Double-walled heat shield with baffle sandwich structure and method of forming a heat shield air film

Abstract

The present application relates to a kind of double-wall heat shields with baffle sandwich structure, double-wall heat shield is gas film orifice plate and impact orifice plate and turbulence baffle structure jointly constitutes the double-wall heat shield described;Turbulence baffle structure includes first helical baffle and second helical baffle vertically arranged on gas film orifice plate, and multiple separate turbulence spaces are enclosed by two baffle plates crossing each other;Gas film orifice is arranged at the multiple intersection points formed by the first helical baffle and the second helical baffle on the gas film orifice plate;The present application also provides the heat shield gas film forming method, airflow flows out through multiple fan-shaped holes to form gas film outflow and main flow gas mixing, and forms gas film cover layer on wall surface;The present application can not only strengthen the heat exchange inside heat shield, but also improve gas film cold efficiency, in addition, the impact orifice plate-gas film orifice plate double-wall structure with baffle turbulence fixed has good mechanical properties.

Description

Method for forming a double-walled heat insulation screen with a partition sandwich structure and a heat insulation air film Technical Field

[0001] This invention relates to the field of gas turbine engines, and more specifically to a heat shield structure and film formation method for an aero-engine. Background Technology

[0002] During aircraft startup, climb, and emergency maneuvers, aero engines require afterburner combustion to generate additional thrust. In afterburner mode, the temperature of the exhaust gases flowing through the afterburner and exhaust nozzle exceeds 2000K, far exceeding the heat resistance limit of usable high-temperature materials. Therefore, effective thermal protection is essential for the load-bearing structures of the afterburner and exhaust nozzle.

[0003] Heat shields are widely used as a form of thermal protection for afterburners and exhaust nozzles. Several heat shields for afterburners have been previously disclosed, including a porous corrugated plate heat shield (US 005465572A). Its corrugated structure's elasticity effectively prevents the effects of thermal deformation caused by vibration of the exhaust nozzle, and the cooling jets through discrete film cooling holes on the corrugated plate provide film cooling to the high-temperature combustion gas side of the heat shield. However, precisely because of the corrugated structure, the cooling film jets cannot cover the entire surface, resulting in excessively high local wall temperatures and preventing the formation of effective film coverage and heat exchange.

[0004] Another type is the divergent cooling heat shield structure with turbulence columns (US20140096527A1). This structure forms an air film covering the wall surface through divergent cooling, preventing direct contact with the high-temperature combustion gases. Simultaneously, the turbulence columns on the cold air side of the heat shield can turbulently mix the cold air, enhancing convective heat transfer and allowing the cold air to carry away more heat, thus lowering the wall temperature. However, a simple divergent cooling method makes it difficult for the turbulence columns to function optimally; the cooling flow mixing is not strong enough to improve its cooling efficiency.

[0005] Based on the above experience, and combining traditional methods such as film cooling and impact cooling, patent (CN103968418A) discloses a double-walled heat shield for an afterburner. This structure includes a wall surface with film cooling holes near the combustion gas side, a wall surface with impact holes near the cold gas side, and a trapezoidal reinforcing frame between the film cooling plate and the impact cooling plate. This forms a composite cooling system combining impact cooling on the cold gas side, internal convection heat transfer, and film cooling coverage of the combustion gas side. This structure can remove the transferred heat through convection heat transfer, improving the utilization rate of the cold gas, and also has good mechanical properties. However, this structure does not consider the flow resistance introduced by the trapezoidal reinforcing frame during internal convection heat transfer.

[0006] With the development of advanced high-performance gas turbine engines, the temperature of the gas flowing through the afterburner and exhaust nozzle is constantly increasing. In addition, the increased airflow required for mainstream combustion leads to a decrease in the airflow available for cooling. Therefore, it is necessary to apply heat shield structures with high-efficiency cooling capabilities, that is, to achieve better cooling effect with as little cooling air as possible. Summary of the Invention

[0007] The purpose of this invention is to overcome the shortcomings of the prior art and provide a double-walled heat insulation screen with a partition sandwich structure and a method for forming a heat insulation air film, which has a simple structure, good mechanical properties, enhances convective heat transfer within the double-walled structure, and improves the air film cooling efficiency on the air film perforated plate.

[0008] To achieve the above objectives, the technical solution adopted by the present invention is as follows: a double-walled heat insulation screen with a partition sandwich structure, the double-walled heat insulation screen including an air film perforated plate and an impact perforated plate, and a turbulence baffle structure is disposed in the cavity between the air film perforated plate and the impact perforated plate, wherein the air film perforated plate, the impact perforated plate and the turbulence baffle structure together constitute the double-walled heat insulation screen.

[0009] The aforementioned turbulence-disrupting structure includes a first spiral baffle and a second spiral baffle that are fixedly connected to and vertically arranged on the air film perforated plate. The first spiral baffle and the second spiral baffle are continuously and intersecting each other, so that multiple intersection points formed by the continuous intersection of the two baffles are arranged in a matrix within the cavity. At the same time, the two baffles intersect each other to form multiple turbulence-disrupting spaces.

[0010] The helix angles formed by the tangents of the first and second spiral partitions and the straight generatrix of the double-walled heat insulation screen passing through the tangent points of the two tangents are α and β, respectively, and both are 30 to 60 degrees.

[0011] The impact holes are arranged in a matrix on the impact hole plate, and the central axis of the impact holes passes through the spatial center point of the separation turbulence space.

[0012] The air film perforated plate has air film holes arranged in a matrix, and the air film holes are located at multiple intersection points formed by the first spiral partition and the second spiral partition on the air film perforated plate.

[0013] Furthermore, with Sx as the axial spacing of the intersection points and Sy as the circumferential spacing of the intersection points, the opening ratio of the air film holes relative to the axial and circumferential spacing of the intersection points is:

[0014] The area of ​​the air film pores / Sx×Sy = 0.4~4%.

[0015] Furthermore, the air film pores are formed at the intersection by the first spiral partition and the second spiral partition, and are at least four fan-shaped pores with a projected shape of a fan. The four fan-shaped pores form a complete circular air film pore, and each fan-shaped pore is correspondingly located at the corner of the separated turbulence space; the center point of the ring formed by the four fan-shaped pores is located at the center of the intersection.

[0016] Furthermore, the distance between the air film orifice plate and the impact orifice plate is H; the equivalent orifice diameter of the air film orifice is d, and the equivalent orifice is a circular orifice with the same area as the total area of ​​at least four sector orifices, then:

[0017] H / d = 0.1~20.

[0018] Furthermore, the thickness of the first spiral partition and the second spiral partition is... δ The height is l; the equivalent aperture of the air film pore is d, and the equivalent aperture is a circular hole with the same area as the total area of ​​at least four sector-shaped holes, i.e.:

[0019] l / d = 0.1~20mm;

[0020] δ <0.2d; d=0.5~1.5mm;

[0021] Therefore, the sector radius of the sector-shaped hole is 0.1–0.5 mm, and the thickness is... δ The radius of the sector does not exceed that of the sector-shaped hole (11-1).

[0022] Furthermore, the center points of the four fan-shaped holes are located at the intersection of the first and second spiral partitions within the separated turbulence space. The four fan-shaped holes are holes that extend from the center points along the direction of the two partition walls. The central angles of the four fan-shaped holes are the four intersecting angles at the intersection of the first and second spiral partitions.

[0023] Furthermore, the air film pores are normal through holes or inclined holes on the air film pore plate;

[0024] When the holes are inclined, the inclination angle between the air film holes and the normal of the air film orifice plate is 10-60 degrees; the sector radius of the four sector holes that make up the air film holes is 0.3-5mm.

[0025] Furthermore, the height of the first and second partitions is consistent with the height of the cavity between the air film perforated plate and the impact perforated plate, and the upper and lower ends of the two partitions are fixedly connected to the air film perforated plate and the impact perforated plate to form an integrated structure.

[0026] Furthermore, the impact hole is a normal through hole or an inclined hole in the impact hole plate;

[0027] When the hole is inclined, the inclination angle between the impact hole and the normal of the impact hole plate is 10-60 degrees, and the diameter of the impact hole is 0.6-10mm.

[0028] The present invention also provides a method for forming a heat-insulating air film of the heat insulation screen. The impact jet C1 enters the double-wall cavity through the impact hole and is subjected to impact cooling on the bottom surface of the partition space formed by the intersection of the first and second spiral partitions. Starting from the impact stagnation point, a wall-adhering jet C2 is formed and diffuses outward. A portion of the airflow C3 of the wall-adhering jet C2 directly enters the fan-shaped holes at the four corners of the partition turbulence space through the wall-adhering flow. Another portion of the airflow collides with the first and second spiral partitions to form a reverse flow C4, and is then spirally drawn into the fan-shaped holes at the four corners of the partition turbulence space. The partition turbulence space is used on the one hand to block the interference between adjacent impact jets and weaken the impact effect between them, so that a single impact jet can exert its maximum impact cooling effect. On the other hand, it is used to increase the convective heat transfer area through the partitions around the perimeter, thereby enhancing the convective heat transfer effect in the channel.

[0029] The airflow flows out through the air film holes to form an air film outflow C5, which is mixed with the mainstream gas C6. This reduces the gas temperature near the wall and forms an air film covering layer on the wall. Since the turbulence barrier structure weakens the momentum ratio of the air film outflow, it not only improves the coverage effect of the air film outflow, but also improves the air film cooling, flow heat transfer and overall cooling efficiency.

[0030] The beneficial effects of this invention are as follows: This invention proposes a double-walled heat shield with a baffle turbulence structure, mainly used in combustion chambers and tail nozzles. Its structure includes a gas film perforated plate on the gas side, an impact perforated plate on the cold gas side, and a baffle turbulence structure between the gas film perforated plate and the impact perforated plate. The impact perforated plate forms a cold gas duct with the outer wall of the combustion chamber or tail nozzle, and the gas film perforated plate is the inner wall of the cylinder of the combustion chamber or tail nozzle, directly contacting the mainstream gas. The impact perforated plate and the gas film perforated plate form a convective heat exchange channel.

[0031] As an internal cooling structure, the baffle turbulence can adjust its structural parameters to meet the optimal arrangement of impact cooling and film cooling. On the other hand, it can increase the heat exchange area with a small volume ratio, enhance convective heat transfer, improve film cooling efficiency, effectively reduce wall temperature, and improve the utilization rate of cold air.

[0032] The outstanding advantage of this invention is that it enhances both internal heat exchange and improves film cooling efficiency, thus simultaneously improving both internal and external cooling effects. Furthermore, the double-walled structure of the impactor plate-film cooling plate with baffled flow control provides excellent mechanical properties. Attached Figure Description

[0033] Figure 1 is a schematic diagram of the present invention, namely, a double-walled heat insulation screen with a baffle turbulence structure;

[0034] Figure 2 is an axial sectional view of the present invention with double-walled structure;

[0035] Figure 3 is a flow diagram of the internal streamlines of the double-layered wall of the baffle plate of the present invention.

[0036] (a) shows the streamlines within a baffled double-walled cavity, and (b) shows the streamlines within multiple double-walled cavities.

[0037] Figure 4 is a comparison diagram of the spanwise average air film cooling effect of the present invention;

[0038] Figure 5 is a comparison of the spanwise average comprehensive cooling efficiency of the present invention;

[0039] Figure 6 is a cloud diagram of the heat transfer coefficient of the impact target surface of the present invention, wherein:

[0040] (a) is a cloud diagram of the heat transfer coefficient of the straight column turbulent double-walled target surface;

[0041] (b) is a cloud diagram of the heat transfer coefficient of the double-walled target surface of the baffle turbulence of the present invention.

[0042] In the figure: 1. Film air plate; 11. Film air hole; 11-1. Fan-shaped hole; 2. Impact plate; 21. Impact hole; 3. Turbulence baffle structure; 31. First spiral baffle; 32. Second spiral baffle; 4. Separated turbulence space. Detailed Implementation

[0043] The principles and features of the present invention are described below with reference to the accompanying drawings. The examples given are only for explaining the present invention and are not intended to limit the scope of the present invention.

[0044] To achieve the above objectives, the present invention provides the following specific embodiments:

[0045] Example 1: As shown in Figures 1-3, a double-walled heat insulation screen with a partition sandwich structure is provided. The double-walled heat insulation screen includes an air film perforated plate 1 and an impact perforated plate 2. A turbulence baffle structure 3 is disposed in the cavity between the air film perforated plate 1 and the impact perforated plate 2. The air film perforated plate 1, the impact perforated plate 2 and the turbulence baffle structure 3 together constitute the double-walled heat insulation screen.

[0046] The turbulence-disrupting structure 3 includes a first spiral baffle 31 and a second spiral baffle 32 fixedly connected and vertically arranged on the air film perforated plate 1. The first spiral baffle 31 and the second spiral baffle 32 are continuously and intersecting each other, so that multiple intersection points formed by the continuous intersection of the two baffles are arranged in a matrix within the cavity. At the same time, the two baffles intersect each other to form multiple separated turbulence spaces 4. The height of the first baffle 31 and the second baffle 32 is consistent with the height of the cavity between the air film perforated plate 1 and the impact perforated plate 2, and the upper and lower ends of the two baffles are fixedly connected to the air film perforated plate 1 and the impact perforated plate 2 to form an integrated structure.

[0047] The helical angles formed by the tangents of the first spiral partition 31 and the second spiral partition 32 and the straight generatrix of the double-wall heat insulation screen passing through the tangent points of the two tangents are angle α and angle β, respectively, and both are 30 to 60 degrees.

[0048] The impact orifice plate 2 has impact holes 21 arranged in a matrix. The central axis of the impact holes 21 passes through the center point of the space separating the turbulence space 4. The impact holes 21 are normal through holes or inclined holes of the impact orifice plate 2.

[0049] When the hole is inclined, the inclination angle between the impact hole 21 and the normal of the impact hole plate 2 is 10-60 degrees, and the diameter of the impact hole 6 is 0.6-10mm.

[0050] The air film perforated plate 1 has air film holes 11 arranged in a matrix. The air film holes 11 are located at multiple intersections formed by the first spiral partition 31 and the second spiral partition 32 on the air film perforated plate 1.

[0051] With Sx as the axial spacing of the intersection points and Sy as the circumferential spacing of the intersection points, the opening ratio of the air film holes 1 relative to the axial and circumferential spacing of the intersection points is:

[0052] The area of ​​the air film pores / Sx×Sy = 0.4~4%.

[0053] The air film pore 11 is formed by the first spiral baffle 31 and the second spiral baffle 32 at the intersection, and at least four fan-shaped pores 11-1 with a projected shape of fan. The four fan-shaped pores 11-1 form a complete circular air film pore 11, and each fan-shaped pore 11-1 is correspondingly set at the corner of the separated turbulence space 4. The center point of the ring formed by the four fan-shaped pores 11-1 is located at the center of the intersection.

[0054] The distance between the air film orifice plate 1 and the impact orifice plate 2 is H; the equivalent orifice diameter of the air film orifice 11 is d, which is a circular orifice with the same area as the total area of ​​at least four sector orifices 11-1. Therefore:

[0055] H / d = 0.1~20.

[0056] The thickness of the first spiral partition 31 and the second spiral partition 32 is δ The height is l; the equivalent aperture of the air film pore 11 is d, which is a circular hole with the same area as the total area of ​​at least four sector pores 11-1, i.e.:

[0057] l / d = 0.1~20mm;

[0058] δ <0.2d; d=0.5~1.5mm;

[0059] Therefore, the sector radius of sector hole 11-1 is 0.1~0.5mm, and the thickness is... δThe sector radius shall not exceed that of sector hole 11-1.

[0060] The center point of the four fan-shaped holes 11-1 is set at the intersection of the first spiral baffle 31 and the second spiral baffle 32 in the separation turbulence space 4. The four fan-shaped holes 11-1 are holes that extend from the center point along the direction of the two baffle walls. The central angles of the four fan-shaped holes 11-1 are the four intersecting angles at the intersection of the first spiral baffle 31 and the second spiral baffle 32.

[0061] The air film orifice 11 is a normal through hole or inclined hole on the air film orifice plate 1;

[0062] When the holes are inclined, the inclination angle between the air film hole 11 and the air film orifice plate 1 in the normal direction is 10-60 degrees; the sector radius of the four sector holes 11-1 that make up the air film hole 11 is 0.3-5mm.

[0063] Based on the same opening ratio of the air film plate, the opening ratio of the impact plate, and the diameter of the turbulence column, and with the flow parameters kept consistent, the baffle turbulence double-wall structure was compared with the traditional circular straight column turbulence double-wall structure. The air film cooling efficiency, overall cooling efficiency, and heat transfer distribution of the impact target surface are shown in Figures 4 and 5. It can be seen from the figures that compared with the circular straight column air film hole flow double-wall structure, the baffle turbulence double-wall structure provided by the present invention has a significantly higher air film cooling efficiency and overall cooling efficiency.

[0064] As shown in Figure 6, for target surface heat exchange, there are low heat transfer zones on both sides of the tail of the straight column air film hole turbulence. The baffle turbulence structure provided by the present invention can effectively avoid the occurrence of this low heat transfer zone.

[0065] Example 2: Same as Example 1, except that: the impact hole 21 is a normal through hole of the impact orifice plate 2; the air film hole 11 is a normal through hole on the air film orifice plate 1.

[0066] Example 3: Same as Example 1, except that: the impact hole 21 is an inclined hole of the impact orifice plate 2, and the inclination angle between the impact hole 21 and the normal of the impact orifice plate 2 is 10-60 degrees; the air film hole 11 is an inclined hole on the air film orifice plate 1, and the inclination angle between the air film hole 11 and the normal of the air film orifice plate 1 is 10-60 degrees; the fan radius of the four fan-shaped holes 11-1 that make up the air film hole 11 is 0.3-5mm.

[0067] Example 4: As shown in Figure 3, the present invention also provides a method for forming the heat insulation film of the heat insulation screen as follows: the impact jet C1 enters the double-wall cavity through the impact hole 2 and is subjected to impact cooling on the bottom surface of the partition space 4 formed by the intersection of the first spiral partition 31 and the second spiral partition 32, and forms a wall-attached jet C2 that diffuses outward from the impact stagnation point.

[0068] As shown in Figures 3(a) and (b), a portion of the airflow C3 from the wall-mounted jet C2 directly enters the fan-shaped holes 11-1 at the four corners of the partitioned turbulence space 4 through the wall-mounted flow; another portion of the airflow collides with the first spiral baffle 31 and the second spiral baffle 32 to form a reverse flow C4, and is then spirally drawn into the fan-shaped holes 11-1 at the four corners of the partitioned turbulence space 4. The partitioned turbulence space 4 serves two purposes: firstly, to block the interference between adjacent impact jets and weaken their mutual impact effects, allowing a single impact jet to exert its maximum impact cooling effect; secondly, to increase the convective heat transfer area through the surrounding baffles, thereby enhancing the convective heat transfer effect in the channel; the airflow flows out through the film gas hole 11 to form a film gas outflow C5 and mixes with the mainstream combustion gas C6, reducing the temperature of the combustion gas near the wall while forming a film gas covering layer on the wall. Since the turbulence baffle structure 3 weakens the momentum ratio of the film gas outflow, it not only improves the coverage effect of the film gas outflow, but also improves the film gas cooling, convective heat transfer, and overall cooling efficiency.

[0069] The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the protection scope of the present invention.

Claims

1. A double-walled heat insulation screen with a partition sandwich structure, characterized in that, The double-walled heat insulation screen includes an air-film perforated plate (1) and an impact perforated plate (2). A turbulence baffle structure (3) is disposed in the cavity between the air-film perforated plate (1) and the impact perforated plate (2). The air-film perforated plate (1), the impact perforated plate (2), and the turbulence baffle structure (3) together constitute the double-walled heat insulation screen. The turbulence baffle structure (3) includes a first spiral baffle (31) and a second spiral baffle (32) fixedly connected and vertically disposed on the air-film perforated plate (1). The first spiral baffle (31) and the second spiral baffle (32) are continuously and intersecting each other, so that multiple intersection points formed by the continuous intersection of the two baffles are arranged in a matrix within the cavity. At the same time, the two baffles intersect each other. The spirals intersect to form multiple separation and turbulence spaces (4); the tangents of the spiral lines of the first spiral baffle (31) and the second spiral baffle (32) form spiral angles α and β respectively with the straight generatrix of the double-walled heat insulation screen passing through the tangent points of the two tangents, and both are 30~60 degrees; the impact hole plate (2) is matrix-arranged with impact holes (21), and the central axis of the impact holes (21) passes through the spatial center point of the separation and turbulence space (4); the air film perforated plate (1) is matrix-arranged with air film holes (11), and the air film holes (11) are set at multiple intersection points formed by the first spiral baffle (31) and the second spiral baffle (32) on the air film perforated plate (1).

2. The double-walled heat insulation screen with a partition sandwich structure as described in claim 1, characterized in that, With Sx as the axial spacing of the intersection points and Sy as the circumferential spacing of the intersection points, the opening rate of the air film holes (11) relative to the axial and circumferential spacing of the intersection points is: area of ​​air film holes / Sx × Sy = 0.4~4%.

3. The double-walled heat insulation screen with a partition sandwich structure as described in claim 1, characterized in that, The air film hole (11) is formed by the first spiral partition (31) and the second spiral partition (32) at the intersection, and at least four fan-shaped holes (11-1) with a projected shape of fan. The four fan-shaped holes (11-1) form a complete circular air film hole (11), and each fan-shaped hole (11-1) is correspondingly set at the corner of the separated turbulence space (4). The center point of the ring formed by the four fan-shaped holes (11-1) is located at the center of the intersection.

4. The double-walled heat insulation screen with a partition sandwich structure as described in claim 3, characterized in that, The distance between the air film perforated plate (1) and the impact perforated plate (2) is H; the equivalent aperture of the air film perforation (11) is d, and the equivalent aperture is a circular hole with the same area as the total area of ​​at least four fan-shaped holes (11-1), so H / d = 0.1~20.

5. The double-walled heat insulation screen with a partition sandwich structure as described in claim 3, characterized in that, The thickness of the first spiral partition (31) and the second spiral partition (32) is δ, and the height is l; the equivalent aperture of the air film hole (11) is d, and the equivalent hole is a circular hole with the same area as the total area of ​​at least four fan-shaped holes (11-1), that is: l / d=0.1~20mm; δ<0.2d; d=0.5~1.5mm; then, the fan radius of the fan-shaped hole (11-1) is 0.1~0.5mm, and the thickness δ does not exceed the fan radius of the fan-shaped hole (11-1).

6. The double-walled heat insulation screen with a partition sandwich structure as described in claim 3, characterized in that, The center point of the four fan-shaped holes (11-1) is set at the intersection of the first spiral partition (31) and the second spiral partition (32) in the separated turbulence space (4). The four fan-shaped holes (11-1) are holes that extend from the center point along the direction of the two partition walls. The central angle of the four fan-shaped holes (11-1) is the four intersecting angles at the intersection of the first spiral partition (31) and the second spiral partition (32).

7. The double-walled heat insulation screen with a partition sandwich structure as described in claim 6, characterized in that, The air film hole (11) is a normal through hole or an inclined hole on the air film orifice plate (1); when it is an inclined hole, the inclination angle between the air film hole (11) and the normal of the air film orifice plate (1) is 10-60 degrees. The sector radius of the four sector holes (11-1) that make up the air film pore (11) is 0.3-5 mm.

8. The double-walled heat insulation screen with a partition sandwich structure as described in claim 1, characterized in that, The height of the first spiral partition (31) and the second spiral partition (32) is consistent with the height of the cavity between the air film perforated plate (1) and the impact perforated plate (2), and the upper and lower ends of the two partitions are fixedly connected to the air film perforated plate (1) and the impact perforated plate (2) to form an integrated structure.

9. The double-walled heat insulation screen with a partition sandwich structure as described in any one of claims 1-8, characterized in that, The impact hole (21) is a normal through hole of the impact hole plate (2) or an inclined hole; when it is an inclined hole, the inclination angle between the impact hole (21) and the normal of the impact hole plate (2) is 10-60 degrees, and the diameter of the impact hole (21) is 0.6-10mm.

10. A method for forming a heat-insulating air film of a heat-insulating screen as described in any one of claims 1-8, characterized in that, The impact jet C1 enters the double-walled cavity through the impact hole (21) and undergoes impact cooling on the bottom surface of the partitioned turbulence space (4) formed by the intersection of the first spiral baffle (31) and the second spiral baffle (32). Starting from the impact stagnation point, a wall-attached jet C2 is formed and diffuses outward. A portion of the airflow C3 of the wall-attached jet C2 directly enters the fan-shaped holes (11-1) at the four corners of the partitioned turbulence space (4) through the wall-attached flow. Another portion of the airflow collides with the first spiral baffle (31) and the second spiral baffle (32) to form a reverse flow C4, which is then spirally drawn into the fan-shaped holes (11-1) at the four corners of the partitioned turbulence space (4). The partitioned turbulence space (4) serves two purposes: firstly, to block interference between adjacent impact jets and weaken their impact effects, allowing a single impact jet to exert its maximum impact cooling effect; secondly, to increase the convective heat transfer area through the surrounding partitions, thereby enhancing the convective heat transfer effect in the channel. The airflow flows out through the air film hole (11) to form an air film outflow C5, which is mixed with the mainstream gas C6. This reduces the gas temperature near the wall while forming an air film covering layer on the wall. Since the turbulence partition structure (3) weakens the momentum ratio of the air film outflow, it not only improves the coverage effect of the air film outflow but also improves the air film cooling, convective heat transfer, and overall cooling efficiency.

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