (11) is connected to the fourth sidewall (14) through a first arc-shaped sidewall (21), and the other end of the first sidewall (11) is connected to the second sidewall (12) through a second arc-shaped sidewall (22), and the first arc-shaped sidewall (21) is parallel to the fourth sidewall (14). The second arc-shaped sidewall (22) is close to the inlet (1); the line connecting the two ends of the third sidewall (13) extends parallel to the first direction, one end of the third sidewall (13) is connected to the fourth sidewall (14) through the third arc-shaped sidewall (23), the other end of the third sidewall (13) is connected to the second sidewall (12) through the fourth arc-shaped sidewall (24), and the third arc-shaped sidewall (13) is closer to the inlet (1) relative to the fourth arc-shaped sidewall (14); The radius (R) of the first arc-shaped sidewall (21) is smaller than the radius (R) of the second arc-shaped sidewall (22); And / or, the R angle of the third arcuate sidewall (23) is smaller than the R angle of the fourth arcuate sidewall (24).

8. The heat exchanger according to claim 7, characterized in that, The plurality of protrusions (4) are arranged parallel to the first direction, and the length between the centers of two adjacent protrusions (4) is S; the plate includes a first plate (15) and a second plate (16), the first plate (15) and the second plate (16) are stacked, and the protrusions (4) of the first plate (15) are offset by 1 / 4S or 1 / 2S relative to the protrusions (4) of the second plate (16).

9. The heat exchanger according to claim 4 or 8, characterized in that, Along the direction perpendicular to the substrate portion (3), the distance between the substrate portions (3) of two adjacent plates is defined as the plate distance; the heat exchanger is provided with a plurality of first plate channels (19) and a plurality of second plate channels (20) that are isolated from each other, and the plate distance H1 of the first plate channel (19) and the plate distance H2 of the second plate channel (20) satisfy the following relationship: H1 < H2.

10. The heat exchanger according to claim 9, characterized in that, The protrusion (4) of the second plate (16) is welded to the substrate portion (3) of the first plate (15), and the height of the protrusion (4) of the second plate (16) relative to the substrate portion (3) of the second plate (16) is H4; the protrusion (4) of the first plate (15) is welded to the substrate portion (3) of the second plate (16), and the height of the protrusion (4) of the first plate (15) relative to the substrate portion (3) of the first plate (15) is H3, and H3 and H4 satisfy the following relationship: H3 > H4.

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