Noise reduction support plate structure of turbo expander

Abstract

The invention relates to the technical field of impeller machinery, in particular to a turbo expander noise reduction supporting plate structure which comprises a supporting plate body, a tooth-shaped tail edge and sound absorption holes, the tooth-shaped tail edge is arranged on one side of the supporting plate body, the two ends of the supporting plate body are connected with the inner wall of an exhaust pipe and a flow guide cone respectively, and the supporting plate body is arranged close to an air inlet. The tooth-shaped tail edge is arranged close to the exhaust port; sound absorption holes are formed in the side face of the supporting plate body. Noise generated by an upstream turbine blade grid is absorbed through the sound absorption holes, an efficient through-flow structure is formed through the tooth-shaped tail edge, poor flow structures such as flow separation, falling vortex and wake loss are changed, and the aerodynamic noise of the turbine blade grid is restrained.

Description

Technical Field

[0001] This invention belongs to the field of turbomachinery technology, and particularly relates to a noise reduction support plate structure for a turbo expander. Background Technology

[0002] Turbine expanders are core components for obtaining cooling energy in air separation, natural gas liquefaction separation, and cryogenic pulverization equipment. They achieve cooling by performing work through the adiabatic expansion of gas. Their working principle is similar to that of a piston expander, and the output energy is recovered by a coaxial compressor or brake fan. Their operation requires maintaining stable bearing gas pressure, precise component clearances, proper dynamic balance, and tight nuts.

[0003] The working principle of a turbo expander is to convert the internal energy of the gas into mechanical energy by expanding the gas in the impeller. In this process, the high-speed flow of gas and the high-speed operation of mechanical parts will generate high-intensity noise. Relevant research data shows that the noise generated by traditional turbo expanders can reach 85-100 decibels, far exceeding the safe operating noise threshold (generally, the safe noise threshold for 8 hours of exposure is considered to be 85 decibels). Therefore, effectively reducing the noise during the operation of turbo expanders is of great significance for protecting the health of operators, improving the stability of equipment operation, and meeting environmental protection regulations.

[0004] To address the aforementioned issues, existing patent CN212079427U discloses a noise reduction and energy-saving device for an expander generator, comprising an expander, a noise reduction mechanism, an oil cooler, and a gearbox. The expander's outlet is connected to an outlet pipe, the other end of which is connected to the inlet of the noise reduction mechanism. The noise reduction mechanism's outlet is connected to a connecting pipe, the other end of which is connected to the interior of the oil cooler's outer shell. An oil inlet pipe is connected to the other side of the oil cooler, and an oil outlet pipe is located parallel to the oil inlet pipe on the other side of the oil cooler. Both the inlet and outlet pipes are connected to the gearbox, which is mounted on one side of the expander. The noise reduction mechanism consists of a silencer pipe, a sound reflector, a sound-absorbing plate, and an outer shell. The sound reflector is welded to the center of the outer shell, and a silencer pipe runs through it. The long end of the silencer pipe is near the inlet of the noise reduction mechanism, and a sound-absorbing plate is located inside the outer shell near the outlet of the noise reduction mechanism. The problem with the above technology is that it mainly involves installing a silencer at the expander outlet to suppress the noise, rather than directly controlling the source of the noise. Summary of the Invention

[0005] In view of this, the present invention aims to provide a noise reduction support plate structure for a turbine expander, wherein sound-absorbing holes are arranged on the support plate of the expander exhaust section to absorb the noise generated by the upstream turbine blades, and at the same time, the pit structure formed by the sound-absorbing holes themselves can control the flow separation on the surface of the support plate and control vortex-induced noise.

[0006] To achieve the above objectives, the technical solution created by this invention is implemented as follows: A noise-reducing support plate structure for a turbine expander is disclosed, used to connect a coaxially arranged exhaust pipe and a guide cone. One end of the cavity formed between the exhaust pipe and the guide cone is an air inlet, and the other end of the cavity is an exhaust outlet. The structure includes a support plate body, a toothed tail edge, and three sets of sound-absorbing holes. The toothed tail edge is located on one side of the support plate body, and both ends of the support plate body are connected to the inner wall of the exhaust pipe and the guide cone, respectively. The support plate body is located near the air inlet, and the toothed tail edge is located near the exhaust outlet. Sound-absorbing holes are provided on the side of the support plate body to reduce noise. The vertical height of the support plate body is H.

[0007] Furthermore, the main body of the support plate is vertically positioned between the exhaust pipe and the guide cone, and the cross-section of the toothed tail edge is triangular. The width W of the main body of the support plate ranges from 0.01 times to 0.9 times H. The toothed tail edge can reduce the aerodynamic noise generated by flow separation or vortices during the flow of air around the main body of the support plate.

[0008] Furthermore, the diameter L of the sound-absorbing hole ranges from 0.01 to 0.9 times H, the depth D of the sound-absorbing hole ranges from 0.01 to 0.9 times H, the depth A of the toothed trailing edge ranges from 0.01 to 3 times H, and the width B of the toothed trailing edge ranges from 0.01 to 0.5 times H. By combining the sound-absorbing hole and the toothed trailing edge, the aerodynamic noise generated by flow separation or vortices during the flow of air around the main body of the support plate is reduced.

[0009] Furthermore, the main body of the support plate is inclined between the exhaust pipe and the guide cone support. The angle α between the main body of the support plate and the vertical direction ranges from 0° to 170°. The cross-section of the toothed tail edge in the middle is square, the cross-section of the toothed tail edge at both ends is triangular, and the cross-section of at least one set of sound-absorbing holes in the middle is square. The cross-section of the two sets of sound-absorbing holes at both ends is circular. The aerodynamic noise generated by flow separation or vortex during the flow of air around the main body of the support plate is reduced by the cooperation of the sound-absorbing holes and the toothed tail edge.

[0010] Furthermore, each set of sound-absorbing holes at both ends is arranged in a triangular shape, with the vertical distance C1 between two adjacent sound-absorbing holes ranging from 0 to 0.8 times W; the sound-absorbing holes in the middle are all arranged in a quadrilateral shape, with the vertical distance d1 between two adjacent sound-absorbing holes in the horizontal direction ranging from 0 to 0.8 times W, and the vertical distance d2 between two adjacent sound-absorbing holes in the vertical direction ranging from 0 to 0.8 times W, in order to increase the sound absorption effect.

[0011] Furthermore, the range H2 of the sound-absorbing holes located in the middle with a quadrilateral cross-section is 0 to 0.8 times H; the range of the sound-absorbing holes located in the middle with a quadrilateral cross-section to the vertical height H1 of the exhaust pipe is 0 to 0.8 times H; and the range of the sound-absorbing holes located in the middle with a quadrilateral cross-section to the vertical height H3 of the guide cone 11 is 0 to 0.8 times H, in order to increase the sound absorption effect.

[0012] Furthermore, the width B1 of the toothed trailing edge at the end ranges from 0.001 to 0.5 times H, the depth A1 of the toothed trailing edge at the end ranges from 0.001 to 3 times H, the depth A2 of the toothed trailing edge in the middle ranges from 0.001 to 3 times H, and the sum of the vertical distance between two adjacent toothed trailing edges in the middle and the thickness between a toothed trailing edge B2 ranges from 0.001 to 0.5 times H. The toothed trailing edge can reduce the aerodynamic noise generated by flow separation or vortices during the flow of air around the main body of the support plate.

[0013] Furthermore, the main body of the support plate includes a straight section, a first arc-shaped section, and a second arc-shaped section. The top end of the straight section is connected to the exhaust pipe through the first arc-shaped section, and the other end of the straight section is connected to the guide cone through the second arc-shaped section. A toothed tail edge is provided on the straight section, and a set of sound-absorbing holes are opened on the side of the first arc-shaped section. The angle α1 between the first arc-shaped section and the vertical direction is in the range of 0°-180°, and the angle α2 between the second arc-shaped section and the horizontal direction is in the range of 0°-180°.

[0014] Furthermore, a set of sound-absorbing holes is arranged in two rows, the vertical distance C2 between two adjacent sound-absorbing holes ranges from 0.001 to 0.5 times W, the overall height H4 of the two rows of sound-absorbing holes ranges from 0.01 to 0.5 times H, and the vertical distance H5 between the two rows of sound-absorbing holes and the guide cone ranges from 0.01 to 0.5 times H.

[0015] Furthermore, the overall vertical height H6 of the three toothed trailing edges is 0.001 to 0.9 times H, the vertical distance H7 between the lowermost toothed trailing edge and the guide cone 11 is 0.001 to 0.9 times H, the width B3 of the toothed trailing edge is 0.001 to 0.5 times H, and the depth A3 of the toothed trailing edge is 0.001 to 0.5 times H.

[0016] Compared with the prior art, the present invention can achieve the following beneficial effects: (1) The main body of the present invention has sound-absorbing holes to absorb the noise generated by the upstream turbine blade cascade. Furthermore, the cross section of the main body of the support plate adopts a high-efficiency aerodynamic blade shape and forms a high-efficiency flow structure to control the flow separation, shedding vortex, wake loss and other undesirable flow structures, thereby suppressing its own aerodynamic noise.

[0017] (2) The main body of the support plate described in this invention has a toothed tail edge, which forms an efficient flow control structure to control undesirable flow structures such as flow separation, shedding vortex, and wake loss, suppressing its own aerodynamic noise, enabling the turbine expander to operate with low noise and achieve the goal of energy saving and environmental protection. Attached Figure Description

[0018] The accompanying drawings, which form part of this invention, are used to provide a further understanding of the invention. The illustrative embodiments and descriptions of the invention are used to explain the invention and do not constitute an undue limitation of the invention. In the drawings: Figure 1 A cross-sectional view of a turbine expander noise reduction support plate structure as described in Embodiment 1 of this invention; Figure 2 for Figure 1 Enlarged structural diagram of section E in the middle; Figure 3 for Figure 1 Enlarged structural diagram of section F in the middle; Figure 4 A cross-sectional view of a turbine expander noise reduction support plate structure as described in Embodiment 2 of the present invention; Figure 5 for Figure 4 Enlarged structural diagram of section G in the middle; Figure 6 A cross-sectional view of a turbine expander noise reduction support plate structure as described in Embodiment 3 of this invention; Figure 7 for Figure 6 Enlarged structural diagram of the middle J section.

[0019] Explanation of reference numerals in the attached figures: 10. Exhaust pipe; 11. Guide cone; 12. Air inlet; 13. Exhaust outlet; 20. Main body of the support plate; 21. Toothed tail edge; 22. Sound-absorbing hole; 201. Straight section; 202. First arc-shaped section; 203. Second arc-shaped section. Detailed Implementation

[0020] 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 specific embodiments. It should be understood that the specific embodiments described herein are merely illustrative of the invention and do not constitute a limitation thereof.

[0021] It should be noted that, unless otherwise specified, the embodiments and features described in the present invention can be combined with each other.

[0022] In the description of this invention, it should be understood that the terms "center," "longitudinal," "lateral," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," and "outer," etc., indicating orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, are only for the convenience of describing this invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation on this invention. Furthermore, the terms "first," "second," etc., are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of indicated technical features. Thus, features defined with "first," "second," etc., may explicitly or implicitly include one or more of that feature. In the description of this invention, unless otherwise stated, "a plurality of" means two or more.

[0023] In the description of this invention, it should be noted that, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "linking" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection of two components. Those skilled in the art will understand the specific meaning of the above terms in this invention based on the specific circumstances.

[0024] The invention will now be described in detail with reference to the accompanying drawings and embodiments.

[0025] Example 1 like Figures 1 to 3 As shown, a noise reduction support plate structure for a turbine expander is used to connect an exhaust pipe 10 and a guide cone 11 arranged coaxially. One end of the cavity formed between the exhaust pipe 10 and the guide cone 11 is an air inlet 12, and the other end of the cavity is an exhaust outlet 13. The structure includes a support plate body 20, at least three toothed trailing edges 21, and at least three sets of sound-absorbing holes 22. The at least three toothed trailing edges 21 are disposed on one side of the support plate body 20. The toothed trailing edges can further reduce the aerodynamic noise generated by flow separation or vortices when the airflow flows around the support plate. The two ends of the support plate body 20 are respectively connected to the inner wall of the exhaust pipe 10 and the guide cone 11. The support plate body 20 is disposed near the air inlet 12, and the at least three toothed trailing edges 21 are disposed near the exhaust outlet 13. At least three sets of sound-absorbing holes 22 are opened on the side of the support plate body 20, and the vertical height of the support plate body 20 in the vertical direction is H.

[0026] The support plate body 20 is vertically arranged between the exhaust pipe 10 and the guide cone 11. The cross-section of the toothed tail edge 21 is triangular. The width W of the support plate body 20 ranges from 0 times to 0.00001 times H. The toothed tail edge 21 can reduce the aerodynamic noise generated by flow separation or vortex during the flow of air around the support plate body 20.

[0027] The diameter L of the sound-absorbing hole 22 ranges from 0.01 to 0.9 times H. When L is 0.9 times H, only one sound-absorbing hole 22 is provided. The depth D of the sound-absorbing hole 22 ranges from 0.01 to 0.9 times H. When D is 0.9 times H, the sound-absorbing hole 22 is provided on one side. The depth A of the toothed tail edge 21 ranges from 0.01 to 3 times H, and the width B of each tooth on the toothed tail edge 21 ranges from 0.01 to 0.5 times H. The aerodynamic noise generated by flow separation or vortex during the flow of air around the support plate body 20 is reduced by the cooperation of the sound-absorbing hole 22 and the toothed tail edge 21.

[0028] The distribution characteristics of each group of sound-absorbing holes 22 along the main body 20 of the support plate are: axial distribution, radial distribution, and simultaneous axial and radial distribution; each group of sound-absorbing holes 22 can also be concentrated in the front edge region, middle section region, and rear edge region of the support plate. The sound-absorbing holes 22 on the main body 20 of the support plate can ensure the maximum sound absorption effect.

[0029] The toothed tail edge 21 is distributed along the main body 20 of the support plate as follows: distributed within the height range of the main body 20 of the support plate, distributed within the root area of ​​the main body 20 of the support plate, and distributed within the top area of ​​the main body 20 of the support plate, in order to ensure the maximum sound absorption effect.

[0030] The cross-section of the main body 20 of the support plate adopts a high-efficiency aerodynamic blade shape. By forming a high-efficiency flow passage structure, it controls undesirable flow structures such as flow separation, shedding vortex, and wake loss, and suppresses its own aerodynamic noise.

[0031] Four sets of structures according to this application can be used to connect the exhaust pipe 10 and the guide cone 11.

[0032] In this embodiment, the support plate structure is used in a turbo expander. The working fluid used in the turbo expander includes air, nitrogen, helium, argon, carbon dioxide, flue gas, natural gas, water vapor, etc.

[0033] Example 2 like Figures 4 to 5As shown, the difference between Embodiment 2 and Embodiment 1 is that the support plate body 20 is inclined between the exhaust pipe 10 and the guide cone 11, the inclination angle α between the support plate body 20 and the vertical direction ranges from 0° to 170°, the cross-section of the toothed tail edge 21 in the middle is square, the cross-section of each tooth on the toothed tail edge 21 at both ends is triangular, the cross-section of at least one set of sound-absorbing holes 22 in the middle is square, and the cross-section of the two sets of sound-absorbing holes 22 at both ends is circular. The aerodynamic noise generated by flow separation or vortex during the flow of air around the support plate body 20 is reduced by the cooperation of the sound-absorbing holes 22 and the toothed tail edge 21.

[0034] Each set of sound-absorbing holes 22 at both ends is arranged in a triangle. The vertical distance C1 between two adjacent sound-absorbing holes 22 ranges from 0 to 0.8 times W. When C1 is 0 times W, the two sound-absorbing holes 22 are connected. The vertical distance C1 between adjacent sound-absorbing holes 22 can be the same or different. The sound-absorbing holes 22 in the middle are arranged in a quadrilateral. The vertical distance d1 between two adjacent sound-absorbing holes 22 in the horizontal direction ranges from 0 to 0.8 times W. When d1 is 0 times W, the two sound-absorbing holes 22 are connected. The vertical distance d2 between two adjacent sound-absorbing holes 22 in the vertical direction ranges from 0 to 0.8 times W. When d1 is 0 times W, the two sound-absorbing holes 22 are connected. This arrangement is used to increase the sound absorption effect.

[0035] The arrangement range H2 of the sound-absorbing holes 22 located in the middle with a quadrilateral cross-section is 0 to 0.8 times H. When H2 is 0 times H, no sound-absorbing holes 22 are set in the middle. The arrangement range of the sound-absorbing holes 22 located in the middle with a quadrilateral cross-section to the vertical height H1 of the exhaust pipe 10 is 0 to 0.8 times H. When H1 is 0 times H, the sound-absorbing holes 22 with a quadrilateral cross-section are set close to the exhaust pipe 10, and no sound-absorbing holes 22 arranged in a triangle are set here. The arrangement range of the sound-absorbing holes 22 located in the middle with a quadrilateral cross-section to the vertical height H3 of the guide cone 11 is 0 to 0.8 times H. When H3 is 0 times H, the sound-absorbing holes 22 with a quadrilateral cross-section are set close to the guide cone 11, and no sound-absorbing holes 22 arranged in a triangle are set here, in order to increase the sound absorption effect.

[0036] The width B1 of each tooth on the toothed trailing edge 21 at the end ranges from 0.001 to 0.5 times H. The width B1 of the toothed trailing edge 21 at both ends can be the same or different. The depth A1 of the toothed trailing edge 21 at the end ranges from 0.001 to 3 times H. The depth A1 of the toothed trailing edge 21 at both ends can be the same or different. The depth A2 of the toothed trailing edge 21 in the middle ranges from 0.001 to 3 times H. The width B2 of each tooth on the toothed trailing edge 21 in the middle ranges from 0.001 to 0.5 times H. The toothed trailing edge 21 can reduce the aerodynamic noise generated by flow separation or vortices during the flow of air around the support plate body 20.

[0037] The support plate structure in this embodiment 2 is used in a turbo expander, and the working fluid used in the turbo expander is air.

[0038] Example 3 like Figures 6 to 7 As shown, the difference between Embodiment 3 and Embodiment 2 is that the main body 20 of the support plate includes a straight section 201, a first arc-shaped section 202, and a second arc-shaped section 203. The top end of the straight section 201 is connected to the exhaust pipe 10 through the first arc-shaped section 202, and the other end of the straight section 201 is connected to the guide cone 11 through the second arc-shaped section 203. A toothed tail edge 21 is provided on the straight section 201, and a set of sound-absorbing holes 22 are opened on the side of the first arc-shaped section 202. The angle α1 between the first arc-shaped section 202 and the vertical direction is in the range of 0°-180°, and the angle α2 between the second arc-shaped section 203 and the horizontal direction is in the range of 0°-180°. The arc-shaped structure of the first arc-shaped section 202 and the second arc-shaped section 203 reduces the flow resistance.

[0039] A set of sound-absorbing holes 22 are arranged in two rows. The vertical distance C2 between two adjacent sound-absorbing holes 22 ranges from 0.001 to 0.5 times W. The overall height H4 of the two rows of sound-absorbing holes 22 ranges from 0.01 to 0.5 times H. The vertical distance H5 between the two rows of sound-absorbing holes 22 and the guide cone 11 ranges from 0.01 to 0.5 times H, which is used to increase the sound absorption effect.

[0040] The overall vertical height H6 of the three toothed trailing edges 21 is 0.001 to 0.9 times H. The vertical distance H7 between the lowermost toothed trailing edge 21 and the guide cone 11 is 0.001 to 0.9 times H. The width B3 of each tooth on the toothed trailing edge 21 ranges from 0.001 to 0.5 times H. The depth A3 of the toothed trailing edge 21 ranges from 0.001 to 0.5 times H. The toothed trailing edge 21 can reduce the aerodynamic noise generated by flow separation or vortices during the flow of air around the main body of the support plate 20.

[0041] The support plate structure in this embodiment 3 is used in a turbo expander, and the working fluid used in the turbo expander is nitrogen.

[0042] The sound-absorbing holes 22 in this application have shapes including but not limited to circles, rectangles, triangles, ellipses, trapezoids, etc. The main body of the support plate uses sound-absorbing holes to ensure maximum sound absorption effect.

[0043] The shape of each tooth on the toothed tail edge 21 of this application includes, but is not limited to, triangles, rectangles, and trapezoids. The specific shape of the outer edge of the tooth can also be a sine curve, a cosine curve, or a combination of different shapes. The toothed tail edge is installed on the support plate to ensure maximum sound absorption effect.

[0044] The specific embodiments described above do not constitute a limitation on the scope of protection of this invention. Those skilled in the art should understand that various modifications, combinations, sub-combinations, and substitutions can be made according to design requirements and other factors. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of this invention should be included within the scope of protection of this invention.

Claims

1. A noise reduction support plate structure for a turbine expander, used to connect a coaxially arranged exhaust pipe (10) and a guide cone (11), wherein a cavity is formed between the exhaust pipe (10) and the guide cone (11), one end of the cavity is an air inlet (12), and the other end of the cavity is an exhaust outlet (13), characterized in that: The noise reduction support plate structure of the turbine expander includes a support plate body (20), a toothed tail edge (21), and a sound-absorbing hole (22). The toothed tail edge (21) is located on one side of the support plate body (20) to reduce aerodynamic noise generated by flow separation or vortex. The two ends of the support plate body (20) are respectively connected to the inner wall of the exhaust pipe (10) and the guide cone (11). The support plate body (20) is located near the air inlet (12), and the toothed tail edge (21) is located near the exhaust port (13). The sound-absorbing hole (22) is opened on the side of the support plate body (20) to reduce noise. The vertical height of the support plate body (20) in the vertical direction is H.

2. The noise reduction support plate structure for a turbine expander according to claim 1, characterized in that: The support plate body (20) is vertically arranged between the exhaust pipe (10) and the guide cone (11). The cross-section of the toothed tail edge (21) is triangular. The width W of the support plate body (20) ranges from 0.01 times to 0.9 times H. The toothed tail edge (21) reduces the aerodynamic noise generated by flow separation or vortex during the flow of air around the support plate body (20).

3. The noise reduction support plate structure for a turbine expander according to claim 2, characterized in that: The diameter L of the sound-absorbing hole (22) is 0.01 to 0.9 times the H, the depth D of the sound-absorbing hole (22) is 0.01 to 0.9 times the H, the depth A of the toothed tail edge (21) is 0.01 to 3 times the H, and the width B of each tooth on the toothed tail edge (21) is 0.01 to 0.5 times the H. The combination of the sound-absorbing hole (22) and the toothed tail edge (21) reduces the aerodynamic noise generated by flow separation or vortex during the flow of air around the support plate body (20).

4. The noise reduction support plate structure for a turbine expander according to claim 1, characterized in that: The main body of the support plate (20) is inclined between the exhaust pipe (10) and the guide cone (11). The angle α between the main body of the support plate (20) and the vertical direction ranges from 0° to 170°. The cross-section of the toothed tail edge (21) in the middle is square. The cross-section of each tooth on the toothed tail edge (21) at both ends is triangular. The cross-section of at least one set of sound-absorbing holes (22) in the middle is square. The cross-section of the two sets of sound-absorbing holes (22) at both ends is circular. The aerodynamic noise generated by flow separation or vortex during the flow of air around the main body of the support plate (20) is reduced by the cooperation of the sound-absorbing holes (22) and the toothed tail edge (21).

5. The noise reduction support plate structure for a turbine expander according to claim 4, characterized in that: Each set of sound-absorbing holes (22) at both ends is arranged in a triangular shape, and the vertical distance C1 between two adjacent sound-absorbing holes (22) is 0 to 0.8 times the value of W; the sound-absorbing holes (22) in the middle are arranged in a quadrilateral shape, and the vertical distance d1 between two adjacent sound-absorbing holes (22) in the horizontal direction is 0 to 0.8 times the value of W, and the vertical distance d2 between two adjacent sound-absorbing holes (22) in the vertical direction is 0 to 0.8 times the value of W, in order to increase the sound absorption effect.

6. The noise reduction support plate structure for a turbine expander according to claim 5, characterized in that: The arrangement range H2 of the sound-absorbing hole (22) located in the middle and having a quadrilateral cross-section is 0 to 0.8 times the value of H; the arrangement range of the sound-absorbing hole (22) located in the middle and having a quadrilateral cross-section to the vertical height H1 of the exhaust pipe (10) is 0 to 0.8 times the value of H; the arrangement range of the sound-absorbing hole (22) located in the middle and having a quadrilateral cross-section to the vertical height H3 of the guide cone (11) is 0 to 0.8 times the value of H, in order to increase the sound absorption effect.

7. The noise reduction support plate structure for a turbine expander according to claim 6, characterized in that: The width B1 of each tooth on the toothed trailing edge (21) at the end ranges from 0.001 to 0.5 times H, the depth A1 of the toothed trailing edge (21) at the end ranges from 0.001 to 3 times H, the depth A2 of the toothed trailing edge (21) in the middle ranges from 0.001 to 3 times H, and the B2 of each tooth on the toothed trailing edge (21) in the middle ranges from 0.001 to 0.5 times H. The toothed trailing edge (21) reduces the aerodynamic noise generated by flow separation or vortices during the flow of air around the support plate body (20).

8. The noise reduction support plate structure for a turbine expander according to claim 1, characterized in that: The main body (20) of the support plate includes a straight section (201), a first arc-shaped section (202) and a second arc-shaped section (203). The top end of the straight section (201) is connected to the exhaust pipe (10) through the first arc-shaped section (202), and the other end of the straight section (201) is connected to the guide cone (11) through the second arc-shaped section (203). The toothed tail edge (21) is provided on the straight section (201). A set of sound-absorbing holes (22) are opened on the side of the first arc-shaped section (202). The angle α1 between the first arc-shaped section (202) and the vertical direction is in the range of 0°-180°, and the angle α2 between the second arc-shaped section (203) and the horizontal direction is in the range of 0°-180°. The flow resistance is reduced by the arc-shaped structure of the first arc-shaped section (202) and the second arc-shaped section (203).

9. The noise reduction support plate structure for a turbine expander according to claim 8, characterized in that: A set of sound-absorbing holes (22) are arranged in two rows. The vertical distance C2 between two adjacent sound-absorbing holes (22) is 0.001 to 0.5 times the value of W. The overall height H4 of the two rows of sound-absorbing holes (22) is 0.01 to 0.5 times the value of H. The vertical distance H5 between the two rows of sound-absorbing holes (22) and the guide cone (11) is 0.01 to 0.5 times the value of H, which is used to increase the sound absorption effect.

10. The noise reduction support plate structure for a turbine expander according to claim 9, characterized in that: The vertical height H6 of the toothed trailing edge (21) is 0.001 to 0.9 times that of H. The vertical distance H7 between the toothed trailing edge (21) and the guide cone 11 is 0.001 to 0.9 times that of H. The width B3 of each tooth on the toothed trailing edge (21) is 0.001 to 0.5 times that of H. The depth A3 of the toothed trailing edge (21) is 0.001 to 0.5 times that of H. The toothed trailing edge (21) can reduce the aerodynamic noise generated by flow separation or vortex during the flow of air around the support plate body (20).

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