Pressure-bearing thermal protection self-compensation runner structure

Abstract

The invention relates to a pressure-bearing thermal protection self-compensation flow channel structure, belongs to the technical field of flow channel structures, and solves the problems that in the prior art, an existing structure is poor in external pressure stability, poor in thermal protection and inconsistent in thermal deformation of an inner shell and an outer shell. The structure comprises a plurality of half pipes, a plurality of outer pressure-bearing shell plates and an inner pressure-bearing shell, the section of each half pipe is fixedly arranged on the inner pressure-bearing shell, and an outer pressure-bearing shell plate is fixedly arranged between every two adjacent half pipes. Wherein the outer pressure-bearing shell plate is fixedly arranged on the outer side of the corresponding half pipe, and a set distance is formed between the outer pressure-bearing shell plate and the inner pressure-bearing shell.

Description

Technical Field

[0001] The invention relates to the technical field of flow channel structures, and in particular to a pressure-bearing thermal protection self-compensating flow channel structure. Background Art

[0002] In the pressure vessel, pipeline, ventilation, wind tunnel, boiler, thermal environment and other industries, there are strict requirements for the stability of large-sized external pressure vessels and pipelines, and the material protection of high-temperature thermal environments, especially large pressure vessels or pipelines, and thermal environment systems. In traditional high-temperature pressure environments, internal insulation or thermal insulation is generally used to reduce the heat transfer of the high-temperature environment to the pressure shell. There are also cases where the cooling water jacket structure is used to protect the internal pressure shell, but these all have some shortcomings to a greater or lesser extent, such as the short service life of the internal insulation, the trouble of replacement, the thermal insulation increases the dead space inside the equipment, which is not conducive to the cleaning and maintenance of the equipment, and the traditional water jacket has too high circulating water pressure. In order to ensure the stability of the equipment, a large number of anti-instability ribs need to be added.

[0003] In summary, at present, in the pressure vessel, pipeline, ventilation, wind tunnel, boiler, thermal environment and other industries, especially in the high-temperature internal pressure pipeline, pressure vessel, boiler, and equipment in the thermal environment, the internal insulation or thermal insulation floor and water jacket structure are used, which have the problems of poor external pressure stability, poor thermal protection, and uncoordinated thermal deformation of the inner and outer shells. Summary of the invention

[0004] In view of the above analysis, an embodiment of the present invention aims to provide a pressure-bearing thermal protection self-compensating flow channel structure to solve the problems of poor external pressure stability, poor thermal protection, and uncoordinated thermal deformation of the inner and outer shells in the existing structure.

[0005] The embodiment of the present invention provides a pressure-bearing thermal protection self-compensating flow channel structure, comprising a plurality of half-tubes, a plurality of outer pressure-bearing shell plates and an inner pressure-bearing shell;

[0006] The cross section of each half pipe is fixedly arranged on the inner pressure-bearing shell, and an outer pressure-bearing shell plate is fixedly arranged between two adjacent half pipes;

[0007] The outer pressure-bearing shell plate is fixedly arranged on the outer side of the corresponding half-tube, and the outer pressure-bearing shell plate is at a set distance from the inner pressure-bearing shell.

[0008] Based on a further improvement of the above solution, a plurality of grooves are arranged on the cross section of each half pipe.

[0009] Based on the further improvement of the above solution, if the inner pressure-bearing shell is a cylinder or a sphere, the half-tubes are evenly distributed circumferentially on the inner pressure-bearing shell and the half-tubes are arranged along the axial direction of the inner pressure-bearing shell.

[0010] Based on the further improvement of the above scheme, if the inner pressure-bearing shell is a cylinder or a sphere, the number of half pipes is determined by the following method:

[0011] Based on the radius and thickness of the inner pressure shell, the instability wave number is determined, and then the number of the first half pipe is obtained;

[0012] Based on the thickness of the inner pressure-bearing shell and the distance between the inner pressure-bearing shell and the outer pressure-bearing shell, the spacing between adjacent half-tubes and the circumference of one end of the inner pressure-bearing shell are determined, thereby obtaining the second number of half-tubes; wherein the spacing between adjacent half-tubes is the distance between the centers of the half-tube end surfaces of adjacent half-tubes at one end of the inner pressure-bearing shell;

[0013] The number of half pipes is obtained based on the first number of half pipes and the second number of half pipes.

[0014] Based on the further improvement of the above solution, the number N1 of the first half pipes is expressed as:

[0015]

[0016] in,

[0017]

[0018] In the formula, n represents the instability wave number, R and δ represent the radius and thickness of the inner pressure shell, respectively, and L represents the calculation length. Indicates rounding up.

[0019] Based on the further improvement of the above solution, the second half pipe number N2 is expressed as:

[0020]

[0021] in,

[0022]

[0023] Where, L cf Indicates the circumference of one end of the inner pressure shell, L c represents the distance between adjacent half-tubes, δ represents the thickness of the inner pressure shell, [σ] t represents the allowable stress at the set temperature t, J represents the first coefficient, and p c represents the calculated pressure of the cooling medium, h represents the distance between the inner pressure shell and the outer pressure shell plate, L s represents the first intermediate parameter, Indicates rounding down.

[0024] Based on the further improvement of the above solution, the first intermediate parameter L s It is expressed as:

[0025]

[0026] Wherein, Z represents the second coefficient.

[0027] Based on the further improvement of the above solution, the number N of the half pipes is expressed as:

[0028] N=max{N1,N2}

[0029] Wherein, N1 represents the number of first half pipes, and N2 represents the number of second half pipes.

[0030] Based on the further improvement of the above solution, if the inner pressure-bearing shell 3 is a cylinder or a sphere, when used in a vacuum condition, the thickness of the inner pressure-bearing shell is adjusted by the following method:

[0031] Based on the critical pressure threshold of instability, the minimum thickness of the inner pressure shell is obtained;

[0032] If the thickness of the current inner pressure-bearing shell is greater than or equal to the minimum thickness value, the thickness of the current inner pressure-bearing shell is not adjusted; otherwise, the thickness of the current inner pressure-bearing shell is adjusted.

[0033] Based on the further improvement of the above scheme, the minimum thickness of the inner pressure shell is obtained by the following formula:

[0034]

[0035] in,

[0036]

[0037] In the formula, p k,th represents the critical pressure threshold of instability, E represents the elastic modulus of the inner pressure shell, and μ represents the Poisson's ratio.

[0038] Compared with the prior art, the present invention can achieve at least one of the following beneficial effects:

[0039] The present invention provides a pressure-bearing thermal protection self-compensating flow channel structure, which includes a plurality of half-tubes, a plurality of outer pressure-bearing shell plates and an inner pressure-bearing shell; the cross-section of each half-tube is fixedly arranged on the inner pressure-bearing shell, an outer pressure-bearing shell plate is fixedly arranged between two adjacent half-tubes, and the outer pressure-bearing shell plate is fixedly arranged on the outside of the corresponding half-tube, and the outer pressure-bearing shell plate is a set distance away from the inner pressure-bearing shell. When the structure is working, the inner shell is the main pressure-bearing shell, the half-tubes are welded to the outer wall of the inner shell to form countless flow channels or chambers, and then the half-tubes are welded with pressure-bearing steel plates, and the pressure-bearing steel plates are arranged between the outer wall of the inner shell and An outer flexible protection structure is formed between the vertices of the half-tubes; this structure can improve the external pressure stability of the pressure-bearing equipment, and at the same time compensate for the thermal displacement of the structure caused by the thermal environment, has a long service life, reduces the thickness of the structure, is conducive to the use of large-size pressure-bearing structures or thermal environments, and reduces the cost of the structure; grooves are evenly spaced at the places where the half-tubes are welded to the outer wall of the inner shell to allow the fluids between the half-tube flow channels to flow to each other, preventing the fluid in each half-tube from becoming a separate dead cavity that causes problems that are difficult to clean and maintain, and avoiding excessive temperatures in a single flow channel, thereby achieving thermal protection and self-compensation functions.

[0040] In the present invention, the above-mentioned technical solutions can also be combined with each other to achieve more preferred combination solutions. Other features and advantages of the present invention will be described in the subsequent description, and some advantages can become obvious from the description, or can be understood by practicing the present invention. The purpose and other advantages of the present invention can be realized and obtained through the contents particularly pointed out in the description and the drawings. BRIEF DESCRIPTION OF THE DRAWINGS

[0041] The drawings are only for the purpose of illustrating particular embodiments and are not to be considered limiting of the present invention. Like reference symbols denote like components throughout the drawings.

[0042] Figure 1 A schematic diagram of a pressure-bearing thermal protection self-compensating flow channel structure provided by an embodiment of the present invention;

[0043] Figure 2 A schematic diagram of a half pipe provided by an embodiment of the present invention;

[0044] Figure 3 A schematic diagram of a cross section of a flow channel structure provided by an embodiment of the present invention;

[0045] Reference numerals:

[0046] 1-half pipe; 2-external pressure-bearing shell plate; 3-inner pressure-bearing shell; 11-groove. DETAILED DESCRIPTION

[0047] The preferred embodiments of the present invention are described in detail below in conjunction with the accompanying drawings, wherein the accompanying drawings constitute a part of this application and are used together with the embodiments of the present invention to illustrate the principles of the present invention, but are not used to limit the scope of the present invention.

[0048] A specific embodiment of the present invention discloses a pressure-bearing thermal protection self-compensating flow channel structure, such as Figure 1 As shown, it includes a plurality of half-tubes 1, a plurality of outer pressure-bearing shell plates 2 and an inner pressure-bearing shell 3;

[0049] The cross section of each half pipe 1 is fixedly arranged on the inner pressure-bearing shell 3, and an outer pressure-bearing shell plate 2 is fixedly arranged between two adjacent half pipes 1;

[0050] The outer pressure-bearing shell plate 2 is fixedly arranged on the outer side of the corresponding half pipe 1 , and the outer pressure-bearing shell plate 2 is at a set distance from the inner pressure-bearing shell 3 .

[0051] It can be understood that the pressure-bearing heat protection self-compensating flow channel structure in this embodiment can be set in pressure vessels, pipelines, ventilation, wind tunnels, boilers, thermal environments and other industries, especially in high-temperature internal pressure pipelines, pressure vessels, boilers, and high-temperature heat exchangers, such as the outer wall of the heat exchanger pipeline. The half-pipe structure plus the pressure-bearing shell in this embodiment can not only solve the instability problem caused by the pressure in the jacket, but also, the nature of the arc tube itself can adaptively solve the thermal expansion problem caused by the incoordination of thermal deformation.

[0052] Preferably, the cross section of each half pipe 1 is provided with a plurality of grooves 11. It is understandable that the provision of the grooves 11 increases the mutual flow of fluids and avoids uneven temperature.

[0053] Specifically, the length of the groove 11 ranges from 100 mm to 200 mm, the height of the groove 11 ranges from 10 mm to 20 mm, and the spacing between the grooves 11 is the same as the length of the groove 11. It can be understood that the groove 11 can maximize the mutual flow of fluids under the requirement while ensuring the strength and stiffness of the half pipe.

[0054] Specifically, the inner pressure-bearing shell 3, the outer pressure-bearing shell plate 2 and the half pipe 1 are fixed by welding.

[0055] During implementation, the distance between each of the outer pressure-bearing shell plates 2 and the inner pressure-bearing shell 3 is set to 0.4 to 0.6 times the radius of the half-tube 1 to achieve the flexibility of the entire outer pressure-bearing shell formed by the half-tube 1 and the outer pressure-bearing shell plate 2, thereby achieving thermal displacement compensation between the pressure-bearing inner shell and the entire outer pressure-bearing shell formed by the half-tube 1 and the outer pressure-bearing shell plate 2.

[0056] Specifically, the radius of the half pipe 1 is in the range of 80 mm to 160 mm. It is understandable that this setting can make the distance between the inner pressure-bearing shell and the outer pressure-bearing shell plate within an appropriate range without increasing the difficulty of manufacturing.

[0057] In practice, if the inner pressure-bearing shell 3 is a cylinder or a sphere, the half pipes 1 are evenly distributed circumferentially on the inner pressure-bearing shell 3 and the half pipes are arranged axially along the inner pressure-bearing shell 3. Figure 3 The example shown is that the inner pressure-bearing housing 3 is a cylinder.

[0058] During implementation, if the inner pressure-bearing shell 3 is a cylinder or a sphere, the number of half pipes is determined by the following method:

[0059] Based on the radius and thickness of the inner pressure shell, the instability wave number is determined, and then the number of the first half pipe is obtained;

[0060] Based on the thickness of the inner pressure-bearing shell and the distance between the inner pressure-bearing shell and the outer pressure-bearing shell plate, the spacing between adjacent half-tubes and the circumference of one end of the inner pressure-bearing shell are determined, thereby obtaining the second number of half-tubes; wherein the spacing between adjacent half-tubes is the distance between the centers of the half-tube end surfaces of adjacent half-tubes at one end of the inner pressure-bearing shell;

[0061] The number of half pipes is obtained based on the first number of half pipes and the second number of half pipes.

[0062] It should be noted that one end of the inner pressure-bearing shell refers to the end surface of the same side of each half-tube on the inner pressure-bearing shell.

[0063] In a specific implementation, the number N1 of the first half pipes is expressed as:

[0064]

[0065] in,

[0066]

[0067] In the formula, n represents the instability wave number, R and δ represent the radius and thickness of the inner pressure shell, respectively, and L represents the calculation length. Indicates rounding up.

[0068] In a specific implementation, the number N2 of the second half pipes is expressed as:

[0069]

[0070] in,

[0071]

[0072]

[0073] Where, Lcf Indicates the circumference of one end of the inner pressure shell, L c represents the distance between adjacent half-tubes, δ represents the thickness of the inner pressure shell, [σ] t represents the allowable stress at the set temperature t, J represents the first coefficient, and p c represents the calculated pressure of the cooling medium, h represents the distance between the inner pressure shell and the outer pressure shell plate, L s represents the first intermediate parameter, Indicates rounding down.

[0074] Specifically, the first intermediate parameter L s It is expressed as:

[0075]

[0076] Wherein, Z represents the second coefficient.

[0077] Specifically, the second coefficient Z, when δ≤11 mm, Z=2.1; otherwise, Z=2.2.

[0078] Specifically, the first coefficient J is determined according to Table 1.

[0079] Table 1 Values ​​of the first coefficient J

[0080]

[0081]

[0082] In a specific implementation, the number N of the half pipes is expressed as:

[0083] N=max{N1,N2}

[0084] Wherein, N1 represents the number of first half pipes, and N2 represents the number of second half pipes.

[0085] It is understandable that when the half-tubes are arranged along the circumferential direction, they can be arranged at intervals re-determined according to the circumference of the inner pressure-bearing shell and the number of the half-tubes.

[0086] During implementation, if the inner pressure-bearing shell 3 is a cylinder or a sphere, when used in a vacuum condition, the thickness of the inner pressure-bearing shell is adjusted by the following method:

[0087] Based on the critical pressure threshold of instability, the minimum thickness of the inner pressure shell is obtained;

[0088] If the thickness of the current inner pressure-bearing shell is greater than or equal to the minimum thickness value, the thickness of the current inner pressure-bearing shell is not adjusted; otherwise, the thickness of the current inner pressure-bearing shell is adjusted.

[0089] Specifically, when the thickness of the current inner pressure-bearing shell is adjusted, the thickness of the current inner pressure-bearing shell is adjusted to a minimum thickness value.

[0090] Specifically, the minimum thickness of the inner pressure shell is obtained by the following formula:

[0091]

[0092] in,

[0093]

[0094] In the formula, p k,th represents the critical pressure threshold of instability, E represents the elastic modulus of the inner pressure shell, and μ represents the Poisson's ratio.

[0095] During implementation, if the inner pressure-bearing shell 3 is a rectangular parallelepiped, the half pipes 1 are evenly arranged on the inner pressure-bearing shell 3; the number of the half pipes is determined by the following method:

[0096] Based on the thickness of the inner pressure shell and the distance between the inner pressure shell and the outer pressure shell plate, the spacing between adjacent half-tubes is determined, thereby obtaining the number of half-tubes; wherein the spacing between adjacent half-tubes is the distance between the half-tube axes.

[0097] Specifically, the number N of the half pipes is expressed as:

[0098]

[0099] in,

[0100]

[0101] Where, L f Indicates the length of the inner pressure shell, L c represents the distance between adjacent half-tubes, δ represents the thickness of the inner pressure shell, [σ] t represents the allowable stress at the set temperature t, J represents the first coefficient, and p c represents the calculated pressure of the cooling medium, h represents the distance between the inner pressure shell and the outer pressure shell plate, L s represents the first intermediate parameter, Indicates rounding down.

[0102] Specifically, the first intermediate parameter L s It is expressed as:

[0103]

[0104] Wherein, Z represents the second coefficient.

[0105] Compared with the prior art, the present embodiment provides a pressure-bearing thermal protection self-compensating flow channel structure, including multiple half-tubes, multiple outer pressure-bearing shell plates and an inner pressure-bearing shell; the cross-section of each half-tube is fixedly arranged on the inner pressure-bearing shell, an outer pressure-bearing shell plate is fixedly arranged between two adjacent half-tubes, and the outer pressure-bearing shell plate is fixedly arranged on the outside of the corresponding half-tube, and the outer pressure-bearing shell plate is a set distance away from the inner pressure-bearing shell. When the structure is working, the inner shell is the main pressure-bearing shell, the half-tubes are welded to the outer wall of the inner shell to form countless flow channels or chambers, and then the half-tubes are welded with pressure-bearing steel plates, and the pressure-bearing steel plates are arranged on the inner shell. An outer flexible protection structure is formed between the outer wall surface and the apex of the half-tube; this structure can improve the external pressure stability of the pressure-bearing equipment, and at the same time compensate for the thermal displacement of the structure caused by the thermal environment, has a long service life, reduces the thickness of the structure, is conducive to the use of large-size pressure-bearing structures or thermal environments, and reduces the cost of the structure; grooves are evenly spaced at the welding points between the half-tube and the outer wall of the inner shell to allow the fluids between the half-tube flow channels to flow to each other, preventing the fluid in each half-tube from becoming a separate dead cavity that causes problems that are difficult to clean and maintain, and avoiding excessive temperatures in a single flow channel, thereby achieving thermal protection and self-compensation functions.

[0106] Those skilled in the art will appreciate that all or part of the processes of the above-mentioned embodiments can be implemented by instructing related hardware through a computer program, and the program can be stored in a computer-readable storage medium, wherein the computer-readable storage medium is a disk, an optical disk, a read-only storage memory, or a random access memory, etc.

[0107] The above description is only a preferred specific implementation manner of the present invention, but the protection scope of the present invention is not limited thereto. Any changes or substitutions that can be easily conceived by any technician familiar with the technical field within the technical scope disclosed by the present invention should be covered within the protection scope of the present invention.

Claims

1. A pressure-bearing thermal protection self-compensating flow channel structure, characterized in that: It comprises a plurality of half-tubes (1), a plurality of outer pressure-bearing shell plates (2) and an inner pressure-bearing shell (3); The cross section of each half pipe (1) is fixedly arranged on the inner pressure-bearing shell (3), and an outer pressure-bearing shell plate (2) is fixedly arranged between two adjacent half pipes (1); The outer pressure-bearing shell plate (2) is fixedly arranged on the outside of the corresponding half pipe (1), and the outer pressure-bearing shell plate (2) is at a set distance from the inner pressure-bearing shell (3).

2. The pressure-bearing thermal protection self-compensating flow channel structure according to claim 1 is characterized in that: The cross section of each half pipe (1) is provided with a plurality of grooves (11).

3. The pressure-bearing thermal protection self-compensating flow channel structure according to claim 1 is characterized in that: If the inner pressure-bearing shell (3) is a cylinder or a sphere, the half-tubes (1) are evenly distributed circumferentially on the inner pressure-bearing shell (3) and the half-tubes (1) are arranged axially along the inner pressure-bearing shell (3).

4. The pressure-bearing thermal protection self-compensating flow channel structure according to claim 3 is characterized in that: If the inner pressure-bearing shell (3) is a cylinder or a sphere, the number of half pipes is determined by the following method: Based on the radius and thickness of the inner pressure shell, the instability wave number is determined, and then the number of the first half pipe is obtained; Based on the thickness of the inner pressure-bearing shell and the distance between the inner pressure-bearing shell and the outer pressure-bearing shell, the spacing between adjacent half-tubes and the circumference of one end of the inner pressure-bearing shell are determined, thereby obtaining the second number of half-tubes; wherein the spacing between adjacent half-tubes is the distance between the centers of the half-tube end surfaces of adjacent half-tubes at one end of the inner pressure-bearing shell; The number of half pipes is obtained based on the first number of half pipes and the second number of half pipes.

5. The pressure-bearing thermal protection self-compensating flow channel structure according to claim 4 is characterized in that: The first half pipe number N1 is expressed as: in, In the formula, n represents the instability wave number, R and δ represent the radius and thickness of the inner pressure shell, respectively, and L represents the calculation length. Indicates rounding up.

6. The pressure-bearing thermal protection self-compensating flow channel structure according to claim 5, characterized in that: The second half pipe number N2 is expressed as: in, Where, L cf Indicates the circumference of one end of the inner pressure shell, L c represents the distance between adjacent half-tubes, δ represents the thickness of the inner pressure shell, [σ] t represents the allowable stress at the set temperature t, J represents the first coefficient, and p c represents the calculated pressure of the cooling medium, h represents the distance between the inner pressure shell and the outer pressure shell plate, L s represents the first intermediate parameter, Indicates rounding down.

7. The pressure-bearing thermal protection self-compensating flow channel structure according to claim 6 is characterized in that: The first intermediate parameter L s It is expressed as: Wherein, Z represents the second coefficient.

8. The pressure-bearing thermal protection self-compensating flow channel structure according to claim 4 is characterized in that: The number N of half pipes is expressed as: N=max{N1,N2} Wherein, N1 represents the number of first half pipes, and N2 represents the number of second half pipes.

9. The pressure-bearing thermal protection self-compensating flow channel structure according to claim 5, characterized in that: If the inner pressure-bearing shell (3) is a cylinder or a sphere, when used in a vacuum condition, the thickness of the inner pressure-bearing shell is adjusted by the following method: Based on the critical pressure threshold of instability, the minimum thickness of the inner pressure shell is obtained; If the thickness of the current inner pressure-bearing shell is greater than or equal to the minimum thickness value, the thickness of the current inner pressure-bearing shell is not adjusted; otherwise, the thickness of the current inner pressure-bearing shell is adjusted.

10. The pressure-bearing thermal protection self-compensating flow channel structure according to claim 9, characterized in that: The minimum thickness of the inner pressure shell is obtained by the following formula: in, In the formula, p k,th represents the critical pressure threshold of instability, E represents the elastic modulus of the inner pressure shell, and μ represents the Poisson's ratio.

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